Residential Ventilation en
Residential Ventilation en
Residential Ventilation en
Note : comfort fans are treated in another document, this report is about ventilation fans.
Legal disclaimer
The sole responsibility for the content of this report lies with the authors. It does not represent the
opinion of the European Community. The European Commission is not responsible for any use that
may be made of the information contained therein.
CONTENTS
1
STATE-OF-THE-ART IN APPLIED RESEARCH FOR THE PRODUCT INSIDE AND OUTSIDE EUROPE
113
6.2 IMPROVEMENTS IN MOTOR DESIGN ....................................................................................... 113
6.3 IMPROVEMENTS IN FAN DESIGN ............................................................................................ 116
6.4 IMPROVEMENTS IN INTERIOR AIR FLOW DESIGN ................................................................... 117
6.5 IMPROVEMENTS IN MOTOR AND FAN CONTROL .................................................................... 117
6.6 LIMITATION OF ELECTRIC DEMAND IN CASE OF HEAT RECOVERY. ....................................... 119
6.7 STATE-OF-THE-ART FOR NOISE CONTROL ............................................................................. 120
TASK 6 SUMMARY............................................................................................................................ 121
7
LIST OF FIGURES
Figure 1-1: Different types of fans according to fluid mechanics, from Cory (1992)............................. 9
Figure 1-2: Different types of building ventilation, extract from Lot 11 study on ventilation in non
residential buildings (Radgen, 2007)..................................................................................................... 11
Figure 1-3: Roof fan implantation scheme (Cory, 1992) ...................................................................... 12
Figure 1-4: Roof fan figures from (Cory, 1992).................................................................................... 12
Figure 1-5: appearance of kitchen hoods (courtesy of manufacturers, 2008) ....................................... 12
LIST OF TABLES
Table 1-1a: Different aspects and locations of decentralised ventilation fans (used for local ventilation)
and their technical characteristics.......................................................................................................... 13
Table 1-2a: Hoods compared with other decentralised ventilation fans and their technical
characteristics ........................................................................................................................................ 13
Table 1-3: Prodcom segmentation for ventilators ................................................................................. 18
Table 1-4: Residential ventilation, energy performance standards ....................................................... 23
Table 1-5: SFP classes in W/(m3/s), from standard EN 13779............................................................. 28
Table 1-6: Presentation of the test results at minimum flow rate conditions - example, UK building
code (SAP, 2005) .................................................................................................................................. 29
Table 1-7: Presentation of the test results at minimum flow rate conditions - exemple, UK building
code (SAP, 2005) .................................................................................................................................. 30
Table 1-8: NF VMC, minimal range of operation for a product to be qualified within the NF VMC.. 30
Table 1-9: Criteria for ENERGY STAR Qualified Residential Ventilating Fans Minimum Efficacy
Levels .................................................................................................................................................... 34
Table 2-1: Production of Hoods (29.71 15.50) according to prodcom............................................... 37
Table 2-2: National Input/Ouput of Hoods 29.71 15.50 for year2005 ............................................... 39
Table 2-3: Manufacturing of fans under 29.71.15.30 (that will be considered now as ventilation fans)
............................................................................................................................................................... 40
Table 2-4: Sharing the 2005 EU production of products under 29.71.15.30 according to number of
recently constructed dwellings .............................................................................................................. 41
Table 2-5: German sales of ventilation products, (TZWL, 2007) ......................................................... 42
Table 2-6: Market sales of residential centralized mechanical ventilation products in France, from
(Uniclima, 2007) ................................................................................................................................... 43
Table 2-7: Ventilation equipment rate of individual housing in France, from (ATEE, 2006) .............. 44
Table 2-8: Ventilation equipment rate of individual and collective housing in France, from (ATEE,
2006)...................................................................................................................................................... 44
Ventilation fans ensure air renewal in occupied dwellings; it is necessary for three reasons:
- comfort and hygiene for occupants (fresh air),
- durability of the building (avoid odours and moisture condensation on surfaces inside
dwelling),
- safety (face to combustion devices for example),
Structure of ventilation systems and values of air flow rates are the result of Member States national
building codes and national traditions. The requirement for fresh air flow has important energy
consequences because of forcing cold air inside in winter and hot air inside in summer. Nevertheless,
the thermal consequences and energy consequences is faced by different measures at building thermal
envelope level implemented by Member States national building codes and the Energy Performance of
Buildings Directive 2002/91/EC. Following the Article 15, alinea 2.c of the EuP directive 2005/32/EC,
it can be said that the Community addresses this issue. As a consequence, the heat or coolness
consequence of residential ventilation seems beyond the scope of the study. The study will so focus
only on the efficiency of residential ventilation fans regarding their main duty, which is to provide
fresh air for hygienic purpose. Some MS also require or recommend several airflows in dwellings (i.e.
base, boost...) and therefore some control of the airflows. The study will take these features into
account because they determine the product, but our work is about the product itself.
Building ventilation can be roughly divided into three categories: natural ventilation, local
mechanical ventilation (room by room) and central mechanical ventilation (various rooms). Each
kind of ventilation requires specific energy using products. Mechanical ventilation includes all the
motorized devices used to renew the indoor air. Hybrid ventilation systems are defined in EN12792
(under discussion for modification) as "ventilation where natural ventilation may be at least in a
certain period supported or replaced by powered air movement component" to enlarge the notion not
only to fans but to the full building which has to be designed in a certain way. Mechanical ventilation
is associated to the presence of fans. The required energy using products for ventilation are shortly
described hereafter respecting the three main types of ventilation
A ventilation fan consists of a bladed rotor that is connected to an electric motor through a shaft or a
belt. The rotor can be preceded or followed by a stationary blade row and the ventilator can be linked
to inlet and outlet ducts. In the domain of ventilation the fan and the motor are sold together, whether
they are linked by a shaft or by a belt. Ventilators performances are characterized by the pressure and
the airflow they can provide along with the required input power. These performances vary
importantly among the vast amount of existing ventilators, a first segmentation (technical) is usually
performed regarding how the air flow is deviated by the device, (Cory, 1992). Tangential fans may be
called crossflow. The variety of shapes of blades is developed in a technical annex.
Figure 1-1: Different types of fans according to fluid mechanics, from Cory (1992)
.
Generally speaking, axial and centrifugal fans are the most frequent technical types. A propeller is an
axial fan with few blades, designed to operate through a partition. For small fans, which are the most
frequent in residences ventilations, the dominant rotor will be centrifugal (with either forward or
backward curved blades) and the dominant motor an asynchronous AC motor. However there are
some EC (Electronic Commutation) motors and some DC motors.
1.1.1.1
The air enters the dwelling through cracks, windows, slots and exits through vertical ducts. Each room
of the dwelling or a set of rooms is equipped with vertical ducts and no ventilation device is required.
Air motion is due to the difference between indoor and outdoor temperatures and to the wind pressure
on the building shell. As a result, air renewal varies with climatic conditions and can be very
insufficient in summer when the temperature difference between indoor and outdoor temperature is
low or when there is no wind. Further status of natural ventilation depends on national building
construction codes; UK offers the possibility to design natural ventilation whereas mechanical
ventilation is mandatory in France1. Natural ventilation is not an EuP, nor a performance option since
the choice between types of ventilation is regulated by Member States through national building
codes, hygiene regulations, etc. Specialists usually separate the notion of airing (through manual
window opening) from the notion of natural ventilation which is "designed" or "predictable" (see
EN12792), with a designed system (including natural ventilation passive stack or automatic window
opening on some criteria)
1.1.1.2
According to most countries building codes, the electricity consumption of a well balanced and tuned
mechanical ventilation is limited compared with thermal energy saved by avoiding the direct effect of
the wind in a poorly designed natural ventilation. Thermal energy used in buildings as a result of
artificial or natural ventilation represents 30 to 40 % of heating demand in residential buildings (CFP,
1
Mechanical ventilation is mandatory in France in all new dwellings since 1982 and in case of retrofit
since 1969 in France according to (Ebm-Papst, 2006) and (Uniclima, 2006)
9
From now on, the study will speak only of the EuP under consideration (the fan in charge of
mechanical ventilation) and of its electricity consumption.
1.1.1.3
The ventilation system can be designed as such as to generate underpressure in the rooms (general
case) or over pressure.
Decentralised mechanical ventilation means that several extraction ventilators are used to renew the air
of a complete house (without designed transfer between rooms in the dwelling). Three configurations
are possible, as described by lot 11: a natural air supply with mechanical extract with fans, a
mechanical air supply with natural extract (Positive insufflation ventilation, forbidden in some
countries for dwellings due to the risk of pushing humidity in the walls), a mechanical air supply with
mechanical extract. Fan assisted has been used in lot 11 for mechanical.
10
The second configuration of figure 1.2 is by far the most common in Europe among the three fan
assisted systems. The air comes into the room through cracks, windows, slots (natural air supply) and
the slate air is evacuated by small sized fans or by hoods that can be located on the roof, the ceiling,
the walls or in the windows. These fans also generate a depression enabling the outside air to naturally
come into the room. For other configurations, fans can also be used for direct introduction of outside
air inside, the fans used in this case are similar to the others. Residential ventilation fans usually
include the motor, as opposed to larger power fans, they are tested under specific standards (EN 13141
parts 4 and 6 and CEI/IEC 61 591) and provide lower pressure differences, as we will see.
The decentralised mechanical ventilation can use fans with different locations and aspects, as seen
from outside:
- Roof fans are located on the roof of the room or may be linked to a ducted system.
- Extraction fans can eject the air through the walls or the ceiling directly or through a short
duct. Extraction fans are located inside whereas roof fans are located outside.
- Window fans are embedded in a window glass. They can also be located in the frame of the
window (see Table 1-1).
- In the residential sector, hoods are located close to pollution sources (in the kitchen). The user
can turn it on or off when he wants. Three different types of hoods can be found. The hood
may be simply a frame and a filter to be plugged on a centralized ventilation system when
authorized by the regulation (in France connecting a mechanical hood on the ventilation
system of a building is forbidden due to fire protection law and hygiene law). In that case,
there is no specific consumption for this product, which is not considered in this study. The
hood can be plugged directly outdoor: polluted air is extracted inside and rejected directly
outside; this is a decentralized ventilation system to be considered in this study. The third type
is the assembly of a fan and a filtration system that filters indoor air and rejects it in the same
room, typically above the hood, to be classified in the category air purifiers, not ventilation
fans.
- There is a ventilation mode in single-duct air conditioners, that is studied in that lot, because
the purchasing and using rationale is different.
In all categories, the fact they are ducted or not is translated by type A,B,C,D in ISO5801:
Type (A), free inlet, free outlet;
Type (B), free inlet, ducted outlet;
Type (C), ducted inlet, free outlet;
Type (D), ducted inlet, ducted outlet
Among decentralised systems, one finds the very common roof fans, window fans, etc. Roof fans
(tourelles) refers to free discharge fans installed on roof, and can be centralized, local or even
assistance for passive stack. A roof fan is represented in the figure 3.
11
The figure 4 below shows that internally, it combines the motor and the fan itself. For decentralised
systems, the ducts are short, as shown in the figure below, if any.
Coming to kitchen (or range) hoods, four (at least) geometries of kitchen hoods can be seen as distinct
from outside, as in figure 5. The bottom-of-the-market hoods (under cabinet) are less expensive
today.
12
Type
Operating scheme
Typical characteristics
-
Window glass
Example
Consumption: 20 100 W
Airflow: 200 1400 m/h
Non ducted
Usually axial
Fix
Helios
Window
(Inside the
frame)
- Consumption:120W
Another type of window - Reversible air flow
fan, located in the frame of - Non ducted
the window
- Usually axial
- Movable
Honeywell
- Consumption:10 50 W
- 100 400 m3/h
- Connected to a short
ducted system
- Usually axial
- Fix
Wall/ceiling
Atlantic
- Often connected to a
ducting system
- Centrifugal or mixed fan
- Outside the building
Roof
Table 1-1a: Different aspects and locations of decentralised ventilation fans (used for local ventilation)
and their technical characteristics
Type
Hoods
Operating scheme
Typical characteristics
Example
Table 1-2a: Hoods compared with other decentralised ventilation fans and their technical
characteristics
13
1.1.1.4
Centralized mechanical ventilation means that one extractor and a ducted system are used to renew the
air of a whole dwelling (made of several rooms).
Three configurations can be found in the residential area: a natural air supply with mechanical
extract, a mechanical air supply with natural extract and a mechanical air supply together with
a mechanical extract.
Single extract centralized mechanical ventilation (Natural air supply and mechanical extract)
Because of the depression generated by the extractor, the air comes through the dwelling from the less
polluted rooms (bedrooms, living rooms) to the most polluted ones (kitchen, toilets) by spaces around
the doors, mostly under the doors. The air comes into the dwelling through cracks, windows, slots.
Extract air is sucked by the extractor, evacuated by openings from the most polluted rooms. In terms
of energy using products, this kind of ventilation requires an extractor larger than small sized fans (as
defined in the previous subsection local ventilation). An extractor consists generally in a centrifugal
fan driven by an asynchronous motor.
Extractor
Figure 1-6: Centralized ventilation with natural air supply and mechanical extract fans, Atlantic (left:
individual house, right : collective dwellings)
Figure 1-7: Simple flow extractor, Atlantic (left: individual house, right : collective dwellings)
Usually the electric power is under 80 W for individual houses and under 500W for collective
dwellings ventilation.
In mechanical ventilation balanced systems or positive input ventilation (PIV), the air supply is
sometimes made through a ground coupled air to earth heat exchanger, also called Canadian well,
which allows partial cooling of the air in summer. In that case, mechanical ventilation can help to
14
Figure 1-8: Balanced double flow ventilation unit, Courtesy Swedish manufacturers
15
Figure 1-9: Balanced double flow ventilation system and unit, Courtesy Alds -CFP
Balanced or Double flow centralized mechanical ventilation: the extract air is extracted in the
kitchen, the toilets and the bathrooms. New air is introduced in other rooms with another network
but the same extractor block.
Centralization allows to process the new air (filtration, heating, humidification) and by
gathering the two networks (extraction of slate air and extraction of new air) to preheat the new air
by recovering heat on the extracted air thanks to a plate heat exchanger. As a result, double flow
ventilation coupled with heat recovery heat exchanger enables to economize heating energy.
This system enables to recover an important part of the energy lost because of the introduction of
fresh air for ventilation need in winter but increases electricity use in the product. Double flow
heat recovery ventilation is generally a stand alone product to be installed on the ventilation
network in dwellings. The head losses being different, the electricity use cannot be compared
directly with the other products.
Centralized mechanical ventilation systems can become the basis of a reversible heat pump system
that uses extract air as the cold source in winter and as the hot source in summer. This space
heating system can be called balanced flow thermodynamic ventilation. It supplies both
cooling in summer and heating in winter but the heating and cooling energy does not enable to
cover all the heating and cooling needs because ventilation air flow rates are quite small. As for
plate heat exchanger, heat or cool recovered will depend on outside conditions. This system
enables to recover from 50 % to 200 % of the energy lost because of the introduction of fresh air
for ventilation need in winter and in summer according to (Promotelec, 2006). Both in cooling and
heating modes, this system can only supply part of the thermal requirements of a standard
dwelling. It is covered by EPBD consistent national prescriptions and should be compared with
other heating equipment like boilers.
16
Figure 1.1-10: Passive stack fan assisted natural ventilation, Courtesy Aereco www.aereco.fr
1.1.2
In the Prodcom inventory, ventilation fans are covered both by PRODCOM 29.23 (Manufacture of
non-domestic cooling and ventilation equipment) and PRODCOM 29.71 (Manufacture of electric
domestic appliances). Categories within PRODCOM 29.23 are meant for non residential products
and mainly rely upon the type of fan (as presented in the first section of this study: centrifugal,
axial) with an electrical input lower limit of 125 W. Categories within PRODCOM 29.23 are thus
not useful in our study of residential ventilation.
Fans covered by PRODCOM 29.23 (Manufacture of non-domestic cooling and ventilation
equipment)
29.23.20.30
Axial fans (excluding table, floor, wall, window, ceiling or roof fans with a selfcontained electric motor of an output <= 125 W)
29.23.20.70
Centrifugal fans (excluding table, floor, wall, window, ceiling or roof fans with a selfcontained electric motor of an output <= 125 W)
29.23.20.70
Fans (excluding table, floor, wall, window, ceiling or roof fans with a self-contained
electric motor of an output <= 125 W)
Table, floor, wall, window, ceiling or roof fans, with a self contained electric motor of
an output <= 125 W
Ventilating or recycling hoods incorporating a fan, with a maximum horizontal side <=
120 cm2
The indication about size is not present in the other languages than english and should be understood
as an indication not a category limit since there is no category for the hoods that would happen to be
larger
17
Within PRODCOM 29.71 one finds the residential products. We eliminate here 29.71.15.30, because
we treat separately the comfort fans and we finally recognise the products under study in the present
report under the three remaining categories. However note that products over 125 W are covered by
PRODCOM 29.23 and that we have not included that category. All products over 125 W have been
treated in lot 11, residential ventilation fans together with non residential, in consistency with
PRODCOM statistics. The scope of recommendations of the present report will be limited to
residential ventilation fans under 125W and to all kitchen hoods (a separate PRODCOM category), but
we will not delete the results that we will gather or generate that may be useful for the study of
residential ventilation fans over 125W.
Categories according to EN- products standards, namely testing standard EN 13141
Part 4 is applicable to encased ventilation fans having several inlets, as well as ducted and non ducted
fans, without defining them more precisely.
Part 6 defines Exhaust ventilation system packages used in a single dwelling
A package is perfectly defined in the standard (two extents):
ventilation system package (for a single dwelling)
Combination of compatible components which are tested, delivered and installed as specified by the
manufacturer to complete a residential ventilation system when sold as a single product.
exhaust ventilation system package
System package comprising all components necessary to complete at least the exhaust part of a
ventilation system in a dwelling.
Part 7 defines a mechanical supply and exhaust ventilation unit (including heat recovery) for
mechanical ventilation systems intended for single family dwellings as
In general such a unit contains:
- supply and exhaust air fans;
- air filters;
- air to air heat exchanger with/without air to air heat pump for exhaust air heat recovery;
- control system.
Such equipment can be provided in more than one assembly, the separate assemblies of which are
designed to be used together.
Part 8 defines an un-ducted mechanical supply and exhaust ventilation unit (including heat recovery)
for mechanical ventilation systems intended for a single room
In general, such a unit contains:
- supply and exhaust air fans;
- air filters;
- air to air heat exchanger for exhaust air heat recovery;
- control system.
Such equipment can be provided in more than one assembly, the separate assemblies of which are
designed to be used together.
Categories according to EN- systems standards, namely terminology standard EN 12792
The present report has used the distinction coming from that standard (extract air refers to extraction
from the room, exhaust refers to rejection outside)
Air Terminal Devices is a general name for products that one may call occasionally grilles, inlets,
outlets, extracts, The definition is :
18
Functional analysis
The primary function of ventilation fans is generally to change indoor air of a room or dwelling and
the corresponding functional parameter is the air flow rate. To perform this function the system has
to generate a certain pressure difference that is intrinsically related with the flow and so is part of the
primary function. However this pressure difference varies between countries and is different from one
product to another.
Double flow systems with heat recovery or thermodynamic double flow systems, have respectively
two and three additional primary functions:
- double flow with heat recovery: change indoor air, recover heat;
- thermodynamic double flow: change indoor air, recover heat, recover coolness.
Hoods provide far more primary functions than other decentralized ventilation products : grease
removal from the extract air, lighting of the working plan, etc.
Given that we already mentioned that the thermal consequences of residential ventilation were already
addressed by other Community legislation3, we will not consider further the other (thermal) functions
of double flow mechanical ventilation and thermodynamic double flow ventilation. However, the
product displaying those thermal aspects will have more head losses, and two fans, which will lead to
higher electricity use. We shall try to base our calculations on the ventilation function, by correcting
for the other functions.
For this study, we are interested in products, motor, shaft or belt, fans, including the packaging if any,
but not in the system, Air Terminal Devices, extracts, fresh air grilles and connecting ducts for
instance for centralized systems; they will affect the product environmental impact but are not
considered inside the EuP product in the rest of the study.
Thus, the product to be considered are individual mechanical extract fans for centralized or
decentralized residential mechanical ventilation as defined previously:
- Fans for decentralized mechanical ventilation:
o Roof fans,
o Window fans,
o Wall fans,
o Hood fans.
- Fans for centralized ventilation
o Extract fan,
3
Supply fan,
Extract and supply (balanced or double flow),
Extract and supply (balanced or double flow) with heat recovery.
In Appendix 2 of lot 11 report many variables and parameters that can be considered are listed. From
the physical point of view common to lot 10 and lot 11, there are two characteristics that can be
considered as the primary functional parameters of a fan :
the increase in pressure of the gaseous flow4 (p)
the velocity of the flow (m3/s).
Apart from the two characteristics mentioned above there are a lot of other technical issues that have
to be considered when selecting an appropriate fan. However they are clearly secondary.
The most important ones are:
Diameter of the fan (m)
Volume and weight of the fan
Type of the fan (axial/centrifugal, backward/forward-inclined etc.)
Type of drive and electrical supply
Noise level and vibration
Control systems
Mounting arrangements and inlet/outlet sizes.
Can we choose between the two characteristic parameters? The existence of two functions (flow and
pressure requested by the network and the other conditions) is the basis of the divergence between
national building codes, which have specified national values. Furthermore they have taken distinct
strategies to adapt to part load conditions. Our challenge here is to characterize the efficiency of the
products (all products) in a way that does not contradict such national specifications.
The air flow rate and the pressure difference generated will be kept as main functional parameters.
They are related by a curve that is obtained through testing and giving the air flow rate for a certain
level of difference, and vice versa.
Scope proposal
Limitation to residential (individual ventilation fans, since collective are in lot 11) leads to the
following scope proposal:
- Fans for decentralized (local) mechanical ventilation with or without HR:
o Roof fans (Elec power < 125 W)
o Window fans (Elec power < 125 W)
o Wall fans (Elec power < 125 W)
o Hood fans (remaining in the residential domain, like in the PRODCOM)
o Decentralised ventilation includes local ventilation and kitchen ventilation by
hoods
- Fans for central ventilation serving various rooms, which can be differentiated between fans
serving one individual house (Elec power < 125 W) treated here and fans serving various
dwellings in the same collective building (see lot 11); those products are also called encased
fans and may be sold alone or as packages with the extracts and/or supply grilles, the roof
outlets and/or inlets.
o Extract fan, including assistance fans in hybrid ventilation
4
EN 13141-4 indicates in definition 3.1 that total (dynamic) pressure is to be considered when
referring to the pressure difference between the two sides of a fan; IEC 61 591 uses the same
definition (part 11)
20
Supply fan
Extract and supply (balanced or double flow).
Extract and supply (balanced or double flow) with heat recovery.
21
Test Standards
Energy use
Main EU standards applicable to ventilation products are gathered in the table below. The main test
standard is the EN 13141 standard, except for kitchen hoods which have their own very consistent
standard. Standards with potential impact on the design of the products are also reported.
ISO test standard
ISO 5801 : test method for fans ;European standards below refer to this one
EU test standard
EN 13141, Ventilation for buildings - Performance testing of components/products for
residential ventilation
- Part 1: Externally and internally mounted air transfer devices May 2004.
- Part 2: Exhaust and supply air terminal devices, Sept 2004.
- Part 3: Range hoods for residential use Apr 2004.
- Part 4: Fans used in residential ventilation systems Apr 2004.
- Part 5: Cowls and roof outlet terminal devices - Jan 2005.
- Part 6: Exhaust ventilation system packages used in a single dwelling - Apr 2004.
- Part 7: Performance testing of mechanical supply and exhaust ventilation units (including
heat recovery) for mechanical ventilation systems used in a single dwelling - Sept 2004.
- Part 8: Performance testing of un-ducted mechanical supply and exhaust ventilation units
(including heat recovery) for a single room, May 2006.
- (Project) Part 9: humidity controlled air inlet, Oct 2006.
- (Project) Part 10: hygrometric air outlet, Oct 2006.
- (Project) Part 11: Positive pressure ventilation systems.
EN 13142, Ventilation for buildings - Components/products for residential ventilation Required and optional performance characteristics
The performance characteristics of the components/products for residential ventilation are given in
EN 13142. This document specifies the performance characteristics (required or optional) of
components/products which may be necessary for the design and dimensioning of residential
ventilation systems so that the predetermined conditions of comfort in terms of air change,
temperature, speed, moisture and noise in the occupied area are guaranteed. We can say its a
summary of the core outputs of each of the preceding standards, except that it defines in addition
what should be marked on the product. We should investigate if this marking can be used for energy
efficiency characterization.
22
y=
PF
.q v
where
PF is the mechanical energy (in J.kg-1)
is the inlet air density (in kg.m-3)
The standard uses the total (dynamic) pressure, not the static one; we are doing the same.
24
Figure 1-11: Standard scheme of a mechanical natural supply mechanical exhaust system
Such a package is the scope of an ecodesign measure due to the encased fan itself for individual
houses. For collective housing, the performance indicators have to be limited also to the encased fan
itself and its control.
