RU2595583C1 - Ventilation plant with forced drying and evaporation cooling system - Google Patents

Abstract

FIELD: ventilation.

SUBSTANCE: invention relates to ventilation units. Ventilation plant includes plenum chamber and exhaust chamber of air removed from room separated by horizontal partition with main and additional openings, plenum air cooler, which is made in form of drying and evaporation cooling system, consisting of two rotary recuperators, recuperator-dehydrator and recuperator-cooler, and two adiabatic humidifiers with feed water pipeline, one of which is placed in plenum chamber at recuperator cooler output. Recuperator-dehydrator is composed of adsorption type rotary regenerator, which is built in main opening and has opposed directed suction and exhaust lines, and recuperator-cooler is in form of rotary heat exchanger with inverter and controller built in additional partition window and has external air inflow line. Plenum and exhaust chambers have inlet and outlet branch pipes, air cleaners installed at inlets to plenum and exhaust chambers, and fan units installed at output from chambers. Ventilation plant is equipped with additional exhaust chamber arranged above horizontal partition and divided from main exhaust air chamber by vertical partition, tightly installed between recuperator-dryer and recuperative heat exchanger-cooler, and containing main and additional inlet branch pipes, outlet branch pipe, air cleaner and fan unit, wherein second adiabatic humidifier is arranged in additional exhaust chamber between air cleaner and recuperative heat exchanger-cooler. Outlet branch pipe of extra exhaust chamber is arranged on upper side of chamber above fan unit to form additional exhaust line passing through recuperator-cooler and having opposite to inflow line direction. Ventilation plant is additionally equipped with waste exhaust air recirculating air duct. Outlet branch pipe of main exhaust chamber is equipped with distributing T-pipe on direct output of which there is normally open air valve, and on side output of distributing T-pipe is controlled normally closed air valve, main inlet branch pipe of extra exhaust chamber is equipped with normally-open air valve, and additional inlet branch pipe of extra exhaust chamber is with branch with turning angle 90°. Controlled air valve side outlet of distributing T-pipe and branch pipe of additional inlet branch of additional exhaust chamber are connected to waste exhaust air recirculating air duct to allow connection of end of main line with beginning of additional exhaust line.

EFFECT: broader functional capabilities of ventilation and zero power consumption for cooling and heating of plenum air.

1 cl, 12 tbl, 7 dwg

Description

Ventilation unit with forced dehumidification and evaporative cooling system

The claimed solution relates to the field of ventilation systems serving the production facilities of foundries. Air handling units use exhaust air taken from the upper zone of induction furnaces through an exhaust hood and a cooled air duct, and having an outlet temperature _tout = 60 ° C and a moisture content of _dout = 0. In the cold season, the ventilation units provide heat recovery of the exhaust air, heating and humidification of the supply air to the set temperature and relative humidity, and in the warm season, cooling to the set temperature and relative humidity.

The claimed solution can be used in engineering factories, light, medium and heavy machinery with foundries, and foundries of the military-industrial complex located in climatic regions, as with low negative outside temperatures up to (-26 ° C) in cold weather. the period of the year, and with outdoor temperatures up to (+ 30 ° C) in the warm season.

From the sources of scientific, technical and patent information, a large number of modifications of ventilation units are known. Among these selected plants with drainage and evaporative cooling of air, having limited functionality, allowing serve industrial premises with exhaust air temperature t _stretching no more than 30 ° C and to the air handling unit only in the warm season cooling supply air to 19 ° C, provides the possibility of their improvement in the direction indicated in the claims of the claimed solution.

A known schematic diagram of a ventilation installation that implements the DEC cooling technology described in the article by N.V. Shilkin “Climate Center Klimahaus in Bremerhaven”, which was published in the journal “AVOK” No. 2, 2012, p. 84-93, and on the Internet at http://www.abok.ru/for_spec/articles.php?nid=5181, adopted as a prototype. Schematic diagram of the ventilation installation of the prototype is attached.