Calculation outputs are the resulting flow (total and at each exhaust) and the power, for various
conditions. Based on those ventilation performance indicators, an energy performance indicator like
SFP could be computed, but outside of the standard. The nature of the exhaust device is not
mentioned, namely if they are self adjusting or not. The number of exhausts is not limited. What is
considered as the worst case in the standard is the worst case for flows, not for energy efficiency.
Part 7: Performance testing of mechanical supply and exhaust ventilation units (including heat
recovery) for mechanical ventilation systems used in a single dwelling
Performance testing of mechanical supply and exhaust ventilation units (including heat recovery) for
mechanical ventilation systems used in a single dwelling covers balanced flow equipment. In general
such a unit contains:
- supply and exhaust air fans;
- air filters;
- air to air heat exchanger with/without air to air heat pump for exhaust air heat recovery;
- control system.
Such equipment can be provided in more than one assembly, the separate assemblies of which are
designed to be used together.
This part does not deal with non-ducted units. See part 8.
Since there are two flows the use of SFP would be ambiguous and is avoided. What is mostly given is
pressure / flow characteristic curves and heat recovery effectiveness (complex curves depending on
temperatures, flow and controls). The method of testing for the performances of the heat pumps for
heat recovery is generally given in EN14511 (energy) and in ENV 12102 (noise). EN13141-7 is being
25
27
This applies to an encased fan, as it is a subcase of Air Handling Units. The limitations of SFP are
known: it depends on the pressure demanded. There is an original contribution in the revised version
of EN 13779 under discussion: the extended SFP. The thresholds indicated previously are altered by
adding a value for a filter, for a heat recovery unit, etc. So the AHU is compared with a threshold
corresponding to about the same duty. This idea of a benchmark representing various levels of demand
could clearly be transposed from the non residential sysems into the most complex residential
ventilation systems. An informative annex extends even more the idea by introducing an SFP extended
to the full building.
CEI/IEC 61 591 : 2005 test standard for household range hoods
This standard applies to kitchen hoods, and covers many more aspects than the electricity
consumption; however there is a reasonable consistence with the other ventilation products testing
standards, in terms of definition of characteristic line. Indeed note 1 page 15 requests the full
determination of that line, even if the standard extracts then one point out of that line, for a low
pressure difference in fact. The air purifying filter is not in place during testing but the grease filter
remains in place. We will discuss later the limited influence of the difference in performance
measurement accuracy that can be originated by that fact.
This standard leads hoods manufacturers to generate a number of other informations important for our
study : grease absorption efficacy, that could help to correct the characteristic line if the grease filter
would be important; odour extraction efficacy, if we want to consider the recirculating hood, which is
not the case here (we concentrate on ventilation hoods); effectiveness of the hob light, which is a real
high level ratio of the output (illumination on the work plan) to the electricity consumption for lighting
(including the source the luminaire the position of sources, a good practice example that may have
been addressed in the lighting lot), noise level and some other features.
28
The UK builds explicitly on EN 13141-Part 6 by defining all missing data (duct lengths, elbows) like
in the following graph:
Figure 1-12: Standard residential ventilation system as proposed in standard EN 13141 Part 6
completed for the UK building code, from (SAP, 2005)
Since everything is specified, including the minimum flow demand, an SFP can be computed; this
time it is expressed in W/(l/s):
Fan speed
setting
Total flow
rate (l/s)
Specific fan
power (W/l/s)
Table 1-6: Presentation of the test results at minimum flow rate conditions - example, UK building code
(SAP, 2005)
The ducts can be rigid or flexible, and that makes a big difference in head losses (pressure drop). Both
cases are covered here. The results obtained in the specified conditions are used for compliance both
of the regular building code and for the efficient products promotion in the UK.
An extension of EN 13141- Part 7 for heat recovery products provides all the same functions in this
(thermally) more efficient case. Bearing the same date it is called Performance testing of products for
residential ventilation - Central mechanical supply and exhaust ventilation system packages with heat
recovery used in a single dwelling. The table of results is extended accordingly:
Fan speed
setting
Total
exhaust
flow rate
(l/s)
Temperatre
ratio (%)
29
In the UK, guidance for commissioning and installation is an interesting part of SAP documents.
We can find clear tolerances allowing to say whether an air inlet is self adjustable or not, in the NF
VMC marking process (NF, 2007) in France. There are also clear tolerances allowing to say whether
an exhaust is self adjustable or not, in the NF VMC marking process. It extends to packages which
are said self adjustable or not as well. This marking is understood as a control of manufacturing
stability, but includes technical specifications6.
An exhaust is said adjustable after a test comparable to EN 13141 Part 2. Another passive
component but connected to the product under consideration by a duct. In the French test there is not a
limit telling when the word self adjusting is applicable or not: the self adjustment pressure zone is
the zone where the flow is maintained constant within 0%/+30% of the declared flow. For the
declared pressures the flow should be constant within 0%/+30% of the declared flow. There are also
a number of constraints for the ease and accuracy of mounting..
Figure 1-13: Certification logo of the French NF program for mechanical ventilation
This is then extended to the full package, and applied to both speeds (usually only two speeds).
Hereunder is reported the minimal zone to be covered to be within the NF VMC limits:
Kitchen
Lower fan speed
Higher fan speed
43.5 to 80
131
Air
terminal
device
15 m3/h
13 to 20
14.5 to 21.5
Air
terminal
device
30 m3/h
26 to 40
29 to 43
Table 1-8: NF VMC, minimal range of operation for a product to be qualified within the NF VMC.
Once again this puts transparence on the boundary conditions of our products and on its quality of
answer to the needs, not on its energy efficiency. The same marking regulation puts also limits on
noise, typically Lw under 37 dB(A).
What gives an information about energy efficiency is something coming next which builds on EN
13141 Part 6, without referring to it: a maximum electricity consumption at each speed, expressed in
the ad-hoc unit of Watt Th-C. For these tests the exhaust, ducts and rejection devices are completely
specified. So what is at stake is really our EuP. In the configuration with two exhausts in restrooms, an
extractor with one speed should respect Pelec < 35 W-Th-C. In the case where there are two speeds,
first with three restrooms, Pelec < 50 W-Th-C, and then for two restrooms only, Pelec < 35 W-Th-C is
requested to get the marking. Similar acceptance conditions are defined for each number of connected
exhausts.
The marking regulation that was made available is dated from 2003 and refers to French standards
preceding EN 13141.
30
French standards have been put in line with the EN standards that we just described. It should be said
that there is one (higher) level of package testing practiced in France but which seems not yet under
standardization in Europe: the humidity controlled package with a fan integrated control of moisture.
The standard is called NF-E-51-706.
Installation
EN 14134, Ventilation for buildings - Performance testing and control of installation of ventilation
systems in single dwellings - Aug 2004.
Requirements
EN 13142, Ventilation for buildings - Components/products for residential ventilation Caracteristics
of mandatory and optional requirements, Aot 2004.
1.2.2
Noise
There are ISO test standards for acoustic fan performance. Acoustic tests are described in all parts of
EN13141 and CEI/IEC 61591&60704.
31
1.2.3
Safety
32
Existing legislation
Legislation and Agreements at European Community level
The effect of environmental directives (RoHS, WEEE, Packaging directive) has been investigated and
no stakeholder reported any interaction with present study.
The new building regulations (e.g. developed under the Performance of Buildings Directive) will
increase the share of products with double flow, so will increase electricity use in order to save
thermal energy.
1.3.2
No product legislation has been indicated yet as being relevant by the Member States. Nordic
countries have limited the SFP of ventilation systems, but this can be seen more as a building code
than as a regulation of the product itself. We are aware of some features of French building code
which are of the same nature, even if they use a different physical representation. When there are two
speeds on a residential ventilation system, they use a weighted average of both electricity
consumptions to build a performance index. French regulation admits 14 hours/week of high speed if
the control is made directly by the user and 7 hours per week when its perfectly automatic (timer).
The French building code takes also into account the certification of components, i.e. the
independent verification made of some key figures provided by the manufacturer, by giving a bonus
to certified products. Its the case for extractors, air vents, etc.
1.3.3
This section again deals with the subjects as above, but now for legislation and measures in Third
Countries (extra- EU) that have been indicated by stakeholders (NGOs , industry, consumers) as being
relevant for the product group
ENERGY STAR Program Requirements for Residential Ventilating Fans (2006)
Below is the product specification (Version 2.0) for ENERGY STAR qualified residential ventilating
fans. A product must meet all of the identified criteria to earn the ENERGY STAR.
US Definitions:
- A. Residential Ventilating Fan: A ceiling, wall-mounted, or remotely mounted in-line fan designed
to be used in a bathroom or utility room, or a kitchen range hood, whose purpose is to move
objectionable air from inside the building to the outdoors. Residential ventilating fans used for cooling
(e.g., whole-house fans) or air circulation are excluded. Heat/energy recovery ventilation fans ducted
to the ventilated space and powered attic ventilators (e.g., gable fans) are excluded, but may be
considered in a future version of this specification. Residential ventilating fans with heat lamps are
excluded from this specification. This specification does not address passive ventilation of any kind.
- B. Combination Unit: A residential ventilating fan that contains a light source for general lighting
and/or a night light.
- C. In-line Ventilating Fan: A fan designed to be located within the building structure and requires
ductwork on both intake and exhaust. Those in-line fans with only one intake are referred to as single
port in-line fans, while those with multiple intake ports are referred to as multi-port in-line fans in
this specification.
33
Airflow (cfm)
Minimum
Efficacy
Level
(cfm/W)
Range Hoods
up to 500 cfm
(max)
2.8
Bathroom
and Utility
Room Fans
10 to 80 cfm
1.4
Bathroom
and Utility
Room Fans
90 to 130 cfm
2.8
Bathroom
and Utility
Room Fans
140 to 500
cfm (max)
2.8
In-Line
(single-port
& multi-port)
Ventilating
Fans
2.8
Static
pressure
difference
selected for
testing (Pa)
Airflow
(m3/h)
Minimum
Efficacy
Level W /
(m3/h)
Minimum
Efficacy
Level W /
(m3/s)
Range Hoods
up to 850
m3/h (max)
0.21
757
0.42
1513
25
0.21
757
25
0.21
757
25
0.21
757
50
Bathroom
and Utility
Room Fans
17 to 136
m3/h
Bathroom
and Utility
Room Fans
153 to 221
m3/h
Bathroom
and Utility
Room Fans
238 to
850m3/h
(max)
In-Line
(single-port
& multi-port)
Ventilating
Fans
75 or else
(according to
speed)
Table 1-9: Criteria for ENERGY STAR Qualified Residential Ventilating Fans Minimum Efficacy
Levels
Other US legislation
Some of the ventilation standards have maximum energy requirements, and others leave the energy
regulations to standards dedicated to energy use in buildings (LBL, 2005). The ventilation standards
that have specific requirements for energy usage are the ALA Health House that specifies a maximum
of 0.5 watt per cfm for exhaust fans, and 1 watt per cfm for HRVs. Minnesota requires a maximum of
0.8 W per cfm for residential (constant air volume) systems. California Title 24 is an energy standard
so it dictates that when mechanical ventilation is installed, the power of the fans is and the extra
infiltration load is added to the building energy usage.
34
35
36
According to the MEEuP methodology this task is expected to reconstruct from Prodcom and other
statistics: EU Production, Extra-EU Trade, Intra-EU Trade, Apparent EU-consumption in physical
volume and in money units and split up per Member State.
Production of hoods for years 1995 and 2005
We have had access to Italian CECED data of 1995, this country being the largest manufacturer of
hoods (6 400 000) and small fans (1 600 000) at that time and today. Most of the production was
exported (5 700 000 hoods) but 700 000 hoods were installed in Italy that year. However we dont
know proportion ventilation and recycling hoods. Hoods used as a ventilation mean and hoods used in
recycling mode are the same product: the decision on how to use the hood is made by the final user
and the energy and resources use is the same in both situations, as well as the improvement
possibilities. The main importers of Italian hoods were Germany (1 950 000), France (700 000),
BeNeLux (430 000), UK (700 000), Spain (350 000), the total of exports to other EU countries being
4 600 000 units.
For the recent years the Prodcom series are rather complete. In 2005, Italy remains the main producer,
now with 12 250 000 hoods at a declared cost of 50 Euros. Germany follows with 1 797 000 units
(116 Euros) then Spain with 1 090 000 units (102 Euros) and Poland with 440 000 units (21 Euros).
Many countries have declared their production figure confidential. The declared costs are so different
that they correspond obviously to different stages of manufacturing. However the costs between 20
and 50 Euros and 100 Euros give an indication of manufacturing costs, before any commercial circuit.
The prodcom data give imports, production and exports of hoods. But which share of the hoods is
recycling (purification) and which share is extracting air to the outside (ventilation)? This remains
unknown. We provide first (tables 2.1 and 2.2) gross and treated Prodcom figures and later (table 2.17)
stock figures obtained by assuming that half of hoods installed in Europe are connected to the outside
and so performing ventilation.
Table 2-1: Production of Hoods (29.71 15.50) according to prodcom
1995
6400
Italy
Spain
Poland
Germany
1100
Exports
EU 15
App.Cons. 5300
2000
6895
1153
?
?
2966
In000 units
2001 2002 2003
9142 9622 12329
1137 999
1006
?
339
246
?
?
?
3134 3281 3504
7218
9281
9476
2004
12726
1063
363
?
4184
2005
12256
1089
441
1797*
4322
2000
390
88
?
156
181
2001
431
89
?
164
203
In min. Euro
2002 2003
462
617
91
97
5
?
170
167
232
250
2004
616
106
6
185
296
2005
608
110
9
209
327
* inferred
From these data with assumptions, we could edit in table 2.2:
- EU Production
- Extra-EU Trade (with the assumption that extra EU trade being proportional to total exports between
the two largest EU producers) and Intra-EU Trade (with the assumption of intra EU imports being
proportional to total imports)
37
38
Apparent
Imports
Intra +
Extra
140
208
25
232
241
25
99
1277
1280
297
212
95
151
60
70
11
4
533
422
202
73
165
1096
184
1293
7102
In000 units
Produc Imports
tion
Extra
EU
0
21
0
31
0
4
0
35
3
36
0
4
7
15
0
191
1797
191
0
44
0
32
0
14
12256
23
0
9
3
10
0
2
0
1
0
80
441
63
17
30
0
11
0
25
1089
164
0
28
0
193
15613
1062
Apparent
Imports
Intra +
Extra
17
22
2
12
25
1
7
83
79
21
6
11
2
4
2
0
51
20
16
4
8
73
17
86
569
In min. Euro
Produc Imports
tion
Extra
EU
0
1
0
1
0
0
0
1
3
2
0
0
2
0
0
6
209
5
0
1
0
0
1
608
0
0
0
0
0
0
0
0
0
0
3
77
1
1
1
0
0
0
1
110
5
0
1
0
6
1010
38
Consum Exports
ption
Extra
EU
13
11
2
9
18
1
6
76
124
74
18
6
11
16
217
4
0
2
0
37
78
17
4
2
133
3
81
672
291
It is interesting to note that there has been a steady growth of exports of hoods from the 90s, but also
a quick growth of internal use. This sector of range hoods is really an exporting sector and a sector
concentrated in two (or maximum four) EU countries. The total of hoods sold from 1995 to 2005
(thanks to a linear interpolation) is around 90 million units , which can be seen as an image of the
stock in use. By applying the same stock/market ratio, we will give in table 2.17 a value for the
national stock of each country.
Production of fans for years 1995 and 2005
In principle there are ventilating fans sections in PRODCOM 29.71.15 separate from comfort fans and
called:
29.71.15.33
Roof ventilators
29.71.15.35
Other ventilators
Generally the separate figures are not available. It is necessary to formulate a hypothesis about the way
the MS use the categories provided by Prodcom and to assume that they practically merged into the
general category:
29.71.15.30
Table, floor, wall, window, ceiling or roof fans, with a self-contained electric motor of
an output <= 125 W
where ventilation is not indicated and where comfort fans imports are dominant.
The word roof in the general title of 29.71.15.30 cane seen as a reference to roof ventilators and
justifies our assumption. The existence of a EU production under this item is also in favour of our
assumption. In practical term, the hypothesis leads us to transfer from the comfort fans study to the
ventilating fans study the EU production figures.
39
Table 2-3: Manufacturing of fans under 29.71.15.30 (that will be considered now as ventilation fans)
In000 units
2000 2001 2002 2003 2004 2005
2000
1716 1927 1062 2339 2338 2184
39,403
Italy
200? 300?
637
1059 1423 ? 1800
?
Poland
3074 3014 2848 3897 3790 2707 105,412
UK
0
0
0
0
0
24
0
Portugal
171
168
181
0
0
0
12,820
Sweden
?1500 1470 1483 1671 1641 1922
?
Spain
Germany 4000? 4000? 4000? 4000? 4000? 3859 198,221
TOTAL 10661 10879 10211 12966 13192 10696 355,856
2001
46,154
?
101,171
0
12,841
18,993
?
179,159
In min. Euro
2002
2003
48,102
46,169
3,758
6,963
95,114
96,834
0
0
14,095
0
19,613
18,293
150,783 139,903
332,32 308,162
2004
51,808
8,485
105,222
0
0
20,273
130,404
316,192
2005
49,906
?
95,715
5,757
0
20,470
116,392
288,24
Prodcom data are sometimes available for roof ventilators and other ventilators and indicate for
instance an Italian production for 1998 and 1999: 1 300 000 units with a unitary value of 27 Euros. It
is very consistent with the figures that we obtain for 2000-2005 with our assumption. The fact that
manufacturing takes place in UK, Germany and Spain is also confirmation.
Now that we have the production, how to estimate the national share of ventilation products
(accounted for under 29.71.15.30 by mistake) purchased by each country? First we have to admit
that the small fans are used in many sectors, and we assume half of them is in the non residential
sector (small offices, workshops, etc). Then EU production is split according to the construction of
recent buildings7 in table 2.4 below. Extra-EU Trade has been estimated as negligible in this analysis
up to now, which is a weak point. In the following table we have admitted 33% exports8. Note that
sales of hoods and other ventilation fans seem to be of the same order of magnitude, a point that is of
importance for energy consumption calculation later.
Given by lot 1 study, corrected in the ventilation report, one exception is Portugal, where we assume
national use of the few products manufactured recently
8
This figure corresponds to the export values that was problematic in the comfort fans report
40
Table 2-4: Sharing the 2005 EU production of products under 29.71.15.30 according to number of
recently constructed dwellings
Intra EU
~1000
Dwellings
1990-2005
Total to
EU25
To : A
To : B
To : CY
To : CZ
To : DK
To : EST
To : FIN
To : F
To : D
To : GR
To : H
To : IRL
To : IT
To : LT
To : LIT
To : LUX
To : MT
To : NL
To : PL
To : P
To : SK
To : SLO
To : E
To : S
To : UK
13213
345
519
20
187
119
13
178
1931
1659
346
197
410
440
16
41
22
10
789
860
655
843
48
1421
182
1961
Total
from
EU 25
IT
(From)
PL
(From)
UK
(From)
P
(From)
E
(From)
D
(From)
4194
2200
1800
2700
24
1900
3900
109
164
6
58
38
5
57
609
523
110
61
130
138
6
13
7
3
250
272
230
265
15
449
57
619
19
29
1
10
7
1
10
107
92
19
11
23
24
1
2
1
1
44
48
36
47
3
79
10
109
16
24
1
8
5
1
8
88
75
16
9
19
20
1
2
1
0
36
39
30
38
2
65
8
89
23
35
1
13
8
1
12
131
113
24
13
28
30
1
3
2
1
54
59
45
57
3
97
12
134
17
25
1
9
6
1
9
93
80
17
9
20
21
1
2
1
0
38
41
31
40
2
68
9
94
34
51
2
18
12
1
18
190
163
34
19
40
43
2
4
2
1
78
85
64
83
5
140
18
193
24
By extrapolating back to 1995 and summing up, we have obtained a stock/market ratio that we applied
to get an estimate of national stocks from the Prodcom data, that we will give in table 2.17.
2.2
41
We can add to that aggregates sold for one-family houses under renovation where ventilation is
established (which is very much on the increase) and products used for maintenance. In blocks of flats
where ventilation is most often carried out with central exhaust without heat recovery.
The total Scandinavian market has been estimated by one stakeholder to be around 650 000 units,
likely without the hoods.
German market data generated by (TZWL, 2007) for 1999, 2002, 2003 from the German
manufacturers are reproduced hereunder. The TZWL splits the decentralised solutions (we admit
that they correspond to window, wall and roof fans) and the centralised solutions (real extractor
fans). As suggested by the author they have been corrected due to the lack of 10% of sales in the
statistics. Part of the so called decentralised systems are not used in residences, but we dont know
the proportion. This treatment gives the corrected sales hereunder that we consider completely
underestimated, an impression to be checked from other sources.
Germany
Uncorrected sales
decentralised
Uncorrected sales
centralised
Corrected sales
decentralised
Corrected sales
centralised
1999
2002
2003
82500
116000
160000
62000
41000
30000
91600
128800
177700
68800
45500
33300
For BeNeLux, one stakeholder indicated total yearly sales of 350 000 units, certainly without the
hoods, likely ICV only.
In the Netherlands, the building code will have a strong influence now on the product under
consideration in the present report. The consumption of the ventilating fans is taken into account with
a default value, lower for direct current motors than for AC motors. There is at the same time a big
pressure in favour of heat recovery systems, which increase the head losses, and thus the power
demand.
Figure 2.1 hereunder (ENPER, 2006b) shows the evolution of the share of the various ventilation
systems in newly built dutch buildings. The traditional systems were close from the traditional
42
French market data figures generated by the manufacturers association (Uniclima, 2006) are not
corrected for exhaustiveness by including imports and excluding exports. However the manufacturers
association gather most of the industry and the margin of uncertainty is less than 20%. Since
centralised extraction is almost the rule in France now, we can estimate that we have a saturated
market, and discover the renewal process.
2004
2005
2006
2007*
542 000
567 000
609 000
642 000
ICV&HR sales
3600
3800
5000
8600
240 000
250 000
230 000
250 000
to
350000
to
358000
to
445000
to
465000
DV** (renovation
and maintenance)
247 000
234 000
250 000
308 000
93000
100000
105000
114000
CCV&HR** sales
1100
1400
1700
2400
number of new
CCV dwellings
187000
214000
209000
250000
Same divided by 5
37400
42800
41800
50000
ICV estimated in
renovation and
maintenance
43
This indication is important because by comparing the flux of renovation equipment of table 2.6 and
the stock of installed equipment, we find an apparent lifetime around 10 years.
- for collective housing,
Housing - collective
No ventilation
Nat. ventilation
room by room
Total natural ventilation
Mechanical ventilation
Total ventilation (nat.+mech.)
9%
34 %
2298
5162
7460
17 %
40 %
57 %
Table 2-8: Ventilation equipment rate of individual and collective housing in France, from (ATEE,
2006)
Results of the tables 2.6 and 2.7 added are shown on the graph below.
Figure 2-2: Ventilation equipment rate of individual and collective housing (total stock) in France, from
(ATEE, 2006)
44
For the UK in 1998, BSRIA data reported by (Radgen, 2002) indicate the following sales:
Product
Axial ventilator
Centrifugal ventilator
Heat recovery units
Cooking hoods
Sales
1400000
180000
10000
550000
Table 2-9: UK sales of ventilation products in 1998, source BSRIA extracted from (Radgen, 2002)
Most dwellings would have one or no extract fans, and they would be switch-controlled (often linked
to the lighting of an internal toilet). Continuous operation would be very rare for individual units.
Centralised systems will be mostly in older blocks of flats. Flats account for about 20 % of UK
dwellings, and perhaps 60 % of them are in high-rise blocks. Of these, only municipal blocks (mostly
built in the 1960s or 1970s) are likely to have centralised systems. So 10 % might be reasonable for
pre-1990, but perhaps only 5 % for newer ones (new build has more flats, but they are less likely to be
high-rise or municipally owned).
The number of electrically powered extractor fans in English dwellings has been examined, as
observed by the 2003/04 (combined) English House Condition Survey. The survey identifies the
presence of extractor fans in the kitchen, the bathroom and the WC, marking where a fan is present in
each room. No other rooms are examined and the results should be interpreted as indicating the
minimum number of extractor fans in a dwelling (as other fans may be present elsewhere in the
dwelling, and the rooms that are examined may contain more than one fan). However, it reasonable to
assume that these rooms are the most likely to contain extractor fans across the stock, and that few will
contain more than one fan. A small number (2.7 %) of survey cases recorded missing / unknown data
and it should be noted that these are included in the percentages below.
Number of
extractor fans
Number of
dwellings
Percent of
all dwellings
10,479,000
48.5%
6,504,000
30.1%
3,994,000
18.5%
59,000
0.3%
578,000
2.7%
21,613,000
100%
1
2
3 or more
Missing /
Unknown
Total
House or
bungalow
Total
Number of
dwellings
Percent of
all houses
or
bungalows
3+
Missing /
Unknown
8,898,000
5,436,000
3,098,000
489,000
17,954,000
49.6%
30.3%
17.3%
2.7%
100.0%
45
Flat
Total
Number of
dwellings
Percent of
all flats
Number of
dwellings
Percent of
all
dwellings
1,580,000
1,068,000
896,000
89,000
3659000
43.2%
29.2%
24.5%
2.4%
100.0%
10,479,000
6,504,000
3,994,000
59,000
578,000
21,613,000
48.5%
30.1%
18.5%
0.3%
2.7%
100%
46
Figure 2-3: Ventilation systems in new and existing buildings, from (Ledean, 2007)
This allows to share the stock of dwellings among technical solutions. After considering various
sources of data, namely Impro9, we found that the data generated by Lot 1 about the age of the heated
areas was the most convenient to translate ventilation fans penetration into numbers of fans. We
extracted the following data from version 3 of task 2 report of Lot 1 (VHK Lot1, 2006).
Country
Primary
residences
(1000)
Years
1 or 2
Dwell.
Multi
EU-25
184166
54 %
46 %
A
B
CY
CZ
DK
EST
FIN
F
D
GR
H
IRL
IT
LT
3 280
4325
239
4216
2481
566
2378
24525
38944
3674
3863
1382
22004
915
48%
75%
na
44 %
61 %
32 %
42 %
57 %
46 %
59 %
66 %
91 %
25 %
29 %
52 %
25 %
na
57 %
39 %
68 %
58 %
43 %
54 %
41 %
34 %
9%
75 %
71 %
8%
17 %
7%
15 %
17 %
14 %
9%
13 %
13 %
7%
13 %
8%
11 %
14 %
27 %
29 %
17 %
26 %
28 %
30 %
31 %
18 %
47 %
32 %
26 %
16 %
41 %
28 %
19711980
20 %
16 %
15 %
21 %
23 %
18 %
22 %
23 %
26 %
11 %
25 %
22 %
18 %
20 %
23 %
Floor
Area
(m2)
22 %
13 %
87
12 %
9%
27 %
16 %
10 %
20 %
20 %
10 %
15 %
19 %
18 %
16 %
10 %
21 %
18 %
15 %
8%
7%
5%
14 %
12 %
14 %
7%
32 %
4%
94
86
145
76
109
60
77
90
90
83
75
104
90
55
http://ec.europa.eu/environment/ipp/identifying.htm
47
1346
171
129
6996
13337
3651
20272
685
14187
4454
24346
39 %
71 %
na
69 %
37 %
77 %
49 %
72 %
53 %
48 %
81 %
61 %
29 %
na
31 %
63 %
23 %
52 %
28 %
48 %
52 %
19 %
6%
12 %
15 %
7%
10 %
6%
3%
15 %
9%
12 %
21 %
23 %
15 %
11 %
13 %
13 %
9%
7%
8%
4%
20 %
18 %
33 %
27 %
29 %
31 %
27 %
23 %
35 %
28 %
34 %
33 %
21 %
18 %
15 %
17 %
19 %
18 %
18 %
26 %
24 %
24 %
17 %
22 %
14 %
12 %
16 %
30 %
19 %
44 %
21 %
16 %
14 %
10 %
19 %
6%
17 %
12 %
13 %
7%
9%
16 %
7%
-
61
125
106
98
68
83
56
75
90
92
87
Table 2-12: Characteristics of the EU heated area, residential sector source (VHK Lot1, 2006)
Germany, UK, Italy, Cyprus, Portugal and the Netherlands suffer from a small problem in the original
report. For the six countries with missing figures we split the figure after 1975 equally before and
after 1995. The values obtained have been used in the following.
To cover all countries we generated default values about individual housing, by grouping countries
according to their history in ventilation. The result is given in table 2.13.
Share in
individual
houses10
GROUP 1
Northern
DK FIN S
GROUP 2
Middle North
A IRL SLO UK
D
GROUP 3
Middle South
B F LUX NL
GROUP 4
Southern
CY GR IT MT P
E
GROUP 5
NMS
CZ EST H LT
LIT PL SK
% of DV % of ICV % of DV
before
before
after
1990
1990
1990
15 %
15%
35 %
10%
30 %
40%
35 %
% of
% of
% of ICV
DV&HR
ICV&HR
after
after
after
1990
1990
1990
5%
10%
90%
10%
10%
95 %
5%
20 %
35 %
5%
5%
5%
5%
Table 2-13: Default values of technical shares of ventilation system types to model the EU stock of
ventilation fans in EU single dwellings (excl. collective)
In both individual and collective ventilation, when a dwelling is treated by decentralised ventilation it
means for us 1.5 fan per average dwelling (on average, 0.8 intermittent in the kitchen hood, 0.6
intermittent in a wet room, either wall or window, 0.1 continuous in another wet room). Obviously
some dwellings have two fans and others have one. Many dwellings (all percentages not allocated to
one technique) have no mechanical ventilation.
In collective dwellings all over Europe we consider that Centralised products treat 5 flats per fan. This
last figure (5 flats per fan) takes into account the following: there is more than one exhaust fan per flat
10
Mostly based on table 2-2, GROUP1 on Finland, GROUP 2 on UK, GROUP 3 on FR, GROUP 4
on IT GROUP 5 on PL but adjusted for consistency
48
% of DV
before
1990
% of
CCV
before
1990
% of DV
after
1990
80%
10 %
40%
30 %
% of
DV&HR
after
1990
% of
CCV
after
1990
% of
CCV&HR
after 1990
70%
30%
50%
Table 2-14: Default values of technical shares of ventilation system types to model the EU stock of
ventilation fans in EU collective dwellings
The default values were only provisional and have been substituted with national survey values in
most cases. The work described allowed to generate an estimate of the number of pieces of equipment
in use in both individual and collective dwellings, and of the area covered by the collective techniques
CCV and CCV&HR in collective buildings (area being a factor that appeared more adequate for
energy calculation in that segment).
If we admit the 10 year life time adopted in lot 11 for non residential use, the EU sales for renovation
is of the order of magnitude of one tenth of stock figures. One manufacturer indicated a lifetime from
8 to 10 years. Another manufacturer in the residential area indicated a lifetime of 16 years of the
products. The only documented evidence comes from the French market and is around 10 years. The
value of lot 11 has been kept.
The division of the stock by life duration in years leads us to an estimate of maintenance market
figures in the absence of new buildings (substitution of equipment by similar equipment if the market
were stable and saturated). Then we have to add the units sold in new construction. We estimated it by
computing the flux of new buildings (at the average rate since 1990) from the same VHK source, table
2.12. By doing so we neglect the installation of mechanical ventilation in previously naturally
ventilated buildings, one of the reasons for which adjustment to field data is useful.
By adding the two markets (renovation and new buildings) we found the sales figure that we compare
to the scarce field indications and to the analysis we derived from Prodcom values.
Adjustment of the purely predictive model at EU level to field data
Whatever the limitations of field data, we then made our best to adapt our model to the field data in
the countries having field data. We give now our final estimates obtained by doing so.
49
Table 2-15: Adjusted technical shares of ventilation system types to model the EU stock of ventilation
fans in EU single dwellings (excl. collective)
Share in
individual houses
A
B
CY
CZ
DK
EST
FIN
F
D
GR
H
IRL
IT
LT
LIT
LUX
MT
NL
PL
P
SK
SLO
E
S
UK
% of DV
before
1990
35%
50%
40%
15%
15%
15%
30%
10%
35%
40%
15%
70%
40%
15%
15%
50%
40%
30%
15%
40%
15%
35%
40%
30%
20%
% of ICV
before
1990
10%
40%
% of DV
after 1990
35%
% of
DV&HR
after 1990
5%
35%
5%
30%
5%
30%
15%
10%
35%
35%
5%
70%
35%
5%
5%
5%
40%
35%
40%
10%
5%
35%
5%
35%
35%
30%
30%
5%
% of ICV
after 1990
10%
95%
5%
5%
10%
5%
10%
95%
10%
5%
5%
5%
5%
5%
5%
95%
5%
90%
5%
5%
5%
10%
5%
10%
5%
% of
ICV&HR
after 1990
5%
5%
90%
90%
5%
5%
5%
10%
5%
90%
Table 2-16: Adjusted values of technical shares of ventilation system types to model the EU stock of
ventilation fans in EU collective dwellings
Share in collective
dwellings
A
B
CY
CZ
DK
EST
FIN
F
D
GR
H
IRL
IT
LT
LIT
LUX
MT
NL
PL
P
SK
% of DV
before
1990
20%
15%
15%
15%
15%
10%
20%
15%
15%
80%
15%
15%
15%
15%
15%
10%
15%
15%
15%
% of
CCV
before
1990
40%
40%
40%
80%
40%
80%
35%
40%
40%
10%
40%
40%
40%
40%
40%
40%
40%
40%
40%
% of DV
after 1990
30%
30%
30%
30%
30%
30%
30%
30%
95%
30%
30%
30%
30%
30%
30%
30%
30%
30%
% of
% of
DV&HR
CCV
after 1990 after 1990
10%
50%
50%
50%
70%
50%
70%
100%
10%
50%
50%
5%
50%
50%
50%
50%
50%
50%
50%
50%
50%
% of
CCV&HR
after 1990
30%
30%
50
20%
15%
80%
40%
80%
10%
30%
30%
10%
50%
70%
5%
95%
30%
This adjustment leads us to our third and final estimate of the stock of products in use:
Table 2-17: Adjusted estimate of the stock of distributed ventilation fans in use in number of units in
EU-25 in 2005
Estim.3
Stock
~1000
EU-25
A
B
CY
CZ
DK
EST
FIN
F
D
GR
H
IRL
IT
LT
LIT
LUX
MT
NL
PL
P
SK
SLO
E
S
UK
Nb DV in
Nb DV in
use
use
continuo
On/off
us
4527
63377
92
1292
157
2191
7
97
65
914
21
296
9
122
26
361
216
3021
1063
14887
111
1553
58
806
99
1380
479
6700
14
196
21
289
6
83
4
52
151
2118
210
2940
125
1746
311
4357
21
298
413
5785
60
835
790
11057
Nb
DV&HR
in use
Cont.
84
14
0
0
0
0
0
0
0
67
0
0
0
0
0
0
0
0
0
0
0
0
2
0
0
0
Total DV
stock
67987
1398
2348
104
979
317
130
387
3237
16018
1664
863
1479
7179
210
309
89
56
2269
3150
1871
4669
321
6199
895
11847
Nb hoods
prodcom
+ Est.
47840
383
647
102
802
716
102
326
4987
8569
761
586
383
16076
244
256
45
16
969
590
859
269
130
5451
187
4384
Nb fans
prodcom
+
Est
34223
889
1338
49
473
310
41
465
4969
4268
898
498
1061
1126
49
106
57
24
2040
2220
1877
2162
122
3664
465
5051
Nb DV
prodcom
+
Est
82063
1272
1985
151
1275
1026
143
791
9956
12837
1659
1084
1444
17202
293
362
102
40
3009
2810
2736
2431
252
9115
652
9435
Table 2-18: Adjusted estimate of the stock of centralised ventilation fans in use in number of units in
EU-25 in 2005
Estim.3
Stock
~1000
Nb ICV
in use
1 or 2
dwelling
EU-25
A
B
CY
CZ
DK
EST
FIN
F
D
GR
H
IRL
IT
10992
157
1565
1
7
433
0
272
3439
1791
15
9
20
14
Nb
ICV&HR
in use
1 or 2
dwell.
621
14
24
0
0
95
0
126
84
67
0
0
0
0
Nb CCV
in use
Coll.
Dwell.
6161
6
90
9
196
153
31
217
903
32
125
107
2
1337
Nb
CCV&H
R in use
Coll.
Dwell.
25
0
0
0
0
4
0
12
0
0
0
0
0
0
Area
CCV
Coll.
dwell.
2510121
2886
38590
6592
74516
83636
9353
83474
406222
14195
51761
40092
1087
601534
Area
CCV&H
R
Coll.
Dwell.
11150
0
0
0
0
2215
0
4460
0
0
0
0
0
0
51
1
2
60
0
2293
32
31
35
49
60
611
94
0
0
1
0
72
0
0
0
2
0
135
0
52
67
4
5
180
694
71
858
0
567
367
88
0
0
0
0
0
0
0
0
0
0
10
0
14435
20334
2585
2591
88203
235970
29412
240261
129
254957
168972
38332
0
0
0
0
0
0
0
0
0
0
4475
0
We can make the following analysis of discrepancies between modeling, prodcom and national
figures:
The total stock estimates obtained from this model and from our treatment of the Prodcom data have
the same order of magnitude for DV.
In the case of France the stock of 3.2 million ICV and 3.2 million DV compare quite well with the 4.8
mechanically ventilated dwellings since there are various DV in one dwelling.
The model gives a stock of 11.9 million DV in the UK, while a total of 14.5 million is reported in the
census (we assumed hoods were considered as DV in the census).
If we accept this stock model, the market estimation becomes the following:
Table 2-19: Adjusted estimate of sales data
Market
Estim.3
~1000
Estimate
Market
DV
Of which
Hoods
Of which
Fans
EU-25
A
B
CY
CZ
DK
EST
FIN
F
D
GR
H
IRL
IT
LT
LIT
LUX
MT
NL
PL
P
SK
SLO
E
S
UK
7294
160
240
11
104
32
14
39
324
1701
183
90
180
752
22
33
9
6
237
351
214
492
34
695
89
1283
3883
84
128
6
56
17
7
21
173
901
98
48
96
401
12
17
5
3
126
187
114
263
18
370
48
684
3411
76
112
5
49
15
6
18
151
800
86
42
84
351
10
15
4
3
110
164
100
230
16
324
42
599
Nb hoods
from
Prodcom
(1/2)
5876
47
80
13
99
88
13
40
613
1053
94
72
47
1975
30
32
6
2
119
73
106
33
16
670
23
539
Nb fans
from
Prodcom
(T 2.3)
4194
109
164
6
58
38
5
57
609
523
110
61
130
138
6
13
7
3
250
272
230
265
15
449
57
619
Estimate
Market
ICV
1316
18
187
0
1
44
0
28
450
188
3
1
3
2
0
0
7
0
273
5
5
6
5
10
62
16
Estimate
Market
ICV
&HR
104
2
4
0
0
16
0
21
14
11
0
0
0
0
0
0
0
0
12
0
0
0
0
0
22
0
Estimate
market
CCV
673
1
10
1
21
16
3
23
107
5
14
11
0
139
5
7
0
1
20
77
8
91
0
64
38
9
Estimate
market
CCV&H
R
4
0
0
0
0
1
0
2
0
0
0
0
0
0
0
0
0
0
0
0
0
0
0
0
2
0
We can make the following analysis of discrepancies between modeling and prodcom derived figures,
as well as national figures :
The modeling of the German market is confirmed by the prodcom figures ; our results are far from the
TZWL report which should correspond to something different from the National market.
52
Market trends
The central question is: which building regulations (e.g. developed under the Performance of
Buildings Directive) are leading to forced ventilation as a practical obligation in residences? Which
base cases have been taken for energy consumption calculation (with or without some features of the
equipment)? This information will decide on the future market trends: either the stable evolution as
before or a quick market change in the direction of the centralised extractor. This uncertainty is not
legal (since EPBD is enforced) but largely practical: thermal regulations for buildings generally open
various ways of compliance; forced ventilation with a certain quality may be part of the less costly
package of solutions to comply with the codes in one country and not in another country. Other
uncertainties are related to the part of EPBD demanding energy efficiency improvements in case of
building retrofit and the demand of the end user for more comfort in air quality.
Impact of the EPBD is high in new buildings. The market seems to move from local intermittent to
continuous centralised ventilation, and then towards the introduction of more sophisticated systems. In
many countries moving from natural ventilation to controlled (mechanical) ventilation is among the
most cost effective ways to fit into the new range of energy consumption allowed. The market of ICV
will consequently explode. In countries with mostly natural ventilation the trend will be towards DV
(or directly ICV?).
Some stakeholders have reported that this step into centralised mechanical ventilation is being done in
the frame of EPBD especially in the following countries: Czech Republic, Italy, Poland, Spain, United
Kingdom.
Double flow systems (balanced ventilation) are still infrequent but expanding in new buildings. In the
Netherlands the very strict building codes pushed them up to 30 % of the market recently (ENPER
2006) and we can consider they will have a higher value in the coming years, like 50 %. This
percentage already reaches 6 % in Germany (TZWL, 2007). TZWL also proposed a scenario of future
sales of double flow systems with heat recovery. It has three variants, high, medium and low.
Remember there is decentralised and centralised equipment in the figures.
The EPBD section about large retrofits may also have some effect, difficult to indicate now. We
have limited the effect of improvements to the introduction of a better equipment of the same type in a
maintenance operation, and not considered introduction of a certain type of equipment in a building
designed for another ventilation.
Figure 2-4: Market previsions of the growth of residential mechanical ventilation in Germany (TZML,
2007)
53
A few percent of the market will also be gained in the remaining countries with high standards on
energy in buildings. From our perspective, this category of products a priori requests more electricity
than simple extraction because of the two fans and of the added heat exchanger in the flow air stream.
In some countries, like Finland, heat recovery efficiency is an integral part of the norms. Some
stakeholders from Finland stressed that 90 % of the true matter (the choices made for the ventilation)
is ignored in an EuP study whilst max 10 % of the true energy usage (the electricity part, as opposed to
the heating demand generated by ventilation) gets 100 % of the focus. However, we maintain this
approach of considering only the product and not the system, which includes heat recovery or not,
depending on the country, a factor that we will not change here, and that results from national
decisions taken at the time of EPBD.
In Finland and other Nordic countries, the stakeholders indicate that most new buildings are
equipped with mechanical supply+exhaust ventilation (e.g one-family houses more than 90 % and
commercial buildings practically 100 %), and practically 100 % of these with heat recovery. (If not,
this must be compensated by e.g. additional thermal insulation, or windows with U-value far below 1).
Logically some MS already thought about the electricity consumption added. There is a label with a
certain market significance in Germany: Passivhaus geignete Komponente which, among others
can be applied to the central unit of the balanced double flow unit. It requires a heat exchanger with 75
% effectiveness, an SFP lower than 0.45 W/(m3/h) which seems not as difficult to reach as one could
expect, but includes the effect of the heat exchanger head losses, and leakage rates of air flow rate
lower than 3 %.
There is a kind of label leading to white certificates allowance in France for the central unit of the
balanced double flow unit (ATEE, 2006). It requires a heat exchanger with 85 % effectiveness, an SFP
lower than 0.30 W/(m3/h) for each of the flows, and demands duct insulation higher than 1.2 m2.K/W.
There is a limit of 80 W on total electricity consumption in the case of individual houses. There is
check of air permeability of the building. The revision of building codes may lead to a penetration of
heat recovery following the Netherlands with some delay.
We summarise presently the trends by a marginal penetration rate (in the new dwellings after 2005).
First for individual houses:
54
Table 2-20: Projections to 2025, penetration of mechanical ventilation in new dwellings individual
houses
Share in
individu
al
houses
% of
DV
before
1990
% of
ICV
before
1990
% of
DV
1990
2005
% of
DV&H
R 1990
2005
% of
ICV
1990
2005
% of
ICV&H
R 1990
2005
% of
DV
2005
2025
% of
DV&H
R 2005
2025
% of
ICV
2005
2025
% of
ICV&H
R 2005
2025
A
B
CY
CZ
DK
EST
FIN
F
D
GR
H
IRL
IT
LT
LIT
LUX
MT
NL
PL
P
SK
SLO
E
S
UK
35%
10%
35%
5%
10%
5%
35%
15%
25%
25%
50%
40%
15%
15%
15%
30%
10%
35%
40%
15%
70%
40%
15%
15%
50%
40%
30%
15%
40%
15%
35%
40%
30%
20%
40%
95%
5%
5%
10%
5%
10%
95%
10%
5%
5%
5%
5%
5%
5%
95%
5%
90%
5%
5%
5%
10%
5%
10%
5%
5%
75%
5%
75%
10%
75%
0%
75%
45%
5%
75%
40%
5%
75%
75%
75%
5%
75%
75%
5%
5%
25%
5%
0%
40%
25%
35%
5%
30%
5%
30%
15%
10%
35%
35%
5%
70%
35%
5%
5%
5%
40%
35%
40%
10%
5%
35%
5%
35%
35%
30%
30%
5%
75%
25%
90%
25%
90%
5%
5%
75%
75%
25%
30%
75%
25%
25%
15%
5%
75%
10%
5%
25%
75%
25%
35%
75%
90%
30%
15%
90%
100%
25%
25%
25%
25%
25%
100%
55
20%
15%
CY
CZ
% of
DV&
HR
1990
2005
% of
CCV
1990
2005
% of
CCV
&HR
1990
2005
% of
DV
2005
2025
% of
DV&
HR
2005
2025
% of
CCV
2005
2025
% of
CCV
&HR
2005
2025
10%
10%
5%
5%
30%
10%
75%
40%
30%
50%
45%
50%
15%
40%
30%
50%
30%
50%
15%
40%
30%
50%
50%
50%
DK
EST
% of
DV
1990
2005
80%
15%
FIN
F
10%
20%
GR
15%
40%
70%
30%
30%
50%
80%
70%
35%
100%
50%
50%
30%
50%
50%
50%
75%
25%
25%
30%
10%
65%
10%
40%
30%
50%
30%
50%
15%
40%
30%
50%
50%
50%
IRL
80%
10%
95%
5%
95%
5%
IT
15%
40%
30%
50%
30%
50%
LT
15%
40%
30%
50%
50%
50%
LIT
15%
40%
30%
50%
50%
50%
LUX
15%
40%
30%
50%
25%
50%
MT
15%
40%
30%
50%
30%
50%
NL
10%
40%
30%
50%
25%
50%
PL
15%
40%
30%
50%
50%
50%
15%
40%
30%
50%
30%
50%
SK
15%
40%
30%
50%
50%
50%
SLO
20%
30%
10%
65%
10%
15%
30%
50%
30%
50%
S
UK
40%
80%
80%
10%
70%
95%
5%
30%
90%
50%
25%
25%
25%
50%
50%
5%
5%
Obviously in existing buildings products will be replaced by identical products, in the absence of a
clear application of the EPBD article on retrofits.
Starting from the residential area and repartition from table 2-12, we can estimate the stock from 2005
to 2025. The growth rate of the total residential building stock is of 0,9 % yearly (VHK Lot1, 2006).
MS yearly growth rates give the new built area yearly and thus the increase of total built area. Given
the low level of demolition/removed surfaces, this removal rate is supposed null. Combining tables
2.20 and 2.21 with the total built area gives the stock evolution by country. Stock figures for
equipment can be deduced.
56
Stock estimate
~1000 units
60000
700
50000
600
500
40000
400
30000
300
20000
200
10000
0
100
2005
2010
2015
2020
2025
DV (minus hoods)
31688
34105
36661
39367
42234
Hoods
36215
38978
41899
44991
48268
ICV
10992
13111
15356
17735
20260
ICV&HR
621
1299
2011
2760
3548
CCV
6161
6507
6872
7256
7661
DV&HR
84
207
336
471
613
CCV&HR
25
118
214
315
420
4000
DV&HR
3000
ICV
ICVHR
2000
CCV
CCVHR
1000
0
1995
2000
2005
2010
2015
2020
2025
57
Figure 2-6: Projections to 2025, consumption estimate EU 25 for all forms of residential ventilation (in
TWh)
35
30
25
CCVHR
ICVHR
DV&HR
CCV
ICV
DV
Hoods
20
15
10
0
2005
2010
2015
2020
2025
The expansion of products with heat recovery is clear but still limited because it grows mostly in new
construction.
Figure 2-7: Projections to 2025, consumption estimate EU 25 for residential ventilation products in the
scope of this lot (in TWh)
14
12
10
ICVHR
DV&HR
ICV
DV
Hoods
8
6
4
2
0
2005
2010
2015
2020
2025
58
Hoods
Other DV
ICV
DV&HR
ICV&HR
total
2,38
2,56
2,77
2,98
3,17
0,68
0,73
0,79
0,85
0,90
2,89
3,45
4,09
4,72
5,31
0,03
0,06
0,12
0,18
0,24
0,36
0,67
1,17
1,71
2,24
6,34
7,46
8,94
10,43
11,86
Due to their higher unitary electricity consumption, the growth of products with heat recovery seems
even higher under this form.
59
60
61
Consumer behaviour is often characterised by lack of awareness about the ventilation equipment and
about air quality: the equipment is usually continuously in use and the effects of its operation are not
related to one of the five senses. This lack of functional feedback is a barrier to eco-design measures,
or even to the simplest maintenance and design operations: the equipment and its status are ignored by
the end user, its electricity consumption is some kind of non perceived stand by. That is why
ventilation is a subject for sanitary regulation in all Member States. The relevant use parameters that
influence the environmental impact during product-life are very different from the Standard test
conditions as described in Subtask 1.2 since the product is one single package designed to suit many
practical situations (number of rooms, types of opening control, etc.) and that may be inefficient in a
number of them.
An explanation for the user to understand the important factors of system design having an influence
on product behaviour and related with the end user choices:
1- Ventilation increases the demand for heating and cooling (thermal demand) but is needed for IAQ
(Internal Air Quality) reasons.
2- Natural ventilation can be designed as a system in order to give a flow rate as stable as possible.