(в долях ед.).The ventilation unit prototype consists of a supply and exhaust chambers separated by a horizontal intermediate partition with two windows, a supply air cooler made in the form of a dehumidification and evaporative cooling system - Desiccative and Evaporative Cooling (DEC), consisting of two rotary recuperators (recuperator - dehumidifier and supply air recuperator-cooler), built into the windows of the horizontal intermediate partition, and having opposite directions of the exhaust and inflow regenerative revatelya exhaust air disposed between rotating heat exchanger, and two adiabatic humidifier exhaust and supply air to the feed water supply, air intake and exhaust chambers contain air cleaners mounted on a chamber inlet, and fan units are installed on the outlet of the chambers. The supply pipelines of demineralized water to adiabatic humidifiers are not shown in the schematic diagram of the ventilation unit. In this case, the supply air recuperator-dryer is made by a rotary adsorption-type regenerator, and the supply air recuperator-cooler is made by a rotary heat exchanger. The inverter and controller to the electric drive of the rotary recuperator-cooler are not shown in the circuit diagram of the ventilation unit. An adiabatic extract air humidifier is installed at the inlet to the rotary regenerator, and an adiabatic extract air humidifier is installed at the outlet of the rotor regenerator. The adsorption type rotary regenerator has cells of the rotor storage matrix coated with a composite material into which the active Selicagel is embedded, which is a sorbent of moisture contained in the outside air. In this case, the storage matrix of the adsorption rotor is heated by the flow of exhaust air. The supply air passing through the heated cells of the adsorption rotor is heated in them and simultaneously dried by adsorption of the moisture contained in it. When the adsorption rotor is rotated, the cells of the storage matrix, the sorbing surface of which is filled with moisture, enter the drawing zone. In this case, the heated stream of exhaust air, passing through the cells of the accumulating rotor matrix, desorbs the moisture contained in them, and in relation to the sorbent - its regeneration, while moistening, after which it is emitted into the atmosphere by the exhaust fan unit. The process of heating and drying the supply air is carried out with a dry energy efficiency of a rotary heat exchanger-dryer, equal to

(in units).

, что обеспечивает увеличение фактического перепада температур на выходах из роторного регенератора:A rotary recuperator-cooler cools the supply air at a constant moisture content. The heat removed by the accumulating matrix of the rotary heat exchanger from the supply air is transferred when the rotor is rotated to the exhaust air. The adiabatic extract air humidifier provides adiabatic cooling of the extract air by ~ 6 ° C, and is designed to increase the temperature difference at the inlets to the rotary regenerator

that provides an increase in the actual temperature difference at the exits from the rotary regenerator:

- for supply air cooling Δt _okhl , ° С;

- by heating the exhaust air _LOAD Δt, ° C.

Moreover, in the warm season

- сухая энергетическая эффективность роторного регенератора,

(в долях ед.)where -

- dry energy efficiency of a rotary regenerator,

(in units)

The article discusses the supply air cooling mode, which, in accordance with the given process schedule in the id diagram, is carried out at constant values of the outdoor temperature t ₁ = 31 ° C and exhaust air t ₅ = 25 ° C, having a moisture content of d ₁ = 11.9 g / kg dry air and d ₅ = 10.3 g / kg dry. air

The DEC cooling system used in the prototype ventilation installation provides, at t ₁ = 31 ° C and t ₅ = 25 ° C, the set values of the supply air temperature t ₄ = 19 ° C and relative humidity φ ₄ = 60%.

The indicated parameters of the supply air (t ₄ = 19 ° C and φ ₄ = 60%) at specified outdoor temperatures t ₁ = 31 ° C and t ₅ = 25 ° C of exhaust air having a moisture content of d ₁ = 11.9 and d ₅ = 10.3 g / kg dry air The article proposes to carry out:

1) with indirect cooling of the supply and exhaust air by adiabatic humidifiers to a temperature difference Δt _ochl = 6 ° C, which provides temperatures:

- exhaust air at the inlet to the supply air recuperator-cooler

- supply air at the outlet of the recuperator-cooler

и рекуператора-охладителя приточного воздуха

, которые обеспечивают получение температур:2) at values of dry energy efficiency of the supply air recuperator-dryer

and supply air recuperator-cooler

that provide temperatures:

- supply air at the outlet of the recuperator-dryer:

- exhaust air at the outlet of the supply air recuperator-cooler, which simultaneously heats the exhaust air from temperature t ₆ to t ₇

- exhaust air at the outlet of the regenerative air heater

- exhaust air at the outlet of the supply air recuperator-dryer

Despite the large number of coinciding features of the prototype and the claimed solution, the lack of distinctive features of the latter in the prototype does not provide a technical result, which consists in ensuring zero energy consumption for cooling and heating the supply air at given values of the exhaust air temperature _tout = 60 ° C and moisture content d = 0:

- to a final supply air temperature t ₄ = 18 ° C and its relative humidity φ ₄ = 0.7-0.776% when the outdoor temperature changes in the range t ₁ = 11 ÷ 30 ° C;

- to the final supply air temperature t ₄ = 15 ° C and its relative humidity φ ₄ = 0.726 ÷ 0.690% when the outdoor temperature changes in the range t ₁ = 10 ÷ (-25) ° C

the following reasons:

1) the prototype ventilation unit has one exhaust line with an extract air temperature in the warm season t ₅ = 25 ° C and a moisture content of d ₅ = 10.3 g / kg dry. air, which requires for cooling the supply air in the DEC system to a final temperature t ₄ = 18 ° C at t ₁ = 11 ÷ 30 ° C and the presence of a regenerative extract air heater, that is, it does not provide zero energy consumption for cooling the supply air to warm period of the year;

2) the ventilation unit prototype has one exhaust line with the temperature of the exhaust air in the cold season t ₅ = 23 ° C and a moisture content of d ₅ = 8.77 g / kg dry. air, which requires for heating the supply air in the DEC system to a final temperature of t ₄ = 15 ° C at t ₁ = 10 ÷ (-25) ° C and the presence of an extract air heater, that is, it does not provide zero energy consumption for heating the supply air in the cold season.

According to p. 1 of the disadvantages of the ventilation installation

.The need for a regenerative air heater in the exhaust line of the prototype ventilation installation is due to the fact that the final temperature of the cooled supply air is t ₄ = 18 ° C, obtained in the ventilation installation in the warm season at t ₅ = 25 ° C and t ₁ = 11 ÷ 30 ° C, is ensured by additional heating of the exhaust air in the regenerative air heater to a temperature of t ₈ = 60 ° C, i.e. temperature difference

.

и массовому потоку сухого вытяжного воздуха

, кг/ч.In this case, the calculated power of the regenerative air heater N _V.I. , kW is directly proportional to the temperature difference for heating the exhaust air

and mass flow of dry exhaust air

kg / h

The presence of only one exhaust line in the ventilation installation-prototype with its sequential passage through the recuperator-cooler and recuperator-dryer does not allow to supply to the recuperator-dryer absolutely dry exhaust air with a temperature of t = 60 ° C and a moisture content of d = 0, which would allow outdoor air drying at t ₁ = 11 ÷ 30 ° C, entering the inflow chamber, the moisture content to the desired value providing adiabatic humidification after obtaining the final temperature of supply air t ₄ = 18 ° C, and tnositelnoy humidity φ ₄ = 0,70 ÷ 0,776% without the use of the heater exhaust air.

When supplying exhaust air with a temperature of t ₅ = 60 ° C and a moisture content of d ₅ = 0 to the exhaust line of the ventilation unit without the use of an adiabatic humidifier, the supply air is not cooled in the heat exchanger-cooler.

With adiabatic humidification of the exhaust air with a temperature of t ₅ = 60 ° C and a moisture content of d ₅ = 0, ensuring its indirect cooling to a temperature of t ₆ = 26.7 ° C, a large amount of steam and high moisture content of the exhaust air will be formed at the outlet of the humidifier d ₆ = 22.36 g / kg dry. air, which will not ensure the drying of the supply air in the heat exchanger-dryer, but will lead to excess humidification of the supply air in the range t ₁ = 11 ÷ 30 ° С.