3- Natural ventilation can be designed room by room or taking the dwelling as a full system (inlets in
some rooms, outlets in some other rooms, called the wet rooms)
4- Artificial ventilation avoids fluctuations of air changes (ACH = air change per hour) existing with
natural ventilation: both the high values generating high loads (and discomfort) and the small values
not respecting the proper IAQ. This is obtained by a proper system design (exhausts, ducts, extraction
fan).
5- This mechanical system design can be made room by room (decentralised artificial ventilation,
mostly window, wall and range hood in kitchens) or for the entire dwelling as a single system
(extraction fan).
6- We are concentrating here on the ventilation equipment of local and central artificial ventilation, the
one using electricity, not the system design which belongs to the field of national regulations.
7- Efficiency will be judged at product level but this is only part of ventilation system efficiency, a
trade-off between electricity consumed, thermal energy saved and internal air quality obtained.
8- However some extraction products adapt better with the other components and/or may adapt better
to the various conditions met on the field, by using less electricity for the same result.
The decisions to be taken are not even explained to the end user. In most cases, the home builder or
installer decides on the initial choices, like natural vs mechanical ventilation, as a consequence of
national habits and regulations.
At the end, the installer selects an equipment according to its commercial agreements, substitution is
done to the identical. The coherence may be given by the manufacturers because of the frequently sold
packages or kits with corresponding equipment. In the other cases, it may happen that the
exhausts, inlets and fans are non consistent.
Speaking of retrofit, the air conditioner called single duct can also be considered as a ventilation
system. It has always a pure ventilation option, where it only puts the room in under pressure, expels
some air, but generates a flux into the room coming from another room or from outside. When its
used as an air conditioner it has the two functions at the same time: ventilation and cooling. The
interaction may be productive if the air incoming is cool (free cooling from underground or from
outside) or negative (if the air from outside brings heat into the room).
62
As will be described technically in the following, the pressure of EPBD based and MS regulations
towards the decrease of thermal energy use in heating the air lead to enormous variations in air flow,
i.e. in load, to take into account actual occupation at each instant.
The impact of mechanical ventilation is twofold at system level. A study by Ademe/ATEE (ATEE,
2006) indicates the magnitude of yearly thermal energy gains obtained by introducing a simple
mechanical ventilation with self adjustment by special extracts instead of natural ventilation
(Passive stack ventilation from the 70s in France): from 2894 kWh to 1154 kWh in individual houses
(1740 kWh savings), from 1838 kWh to 733 kWh in flats (1105 kWh savings), in both cases 60% of
initial consumption expressed in useful energy. The associated yearly electricity consumption,
assuming an old 50 W extraction unit is about 437 kWh. This means a significant final energy saving,
but not so much when translated in primary energy with the factor 2.5. For instance with an efficient
boiler in a flat the saving is 1381 kWh primary and the additional consumption is 1092 kWh primary.
The more efficient the extraction is, the more savings can be attributed to mechanical ventilation,
either in final or primary energy.
Noise
Noise impact of ventilation is significant: noise coming from the fan through the ducts, from outside
through air inlets, noise travelling between rooms or apartments through ducts, etc. Passive dampers
are routinely used, and do not solve completely the problem. Noise impact depends more on the
capacities of the installer to use good ducts, dampers, intermediate sound trap than on the acoustic
source itself.
Available end user control
Some ventilation devices are controlled by the light switch (in restrooms for instance) or by timer
(hoods)s. Their real use time is relatively small because of the direct link with another energy service
or because of customer awareness. It is namely the case for decentralised systems or systems having a
constant flow and intermittent use.
Most ventilation devices are integrated in the building. They operate continuously but adapt to
conditions. Some other offer various speeds either as a free choice or associated with the use of the
kitchen hood. The control of two, three or four speeds may be done with a manual command, and
sometimes a timer (the fan comes back to lower speed after one hour). Some only adapt to the pressure
variations in the incoming ducts.
The system is the following (in the case of under pressure).
63
Ventilation
Exhaust grilles
Air ducts
Air inlets
Figure 3-1: Centralized mechanical exhaust and natural supply ventilation system, from (ADEME,
2007)
The envelope openings (cracks or trickle inlets) by which infiltration takes place are an essential part
of the ventilation system. Some windows include already the calibrated trickle inlets. A certain
pressure drop is generated. In some cases the air inlets are self adjusting (keeping air flow constant
despite of pressure or even humidity sensitive). Part of infiltrated air is used in transverse ventilation
due to pressure differences on the outside of the building shell. Part is extracted by the fan.
64
A centralised system should be balanced. This means design or selection of adequate components but
also a balancing work on the field.
The ventilation package interferes with the ducts and mostly with the exhausts through pressure
changes. There is no control using electronic transmission of information to our knowledge: only the
traveling signal given by pressure is used, for obvious cost reasons. The extracts have a constant
opening (most of them) or provide a constant flow (self adjustment of head losses) or for a few recent
products sense IAQ (usually through humidity content) and open gradually in case of occupation of
the room. They all need a certain depression, which is provided by the ventilation package. The more
sophisticated products require a higher depression to operate.
The ducts are made of plastic or metal. Taking into account the pressure drop in the extracts and in the
ducts (of variable length) one could compute an ideal extraction fan. Practically there is only a few
sizes and the fan is always oversized, which is a good thing if we take into account what can happen to
ducts and exhausts (breakage, dust, etc.). The quality of design and installation is poor compared with
what one could expect. Installation should in principle include balancing and tuning operations in
terms of a few Pascals. Papers at AIVC 2005 congress tell more about the ducting problems.
The solutions for demand control in residences are different from the ones used in non residential
buildings, where workers can be followed by infrared detectors to determine the number of people in a
room, or where CO2 is a good indicator of activity (which is not the case in a kitchen for instance).
Only water content of the air is used.
The work of the designer and installer in interaction with the manufacturer
Five ventilation products at least are assembled to realise the ventilation function and they are
assembled at the last minute, on site: (following the flow) we find the trickle inlets for fresh air
entrance into the room, the extracts for partial air extraction (part of the air flowing outside directly),
ducts, the fan, ducts again, air rejection device. Pressure levels command the flow, and outside
pressure varies and is different on every wall, so that the flow varies. The pressure differences we are
speaking about are tens of Pascal, less than 1/1000 of atmospheric pressure. This explains the
problems found in balancing systems (obtaining the flow where we want it and as high as we want
it).
Many designers and installers have little time to devote to ventilation, an issue that we already
characterized as poorly valorised by the end user. Fortunately manufacturers sell often compatible
products as a package: the ventilation product (using electricity) and the other products (passive
products). The various components are designed to operate in a consistent way.
65
66
some others (Scandinavian, e.g.) are leaving the choice to each end user of a centralized
system to open or not an extract which can then have a low pressure drop, but this cannot
always guarantee air quality
others (France f.i.) introduced automatic control of extracts which costs something in
electricity because of the pressure drop generated
some countries (Germany seems the case) are insisting on the total air flow, not on the room
by room balancing, a factor of good air quality
the trend towards direct control of many rotation speeds of the fan (visible in German
products) may get importance or not.
We could go further:
- Overventilation to take advantage of night time cool
- Mechanical ventilation could also be partly controlled by the difference between the
temperature inside and outside that may save energy by avoiding very cool or hot air
(respectively in winter or summer time) to enter the building.
- Mechanical ventilation could be controlled by real occupation sensors, reducing flow rate
when the dwelling is unoccupied.
Load efficiency indicators : progress is needed
By specifying a standardized demand, some national systems can really compare electricity
consumption expressed in Watt directly.
Some other national habits try to characterize the product with less details about the demand. The flow
is an important functional parameter. The ratio of Watt spent to flow generated seems a logical choice
for efficiency. However it depends on the pressure drop to be generated: a conventional value may be
admitted for selection that will be variable on site. The SFP (Specific Fan Power) defined in non
residential EN standard as a performance indicator is not the perfect indicator. It is a ratio between the
electrical consumption and the flow, expressed in W per m3/h. Lets give examples.
SFP is not a perfect indicator of fan efficiency first because the consumption not only depends on the
flow but also on the pressure difference we have to create. However it is a good indicator of the total
ventilation system efficiency, if all the elements are provided by the same manufacturer and that there
is no design or variation possible on the field. To prove it is not an indicator of fan efficiency, lets
consider an innovative system that could request less pressure difference and not be based on an
efficient fan: SFP would say its efficient.
Also there is a limitation on SFP as an indicator because the ventilation system can realise numerous
regimes according to the demand downstream. SFP will then be computed for a design point at very
high flow and the adaptation of the system to the most common- lower flows will not be represented.
We can also understand the problem of defining an SFP for double flow: the SFP is the total electricity
used in the ventilation system divided by the largest of the flows (fresh air or exhaust) or it can be
defined as the electricity used divided by the sum of both flows. SFP is used as a target for a specific
component, like an Air Handling Unit. So we will use it here for the fan of a mechanical ventilation,
but we know the limitations.
The possibilities of audit given to the end user in an existing building
Natural ventilation in buildings per se may be an energy conservation strategy, based on the proper
interaction between building envelope characteristics (air permeability, presence of operable windows,
etc.) and internal layout of the building (presence of convective paths). It needs very professional
design. But natural ventilated buildings with poor air tightness when converted to artificial air
conditioning or artificial ventilation can become huge energy consumers.
67
End-of-Life behaviour
Local Infrastructure
About hoods with a fan integrated, there are problems of connection to the outside about which there
are national regulations. At least in France, the danger associated with connecting them to gas fumes
68
69
Task 3 summary
Consumer behaviour is often characterised by lack of awareness about the ventilation equipment
which is usually continuously in use. This lack of functional feedback can be seen as a barrier to ecodesign measures, or even to the simplest maintenance and design operations.
Ventilation consumption varies accordingly to the pattern of the demanded flow rate. Control
scenarios have been identified and will be named in the following manner:
- continuous use, CONTINUOUS
- control by an on/off switch, ON/OFF
- same with two, three and four flows and corresponding speeds offered to the user, MULTI
SPEEDS
- continuous speed control (mostly obtaining constant pressure drop over fan), named
VARIABLE SPEED .
The degrees of freedom about the speed described here are user related. Every ventilation system has
various operating points according to control or to atmospheric condition. Electricity consumption of
double flow systems will also be sensitive to the pressure balance and its correct maintenance in time.
Because of varied pressure regimes, a SFP with a single point (flow, DP) may not allow correct
comparison of ventilation products.
The degrees of freedom of the fitter are:
- the choice of the product;
- the installation of switches or speed selectors for the user ;
- the choice and installation of products at several speeds, the flows being chosen by the
installer;
- the choice of a product taking account of the presence (in residential sector: H2O content).
Filter maintenance is an important issue, highly cost effective to maintain real life performances of
ventilation products.
Specific care must be taken with hoods connections on the aeraulic circuit. Noise limitation indoors is
a specific constraint to be taken into account for the product design. In specific noisy zones, the
transmission of noise from outdoor can also be a constraint for the product design.
70
Production phase
Before starting this section, we want to thank the manufacturers who have largely contributed to our
data basis.
Data available
We have five ICV. ICV#1 that has been extracted from the lot 11 study. We have estimated the
electrical power to 86 W. Four other BOMs of ICV have been made on purpose by manufacturers. We
have chosen to interpret the BOM provided by manufacturers as a function of electrical power used by
the product allowing us in part 5 to generate a BOM for an average product in each category without
consideration of the maximum flow through the product (not always available for 0 Pa, arbitrary for
any other reference pressure).
Table 4-1: Bills of material of various fans for residential ventilation
DV1
DV2
Type
AC
AC
Pelec
23
Aluminium
Steel
280
Electronics
ICV1
ICV2
ICV3
ICV4
EC
forward
EC
backward
135
66
1613
Centrifugal
AC
(Lot 11) forward
86
ICV5
DV3&HR
78
62
26
1486
108
35
2199
452
1048
1115
505
467
999
17
72
86
87
81
127
Iron
Bulk Plastics
56
457
505
Tech.Plastics
224
67
604
Copper
34
300
Brass
79
198
298
2450
3069
148
146
196
93
109
135
215
11
63
148
Others
1001
29
Total
600
997
3530
3040
2530
1220
3686
5859
Study of DV products
Lets now extract some lessons about each category. First Decentralised Ventilation products.
71
7000
6000
mass (g)
5000
Others
Brass
Copper
Tech.Plastics
Bulk Plastics
Iron
Electronics
Steel
Aluminium
4000
3000
2000
1000
0
1
The two DV materials have a comparable weight if we take power into account but the content is
different : more plastics in product DV2, which is better clothed because it is made to be visible.
The product with heat recovery is very visible (more plastics) and receives the addition of a heat
exchanger made of steel.
For DV hoods manufacturers have not yet proposed BoMs. Due to the nature of the service expected,
the kitchen hoods seem to include a high proportion of plain steel, while the DV fans can be made
significanty (except motor) of plain plastics, as the existing BoMs show.
Study of CV products
Coming to ICV, we have ranked them in the graph in function of their electrical power (ICV5, then 3,
4, 1, 2).
72
4000
3500
3000
Others
Brass
Copper
Tech.Plastics
Bulk Plastics
Iron
Electronics
Steel
Aluminium
2500
2000
1500
1000
500
The product ICV4 (third on the graph) is a real environmental challenger and has been designed as
such by its manufacturer (efficient motor, efficient fan, little materials). We will withdraw it from the
definition of the baseline.
For CCV, the metals seem more important than for ICV, namely steel, because of fire regulations, and
maybe also because of exposition to outside.
Extrapolation methods
We have used our data base of products to correlate the total mass with the flow (this time the absolute
maximum flow not the BEP) or the electrical power. The linear shape obtained would allow to
compute simply from the area ventilated in task 2 a total air flow or a total electrical power and so a
total mass of products either sold one year or in service one year. Here is the graph for Pelec:
73
Figure 4-3: Relationship between electrical power and mass of the product, all products in scope
90
80
70
mass (kg)
60
50
40
30
20
10
0
0
100
200
300
400
500
600
700
Pelec (W)
We have approximately 116 grams per W and half for window and wall fans. After computing the
mass of the reference product we will compute its materials content by using the ratios extracted from
the previous work and shown on table 4.2.
Table 4-2: Bills of material of various fans as percentages of total mass
DV not hood
DV hood
DV&HR
ICV
ICV&HR
Aluminium
0%
0%
1%
24%
24%
Steel
46%
80%
38%
29%
40%
Electronics
1%
1%
0%
2%
2%
Iron
0%
0%
2%
0%
0%
Bulk Plastics
32%
10%
52%
25%
14%
Tech.Plastics
18%
9%
3%
6%
6%
Copper
2%
2%
4%
6%
6%
Brass
0%
0%
1%
0%
0%
Others
0%
0%
0%
8%
8%
Total
100%
100%
100%
100%
100%
4.2
Distribution phase
To our knowledge most products are manufactured in Europe, very often not in the origin country of
the brand. Manufacturers distribute directly the products to gross marketers (regional) DIY shops and
installers, so that there is no reason to change base assumptions of the Ecoreport for the distribution
phase. The mass is known thanks to correlation with nominal air flow rate in Figure 4.2.
74
Assessment of resources consumption during product life (mostly electricity) should be made in offstandard conditions, i.e. at variable load. In this case, variable load implies various operating points.
Only some cases can be computed in the constant load conditions of the standard. Encountered
situations are gathered in the table below; non existing situations have been marked with -.
Table 4-3: Computing energy consumption, characteristics of operation constant or variable load
Calculation
process at
DV
ICV
CCV
HCV
DV&HR
ICV&HR
CCV&HR
4.3.1
CONTINUOUS
ON/OFF
MUTI SPEEDS
constant load
constant load
constant load
constant load
constant load
constant load
constant load
constant load
-
variable load
variable load
variable load
variable load
-
VARIABLE
SPEED
variable load
variable load
The product under consideration has an infinite number of operating points represented graphically by
pairs (flow generated, pressure difference generated). Practically manufacturers provide diagrams with
the full characteristic lines (various lines when the frequency or voltage can be varied to generate
various rotation speeds) and the efficiency lines, which in theory are perpendicular to the characteristic
lines. When the efficiency is not provided one can easily compute from the characteristic line the
hydraulic power generated, P times the volumetric flow, called Phydr here, and then the ratio to
electrical power gives the efficiency (Phydr/Pelec). Hereunder is presented an example of
characteristic lines and equal efficiency lines.
Figure 4-4: Example of characteristic line of a ventilation product
4.3.2
The decentralised products DV have often a characteristic line of the following type (a):
Figure 4-5: Characteristic line of decentralised ventilation product of wall type
Figure 4-6: Characteristic line of decentralised ventilation product of range hood type
Such a range hood extractor reaches relatively high pressures (to be able to combat filter headlosses) at
either speed and unknown chimney.
76
Some of the ICV have two or three speeds between which the user has to make a selection by using a
switch; we call the corresponding lines type (c):
77
Figure 4-8: Characteristic line (Type c) of ICV product with two speeds
Some products are worked out so as to have a large zone of pressure differences in which the flow is
constant (the vertical part of the three lines hereunder), and display a characteristic line of type (d):
Figure 4-9: Characteristic line (Type d) of products with a large zone of pressure differences in which
the flow is constant
On the opposite, there are products with a very horizontal characteristic line, namely (but not only) for
CV, to guarantee an available pressure, type (e):
78
Figure 4-10: Characteristic line (Type e) of products that guarantee a constant pressure difference
Finally by varying the speed one can obtain a perfectly horizontal line. If the pressure sensor is located
at another point of the circuit not at suction point, we can obtain a constant pressure at that point when
the flow varies. The horizontal lines in the following graph are themselves characteristic lines obtained
by automatic control that we will call type (f) and which reduces noticeably the total electrical
consumption:
Figure 4-11: Characteristic line (Type f) of products with variable speed
A further variation of this line will be presented in the BAT analysis in task 6 and is called type (g).
Balanced flow units
In front of the problem of representing both air circuits in case of heat recovery manufacturers use two
options.
Some manufacturers and the standard11 represent two sets of classic characteristic lines, like the
following (here with various possible speed settings):
11
Figure 4-12: Characteristic line of products with heat recovery (here also with multi speed)
Some consider that the flow on both sides is exactly the same, hence only one line is needed (even if
the product is a double flow product with HR).
Figure 4-13: Characteristic line of products with heat recovery, with supposed equal characteristic for
inlet and outlet air flows
Some lump both circuits and give data under the following form.
All these presentations will not generate problems in the future calculations of SFP or efficiency.
80
Figure 4-14: Characteristic line of products with heat recovery, with supposed equal characteristic for
inlet and outlet air flows, complete performance map
81
How to select one representative point on the product characteristic line (definition of
one operating point representative of Full Load : FL)?
In this part we consider the constant load conditions. In the next part we shall consider the variable
conditions. Even at constant flow, the definition of an energy consumption indicator is not easy
because the result given by the testing standard is (with reason) a line, along which performance
varies, and also electricity consumption. We should select one point.
There are typical design conditions of the products, corresponding to various flows and pressure
difference demands in national building codes. So the natural tendency of practitioners is to create
many specific categories, namely in correspondence with the building code of the country where they
operate. For each category, we have one typical operating point for which SFP or efficiency or
electrical consumption can be defined. This is not really a characteristic of the product, so we will
discuss this approach.
We want to propose hereunder one way to escape this influence of national building codes. We think it
solves the problem but we investigate also the other approach, due to its large acceptance. So we find
two options: in option (A) we try to decide on design points as common as possible between countries,
in option (B) we admit the product was designed for a specific point and we judge it on that point.
Option (A): the usual approach of defining national pressure/flow duties on which the product
is judged
National building codes specify the duties of ICV like in the UK SAP-Q or French Th-C: length of
ducting, flow, how many hours in each mode, type of air inlets, etc. The products are optimized for
that set of specifications and an average electricity consumption is defined. However it still depends
on the size of the house or flat, and should be extended to other ranges of products (decentralized,
collective), by defining more and more specifications.
Lets take an example to explain what is defining the duty of one product: the extractor for one
French dwelling. Each extraction point demands 15 m3/h except the kitchen which demands two flow
values: 45 m3/h or 135 m3/h. The grille needs an under pressure 90 Pa<P<160 Pa. Lets say 100 Pa to
generate one single value. It operates 2 h over 24 h at high flow. What we have presented as an
example of duty represents the habits of one country and should be harmonised between the
countries if we want to apply this approach.
An existing study made an attempt to harmonise such definitions over EU countries, despite of the
contradictions between the various building codes (Vialle, 2006, and 2007). It uses the SFP as an
efficiency indicator. The study did not succeed completely because the systems in use were not the
same in the EU countries, resulting in different expectations about pressure and flows from the various
experts interviewed.
The traditional SFP seems not perfect to compare products because it does not correct for the impact
of pressure differences demanded in the standardized duty and so may be prejudicial to some products
with a higher pressure generation P. Even if we defined a set of duties, the end user would have
still to deal with a complexity of figures, 10 kWh/year/m3 for one duty not being like 10 kWh/year/m3
for another duty, e.g., because of the difference in pressures, not in efficiency of products.
We can imagine to edit SFP values for steps of 50 Pa and 100 m3/h width. Such a grid of pressures
and flows makes the result independent from building codes, but is paid by complexity of information.
Even when admitting the complexity the system does not provide the accuracy needed even for a
simple labelling system. Two products belonging to the same class of pressure provided, for instance
100 Pa, can be as different as one providing 75 Pa, and one providing 125 Pa. If we admit they have
the same efficiency, the second one will consume 66 % more than the first one, and its SFP will be 66
% higher. The inaccuracy seems to object to the use of the SFP system in a product labelling system.
82
DeltaP (Pa)
Pmax
Best efficiency point
P*
Characteristic line
Qmax
Q*
Q(50Pa)
Flow m3/h)
The maximum flow Qmax (null depression) and the flow with 50 Pa appearing to us arbitrary, we can:
call nominal flow Q *, the flow at the BEP (maximum of output) and to call reference pressure P *
and not Pmax. We have many possibilities that we have to test in practice
4.3.4
We can define four scenarios by crossing the options just defined in 4.3.1 and 4.3.3.
Option (A) -Scenario 1 SFP at 0, 100, 150, 200 Pa
For each point the laboratory reports Pelec, flow, SFP= Pelec/flow
There is a line of SFP (for instance SFP at 100 Pa) function of Pmax to which compare the specific
equipment.
Option (A) -Scenario 2 Efficiency at 0, 100, 150, 200 Pa
For each point the laboratory reports Pelec, flow, P, Phydr = flow x P, Efficiency= Phydr/Pelec
It can be used directly for performance comparison.
Option (B) -Scenario 3 SFP at BEP
For this point the laboratory reports Pelec, flow Q*, pressure P*, SFP= Pelec/flow
There is a line of SFP function of P* to which compare the specific equipment
Option (B) -Scenario 4 Efficiency at BEP
For this point the laboratory reports Pelec, flow Q*, pressure P*, Phydr = Q* x P*, Efficiency=
Phydr/Pelec
It can be used directly for performance comparison.
4.3.5
We applied this rationale to a number of very different products. Let us show the computational steps
for one single product: the typical extractor with a type (c) line. First we can see it has two speeds
(upper and lower line) and a manual switch to request high speed. So we tested the approach on each
speed. High speed demands 73.1 W input while lower speed demands 27.4 W input.
84
Option (A) is represented by horizontal lines corresponding to an arbitrary pressure demand. Since the
pressure demand is not at all harmonized between the national building codes this generates the
numerous SFP corresponding to those specified design conditions. Option (B) introduces no design
conditions and looks for the optimal operating point (called BEP, Best Efficiency point) at each speed
(*), assuming the products were designed by the manufacturer or will be selected by the installer for
those conditions. Table 4.2 shows the calculation based on figure 4.15.
Table 4-4: Computation of scenarios in options A (given conditions) and B (best efficiency point)
Flow rate
m3/h
DeltaP in
Pascal at
low speed
P elec. In
Watt
Efficiency
DeltaP in P elec. In
SFP at
at low
Pascal full
Watt
low speed
speed
speed
Efficiency
SFP at
at full
full speed
speed
50
250
27.3
12,40%
0,56
100
200
27.4
19,84%
0,28
360
12,16%
0,73
150
100
27.5
14,88%
0,19
340
19,38%
0,49
200
300
72.0
22,80%
0,37
250
270
72.1
25,65%
0,29
300
200
72.2
22,80%
0,24
350
150
72.3
19,95%
0,21
In applying systematically option (A) to the products in our data base we found some practical
problems that we have to report. SFP by itself does not show any optimal value and trying to improve
it leads to the point with less pressure demand, as we were expecting. Usually the low and high P are
not shown, like here. Some individual centralised products and all decentralised products dont reach
the 100 Pa threshold necessary to apply option (A) with this very usual value. Also a limited number
of collective centralised products are over the 100 Pa line and the suggested SFP cannot be computed
at full speed, like here. Obviously the hybrid ventilation products and the products with heat recovery
are not easily covered by scenarios derived from option (A).
Furthermore some products display lower pressure demands (because the corresponding extracts are
not sophisticated) and have very low SFP values without any effort in energy efficiency of the
motor/fan unit.
85
What do the various scenarios say about the product used as example?
Expression of results in Option (A)-Scenario 1 SFP at 0, 100,150, 200 Pa
In a country with a pressure demand of 200 Pa (at full speed), the product has an SFP of 0.24. In a
country with a pressure demand of 150 Pa, the product will deliver 350 m3/h at full speed and 125
m3/h at low speed. The associated SFP will be 0.21 and 0.24. In a country with a pressure demand of
100 Pa (at low speed), the product will deliver 150 m3/h and the SFP will be 0.19. Having in mind the
Pmax, this SFP is better/worse than average
Expression of results in Option (A)-Scenario 2 Efficiency at 0, 100,150, 200 Pa
In a country with a pressure demand of 200 Pa the product will have an efficiency of 22.8% and
operate always at full speed. In a country with a pressure demand of 150 Pa, the product will have an
efficiency of 20% at full speed and 17% at low speed. In a country with a pressure demand of 100 Pa
(at low speed), the product will have an efficiency of 15%. This efficiency is better/worse than
average.
Expression of results in Option (B)-Scenario 3 SFP at BEP
In order to characterize the product itself and not its conditions of use, we keep the point being the
most efficient on each line. At full speed SFP at best efficiency point is 0.29, at low speed it becomes
0.28. We may assume the manufacturer has designed the product having in mind some building codes,
but we dont specify them. After correcting for the P, this SFP is better/worse than average.
Expression of results in Option (B)-Scenario 4 Efficiency at BEP
In order to characterize the product itself and not its conditions of use, we keep the point being the
most efficient on each line. At the lower speed best efficiency is 25.6 %, at upper speed it becomes
19.84 %. We can assume the manufacturer has designed the product having in mind some building
codes, but we dont specify them. This efficiency is better/worse than average
In the rest of the study we will develop more option (B)-scenarios 3 and 4- which seems to us
consistent with the product philosophy of ecodesign studies than option (A) scenarios 1 and 2- which
is more acceptable by professionals with present habits.
4.3.6
Extension of the full load scenarios to range hoods and products with heat recovery
We included in our rationale those two products. Lets explain how this is feasible.
We dont remind here the fact that Heat Recovery products have twice the duty of single flow
extractors and that should be corrected for (for instance by multiplying the flow by a factor 2 before
entering any of the proposed calculation routes).
In both cases (range hoods as part of DV and HR applied to DV and ICV) we have additional head
losses, the filters or the heat exchangers. By using the characteristic line of the total product we are
including the internal pressure losses, which is unfair if we compare SFP or efficiency with any other
product without the same headlosses. The first idea is to generate a specific rating scale for each of
those families but the level of heat recovery and the level of filtering are variable from one product to
another, and directly associated with the level of head losses. One could suggest to make a
measurement of pressure between the fan section and the section with head losses; this has to be tested
but feasibility is not guaranteed (swirl and unstable flows are likely). Our final suggestion is to
substitute at the time of testing the HR section by a pipe with negligible pressure drop on both circuit,
in the case of HR products, and withdrawing the filtering elements, in the case of hoods, and to work
on those modified characteristic lines. They are likely to become comparable with other products after
that operation, and will not necessitate a specific scale. However there is a need of a few years of trials
to be certain of that way of processing. For hoods it seems that the grease filtering element does not
introduce such a perturbation that it has to be withdrawn.
86
Here we identify and possibly quantify those product features that can modify the environmental
impact not only of the product but of the system as a whole. So we consider variable conditions of
flow and pressure demand. In the building codes, there are usually various regimes of functioning. So
the efficiency or SFP for these various duties can be averaged (with the proper weighting) to generate
one single figure. The need for harmonisation is becoming even larger.
4.4.1
The study we mentioned previously (Vialle, 2006, and 2007) made an attempt to harmonise such
averaging definitions over EU countries, despite of the existence of various building codes. We
reproduce hereunder their very interesting approach: We got inspiration for our final proposal from
this work of the French industry and the CETIAT technical center.
For ventilation systems used in single dwellings, the representative running points chosen correspond
to the minimum and maximum speed of the fan for the maximum size of dwelling that the system is
designed for.
Our comment: this is perfect if we are in the field of building codes (which by the way will give
contradictory indications) but we are trying in the present study to characterise the product itself, with
only one characterisation for all EU. We can drop the second half of the sentence.
For the ventilation systems used in multi-family buildings, two representative running points are
chosen, one for the maximum air flow rate and one for the minimum air flow rate. For a system
without any electronic control device, these points are taken on the maximum speed characteristic
curve of the fan. The point corresponding to the maximum air flow rate, Qv max is determined according
a reference total pressure Pvmc_rfQv max that is necessary to achieve in order that the ventilation system
runs properly. This includes the pressure drop of the ductwork and the pressure to maintain for the
operating of the extract terminal device. For ventilation systems using pressure controlled air extract
devices, Pvmc_rfQv max varies according the air flow rate range of the fan unit. (see ranges in table 4.3).
For ventilation systems with humidity controlled extract air terminal devices, Pvmc_rfQv max is 160 Pa.
The point of minimum air flow rate Qv min is corresponding to a proportion of the maximum air flow
rate. This proportion is chosen as 50 % in the case of a ventilation system using pressure controlled
extract air terminal devices and 40 % for a ventilation system with humidity controlled air terminal
devices.
Figure 4.17 illustrates the positioning of the running points corresponding to the maximum and
minimum air flow rates. Our comment: this corresponds well to the centralised products used in some
countries and refers to some specific building and equipment. The general idea is very interesting.
87
Table 4-5: Reference total pressures for pressure controlled extract devices (Vialle & al., 2007)
0 - 1000
100
200
> 8000
250
Figure 4-17: Running points chosen for a fan unit without control system (Vialle & al., 2007)
Curve of the fan for
maximum speed
Pt
Pvmc_rfQv max
Qv min
Qv max
Qv
For a fan unit equipped with a constant pressure control device, the running point for the maximum
air flow rate is determined in the same way as described here above, but the electrical power taken
into account is the one of the running point with the same reference total pressure and an air flow rate
equal to 75 % of Qv max the maximum air flow rate defined for ventilation systems without any control
device. For this kind of fan unit, the running point for the minimum air flow rate is located at (Qv min,
Pvmc_rfQv max) where Qv min represents 50 % of Qv max for a system with pressure controlled terminal
devices and 40 % for a system with humidity controlled terminal devices.
Figure 4.18 illustrates the positioning of the running points for the constant pressure fan unit.
Figure 4-18: Running points chosen for a fan unit with constant pressure control system (Vialle & al.,
2007)
Pt
Reference points for a
ventilation unit without
variable speed system
Pvmc_rfQv max
Qv min
0,75*Qv max
Qv max
Qv
For a fan unit equipped with a constant air flow rate control device, the maximum air flow rate taken
into account is always Qv max defined above, but the electrical power retained is the one corresponding
88
Pt
Pvmc_rfQv max
Reference
points
for a ventilation
unit
with
a
constant air flow
rate system
P'vmc_rfQv max
P"vmc_rfQv min
O
Qv min
0,75*Qv max
Qv max
Qv
The duration of running at the minimum and maximum speed are defined according the French
Building Thermal Regulation. This repartition corresponds to 23/24th of time at the minimum speed
(minimum air flow rate) and 1/24th of time at the maximum speed (maximum air flow rate) if the
ventilation system includes a device limiting time running at the maximum speed, or 11/12 th of time at
minimum speed and 1/12 th of time at maximum speed without such a device.
The study concludes however that the definitions made are not harmonised within the EU:
The analysis of the results of the enquiry about the use of mechanical ventilation systems in Europe
(type of systems, number of speeds and time of running duration for each speed) has shown differences
over the different countries. In consequence, the method developed in this study, suitable for the
French ventilation systems, is not directly applicable in Europe. The establishment of standard
running parameters for Europe is necessary. Especially the reference total pressure for the
determination of the running point of multi-family buildings or non residential ventilation fan units
needs to be dealt with.
We made an attempt to generalize this approach hereunder in part 4.4.3 in a way avoiding to give
common values for pressure demand in MS.
The study by (Vialle & al., 2007) extended the rationale when there is a speed change in the product,
not if the operating point moves along the characteristic line.
4.4.2
Feasibility of one single PL (Part Load) index to represent part load gains
Before extending the approach just described we have to define all situations of part load. We have to
make the reader aware of the difference between the settings that the manufacturer recommends to the
installer to adjust on site once and the manual and automatic controls that will be acting all along the
life of the product without further action of the installer. For the settings of the first type the default
89
90
Caution: Not to confuse manual or automatic adjustment made on site by the user or the
controller and adjustments that fitter makes once for all.
Ideally the pressure would follow the pressure demand which varies like the square of the flow. A real
controller should keep a margin and may look like this:
An ideal pressure demand controller would request sensing pressure on every extract; we think its not
available on the market. To define experimentally the efficiency of such a system one should define a
reference network for testing. We do not want to enter into the definition of the ventilation network
because we want to characterize the product itself. So when the product includes a pressure sensor to
be located at some place, we will leave the pressure sensor at the suction of the fan.
Part load testing required
91
Our EEIPL should have the following features: to give back the selected EEIFL when there is no load
adaptation; to ease yearly calculation of electrical consumption; to give a reward to the innovative
strategies and to treat with equity all MS solutions. Frequency of flow rates under the full load value in
an EU residential ventilation system are estimated as follows:
Table 4-6: Possible of part load flow rates and frequency
Part load value in
% of maximum
flow xi
100%
75%
50%
25%
Frequency of this
situation Fi
10,00%
20,00%
30,00%
40,00%
Certification of the published points by an independent European institution like EuroventCertification or IMQ or one of the national bodies mentioned in part 1 would be a good thing.
An immediate expression is the one of the yearly weighted electrical power, lower in general than
nominal power :
Pelec average= FiPi
92
93
In order to give one example we consider the two speeds ICV for which the manufacturers directory
gives the following graph. Its the product already considered in 4.3.5 with its two speeds (upper and
lower line) and a manual switch to request high speed. There is no automatic setback from high speed,
so high speed is high speed, not a booster. High speed demands 73.1 W input while lower speed
demands 27.4 W input.
Figure 4-20: Typical ICV characteristic line and progression of testing to obtain EEI PL
DeltaP (Pa)
And Pelec (W)
P prop.to Q2
BEP
Pelec
0
0
62 125
25% 50%
187
75%
250
100%
Flow m3/h
Table 4.4 shows the calculation based on figure 4.15. Since speed variation is not continuous and
there is no automatic timer bringing speed down from the highest speed, we have to determine first the
BEP of high speed. Here its for Q*=250 m3/h, also called Q4. The reduced flow Q3 can only be
attained with the high speed with a pressure corresponding to the BEP through the square law, while
Q2 can be attained with the low speed at a reasonable pressure, and Q4 as well.
Table 4-7: Progression of testing at part load
Flow rate
m3/h
P in
Pascal at
high speed
Minimum
DeltaP in
Pascal
DeltaP in
Pascal at
low speed
250
270
Pi (input)
including
sensors &
standby
73,10
0,2
187,5
300
151,875
73.00
0,5
0,3
125
67,5
100
27,5
0,25
0,4
62,5
16,875
230
27,4
Steps
xi (flow
reduction
factor)
Step 1 BEP
high speed
(Q*, P*)
Fi
(frequency
of
occurrence)
0,1
Step 2 :
75% flow
0,75
Step 3 :
50% flow
Step 4 :
25% flow
In order to perform the energy calculation, we have extracted from our data basis the necessary
quantities.
Table 4-8: Computation of options A scenario 1 (SFP at given conditions) and B scenario 4
(Efficiency at BEP) for some products in our data base
Product
type
Range of
max
DeltaP
(Pa)
Range of
max flow
(m3/h)
Nominal
power
demand
(W)
Averaged
SFP at
100 Pa
Averaged
EEI FL
Averaged
EEI PL
Average
Pelec (W)
over
speeds
DV/roof
50 to 400
1000 to
10000
90 W (90
to 1400)
n.a.
(for the
90W)13
16 (for the
90W)
8 (for the
90W)
90
n.a.14
3 for axial
(12 for
cent.)
2 for axial
(up to 20
for cent.)
17 for
axial
DV/window
or wall or
attic
up to 120
70 to 600
13 to 125
(17 for
axial; 58
for cent.)
DV/hoods
300
250
100 to 200
(150)
0.4015
>6
90
ICV
100 to
160
250 to 430
28 to 83
(75)
0.13 to
0.23
19
12
40
CCV
120 to
160
400 to
6000
95 to 600
0.20 to
0.26
16
n.a.
n.a.
HCV
17
400
16
n.a.
12
n.a.
ICV&HR
350
300
136 (2
flows)
0.23
15
na
n.a.
One should immediately remark that in the categories with sufficient information, and whatever the
indicator is, there is a factor 3-5 in performance between the best and the worst performer.
As already discussed its sometimes impossible to compute the SFP at 100 Pa for some products.
About the distributed ventilation products, we didnt see any significant difference between wall and
window fan. About the roof fans we discovered in the data basis that they are not at all suitable for
residential use, when we see the magnitude of flow rates, which would lead to 2 or 3 ACH in a
dwelling. Most of them will not be in the scope of the residential study, except specific collective
applications. We have not found any product integrating heat recovery and double flow ventilation for
collective buildings. The parts should be purchased separately and/or designed specifically for the
project.
13
SFP at 0 Pa being 0.09 so all are compliant with the US Energy Star rating of 0.21
SFP at 0 Pa being 0.10 so all are compliant with the US Energy Star rating of 0.21
15
SFP at 0 Pa being 0.24 so not all compliant with the US Energy Star rating of 0.21
14
95
End-of-life phase
From the declarations of the stakeholders we concluded that all products end up in general disposal
presently.
96
Task 4 summary
The use of the Ventilation product determines its features which fall into one of the categories:
- DV Decentralised
- ICV Individual Centralised
- CCV Collective Centralised
- HCV Hybrid Collective Ventilation
- DV&HR as DV but with heat recovery (doubles at least electrical consumption)
- ICV&HR as ICV but with heat recovery (doubles at least electrical consumption)
- CCV&HR as CCV but with heat recovery (doubles at least electrical consumption)
Each product has an infinity of possible operating points along a line called characteristic line in the
plan (pressure, flow). The characteristic lines have been modified by generations of engineers and may
have various aspects named here from (a) to (f).
This variety of operating conditions possible with each product can be reduced either to one point in
specified conditions (for instance 100 Pa), or to the optimal point assuming that this optimal point has
been carefully chosen by the manufacturers. The second solution seems more favourable, because it
does not collide with the national building codes but has to be accepted. For either one of the points
there is a choice to indicate efficiency itself or SFP at that point.
The authors propose an extension of the SFP or of the efficiency to take into account improvements
taking place at part load. Both SFPw and EEI PL are indices ready for use but not commonly used yet.
Technical and energy characteristics of main products found in directories are given, including Bills of
Materials. It is to be noted that roof fans found on the EU market do not correspond to residential air
flow rates. Collective ventilation products are not fully studied but are investigated in lot 11. HCV can
be fully integrated among ICV in the following.
Independently from the size effects, whatever the indicator is, there is a factor 3-5 in performance
between the best and the worst performer.
97
Product-specific inputs
Avg. EU product weight and Bill-of-Materials, distinguishing materials fractions (weight) at the level
of the EuP EcoReport Unit Indicators as proposed in the MEEUP report. This includes packaging
materials;
- Primary scrap production during sheet metal manufacturing (avg. EU);
- Volume and weight of the packaged product avg. EU;
- Annual resources consumption (energy, water, detergent) and direct emissions during product life
according
- to the test standards defined in subtask 1.2 [EU Standard Base-Case];
- Annual resources consumption (energy, water, detergent) and direct emissions during product life
according to the real-life situation as defined in subtask 3.2 [EU Real-life Base-Case];
- Selected EU scenario at end-of-life of materials flow for:
- Disposal (landfill, pyrolytic incineration );
- Thermal Recycling (non-hazardous incineration optimised for energy recovery);
- Re-use or Closed-loop Recycling.
In order to define the base case we used our data base of models being presently sold in EU 27. Table
5.1 gives the energy aspect and the weight. By applying the ratios of previous part, one can compute
the rest of environmental impacts.
Computation of electricity consumption of the product in the system
In the case of individual dwellings (and collective dwellings when ventilated in a decentralised
manner), where we know the number of DV and ICV in use or being purchased (and the size of each
product) we recommend to base the computation on this knowledge:
Yearly consumption of one product used in one dwelling = average power demand (including the
effect of existence of multi speeds and other controls when relevant)* 8760 hours (or less if
ON/OFF16)
In the case of collective dwellings, we have estimated the number of CCV in use or being purchased
(and the size of each product) but the product is adjusted by a fitter to the size of the buildingso we
recommend to base the computation on the knowledge of ventilated area:
Yearly consumption of one product used for various dwellings = volume ventilated* ACH* DeltaP /
EEI* 8760 hours
Where
- Volume ventilated = area ventilated (the one of task 2)* 2,50 m3/m2
- ACH: number of air change rates, typically 1, may vary according to countries in further work
- DeltaP: here 100 Pa= typical depression generated, may be substituted by pressure difference at
optimal efficiency point.
- EEI: average efficiency of the motor/fan (the product).
Energy use by products in use in 2005
16
Yearly Energy
Consumption
(kWh/unit)
Mass (grams)
Product type
DV/window continuous
17
148,92
986
DV/wall continuous
17
148,92
986
DV/window intermittent
17
12,41
986
DV/wall intermittent
17
12,41
986
DV/hood intermittent
90
65,70
10440
40
350,40
4640
DV&HR continuous
30
262,80
3480
66
578,16
7656
For CCV, the calculation is by square meter not by unit. Provisional value is 2.5 (volume ventilated
per sq.m)* 1 ACH17* 150 (DeltaP18) / 0.16 (average EEI)* 8760 hours, i.e.
Table 5-2: Average energy consumption by product (CCV)
Average power
demand (W/sq.m)
over speeds
Yearly Energy
Consumption
(kWh/sq.m)
Product type
CCV
0,65
5,70
76
CCV&HR
1,30
11,41
151
17
18
CCV
CCV&HR
90,0
40,0
66,0
264,8
529,6
12,4
262,8
66,0
350,4
578,2
2322,3
4648,7
3,5
20,9
9,3
23,0
77,4
123,0
DV/hood intermittent
30,0
DV&HR continuous
DV/window&wall intermittent
17,0
DV/window&wall continuous
17,0
Characteristics
General characteristics
Power demand (W)
2,0
2,0
Mass (g)
986,0
986,0
Composition
Aluminium
0%
0%
1%
0%
24%
24%
33%
36%
Steel
46%
46%
38%
80%
29%
40%
53%
49%
Electronics
1%
1%
0%
1%
2%
2%
2%
2%
Iron
0%
0%
2%
0%
0%
0%
5%
5%
Bulk Plastics
32%
32%
52%
10%
25%
14%
0%
0%
Tech.Plastics
18%
18%
3%
9%
6%
6%
0%
0%
Copper
2%
2%
4%
2%
6%
6%
6%
7%
Brass
0%
0%
1%
0%
0%
0%
0%
0%
Others
0%
0%
0%
0%
8%
8%
1%
1%
Total
100%
100%
100%
100%
100%
100%
100%
100%
100
Using the VHK EuP EcoReport indicate the environmental impact analysis, specifying:
Emission/resources categories as mentioned in the MEEUP Report for:
- Raw Materials Use and Manufacturing;
- Distribution;
- Use;
- and End-of-Life Phase.
and distinguishing for the Use phase between the Standard Base-Case and the Real-life Base-Case.
Furthermore, if more than one type of resource is used in the Use phase, make a split-up between
resources and their individual impacts.
Primary scrap production during sheet metal manufacturing (avg. EU) is kept at the default value of 25
%. Concerning reuse and recycling default values are kept.
101
Table 5-4: Summary of the environmental impacts of base cases, total environmental impact and energy use
DV cont DV interm DV&HR
DV hood
ICV
ICV&HR
CCV
CCV&HR
TOT
USE
Materials
Disposal
kg
0,45
0,45
1,78
2,32
1,54
1,83
2,14
4,24
Recycl.
kg
0,54
0,54
1,68
8,33
3,10
5,83
28,83
57,28
Total
kg
1,00
1,00
3,46
10,65
4,64
7,66
30,96
61,52
MJ
7,5
6,9
50,0
36,8
92,8
662,2
488,2
MJ
7,1
6,9
36,9
36,8
60,9
489,1
488,1
Water (process)
ltr
1,1
0,1
0,5
0,5
2,5
2,5
4,0
4,0
32,6
32,5
Water (cooling)
ltr
8,1
61,9
883,4
568,2
0,8
0,4
0,5
0,0
2,6
0,8
2,0
0,2
2,3
0,8
3,1
1,4
6,6
5,6
12,9
11,2
t CO2 eq.
0,7
0,7
0,1
0,1
1,6
1,6
0,3
0,3
2,4
1,6
4,5
2,6
17,0
10,6
31,6
21,3
mg R-11 eq.
neg. neg.
neg.
neg.
neg.
neg.
neg.
neg.
neg.
Acidification, emissions
t SO2 eq.
4,1
4,0
0,4
0,3
9,6
9,5
2,0
1,8
12,0
9,5
21,7
15,6
83,5
62,8
159,4
125,7
kg
0,0
0,0
0,0
0,0
0,0
0,0
0,0
0,0
0,2
0,0
0,5
0,0
1,7
0,1
2,8
0,2
mg i-Teq
0,1
0,1
0,0
0,0
0,3
0,2
0,2
0,0
0,3
0,2
0,6
0,4
2,5
1,6
4,8
3,2
Heavy Metals
g Ni eq.
0,3
0,3
0,1
0,0
0,7
0,6
0,2
0,1
1,0
0,6
1,9
1,0
7,2
4,2
13,3
8,4
PAHs
g Ni eq.
0,0
0,0
0,0
0,0
0,1
0,1
0,0
0,0
0,6
0,1
1,3
0,1
4,9
0,5
8,6
1,0
kg
0,1
0,1
0,1
0,0
0,4
0,2
0,3
0,0
32,2
0,2
79,2
0,3
266,4
1,3
424,1
2,7
Heavy Metals
g Hg/20
0,1
0,1
0,0
0,0
0,3
0,2
0,1
0,0
0,3
0,2
0,5
0,4
2,1
1,6
4,2
3,2
Eutrophication
g PO4
11
21
15
ng i-Teq
neg.
neg.
neg.
neg.
neg.
neg.
neg.
1,0
0,1
2,5
2,5
16,3
16,3
Emissions (Air)
Emissions (Water)
neg. neg.
102
CCV CCV&HR
264,8
2322,3
529,6
4648,7
800
500
520
2 500
500
1 200
800,0
500,0
3295,9
467,1
5063,0
65%
2500,0
500,0
6597,7
1077,9
10675,6
62%
0,7
538,4
336,5
2218,2
314,4
3407,4
65%
0,0
10,0
2,0
26,4
4,3
42,7
62%
6,16
538,4
336,5
2260,6
320,4
3455,9
0,025
10,0
2,0
18,4
3,0
33,4
The electricity consumption represents from 13 % of the life cycle cost for the end-user for hoods, up
to 88 % for Window and wall fans used continuously. The total income of the ventilation
manufacturing industries would be in the range of 3 billion Euros. With an almost equal comfort level
but a likely higher thermal consumption the use of two or three DV in one dwelling would cost as
much as an ICV.
103
The total weight of products installed in 2005 is about 75 kt. Materials and their end of life fate is
shown in the figure below.
End of life fate of material of products installed in 2005
50,0
45,0
40,0
35,0
kt
30,0
Recyc
25,0
Disp
20,0
15,0
10,0
5,0
0,0
Misc.
Electronics
Coating
Non-ferro
Ferro
TecPlastics
Bulk Plastics
Figure 5-1: End of life fate of material of residential ventilation products installed in 2005
Concerning other resources and waste, the energy consumption is the major contributor. 73% of Total
Energy use, 100% of electricity use, 98% of Water (process) rejection, 100% of Water (cooling)
rejection, 60% of Waste, non-hazardous going to a landfill and 34% of Waste, hazardous to be
incinerated are generated in the use phase, in relation with energy consumption.
Material
3,7
0,5
0,4
0,4
145,7
0,3
Manuf. Distribution
0,9
91,8
0,5
0,2
0,0
0,0
0,2
0,0
3,8
44,5
0,0
0,9
Use
258,8
258,7
17,3
690,0
301,5
6,0
EoL
0,8
0,0
0,0
0,0
4,5
10,7
TOTAL
356,1
260,0
17,6
690,6
500,0
17,9
Table 5-6: Environmental impact of residential ventilation products installed in 2005, energy, water and
waste
Over their lifetime, all residential ventilation products sold in 2005 will consume 25.5 TWh between
2005 and 2015.
104
Manuf.
Distribution
Use
EoL
Waste, non-haz./ landfill,
kt
Waste, hazardous/
incinerated, kt
0%
10%
20%
30%
40%
50%
60%
70%
80%
90% 100%
Figure 5-2: Environmental impact of residential ventilation products installed in 2005, energy, water
and waste
Use
11,3
66,6
0,1
1,7
4,4
0,5
1,4
EoL
0,1
0,1
0,0
0,0
0,3
0,0
1,3
TOTAL
17,1
85,7
1,5
2,9
7,6
4,4
232,9
Table 5-7: Environmental impact of residential ventilation products installed in 2005, emissions to air
105
Material
Manuf.