Under paragraph 2 of the disadvantages of the ventilation installation of the prototype

.The need for a regenerative air heater in the exhaust line of the prototype ventilation installation in the cold season is due to the fact that the final temperature of the heated fresh air is t ₄ = 15 ° C, obtained in the ventilation unit at the temperature of the exhaust air t ₅ = 23 ° C and outdoor air t ₁ = 10 ÷ (-26) ° С is provided due to additional heating of the exhaust air in the regenerative heater to a temperature of t ₈ = 60 ° С, i.e. temperature difference

.

The presence of only one exhaust line in the ventilation installation-prototype with its sequential passage through the recuperator-cooler and recuperator-dryer does not allow to supply to the recuperator-dryer absolutely dry exhaust air with a temperature of t = 60 ° C and a moisture content of d = 0, which would allow drying of the outdoor air at t ₁ = 10 ÷ (-26) ° С entering the supply chamber to the required moisture content, which ensures after its adiabatic moistening the final supply air temperature t ₄ = 15 ° С and relative humidity φ ₄ = 0.726 ÷ 0.69% without the use of an extract air heater.

The task of creating a ventilation installation with a forced system of dehumidification and evaporative cooling - Desiccative Evaporative Cooling (DEC), which provides energy-saving modes of cooling and heating the supply air to the specified temperature and relative humidity in the production rooms of the foundries, the implementation of which the claimed solution is directed, consisted in the future improvement of the known design of an air handling unit with a DEC supply air cooling system, and obtaining technical The second result is the provision of zero energy consumption in the air conditioner at the exhaust air temperature t ₅ = 60 ° С and moisture content d ₅ = 0:

- to cool the supply air to a final temperature t ₄ = 18 ° C and its relative humidity φ ₄ = 0.7 ÷ 0.776 when the outside temperature changes in the range t ₁ = 11 ÷ 30 ° C;

- for heating the supply air to a final supply air temperature t ₄ = 15 ° C and its relative humidity φ ₄ = 0.726 ÷ 0.69 when the outdoor temperature changes in the range t ₁ = 10 ÷ (-26) ° C.

The achievement of the above technical result is ensured by the fact that the ventilation unit with a forced system of dehumidification and evaporative cooling, comprising a supply chamber and a main exhaust chamber of the air removed from the production room, separated by a horizontal intermediate partition with the main and additional windows, the supply air cooler, made in the form systems of drainage and evaporative cooling, consisting of two rotary recuperators - recuperator - a desiccant and a recuperator-cooler, and two adiabatic air humidifiers with a supply pipe of demineralized water, one of which is placed in the supply chamber at the outlet of the recuperator-cooler, while the recuperator-dryer is made in the form of a rotary adsorber-type regenerator, which is built into the main horizontal window of the intermediate partition and has opposite directions of the external air supply and exhaust lines of the air removed from the production room, and the recuperator-cooler - in ide of a rotary heat exchanger with an inverter and a controller, which is built into an additional window of the horizontal intermediate partition and has an external air supply line, the supply and exhaust chambers contain inlet and outlet pipes, air purifiers installed at the inlets of the supply and exhaust chambers, and fan units installed on the exit of the chambers, characterized in that the ventilation unit is equipped with an additional exhaust chamber located above the horizontal intermediate partition, and is divided with the main exhaust chamber of the air removed from the production room with a vertical transverse partition sealed between the recuperator-dryer and recuperator-cooler, and containing the main and additional inlet pipes, an exhaust pipe, an air purifier and a fan unit, while the second adiabatic humidifier is placed in an additional exhaust the chamber between the air purifier and the recuperator-cooler, the inlet pipe of the main exhaust chamber is located on the top panel of the chamber between the vertical transverse partition and the air cleaner, and its outlet pipe is on the upper panel of the chamber above the fan unit, the main inlet pipe of the additional exhaust chamber is located on one end panel with the outlet pipe of the supply chamber, the additional inlet pipe of the additional exhaust chamber is located on the upper panel of the chamber between its end panel and air cleaner, and the exhaust pipe of the additional exhaust chamber is located on the upper panel of the chamber above the fan unit with by an additional exhaust line passing through the recuperator-cooler and having a direction opposite to the inflow line, the exhaust pipe of the main exhaust chamber and the additional inlet pipe of the additional exhaust chamber are located on one longitudinal axis, which is offset from the longitudinal axis of the inlet pipe of the main exhaust chamber and exhaust pipe additional exhaust hood, in addition, the ventilation unit is additionally equipped with a recirculated exhaust duct exhaust air, the outlet pipe of the main exhaust chamber is equipped with a dispensing tee, a normally open controlled insulated multi-leaf air valve is installed at the direct outlet from it, and a normally controlled controllable air valve is installed at the lateral outlet of the distributing tee, the main inlet of the additional exhaust chamber is equipped with a controlled insulated multi-leaf normally open air valve, and an additional inlet pipe of an additional exhaust chamber - a branch with an angle of rotation 90 °, the controlled air valve of the lateral outlet of the distributing tee and the controlled insulated multi-leaf air valves are interlocked with each other, and the controlled air valve of the lateral output of the distributing tee and the outlet of the additional inlet pipe of the additional exhaust chamber are connected by a recirculating exhaust air duct, which together with the controlled insulated multi-leaf air valves and air-operated valve drawing lines with the start of an additional drawing line.