Distribution
Use
EoL
20%
40%
60%
80%
100%
Figure 5-3: Environmental impact of residential ventilation products installed in 2005, emissions to air
Material
0,7
0,0064
Manuf.
0,0
0,0004
Distribution
0,1
0,0012
Use
1,7
0,0080
EoL
0,1
0,0046
TOTAL
2,5
0,0206
Table 5-8: Environmental impact of residential ventilation products installed in 2005, emissions to
water
Eutrophication, kt PO4
Material
Manuf.
Distribution
Use
EoL
Heavy Metals, ton
Hg/20
0%
20%
40%
60%
80%
100%
Figure 5-4: Environmental impact of residential ventilation products installed in 2005, emissions to
water
106
The total weight of all products in use in 2005 is about 80 kt. Materials and their end of life fate is
shown in the figure below.
kt
Recyc
Disp
Misc.
Electronics
Coating
Non-ferro
Ferro
TecPlastics
Bulk
Plastics
Figure 5-5: End of life fate of material of all residential ventilation products in 2005
Material
3,7
0,5
0,4
0,4
145,7
0,3
Manuf. Distribution
0,9
91,8
0,5
0,2
0,0
0,0
0,2
0,0
3,8
44,5
0,0
0,9
Use
228,3
228,2
15,2
608,6
265,9
5,3
EoL
0,8
0,0
0,0
0,0
4,5
10,7
TOTAL
325,6
229,4
15,6
609,2
464,5
17,2
Table 5-9: Environmental impact of all residential ventilation products in 2005, energy, water and
waste
Over their lifetime, all residential ventilation products sold in 2005 will consume 21.1 TWh between
2005 and 2015.
107
Total Energy
(GER),PJ
of which, electricity (in
primary PJ)
Material
Manuf.
Distribution
Use
EoL
Waste, non-haz./
landfill, kt
Waste, hazardous/
incinerated, kt
0%
20%
40%
60%
80%
100%
Figure 5-6: Environmental impact of all residential ventilation products in 2005, energy, water and
waste
Use
10,0
58,8
0,1
1,5
3,9
0,5
1,3
EoL
0,1
0,1
0,0
0,0
0,3
0,0
1,3
TOTAL
15,7
77,8
1,5
2,7
7,0
4,3
232,8
Table 5-10: Environmental impact of all residential ventilation products in 2005, emissions to air
Greenhouse Gases in
GWP100 (Mt CO2 eq)
Acidification, emissions, kt
SO2 eq.
Volatile Organic
Compounds (VOC), kt
Material
Manuf.
Persistent Organic
Pollutants (POP), g i-Teq
Distribution
Use
EoL
10%
20%
30%
40%
50%
60%
70%
80%
90%
100%
Figure 5-7: Environmental impact of all residential ventilation products in 2005, emissions to air
108
Material
0,7
0,0
neg
Manuf. Distribution
0,0
0,1
0,0
0,0
neg
neg
Use
1,5
0,0
neg
EoL
0,1
0,0
neg
TOTAL
2,3
0,0
Neg
Table 5-11: Environmental impact of all residential ventilation products in 2005, emissions to water
Eutrophication, kt PO4
Material
Manuf.
Distribution
Use
EoL
Heavy Metals, ton Hg/20
0%
10%
20%
30%
40%
50%
60%
70%
80%
90%
100%
Figure 5-8: Environmental impact of all residential ventilation products in 2005, emissions to water
109
Total
EU-25
674
337
2379
29
2888
359
14315
127
21110
13,74
6,87
48,51
4,97
41,38
8,19
16,46
0,00
140,11
23,31
11,65
82,26
0,00
411,31
14,07
220,08
0,00
762,68
CY
1,03
0,52
3,65
0,00
0,23
0,00
37,59
0,00
43,03
CZ
9,72
4,86
34,31
0,00
1,95
0,00
424,97
0,00
475,81
DK
3,14
1,57
11,10
0,00
113,75
55,12
476,98
25,26
686,93
EST
1,29
0,65
4,57
0,00
0,12
0,00
53,34
0,00
59,97
FIN
3,84
1,92
13,54
0,00
71,39
72,76
476,06
50,88
690,39
32,14
16,07
113,43
0,00
903,74
48,49
2316,74
0,00
3430,62
158,36
79,18
558,91
23,54
470,79
38,84
80,96
0,00
1410,56
GR
16,52
8,26
58,31
0,00
3,99
0,00
295,20
0,00
382,28
8,57
4,28
30,24
0,00
2,35
0,00
228,65
0,00
274,09
IRL
14,68
7,34
51,81
0,00
5,29
0,00
6,20
0,00
85,32
IT
71,27
35,64
251,55
0,00
3,61
0,00
3430,63
0,00
3792,69
LT
2,09
1,04
7,36
0,00
0,14
0,00
82,33
0,00
92,96
LIT
3,07
1,53
10,83
0,00
0,41
0,00
115,97
0,00
131,82
LUX
0,88
0,44
3,11
0,00
15,75
0,60
14,74
0,00
35,51
MT
0,56
0,28
1,97
0,00
0,11
0,00
14,78
0,00
17,69
NL
22,53
11,26
79,52
0,00
602,58
41,86
503,04
0,00
1260,80
PL
31,28
15,64
110,39
0,00
8,43
0,00
1345,77
0,00
1511,50
18,57
9,29
65,56
0,00
8,13
0,00
167,74
0,00
269,29
SK
46,35
23,17
163,59
0,00
9,14
0,00
1370,24
0,00
1612,48
SLO
3,17
1,58
11,18
0,78
12,96
1,28
0,74
0,00
31,69
61,54
30,77
217,20
0,00
15,81
0,00
1454,05
0,00
1779,37
8,88
4,44
31,35
0,00
160,69
77,87
963,67
51,04
1297,94
UK
117,62
58,81
415,11
0,00
24,62
0,00
218,61
0,00
834,77
110
PJ
TWh
mln.m3
kton
kton
325,6
21,9
15,6
464,5
17,2
mt CO2eq.
kt SO2eq.
kt
g i-Teq.
ton Ni eq.
ton Ni eq.
kt
15,7
77,8
1,5
2,7
7,0
4,3
232,8
17,8
87,6
1,7
3,1
7,9
5,0
266,2
Emissions (Air)
19,9
22,2
97,9
108,8
1,9
2,2
3,4
3,7
8,9
9,9
5,6
6,3
301,4
338,4
24,5
120,3
2,4
4,1
10,9
7,0
377,5
1,4
0,007
2,6
0,022
Emissions (Water)
2,9
3,2
0,024
0,026
3,5
0,029
2005
2025
505,6
33,3
23,7
710,5
25,9
Total impact is of the same order of magnitude as for air conditioners for the stock of products in 2005
but the stock and environmental impact growth is slower than for air conditioning according to the
hypothesis made in both studies.
111
112
State-of-the-art in applied research for the product inside and outside Europe
The actions leading to improvement in ventilation systems are split between the ones that can be
implemented on the ventilation product itself, and some others that can be applied in the specification
or design of buildings which take place in the frame of national or regional building codes, and also
habits and traditions. If we had the degree of freedom of national building codes, we would need in
principle a technical analysis not only of available technology for products, but also a technical
analysis of potential gains at the level of the full ventilation system, by simulating completely air and
heat movement into the building, which is not the scope of this study. In our scope is certainly the
improvement of the fan and motor in the single flow system and their control. The case of double flow
when building codes consider that heat recovery is justified will be discussed later.
Just to mention what is outside of our scope: an improvement of the ventilation systems implies the
selection and control of a well chosen flow rate of air depending on sanitary considerations, the work
on the construction products to reach the proper control of inlets for air entrance (possibly self
controlling air flow), the selection of extracts adequate to each room (the type of control being
adequate to the source of pollutants inside the room), a control system to modulate and balance the
flow, correct fitting, anti-leakage treatment and insulation of the air ducts, provision for maintenance
of the full system.
Our scope is to consider the improvement of the product itself, for external conditions given and
accepted as they are. The analysis of the environmental balances shows that energy in use phase is by
far the largest environmental impact, the one we have to concentrate on (2/3 of energy is for use phase,
explaining most of global warming and acidification impacts, while the others are rather negligible).
There are no improvements that could be proposed by parts suppliers, since the EU manufacturers
have a full control of their technology. In a similar way, there is no reason to give a special importance
to the ventilation products manufactured abroad, as lot 11 already stated. The manufacturers inside the
European Union are well known for the quality and efficiency of their products. They are serving not
only the European but the international market. So we have not found better products outside the EU.
Instead cheap but low efficient products produced in some countries which are entering the European
market tend to lower the efficiency levels. Products from these low wages countries are typically not
designed using CFD to optimise blades, using low efficient AC motors and often simple straight sheet
metal blades. So these products can not help to increase efficiency of the products but instead are
lowering the average efficiencies as they are imported and used in Europe due to their highly
competitive price in first cost.
6.2
To keep prices down, manufacturers use inexpensive motors. We can have access to some values for
small motors and we can extrapolate some values of lot 11 to a smaller range.
The lowest cost motor is the one phase shaded pole motor (squirrel) which can be substituted by
collector or universal motors with an efficiency increase estimated by some as a transition from
20% to 40%. The real improvement on the market has been the introduction of motors with electronic
commutation that can be recognised because they can operate in DC, which are said to be able to reach
80 to 90 % according to stakeholders. EC-Motor Electronically commutated direct current motors are
113
We keep a value of 70% efficiency for such EC motors in our size. One stakeholder has given all the
data on one example of the same turbine equipped with two motors and put in the same duty
conditions (340 m3/h, 100 Pa): the asynchronous motor requests 98 W, when the electronic
commutation motor demands only 58 W, a 60 % saving, a change in efficiency from 9,64 % to 13,89
%. This fits well with our estimate of efficiency increase from 40% to 70%.
Lot 11 gives some indications that allow to check if there is an environmental impact in the transition
from classic motors to EC motors. However the values are for power levels 5 to 10 times larger than
our motors and the EFF1 or EFF2 motors are already better than our basic motors. However this gives
us confidence in the lack of adverse environmental effects of the improvement of motors.
Table 6-1: BOM of an improved motor according to lot 11
114
Our interpretation of lot 11 values in the following table shows a decrease of mass and some variations
of materials use that we could import into the Ecoreport.
Table 6-3: BOM comparison from lot 11
EFF1
EFF2
EC-Brushless
Steel
58%
54%
30%
Iron
15%
20%
16%
Aluminium
13%
13%
34%
Copper
11%
10%
12%
Plastics
2%
3%
6%
Electronics
0%
0%
2%
16,55
12,69
6,1
The change in motor cannot result in a large change in environmental impact in production phase or at
end of life.
Our values for efficiency improvement seem also compatible with the following graph of the annex
3.1 of lot 11 report.
Figure 6-2: Efficiency of motors according to lot 11
115
6.3
Another source of difference between products after the change of motor would be in the design of the
air movement inside the product. Here we give an image of potential improvements in the fan itself.
Like lot 11 we refer to AMCA for definitions (see annex).
The aerodynamic losses can be significantly reduced by aerofoil bladed design (curved and twisted
profiles instead of flat plastic or metal blades) and additional features such as winglet as the end of the
profile to reduce tip losses. Aerofoil blade designs are today designed using CFD software as we could
see when visiting the development laboratories; however production of such complex geometries is
much more expensive, and the products are often submitted to the requisites of low cost
manufacturing, namely constant width of fans.
In practice, axial flow fans are frequently of the tube-axial type (i.e., without guide vanes). The
rotational energy at the outlet is lost and real efficiency on blowing systems is often moderate.
Replacement by, or modification to, the vane-axial alternative should give a higher usable efficiency.
The axial fans of 100 to 150 mm diameter can hardly reach 20% mechanical efficiency with present
geometry, often less because of manufacturing constraints deriving from cost objectives.
The centrifugal impellers are forward curved. Transition to backward curved impellers is seen as
costly by the stakeholders in residential applications since the higher speed needed (for instance 2000
rpm instead of 1000 rpm for the same flow) necessitate a strong acoustic treatment, far more than what
is done for the medium range products. The smaller and cheap mass-produced centrifugal fans with
ladder strip impellers (forward) often can hardly achieve 60 % with an evenly distributed flow. It is
possible that backward curved impellers permit a higher performance like 70%, or at least the same.
When forward curved rotors are put in situation of lateral fixing where the motor opposes to air
distribution the flow is poorly distributed on the blades and some stakeholders have estimated the
efficiency to 40% or less.
116
The aerodynamic losses can be significantly reduced by interior design, balancing of flow, etc. Such
interior surfaces could be designed using CFD software; however production costs often prevent the
addition of the interior surfaces that would ease the flow. The state of the art seems very different in
the case of hoods (large spaces, balancing effect of the grease filter), in the case of extractors which
can in some cases still include a lot of elbows and in the case of axial flow, that are still sold without
guide vanes. We have a very rough estimate of the potential gain because it has to be designed on a
case by case basis, and has been indicated as being of the order of 10% in one case by one stakeholder.
.
6.5 Improvements in motor and fan control
Single speed
If no provision is made for vaying the flow (continuously or not), fan performance is controlled or
adjusted for once by means of a damper, either on the inlet or on the outlet, creating a variable
additional system resistance, and a considerable loss of performance. The same type of permanent
adaptation of the fan can be obtained by changing its feed voltage.
Multi speed
There are three modes of reduction of mechanical power that do not have the same efficiency 1suppression of voltage in some circuits 2- through electronics then 3-by a chopper. They are selected
by the manufacturer according to the range and image of the product.
Speed can be really varied in various ways : either by steps by feeding part of the electrical wiring of
the motor (which looses performance) or thanks to a variable speed motor (inverter, slipping coupling,
vane control, or a gearbox). We call these two solutions respectively multi speed and variable speed.
Variable speed
Variable speed control is now frequent with a variable speed motor. Vane control controlling the swirl
at the fan inlet or variable blade pitch control (normally only for axial-flow fans), adjustable pitch are
not used in such small products.
The first family of gains : direct user control of multispeeds
The small axial products do not have various speeds.
In centrifugal ICVs there is a manual selection of the speed, that can be remote. Very often the highest
speed is associated in some way (position, logo) with the use of the passive cooking hood.
The cooking hoods have many speeds and the highest is often called booster or intensive and left apart
in publication of standard testing results, a fact that we will discuss later to know if we can accept it.
The second family of gains : adaptation to of speed to balance a pressure which varies with
demand.
The fan is determined by the maximum flow demand and by the minimum pressure demanded at that
flow. These are the two extremes of the characteristic curve. When all ATDs are open there should be
enough pressure everywhere. To be energy efficient, the fan should have a flat characteristic curve
to adapt to variations of flow due to opening and closing of extractions: the flow could vary but the
pressure would not increase.
117
The fan by itself cannot have such a flat curve. The solution is to keep the pressure constant. It is used
for large systems presently, and we have called this type of characteristic curve type (f) in part 4, and it
could be adapted for smaller products.
The third family of gains : demand controled ventilation.
Ventilation should be adapted to real needs
- people (CO2, H2O, odours),
- cooking (CO2, H2O, odours)
- which vary a lot over time.
First lets consider real electronic sensing of pollutants. In non residential buildings there are high and
typical values of gains published (CFP, 2006): 40 to 70% if there is a real measure of presence (CO2
or movement detection), 20 to 40% if there is only a detection by Yes or No of presence. However this
is often not reflected at extractor level, so that about the same electricity is used. When the extractor
has the information and if it can adapt, significant gains in electricity are possible. There is a system
used for large rooms that could be used in smaller applications providing variable flow (depending on
sensed occupation) in an original way. Instead of varying continuously the flow (which is a source of
unbalance, poor distribution of the fresh air in the room and requires more costly equipment) they
operate at full speed but part of the time (for instance three minutes in a sensing time step of 10
minutes).Nothing of that is available in the field of residential ventilation. On total electronic sensing
of demand has to be considered as a BNAT, not a BAT
In dwellings we find some mechanical systems performing partly the same function but locally : the
usual variable deciding on the flow in such systems is water content measured by the relative humidity
on a psychometric mesh. The flow is adapted (without motor: its a purely mechanical system). The
water content flow control of the ATDs generates energy savings, improves comfort (relative humidity
remains in the zone of comfort in comfort standards and adapts to outside conditions (outside air
moisture and temperature). A simpler adaptation of the motor speed is made with the objective of
maintaining a pressure at some point constant while the extracts adapt locally but not perfectly to
conditions, and generate additional headlosses.
The key point of gains in BAT : adaptation of the motor speed for decreasing pressure demand.
118
This a NABT, that is not really on the market, even if discussed by manufacturers.
6.6
This type of option is not usually combined with the previous one. Either we try to lower the flow of
fresh air, or we try to heat it up, at a reasonable and constant flow.
Studying this double flow system is an option permitted by the new CEN standard derived from the
EPBD directive. The benefits are: obtaining of a certain air change room by room not depending on
what happens in the other rooms, on the pressure field on the outside, the possibility to filter the
incoming air (usual filters are G4/F5). There are additional components in this new system: additional
air ducts, flow rate controllers (demanding an overpressure between 50 and 150 Pa) or calibrated
dampers, demanding new balancing operations if the installer is trained for this. Installation and
maintenance become more complex. Double flow provides also the opportunity for a heat exchanger
(heat recovery), for preheating or cooling of air (neutral air entrance in the building, more
comfortable), requesting then some insulation of the air ducts.
When we add a heat pump in a balanced double flow this complex system provides an alternative to
classic air conditioners in moderate climates.
The design of the building shell for double flow system is different from the case of single flow: less
air inlets. Even with less inlets there is a significant air entrance because the building is not in
underpressure and all sides of it may leave air in. This may be a problem for retrofit if double flow is
the retrofit option: in France a professional rule says that the building envelope should be first treated
to lower infiltration down to 0.6 ACH to allow double flow ventilation.
The double flow system is more easily integrated in non residential buildings (where the additional air
ducts can be easily hidden, or even shown) than in residences where they cannot be easily integrated,
nor shown. Also in non residential buildings constant flow is more often used.
119
The heat exchanger can be a static one or a rotating one. This last solution is, relatively common in
non residential buildings in the USA. In small sizes those rotating heat exchangers are substituted by
static ones made of ondulated aluminium plates.
Effectiveness is defined and measured in standard EN 13141-7. For static heat exchangers,
effectiveness between 50 and 99% is reported, presumably depending on flow organisation and area.
Any higher efficiency is usually correlated with more head losses, so more electricity consumption.
Here again a gain in final energy may disappear when converted in primary energy. Rotating heat
exchangers have effectiveness in the 70-80% range.
Heat exchangers have to be protected by filters against fouling, sometimes only G1, often G3 or G4.
For a better air quality a second filtering stage between F5 to F7 is often proposed, or even F8 (against
pollens). Filters increase even more the headlosses and the electricity demand of the product. When
they are colmated they leave dust go along. Some systems indicate the need to change the filters. We
suggest here again to take away the filters for testing in order to get values comparable with other
products. Heat exchangers used in balanced flow system are subject to freezing like heat pumps and
request electric heating at low temperatures.
Some balanced flow systems may provide additional air heating after the heat exchanger either by
electricity or by hot water. A bypass on the fresh air can be activated for mid seasons, to provide some
cooling at higher flow.
The double flow has significant benefits that can be found at system level. It is not an option that can
substitute our base case, it is a full system, including a double circulation of air ducts. The Heat
Recovery option will use more energy in our product, and the benefit can only be found in the heating
and cooling bill, not in the ventilating bill.
Due to the various factors analysed our recommendation is that the manufacturers of equipment with
heat recovery are not obliged in a first phase (that could last three years for instance) to enter into an
information scheme for end users, because the method we propose is not sufficiently tested (testing
with substitution of HR section by no headlosses pipes). They can however enter into the scheme if
they want by considering their product as an extractor with the real extraction flow rate and half the
electricity demand.
6.7
Ventilations systems should not only be efficient but also producing a low noise level. Compared to
industrial and non residential applications the noise level of products in residential ventilation
applications should be as low as possible. However, the simplest way of increasing performance is
often to increase the flow and it has an interest to set limits on noise when trying to optimize the
product, in order to avoid solutions that the market will not accept.
Limits on noise: a new approach. A small high tech company proposed an active treatment of noise in
ventilation systems, which seem to interest one ventilation manufacturer (Direct, 1997).
120
121
First we established a list of the penetration of BAT because some are used in some products and not
in the others and this transfer of BAT from one family to another is already part of the optimisation
potential. The table gives the indicative penetration of each BAT of chapter 6 in the range of products
defined. Improvements related with rotation speed can be used in the product but may be limited by
the building codes which define pressure levels requested at lower flows. These improvements cannot
have the same level of implementation as the full load improvements.
Table 7-1: Improvement potential of the different residential ventilation products
Estimated
penetration of BAT
in
Motor
1st
improvement
Motor
2nd
improvement
Motor
3rd
improvement
Axial
Cent
lateral fix
Cent lat Cent.
central fix
Forward
Backward
Aeraulic
design
easing
Single Speed MS
.DV
hoods
..DV not
..ICV
hoods
Partial
Eff. gain
Observations
9%
0%
1%
0%
0%
0%
90 %
0%
10 %
0%
10 %
Size problems
40 60 %
1%
40 60 %
1%
0%
n.a.
100 %
1%
MS VS
0%
0%
1%
0%
90 %
90 %
20 30 %
30 40 %
40 70 %
20 40 %
of 10%?
a ?
of ?
of 10%?
122
The range of total efficiencies (starting from 1%) can only be explained if the less efficient motor is
used with an axial flow turbine (leading to 4-5% total efficiency) and that some design errors are made
in some models. The potential of gains is enormous if we use new technology : vanes, low speed
centrifugal, etc. However, if we stick to BAT, the technical studies of chapter 6 indicates as first
objective a general movement of fan efficiencies up to 40% with a 10% cost increase (a), and the same
for the very small motors considered (b). Efficiency increases less than direct z% = x%+y% addition,
typically following (1-z%)= (1-x%)*(1-y%). We estimated the total efficiency gain resulting from the
combination as 19%. The absolute over costs do add: 20% increase. We have not introduced changes
in BOM, following the analysis of chapter 6. This revolution would have lead to the following LCC
changes, if it had taken place in 2005.
Table 7-2: LCC input and results of decentralised ventilation products
Base case Base case
(a)
(a)
(b)
(b)
(a+b)
(a+b)
DV cont DV interm DV cont DV interm DV cont DV interm DV cont DV interm
General characteristics
15,3
15,3
15,3
15,3
17,0
17,0
13,8
13,8
Power W
134,0
11,2
134,0
11,2
120,6
10,0
148,9
12,4
Elec. kWh
LCC input (euros)
30,0
30
31
31
31
31
32
32
Price
Installation
Maint. 4%
LCC unit (euros)
30,0
30,0
31
31
31
31
32
32
Product price
0,0
0,0
Installation costs
211,3
17,6
190,2
15,9
190,2
15,9
171,2
14,2
Electricity
0,0
0,0
0,0
0,0
0,0
0,0
0,0
0,0
Rep & maint.
241,3
47,6
203,2
46,2
TOTAL
221,2 46,9 221,2 46,9
88%
37% 86%
83%
28%
Elec / total ratio
34%
86%
34%
LCC of new products installed in 2005 (euros)
Number of products (M)
0,3
4,4
0,3
4,4
0,3
4,4
0,3
4,4
9,5
133,2
10
137,6
10
137,6
10,1
142,1
Product price
0,0
0,0
0,0
0,0
0,0
0,0
0,0
0,0
Installation costs
67,0
78,1
44,7
52,3
44,7
52,3
40,3
46,7
Electricity
0,0
0,0
0,0
0,0
0,0
0,0
0,0
0,0
Rep & maint.
76,5
211,3
55
190,0
55
190,0
50,4
188,8
TOTAL
88%
37%
85%
34%
85%
34%
83%
28%
Elec / total ratio
LCC variations
Among the changes in environmental impact, the ones related with energy are the only significant, but
they represent a large potential of improvement. The same product is used continuously or
discontinuously and so it has a real meaning to study a weighted average of use scenarios.
7.3
Case study 1 : three comparable models in the same manufacturer with one using two BATs
One stakeholder (one of the top runner manufacturers) has shown to us the impact of his choices of
motor and fan quality. The comparison is made for a typical duty of 290m/h @ 200Pa (overall
pressure: internal plus external). He considered:
- a centrifugal blower with AC motor, forward curved impeller, 93W, 82 Euros
123
Figure 7-1: Comparison of performance and efficiency characteristics of a standard and improved ICV
160
140
120
pressure basic
100
efficiency basic
80
pressure optimised
60
efficiency optimised
40
20
0
0
100
200
300
400
500
The best efficiency values are respectively 20,1 % (at 110 Pa) and 31,6 % (also at 110 Pa), based on
full load. The yearly average power demand moves from 40 W to 28 W, a significant improvement.
Public prices with tax are 234 and 342 Euros. In this case gains are significant at full load, but
relatively expensive to obtain.
Case study 3 : two comparable models in the same manufacturer with one using multi speed
This is the example given by one manufacturer (one of the top runner manufacturers)
when
introducing a lower speed in an existing product. The grey line in the following graph represents this
new speed created.
Figure 7-2: Comparison of performance and efficiency characteristics of a standard and improved ICV
124
The lower speed does not change the EEI at full load which remains at 13.7%. The EEI (PL) is 17,6%
for the one speed product and becomes 30% for the two speed product, displaying an enormous
efficiency progression. Electricity consumption on a yearly basis goes down from 37 W to 26 W. The
manufacturer has chosen to introduce the new equipment at the same price than the previous one, 192
euros, which does not mean that there is no over cost, but that its gains in productivity over the last
years may cover this cost increase. Due to the nature of the improvement (electrical switch, new
cabling of the motor) we estimate to 5% the over cost of multi speed. Note that most gains are due to
flow reduction and should be measured at part load.
Summary of case studies
Lets start from the reference situation in chapter 5: a 19% full load efficiency equipment. Based on
the case studies 1 and 3, we can consider a 18% improvement in full load efficiency (18% means 18
points) for an over cost of 60%, or a 12% improvement for an overcost of 45% (called option b
hereunder). These two indications dealing with full load improvement are consistent. We transform
the first one into its marginal effect : a 7% improvement for a 15% overcost, called (a). Moving to
multi speed control gives another 13% move for an over cost of 5%. We call (c) this improvement.
Starting from the reference model we obtain :
Table 7-3: LCC variations of ICV with different options
LCC variations
Base case
Base case Base case Base case Base case Base case Base case Base case
ICV+a
ICV
ICV + a ICV+b ICV+a+b ICV+c ICV+a+c ICV+b+c
+b+c
General characteristics
Power W
40,0
29,2
24,5
20,0
26,2
20,0
17,7
15,2
Elec. KWh
350,4
256,1
214,8
175,2
229,6
175,2
154,8
133,2
250
287,5
362,5
400
262,5
300
375
412,5
Installation
250
250
250
250
250
250
250
250
Maint. 4%
Product price
250
287,5
362,5
400
262,5
300
375
412,5
Installation costs
250
250
250
250
250
250
250
250
125
497,3
363,5
304,9
248,7
325,9
248,7
219,7
189,0
179,7
179,7
179,7
179,7
179,7
179,7
179,7
179,7
TOTAL
1177,0
1080,6
1097,0
1078,3
1018,0
978,3
1024,4
1031,2
42%
34%
28%
23%
32%
25%
21%
18%
The benefit of option ( c) is dominant but the present testing standard does not take part load control
into account. We made before a suggestion for a part load efficiency index EEIPL
7.4
The inside parts of a hood are similar to the internal parts of an ICV. By introducing the generic
change of motor and the changes considered in case studies 1 and 2 of ICV into the reference kitchen
hood we can generate an approximate LCC curve. The over costs are directly extracted from the
previous studies (generic& ICV). We call Improved hood the one with only the generic motor
improvement, then a and b are the improvements of ICV.
Table 7-4: LCC variations of a hood with different options
LCC variations
Power W
Elec. KWh
Base case Imp Case Imp case Imp case Imp case
HOOD HOOD HOOD + a HOOD+b HOOD+a+b
General characteristics
59,1
49,6
40,5
90,0
81,0
66,0
60,0
43,8
36,8
30,0
400
401
438,5
513,5
551
Installation
250
250
250
250
250
Maint. 4%
Product price
400,0
Installation costs
250,0
401
250
438,5
250
513,5
250
551
250
Electricity
94
85
62
52
43
0,0
0,0
0,0
0,0
0,0
TOTAL
744
13%
736
12%
751
8%
816
6%
844
5%
7.5
Ranking of the individual design options by LCC (e.g. option 1, option 2, option 3);
Determination/ estimation of possible positive or negative (rebound) side effects of the individual
design measures;
Estimating the accumulative improvement and cost effect of implementing the ranked options
simultaneously (e.g. option 1, option 1+2, option 1+2+3, etc.), also taking into account the above
side-effects;
Ranking of the accumulative design options, drawing of a LCC-curve (Y-axis= LLCC, X-axis=
options) and identifying the Least Life Cycle Cost (LLCC) point and the point with the Best Available
Technology (BAT).
126
300
250
200
all DV
DV used constantly
DV used intermittently
150
100
50
0
0%
5%
10%
15%
20%
power reduction
The products used continuously show a LLCC for a reduction in electricity demand between 10% and
20%. As the same products are used either continuously or not, we consider the market improvement
should consider the weighted average of all products (line called : all DV). This leads to the same
improvement, with the same LLCC. The value of BAT is very uncertain in this analysis. In any case
the BAT EEIFL more than 3 and would become more than 6 with a multi speed strategy.
LCC curve of an ICV of average size
Figure 7-4: LCC curve of an ICV with all options
127
1400
1200
1000
LCC
800
600
400
200
0
0%
10%
20%
30%
40%
50%
60%
70%
% demand reduction
The reduction in total cost is limited but the energy gain is huge at LLCC (50%). The most profitable
option adapts pressure to the demand, a freedom that some countries may not have. So we drew a LCC
curve excluding this option.
Figure 7-5: LCC curve of an ICV if part load options are neglected
1200
1180
1160
LCC
1140
1120
1100
1080
1060
0%
10%
20%
30%
40%
50%
60%
% reduction
The optimum is flat but the 50% reduction is still optimal. A significant share of gains is due to flow
reduction and should be measured at part load. The value of BAT at part load is between 30 and 45
and at LLCC around 25.
LCC curve of a DV hood of average size
Figure 7-6: LCC curve of a DV-hood
128
860
840
LCC (euros)
820
800
780
760
740
720
0%
10%
20%
30%
40%
50%
60%
% reduction
Savings are possible but they dont pay for themselves all with the present over costs values The value
of BAT is over 15 and the LLCC over 9.
7.6
Discussion of long-term technical potential on the basis of outcomes of applied and fundamental
research, but still in the context of the present product archetype
.
Discussion of long-term potential on the basis of changes of the total system to which the present
archetype product belongs: Societal transitions, product-services substitution, dematerialisation, etc.
Hybrid ventilation
Passive stack natural ventilation can be stabilized by an hybrid fan. This small power fan can be
designed not to create any additional pressure loss when stopped since its central blades are parallel
with the airflow. So it allows the normal operation of the passive stack ventilation when the fan is off.
This technology which is just starting to be deployed in some countries is not at all allowed in some
other countries. The only question on which we can take position in this study is to decide if the
scheme should be applied to those products. The product that we could study, despite being in the
range of power of the DV, has the flow of an ICV (300 m3/h) and an efficiency far higher than other
DVs. We conclude that their integration in the same scale as other fans, if it does not show all their
benefits, will not disqualify them if the size effect in the assessment is expressed in terms of electrical
power, not air flow rate.
Air purification
Air purification (odours, CO2, H2O) without real air change would be optimal for saving thermal
energy but is not a BNAT for electricity consumption reduction. It is a BNAT for the thermal building
regulations decided by MS.
The hood in recycling is an example of this thermal BNAT compared with the remainder of ventilation
(it provides air cleaning without air rejection to the outside!) but CO2 is not treated. Nobody is
perfect.
129
The ultimate mechanical ventilation BNAT will supply natural air in a completely motorized way with
sensors of IAQ and use of natural ventilation when possible. Lets start with the most ambitious vision
before introducing some medium term options.
The most ambitious ventilation systems are based on demand-controlled hybrid (natural+mechanical)
technologies. Reshyvent research project (www.reshyvent.htm) tries to combine natural ventilation
and demand control. Within A Demand Controlled Hybrid Ventilation System is a two-mode system
using natural forces as long as possible and electric fans only if necessary. Sensor technologies are
used to establish the exact required air flow for indoor air quality and thermal comfort to a minimal
energy demand. Within the Fifth Framework Programme of the European Commission a research
project RESHYVENT has been started since january 2002.
The aim of the RESHYVENT project was to research, develop, and construct demand controlled
hybrid ventilation concepts for residential buildings. The objectives were:
* to integrate renewables and hybrid technologies in ventilation concepts
* to determine the impact on GHG mitigation, energy use, IAQ, thermal comfort, noise, further
application of renewables and use of low valued energy for heating and cooling
* to define the parameters for controlling indoor air quality and thermal comfort
* to give recommendations and proposals for national and international (CEN) standardisation of
(advanced) ventilation systems
* to develop measurement and control strategies for hybrid ventilation systems for different relevant
EU climates (severe, cold, moderate, mild and warm)
* to give specifications, guidelines and terms of references to develop demand controlled hybrid
ventilation system including practical application guide and descriptions, suitable to be implemented
in EU industries, easy accessible by ICT networks
* to develop and construct four complete demand controlled hybrid ventilation systems covering
four (severe, cold, moderate and mild/warm) European climates
* to identify market chances, threats and barriers
The output of Reshyvent is not exactly known.
In the meanwhile there are some techniques routinely used in non residential ventilation like
monitoring of agitation, presence, CO2 that can be transferred to residential ventilation. Since they
monitor closely the behaviour of people at home, its unlikely that there is a large social acceptance.
Also the electronics can be used in an even more modest way : balancing the distribution of fresh air,
while keeping the present user interface. At the maximum we have presently one pressure sensor that
can be located at suction of fan or somewhere else in the network. One NABT would be to offer four
or five sensors and actuators controlled centrally to balance the flow and reduce the speed as much as
possible. The present level of reduction of flow that we called (g) is in fact limited by this lack of
central knowledge and distributed actuation.
130
Task 7 summary
The penetration of BAT varies : some are used in some products and not in the others and this transfer
of BAT from one family to another is already part of the optimisation potential. Improvements related
with rotation speed can be used in the product but may be limited by the building codes which define
pressure levels requested at lower flows. These improvements cannot have the same level of
implementation as the full load improvements.
DV not hood show a LLCC for a reduction in electricity demand around 10%. As the same products
are used either continuously or not, we consider the market improvement should consider the weighted
average of all products. This leads to the same improvement objective, with the same LLCC. The
range of total efficiencies (starting from 1%) can only be explained if the less efficient motor is used
with an axial flow turbine (leading to 4-5% total efficiency) and that some design errors are made in
some models.
Impacts of options on an ICV is important in energy terms. The reduction in total cost is limited but
the energy gain is huge at LLCC (50%). The most profitable option adapts pressure to the demand, a
freedom that some countries may not have.
By introducing the of options on a DV-hood having the 9% reference kitchen hood (the multi speed
option 3- is already generalized) we can generate an approximate LCC curve. Savings are possible
but they dont pay for themselves with the present values (very uncertain however).
A testing procedure is summarized, based on chapter 4, that allows to give the benefit to all techniques
used to reach the BAT.
The following rough summary of BAT and LLCC targets can be proposed:
EEI at PL
BAU
LLCC
BAT
Local
ventilation=DV
2
3
>3 (estimated 4)
Hoods
6
9
>15 (estimated 18)
Central
ventilation=ICV
12
24
>30 (estimated 38)
About BNAT, the most promising is Passive stack natural ventilation can be stabilized by an hybrid
fan. This small power fan can be designed not to create any additional pressure loss when stopped
since its central blades are parallel with the airflow. So it allows the normal operation of the passive
stack ventilation when the fan is off. This technology which is just starting to be deployed in some
countries is not at all allowed in some other countries.
Air purification (odours, CO2, H2O) without real air change would be optimal for saving thermal
energy but is not a BNAT for electricity consumption reduction. It is a BNAT for the thermal building
regulations decided by MS.
131
Most categories of fans grouped under PRODCOM 29.71.15 are within the scope of the study. All
fans without Heat Recovery in categories 29.71.15.33 (Roof ventilators), 29.71.15.35 (Other
ventilators), 29.71.15.50 (Ventilating or recycling hoods incorporating a fan, with a maximum
horizontal side <= 120 cm; this indication about size is not present in the other languages than English
and is not a category limit; there is no category for larger hoods ) were examined and found to be
within the scope of potential ecodesign requirements. Among 29.71.15.30 (Table, floor, wall,
window, ceiling or roof fans, with a self contained electric motor of an output <= 125 W) only roof
fans are in the scope.
The power limit of 125W (not applicable to hoods) was agreed between lot 10 and lot 11 and
corresponds both to PRODCOM coding and to the reality of the market for individual residences (as
opposed to collective ones). There are occasionally individual products with a higher power demand
but only for balanced supply and extract flow and the power associated with ventilation itself19 (one
side, no heat recovery) remains under the 125W limit. Residential ventilation fans usually include the
motor, as opposed to larger power fans, they are tested under specific standards (EN 13141 parts 4 and
6 and CEI/IEC 61 591) and provide lower pressure differences. Thus the distinction between the two
groups of fans corresponds to strong technical differences.
The study looked in a quantitative manner at all phases of the lifecycle of the products: materials use,
manufacturing, transport, distribution, installation and maintenance, use, end of life. The
environmental impact of residential ventilation products is largely dominated by energy consumption.
The electricity consumption represents from 13 % of the life cycle cost for the end-user for hoods, up
to 88 % for Window and wall fans used continuously. Energy consumption in the use phase accounts
for 73% of the Total Energy use, 100% of electricity use, 98% of Water (process) rejection, 100% of
Water (cooling) rejection, 60% of Waste, non-hazardous going to landfill and 34% of Waste,
hazardous to be incinerated are generated. Total impact for the stock of products in use in 2005 is of
the same order of magnitude as for air conditioners but the stock and environmental impact growth
rate is slower than for air conditioning appliances. Since there is a factor of 3 to 5 between the best and
worst energy efficiency of residential ventilation products, there is significant potential for reducing
energy consumption and CO2 emissions if we target the electricity use of the products.
19
Roof fans (with Electrical power under 125 W) if it is designed to be situated on a roof
Window fans (with Electrical power under 125 W) if it is designed to be installed in a window
Wall fans (Elec power < 125 W) if it is designed to be installed in a wall.
Illustrations can be found in table 1-1, but despite these appearance differences, the products are in the
same category of local ventilation in residences.
How many products are in the scope?
Residential ventilation fans, including hoods, (estimated at: 7.3 million units/year, of which more than
4 million hoods in ventilation mode20, and 3.3 million local ventilation fans) and the central residential
fans (estimated at 1.4 million units/year) are clearly above the EuP threshold of 200 000 products per
year. The ventilation device with the largest penetration in Europe is the kitchen hood.
Stock of residential ventilation fans
An estimate of the stock of equipment in use has been made and adjusted to existing field data. It
shows a large penetration of local ventilation fans (68 million units, including kitchen hoods
connected to the outside) and central ventilation fans (18 million units). Nevertheless natural
ventilation is the dominant means of providing ventilation. .
It is also to be noted that the environmental impact of residential ventilation products is largely
dominated by collective ventilation, which accounts for about two thirds of all impacts - with an
energy consumption of about 14 TWh in 2005 compared to over 21 TWh for the whole end-use of
residential ventilation. However, the scope of the proposed measures has been limited here to
individual products, under 125W, except for hoods which use a few hundreds Watt. Collective
ventilation fans are within the scope of the Working Document of the Commission Working
document on possible ecodesign requirements for ventilation fans. - continuity of ecodesign
measures will be discussed later.
General issues for all three individual ventilation product groups
The proposal of having a common legislation is the first question. Obviously the possibilities for
improved efficiencies are not the same and the duration of use is not the same. The service is not the
same and somebody purchasing a hood should not think it will provide a full ventilation of the
residence. So the EU should label or generate an obligation and a different name for each category.
The scale for hoods should bear the name Hood, the scale for decentralized ventilation fans except
hoods should be called Local ventilation (when there is only one spigot for air suction) and the
scale for centralized ventilation should be called Central ventilation (multiple spigots or choice of
the manufacturer). On the other hand the three scales of labeling and obligations can be
20
and the rest in recycling mode but also covered by the proposed measures
133
In other words, ventilation products (except hoods) cannot have such low standby consumptions as
other products when it is part of their duty to permanently energise sensors detecting a need for air
change, and to maintain a small flow to reduce the impact of moisture and other pollutants. Except for
kitchen hoods and remote controls, standby consumption for sensors and controllers is included in the
testing process, not excluded and regulated separately. In describing the four tests the testing annex
included in the present chapter mentions this inclusion of standby, sensors & controls in the
overall consumption.
Specific issues of kitchen hoods
First specific problem : the choice of the speed for end user information. Several speeds are
usually available, very often three. The testing standard is often applied at speed N-1 (where N is the
highest speed) for energy use (usually speed 2 if there are three speeds) and also for acoustics (speed 2
is thus designed by the manufacturers to be good in noise), rather than providing the end user aware of
performance at the higher speed often described as "booster speed", or "intensive". Air flow may be
reported at speed N. In practice, it may well be that the highest speed is the one most often used, in
which case sound level, air flow efficiency and efficiency for that same highest speed should serve as
a basis for end user information.
The only limitation to overpower of hoods is the noise that they may generate. A flow of 300 m3/h is
sufficient technically but the customer appreciates overpower. It goes up to 1 000 m3/h. One thus goes
from 5 ACH21 to 20 ACH, which is not good for electricity use but even worse for thermal energy use.
Without suppressing the possibility to have such high flows, the fact of documenting the highest flow
rate (speed N) and not the following one (speed N-1, usually 2 out of three) for both the noise and
electrical effectiveness seems the best choice for consumer information.
Finally it is essential that in labeling an appliance all information should be consistent, i.e.
corresponding to the same situation, in this case the same speed, in the study proposal the
highest speed (the real highest, even if called booster). However if an automatic timer or sensor
brings back the hood to another speed in less than 2 minutes, the highest speed could be
considered as this speed and the other (upper) speeds as real boosters, not suitable for end user
information.
Second problem. The hood has another function of importance: illumination of the working area.
Lighting is very well treated in the testing standard and some manufacturers are making real efforts to
21
ACH is the ratio of the air flow to the volume of the room; a value like 1 or three is frequent;
however for kitchen hoods the service expected is a quick removal of grease and odour, leading to
higher necessities.
134
The proposal made by some manufacturers22 relating to information about lighting integrated in
kitchen hoods is independent of the speed and can be accepted immediately after consistency checks
with the general lighting measures. This should not avoid the need to satisfy any more general
lighting requirements.
Discussion of possible labeling or grading structures
Grading of performance (which product is better and how large the difference is) is based on the BEP
(Best Efficiency Point) of the characteristic line and associated reduced speed points (part load) in the
proposal. This leaves to MS their freedom of choice of pressure and flow requests. It allows a
comparison of products, independently from national regulations and habits, and will ease the
comparison of products. One can consider that the new possibility of comparing products adapted to
different national markets will lead some MS to complement the free circulation of ventilation
22
Posting the lux/watt ratio in the conditions of the testing standard, averaged over the four
measurement points of the IEC standard
135
136
14
12
EEI@PL
10
DV average
DV Hood
ICV continous 2 speeds
6
F
4
G
F
G
0
0
G
100
200
300
400
Next question : what is the extent of the range of grading? There is only room for two classes (F
and G) between zero and the average EEI if we stay with rounded figures, and the study has shown
that the EEI of the BAT is far above the present EEI average values. So its logical to define five
classes between average and BAT, and two classes under present average.
Some manufacturers are afraid of the introduction of energy performance classes in which only
one manufacturer appears immediately in top class. The problem is solved by making an empty
class A based on the BAT which solves this problem of unfair competition (one cannot give A to only
one manufacturer at the starting point). The proposal creates fair competition for the first class A
equipment on the market.
These two considerations lead us to propose the following scheme in table 8.1:
Table 8-1: Efficiency classes proposed for consistency of grading of residential ventilation fans based
on EEI at Part Load (the EEI is shown for the average size product)
Classes
Reminder: value of BAT
Highest or A
B
C
LLCC or D
Just above average or E
F
Lowest or G
Local ventilation of
average size, non cent.
P = 17W
4 (more than 3)
EEI@PL>6
6>=EEI@PL>5
5>=EEI@PL>4
4>=EEI@PL>3
3>=EEI@PL>2
2>=EEI@PL>1
EEI@PL=0 or 1
Hood of average
size = 150W
Central ventilation
of average size = 75W
The grading scale has a wide extent, with an empty class A, and there is no reason to forecast any
change in it before 2015, at the soonest.
137
An immediate MEPS in ventilation cannot be Part Load in the present situation of MS regulations
(because the building codes can impose to keep some pressure level at part load) and of lack of
efficiency reporting. It should be a Full load based MEPS for some time, called MEPS@FL. This
temporary difference between a MEPS based on full load and a labeling system based on weighted
part load is not a big problem since the two tools have different objectives: transforming the market in
the case of labeling, stopping products poorly designed at full load in the case of MEPS23.A Local
ventilation product of average size with an EEI @ PL under 2 is far under the LLCC, as well as
a Hood of average size under 8 at PL and a Central ventilation product of average size
under 12 at PL. The full load MEPS@FL is then established at the same limit, in order that no
product is banned by MEPS1 and allowed by MEPS224. The second MEPS will later (2012?) be
based on Part Load, that will be at that time usual practice, and will ban at that time the
products far under the LLCC. It will be called here MEPS@PL.
Correction factor for size
The limits that have been outlined for the product of average size studied in previous chapters have
now to be applied to a product of any capacity between 0 and 125 W. A linear relationship is found
suitable with a distinct slope for centrifugal products on one hand (Central ventilation and hoods) and
local ventilation products on the other hand (a mix of axial, centrifugal, with or without vanes) as
shown on figure 8-2 hereunder.
Figure 8-2: Correction for size of the real product, to be applied to the average product
23
and the translation by EEI@ PL = EEI@ FL / 2 is immediate, even if penalsing for products with a
good control
24
EEI usually decreases when moving from FL testing to PL testing
138
EEI@PL = f(Power)
30,00
25,00
EEI@PL
20,00
Centrifugal
15,00
Local
10,00
5,00
0,00
0
20
40
60
80
100
120
140
Power (W)
The two dependencies are different. The slope has been found to be 16.47 W-1 in the case of central
ventilation and hoods and 12.07 Watt-1 in the case of local ventilation products. Consequently all
limits are made proportional to the nominal P. The version of the previously defined grading structure
applicable to any product size is given in table 8-2.
Table 8-2: Efficiency classes proposed for consistency of grading of residential ventilation fans based
on EEI at Part Load (the product EEI is rounded to the closest integer)
Classes
Local ventilation of
nominal Power P
Highest or A
EEI@PL>6*P/17
6*P/17>=EEI@PL>5*P
B
/17
5*P/17>=EEI@PL>4*P
C
/17
4*P/17>=EEI@PL>3*P
LLCC or D
/17
Just above average or 3*P/17>=EEI@PL>2*P
E
/17
2*P/17>=EEI@PL>1*P
F
/17
Lowest or G
EEI@PL<= 1*P/17
Hood of nominal
Power P
EEI@PL>18*P/150
18*P/150>=EEI@PL>1
5*P/150
15*P/150>=EEI@PL>1
2*P/150
12*P/150>=EEI@PL>9
*P/150
9*P/150>=EEI@PL>6*
P/150
6*P/150>=EEI@PL>3*
P/150
3*P/150>=EEI@PL
Central ventilation of
nominal Power P
EEI@PL>38*P/75
38*P/75>=EEI@PL>31
*P/75
31*P/75>=EEI@PL>24
*P/75
24*P/75>=EEI@PL>17
*P/75
17*P/75>=EEI@PL>12
*P/75
12*P/75>=EEI@PL>6*
P/75
6*P/75>=EEI@PL
For example, the size dependant version of EEI @ PL under 2 (local) is EEI @ PL under 2*P/17
(17 being the nominal power of the non centrifugal local ventilation device studied in details), as well
as EEI @ PL under 8 (hoods) is EEI @ PL under 8*P/150 and EEI @ PL under 12 (Central
ventilation) is EEI @ PL under 12*P/75. The full load MEPS@FL limits are the same, as already
stated.
8.2
Ecodesign requirements
Lets call Y0 the date of publication of the ecodesign measure (taken as 2009 in the impact study). A
first set of documentation requirements part of scenario1 will be applicable two years later. Labelling
139
A fan is a rotary bladed machine that is used to maintain a flow of a gas, typically air, and which is
driven by an electric motor. The ventilation fans are encased. The products considered here have been
designed for use in one single dwelling or one room of the dwelling or the cooking zone of a kitchen.
There are three categories of residential fans covered by the potential requirements and the design
options : local ventilation fans, kitchen hoods, central ventilation fans. The hoods are easily
identified as such by the manufacturer but for the other products the manufacturer or the laboratory
has to determine if the product belongs to Local ventilation (when there is only one spigot or
terminal device) or Central ventilation (various spigots or terminal devices in the product as sold or
manufacturers decision).
A 'residential ventilation fan' is any fan that are designed to move air from or into a residential
building. This definition is consistent with Prodcom and CEN categories, as of year 2007. EN 13141
in its general title speaks of components/products for residential ventilation and parts 4 and 6 serve as
a basis for the characterization of the products in the scope. PRODCOM categories 29.71.15.33 (Roof
ventilators) and 29.71.15.35 (Other ventilators) with an electrical input under 125W are residential
ventilation fans. Those fans in PRODCOM category 29.71.15.30 (Table, floor, wall, window, ceiling
or roof fans, with a self contained electric motor of an output <= 125 W) are residential ventilation
fans. Among residential ventilation fans there are two categories.
The study proposes three residential ventilation fan categories as follows:
A 'residential kitchen hood' incorporates a fan providing local ventilation or recycling of air in a
kitchen. This is stated in PRODCOM 29.71.15.50. A 'residential kitchen hood' can be tested under
CEI/IEC 61 591: 2005.
A 'local ventilation fan' is any other fan providing local ventilation and designed to serve only one
room and consequently having only one spigot related with the inside of the building. It is in the scope
of the ecodesign measures when it has an Electrical power under 125 W. Part 4 of EN 13141, as of
year 2007, names them encased ventilation fans.
A 'central ventilation fan' is a type of residential ventilation fan designed to serve various rooms and
consequently has various spigots related with the inside of the building or is sold with components that
allow to connect with various terminal devices inside the rooms. A manufacturer can declare as
central ventilation fan an equipment that has only one spigot but has been designed to serve various
rooms by using other components to do so, and consequently shall apply in that case the (more
demanding) limits. It is in the scope of the ecodesign measures when it has an Electrical power under
125 W. Part 6 of EN 13141, as of year 2007, covers Exhaust ventilation system packages used in a
single dwelling, but the scope includes products which move air from outside to inside, and not only
exhaust.
There is no power limit on residential kitchen hoods for them to be in the scope, but there are many
products in the range between 100 and 300W . Hoods used as a ventilation mean are part of residential
ventilation fans but the proposed requirements apply also to hoods used in recycling mode (no ducting
to outside) because its the same product: the decision on how to use the hood is made by the final user
and the energy and resources use is the same in both situations, as well as the improvement
possibilities.
140
The products excluded from the scope of the proposed design options are: comfort fans (which move
the air inside the room, not in relation with outside) that have been subject to a parallel study, all
ventilation products with heat recovery, mostly due to market size, but also to potential interaction
with national EPBD legislation and ongoing testing standard revision, fans integrated into a boiler,
fans used for smoke extraction in case of fire.
Testing
EU industry has good testing standards at full load for products in the scope of the proposed
requirements, on which are based the full and part load Energy Efficiency Indices used in the
recommendations.
The existing (in year 2007) EN 13141, Ventilation for buildings - Performance testing of
components/products for residential ventilation, namely Parts 4 and 6, is consistent with the proposed
categories of residential ventilation.
The existing CEI/IEC 61 591: 2005 called test standard for household range hoods applies to
kitchen hoods, and there is a reasonable consistence with the other ventilation products testing
standards, in terms of definition of characteristic line. However the standard covers many more aspects
than the fan electricity consumption; which are useful for energy efficiency :
- It determines also the effectiveness of the hob light, and this information is a real high value
ratio of the output (illumination on the work plan) to the electricity consumption for lighting
(including the source, the luminaire, the position of sources
- And the noise;
- As well as other non energy parameters like grease filtering efficiency.
Both standards allow the determination of the characteristic line from which one extracts the Best
Efficiency Point. The efficiency at BEP multiplied by 100 gives the Energy Efficiency Index at Full
Load (EEI @ FL).
When there are various speeds, there are various characteristic lines and an adequate weighting allows
to determine an EEI @ PL (Part Load). Part 8.5 explains how to perform this, in the absence of an
harmonized standard for the purpose (this text is proposed to become an annex of any measure). The
EEI @ PL will be the basis of most proposed measures, even if it is sometimes estimated initially with
a simplified procedure from the full load equivalent because it is the index that allows representing a
large share of environmental gains. The transformation of the Annex included in the present chapter
into an EN standard is necessary for any policy taking effect in 2015 and after and deserving a higher
harmonization between MS about ventilation. It is proposed that the Member State test laboratories
and notified body use in the meanwhile the Annex included in the present chapter to characterize the
products. They should be helped by some accompanying measures (described hereunder) to reach
rapidly a sufficient number of tests so as to make the best out of the proposed procedure.
Ecodesign requirements related with energy use
Scenario 1: full load MEPS@FL and part load labelling A-G ; even if no other policy is yet
applicable, it is important that the essential information of EEI @ FL and EEI@PL is made available
rapidly to the end user at the time of purchase (either direct purchase or through an installer). An
141
Also the specific standby and off modes are regulated as follows:
Requirement 2: Standby requirements developed on the basis of the Ecodesign Lot 6 preparatory
study apply to all kitchen hoods and to local (and central) ventilation products controlled by a remote
controller, and only to the standby generated by the remote controller if any. Local and central
ventilation products without remote controllers are excluded from Lot 6 standby preparatory study
requirements due to the specific function of residential ventilation that requires a minimum flow and
may use sensors to control it.
Requirement 3: No product will be put on the market if it is a Local ventilation product with an EEI
@ FL under 0,1176*P, as well as if it is a Hood under 0,0400*P at FL or a Central ventilation
product under 0,1600*P at FL. This is MEPS@ FL, which is dependant on the electrical power
absorbed P. The application of this measure starts at Y0+3. A manufacturer can declare as central
ventilation an equipment that has only one spigot but has been designed to serve various rooms by
using other components to do so, and consequently shall apply the (more demanding) limits.
The labelling requirement may have an autonomous impact and is needed to prepare the further
MEPS@PL. Due to the market structure (SME offering complete products) and to the type of
appliance (size large enough, with a market accessible to end users and not only to installers) the
existing A-G label is adequate. Both the label and the MEPS@FL shall be put in place in three years.
Requirement 4: The efficiency class of the product for energy labelling shall be determined by the
manufacturer on the basis of EEI at Part Load and electric power demanded at Full Load (called P, in
Watt). A manufacturer can declare as central ventilation fan a piece of equipment that has only one
spigot but has been designed to serve various rooms by using other components to do so, and
consequently shall apply the (more demanding) limits. The determination is made with the following
table.
Class
A
B
C
D
E
F (to be banned under
MEPS@PL)
G (to be banned under
MEPS@PL)
Local ventilation
Hoods
Central ventilation
EEI@PL>0,3529*P
EEI@PL>0,1200*P
EEI@PL>0,5067*P
0,3529
0,1200
0,5067*P>=EEI@PL>
*P>=EEI@PL>0,2941*P *P>=EEI@PL>0,1000*P
0,4133*P
0,2941*P>=EEI@PL>0,23 0,1000*P>=EEI@PL>0,08
0,4133
53*P
00*P
*P>=EEI@PL>0,3200*P
0,2353*P>=EEI@PL>0,17
0,0800*P
0,3200*P>=EEI@PL>0,22
65*P
>=EEI@PL>0,0600*P
67*P
0,1765*P>=EEI@PL>0,11 0,0600*P>=EEI@PL>0,04 0,2267*P>=EEI@PL>0,16
76*P
00*P
00*P
0,1176*P>=EEI@PL>0,05 0,0400*P>=EEI@PL>0,02 0,1600*P>=EEI@PL>0,08
88*P
00*P
00*P
0,0588*P>=EEI@PL
0,0200*P>=EEI@PL
0,0800*P>=EEI@PL
142
Local
ventilation
Energy
Efficiency
xxx
Flow in m3/h xx
Power inW
xxx
Noise in dBA xx
Central
ventilation
Energy
Efficiency
xxx
Flow in m3/h xx
Power inW
xxx
Noise in dBA xx
Kitchen
Hood
Energy
Efficiency
Filter Eff. (%)
Lighting Eff.
Flow in m3/h
Power in W
Noise in dBA
xxx
xx
xx
xx
xxx
xx
Requirement 6: As part of documentation available with the product in the MS language a fiche will
represent the four characteristic lines used in determining the EEI@PL and the information requested
under part 3 of Annex I of the Directive. The fiche will explain full and part load, at least with the
following sentences:
143
When the manufacturer does not want to perform part load testing, a simple default rule allows to
estimate this EEI from the full load equivalent. The testing procedure and the simple rule are given in
the annex 8.5 (annex to chapter 8 here).
For balanced flow products without heat recovery the electrical power is divided by 2 and the measure
is applicable.
Scenario 2: proposed MEPS@PL levels on top of scenario 1.
When conditions have been obtained to base the product policy on part load EEI, there is room for a
second MEPS level based on part load performance for a date three years later i.e. Y0+6 (suppressing
G and F), then further steps (suppressing E, etc.) in the following years.
Requirement 7: No product will be put on the market if it is a Local ventilation product with an
EEI @ PL under 0,1176*P, as well as if it is a Hood under 0,0400*P at PL or a Central ventilation
product under 0,1600*P at PL, where P is the electrical power absorbed. A manufacturer can declare
as central ventilation fan an equipment that has only one spigot but has been designed to serve
various rooms by using other components to d so, and consequently shall apply the (more demanding)
limits The application of this measure starts at Y0+6.
General view of evolution and prospects
Unfortunately in some situations, the simplest way of increasing performance is to increase the flow:
there is also pressure to set limits on noise in order to avoid solutions that the market will not accept.
Since noise information is not available usually in directories, except for hoods (but then not for the
highest speed), the MEPS on noise will be defined later, but not after MEPS@PL entry into force.
The other successive MEPS@PL not described here- could lead to BAT (category A in grading) in
2015, provided there is a technical evolution leading to cost reduction for the necessary options.
Figure 8-3 provides a full picture on proposed measures: label, MEPS@FL, MEPS@PL, leading
eventually to LLCC, based on the average product size. Table 8.3 summarises the same information.
Table 8-3: Date of measures if Y0 =2009
Year
Scenario 1
Scenario 2
2010
Info on plate
Info on plate
2011
Full Label @PL
Full Label @PL
2012
MEPS@ FL
MEPS@ FL
2015
MEPS @PL
Figure 8-2: History of measures leading to the transformation of the market in the direction of the
LLCC, applied to the average size product, for easiness of understanding
144
BAU EEI=2
MEPS1
Y0
8.3
MEPS2
Y0 +2 Y0 +3
Y0 +6
Noise and air quality. Among the issues treated in Annex I of the directive, noise is certainly
important. Electromagnetic problems were not found. About air quality, care must be taken with hoods
connections on the aeraulic circuit, so that polluted air cannot come back into the space. Noise
limitation indoors is a specific constraint to be taken into account for the product design. In noisy areas
the transmission of noise from outdoors can also be a constraint for the product design. The less noisy
product will be identified by providing information to the purchaser of the product but most of the
relevant work is done by the fitter who should use the proper passive noise filters as specified in MS
building codes, or in the future, by active noise dampers.
Manufacturing requirements. Easy disassembly of the product should be encouraged which the
WEEE directive will also promote.
Recommendations for installation, maintenance use and end of life. Many things depend on the
installer,in terms of training and environmental consciousness. The fitter will influence:
- the choice of the product;
- the installation of switches or speed selectors for the user ;
- the choice and installation of products at several speeds, the flows being chosen by the
installer;
- the choice of a product taking account of possible air quality requirements (typically moisture)
- the recycling of the product at its end of life and the proper treatment.
Filter maintenance is an important issue, highly cost effective to maintain real life performances of
ventilation products.
Accompanying measures
145
The efficiency levels for best products that could be used e.g. for the purposes of public procurement
or fiscal incentives by Member States should be expressed in terms of EEI@PL, assuming the MS has
no national regulation objecting to the reduction of flow in dwellings. In that case (no national
regulation against part load) the study concludes that a present benchmark in line with category D
corresponds to the LLCC : for Local ventilation: EEI@PL>2, for Hoods : EEI@PL>6, for
Central ventilation=ICV : EEI @ PL>12.
Continuity with other legislation
The first and most important aspect is that a solution has been found that avoids any double action or
conflict with national EPBD legislation. By concentrating on the product itself and on its best
operational point, without any consideration of the pressure and flow where this occurs, the proposed
measures work in the same direction as the EPBD (efficiency), but in a parallel manner. EPBD
national legislation regulates building construction and renovation and may indicate desired pressure
levels and flows or derived quantities like SFP. Taking this for granted the measures will improve the
efficiency of the fan at that operating point.
Considering now continuity with the Working Document of the Commission Working document on
possible ecodesign requirements for ventilation fans., version dated May 2008, it is our understanding
that it uses the same concept as the present study, the efficiency at the Best Efficiency Point. In that
sense continuity is ensured.
Also there is consistency of testing standards. All test methods comply with ISO 5801 : test method
for fans. European standards below refer to this only ISO test standard but build different testing
conditions due to the difference between residential, industrial and tertiary use: EN 13141, Ventilation
for buildings - Performance testing of components/products for residential ventilation, that we have
used and EN13779 : non residential performance of ventilation systems (inc : SFP, filters...) that is in
the domain of non residential use. So the continuity is ensured in that way also.
However the fans considered in the existing WD of ventilation fans are for heavy duty air handling
in tertiary buildings not for residential ventilation, and there is clearly a discontinuity between the
146
Impact analysis
Impact on products
The statistics of products affected in the data basis is given by figure 8-4
Figure 8-3: Share of market (according to estimates limited to products on the scope only (excluding
collective ventilation) affected by MEPS proposed
A-D
24%
E
6%
F-G
70%
In the event that the proposed measures up to the BAT take effect at the indicative dates given, 24 %
of the market models remains unaffected until around 2015 and have to be modified at that date. If the
seven suggested requirements are implemented there is no conflict with MS regulations. The products
reaching or exceeding the LLCC fall into class D class and above
Impact on industry and consumers
Impact on industry and the consumers has been approached by assuming a full transfer of overcosts
from manufacturers to consumers and by basing measures on an affordable consumer life cycle cost.
For instance the labeling could bring back the distribution of EEI@PL to a Gaussian distribution
around the average, and for the MEPS the study assumed truncation of the Gaussian tail. On the short
term the products are from EU and the additional demand will be directed to EU industry. Industry
employment and competitiveness can increase in that sector if the EU products are labeled and have a
minimum performance, because low impact mechanical ventilation can substitute poor existing
mechanical or natural ventilation. The additional income of manufacturers could be put in line with
7000 jobs in 2025 if one accepts the common ratio of 100,000 Euros per job. Such an environmental
147
The data base of the present study was used to simulate the effects of the policy on the distribution of
equipment put on the market sorted by grading categories introduced previously and the results are
shown on table 8-4 and 5. The starting point (column BAU) shows a sharing of products between
one quarter of the market which has already very high performance and the rest which has a quite low
grading. The average EEI@PL are computed for each of the three categories of products.
As a result of scenario 1, the model transforms the frequency distribution, first in the direction of
moving models under average to the average (column labeling & MEPS@FL) and recalculates the
averages.
Then the same for MEPS@PL, which as opposed to MEPS@FL, has a significant impact because it is
based on part load performance.
Finally the reader can compare the simulation of measures with the LLCC and of the BAT, which
proves that the proposed measures are consistent with the objective of the Directive.
Table 8-4: Assumptions made to compute the effects of measures taken on products on the scope
only (not CCV)
Effects of a
certain scenario
on frequency of
classes and
average EEI
BAU
Scenario 1 :
Label@PL +
MEPS@FL
Scenario 2 :
Label@PL +
MEPS@PL
Frequency of A-D
24%
24%
100% over E
Frequency of E
6%
26%
Frequency of F-G
71%
50%
25
UK and French building codes, for example, have not been designed to protect national markets but
request such an adaptation of the product to some specific features or values that they generate a kind
of barrier for products from other countries (see chapter 1)
149
Table 8-5: Results obtained the effects of measures taken on products on the scope only (not CCV)
Effects of a
certain scenario
on frequency of
classes and
average EEI
BAU
Scenario 1 :
Label@PL +
MEPS@FL
Scenario 2 :
Label @PL+
MEPS@PL
LLCC
BAT
Average EEI PL
local ventilation
2,2
3,5
EEI between 3
and 4
Average EEI PL
hoods
10,6
EEI between 9
and 15
18
Average EEI PL
central ventilation
12
20
27,8
EEI between 24
and 30
38
As far as one can predict market evolutions, the simulation of the package of requirements seems in
agreement with the LLCC target, which is defined as a range resulting from the technical studies. As
the reader remembers, obtaining the BAT requires further iterations with MS and R&D on
manufacturers side. The benefits on the unitary consumption and LCC of products are already
significant (tables 8-6 and 7).
Table 8-6: Benefits for the individual consumer of the measures in terms of unitary electricity
consumption -products in the scope only (not collective ventilation of residential buildings)
Scenario 1:
Yearly Energy Consumption
of one single product
local ventilation continuous
(kWh/unit/a)
local ventilation intermittent
(kWh/unit/a)
local ventilation weighted average
(kWh/unit/a)
Hood intermittent (kWh/unit/a)
central ventiation continuous
(kWh/unit/a)
BAU
(kWh/unit/a)
Label@ PL
+MEPS@FL
(kWh/unit/a)
148,92
Scenario 2:
Label +MEPS@
PL
(kWh/unit/a)
BAT
(kWh/unit/a)
135,4
85,1
74,5
12,41
11,3
7,1
6,2
26.0
23,6
14,9
13,0
65,7
262,8
43,8
223,4
37,2
160,7
26,3
148,9
Table 8-7: Benefits for the individual consumer of the measures in terms of LCC -products in the
scope only (not collective ventilation of residential buildings)
Scenario 1:
Scenario 2 :
Purchase+
Label
Label+
installation
@PL+MEPS
@FL
MEPS@ PL
LCC (Euros) of one single product price of BAU LCC of BAU
(Euros)
(Euros)
(Euros)
(Euros)
30
241
221
=221
local ventilation continuous (Euros)
local ventilation intermittent
30
48
47
=47
(Euros)
local ventilationweighted average
30
64
63
=63
(Euros)
650
744
=744
=744
Hood intermittent (Euros)
BAT
(Euros)
>221
>47
>63
847
150
500
1177
1100
1030
>1030
Some values (displayed with a = or a >) are shown equal to (or higher than) their neighbour in the
table 8.7 when the differences are of the order of magnitude as the uncertainty and so cannot be
certain. We have to analyse two situations of collateral impacts. On one hand for hoods all the
calculations made for hoods used in ventilation (impact computed here) are applicable in recirculation
mode and the end user will have about the same cost and benefit; the collateral aspect is positive. For
local ventilation, if there were no permanent use, the benefit would not pay for the costs. With the very
small percentage of permanent use fans assumed in the study, the total effect of the policy is already a
significant gain, but concentrated on end users having a permanent use.
Benefits to the environment
The benefits in monetary and environmental terms are given hereunder for the full set of requirements,
without harmonization of ventilation issues among MS. First, yearly consumption of one product used
in one dwelling is computed as average power demand (including the effect of existence of multi
speeds and other controls when relevant)* 8760 hours (or less if ON/OFF ). Typically hoods and
intermittent local ventilation fans are used ON/OFF and operate two hours a day. Electricity average
price is 0.158 euro / kWh and discount rate equals 2 % in the economic calculation of benefits . The
numbers of individual residences and apartments, as well as the ownership rates have been determined
in the study and validated on existing field data. When and if the requirements are applied on the total
stock of equipment in use, figure 8.4 gives the total gains of the proposed policy.
Figure 8-4: Impact of MEPS proposed applied to products on the scope only (excluding CCV)
14
12
10
BAU
Label in 2009
all IM in 2012
BAT in 2015
8
6
4
2
0
2000
2005
2010
2015
2020
2025
2030
Year
Tables 8-8 and 9 show the global benefits of the proposed scenarios up to year 2020, the year of
present EU targets.
Table 8-8: Benefits on total electricity consumption of scenarios for products on the scope only
(excluding CCV)
151
2009
2010
2011
2012
2013
2014
2015
2016
2017
2018
2019
2020
Yearly Energy
Consumption
(TWh)
7,20
7,20
7,46
7,74
8,02
8,32
8,62
8,94
9,25
9,56
9,86
10,15 10,43
7,20
7,16
7,38
7,60
7,84
8,08
8,33
8,59
8,85
9,10
9,35
9,59
9,83
7,20
7,16
7,38
7,60
7,72
7,84
7,97
8,10
8,23
8,36
8,48
8,60
8,72
BAU
Scenario 1
Scenario 2
Table 8-9: Benefits on total electricity consumption of scenarios for products on the scope only
(excluding CCV)
2008
2009
2010
2011
2012
2013
2014
2015
2016
2017
2018
2019
2020
CO2
emissions (Mt)
3,10
3,10
3,21
3,33
3,45
3,58
3,71
3,84
3,98
4,11
4,24
4,36
4,49
3,10
3,08
3,17
3,27
3,37
3,47
3,58
3,69
3,80
3,91
4,02
4,12
4,23
BAU
Scenario 1
3,10 3,08
3,17
3,27
3,32
3,37
3,43
3,48
3,54
3,59
3,65
3,70
3,75
Scenario 2
Table 8-10 shows the split of benefits of the proposed scenarios by year 2020, the year of present EU
targets, among the categories.
Table 8-10: Benefits on total electricity consumption of products on the scope only (excluding CCV)
Yearly
Energy
Consum
ption
(GWh)
Product type BAU
local
1030
ventilation in
2020
2980
hoods in
2020
Yearly
Energy Yearly
Consum Energy
ption Consum
(GWh) ption
Label+ (GWh)
MEPS@ MEPS@
FL
PL
Yearly
Energy
Consum
ption
(GWh)
BAT
Energy
Savings
Savings Energy
in
Savings
Savings
in GWh Savings Energy MtCO2
in
for
for
in
in GWh Savings
MtCO2
Label+
for
in GWh Label+
for
MtCO2
MEPS@ MEPS@ for MEPS@ MEPS@ for
FL
BAT
FL
BAT
PL
PL
980
890
860
50
140
170
0,02
0,06
0,07
2880
2720
2680
100
260
300
0,04
0,11
0,13
6430
central
ventilation in
2020
5960
5120
4880
470
1310
1550
0,20
0,56
0,67
10440
9820
8730
8420 620
Total of
all
categories
1710
2020
0,27
0,74
0,87
152
Sensitivity Analysis
Many factors can influence the results. One can consider varying raw materials and electricity prices
and other relevant macro economic variables together consistently with the trends observed up to year
2007. However the LLCC found are robust to these variables.
An increase by 50% of both the electricity and materials price then a decrease by 33% were simulated
and compared with the reference used in all EuP studies. It resulted in LCC curves of figure 8.6,
showing how robust the minimum is. The study assumes that the consumers would pay completely the
improvements at the present cost, and one can expect that the over cost will decrease and the
improvements become more profitable when industrial R&D focuses on the problem
Figure 8-5: Comparison of the average EEI PL values and energy consumption of products showing
some consistency and leaving room for two classes of grading under average
153
1400
1200
1000
800
LCC
standard
50%
-33%
600
400
200
0
0%
10%
20%
30%
40%
50%
60%
70%
reduction
The basic data on the market are uncertain since no market study was pre existing to the present study.
The best data from the manufacturers associations of some MS have still a margin of uncertainty of
20% but it is the best available data approved by the study team and by all stakeholders. The study
mentioned strong uncertainties in PRODCOM reporting. If we use the estimate we mentioned at that
time of +- 20%, electrical consumption in 2020 in the scope is between 8.3 and 12.5 TWh and the
savings possible with the policy between 1.6 and 2.4 TWh.
The projections made are conservative and subject to uncertainty. The central question is: to what
extent are building regulations (e.g. developed under the Performance of Buildings Directive) leading
to forced ventilation as a practical obligation in residences? This information will decide on the future
market trends: either a stable evolution of the existing market or a rapid market change in the direction
of centralised extraction. This uncertainty is not legal (since EPBD is enforced) but largely practical:
thermal regulations for buildings generally open various ways of compliance; forced ventilation with a
certain quality may be part of the less costly package of solutions to comply with the codes in one
country and not in another country. Other uncertainties are related to the part of EPBD demanding
energy efficiency improvements in case of building retrofit and the demand of the end user for more
comfort in air quality. It is proposed that these uncertainties be addressed in the revision of the
proposed requirements in five years from entry into force of these requirements.
For all intermittent local fans (either hoods or not) the duration of use is largely uncertain.
8.6
All the products in the scope should have their performance reported in a way allowing that shows the
benefits of BAT. The procedure is based on test conditions in accordance EN 13141-4 test standard,
except kitchen hoods for which CEI/IEC 61 591 : 2005 test standard is used. The hoods are identified
as such by the manufacturer but for the other products the manufacturer or the laboratory has to
determine if the product belongs to Local ventilation (when there is only one spigot for air suction)
or Central ventilation (multiple spigots) before starting the test. The sections of EN 13141
concerning the two categories are very distinct and an exact reference to the test standard section in
the product documentation avoids mixing products of the two categories. However, a manufacturer
154
26
The standard uses the total (dynamic) pressure, not the static one; we are doing the same.
155
100%
75%
50%
25%
Frequency of this
situation Fi
10,00%
20,00%
30,00%
40,00%
156
157
158
159
160
References
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Radgen, 2007,
Promotelec, 2006,
Cory, W.T.W., 1992: Short History of Mechanical Fans and the Measurement of their Noise. CETIM
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SAP, 2005, - Appendix Q was put in place in 2005, on behalf of the Energy Saving trust
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NF-E-51-706
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(ADEME, 2007)
(SAP, 2006) two installation guides: Standard Assessment Procedure 2005 Appendix Q MEV
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R6-Technical Analysis BAT
AMCA, 1990: Fans and System. Air Movement and Control Association International,
162