The proof of the materiality of the differences of the claimed ventilation unit and the connection of the distinguishing features with the achieved technical result is disclosed in the following order.

1. Ensuring zero energy consumption for cooling the supply air at the temperature of the exhaust air removed from the production room _tout = 60 ° C and moisture content _dout = 0 to the final temperature of the supply air t ₄ = 18 ° C and its relative humidity φ ₄ = 0, 7 ÷ 0.776% when changing the temperature of the outdoor air in the range t ₁ = 11 ÷ 30 ° C.

2. Ensuring zero energy consumption for heating the supply air in the cold season at the temperature of the exhaust air removed from the production room _tout = 60 ° C and moisture content _dout = 0 to the final supply air temperature t ₄ = 15 ° C and its relative humidity φ ₄ = 0.726 ÷ 0.69 when changing the temperature of the outdoor air in the range t ₁ = 10 ÷ (-26) ° C.

Zero energy consumption for supply air cooling at an extract air temperature _tout = 60 ° C and a moisture content of _dout = 0 to a final supply air temperature of t ₄ = 18 ° C and its relative humidity φ ₄ = 0.7 ÷ 0.776% when the outdoor temperature changes air in the range of t ₁ = 11 ÷ 30 ° C is provided by the following advantages of the proposed solution over the prototype.

The main exhaust chamber inventive ventilation installation having inlet exhaust air temperature, t _stretch = t ₈ = 60 ° C and zero water content d _draw = d ₈ = 0, provides a supply of exhaust air directly to the recuperator dehydrator without passage through heat exchanger-cooler and does not need a regenerative air heater designed in the prototype for additional heating of the exhaust air and its additional drying.

The absence in the main exhaust chamber of the inventive ventilation unit of a regenerative air heater provides zero energy consumption for cooling the supply air in the warm season.

Obtaining these advantages in the inventive ventilation installation is provided by the entire combination of essential features of the proposed solution.

The calculation of the parameters of the outdoor, supply and exhaust air to obtain the final exhaust air temperature t ₄ = 18 ° C in the warm season in the range of outdoor air temperatures t ₁ = 11 ÷ 30 ° C without the use of an exhaust air heater is given in table. one.

и

приняты по данным статьи: С.А. Панфилов,

Woods «Два колеса - Twin Wheel лучше, чем одно», опубликованной в журнале АВОК №5, 2014 г., с. 52-54 и на сайте http://www.abok.ru/for_spec/articles.php?nid=5896. Статья прилагается.In the table. 1 value calculations

and

taken according to the article: S.A. Panfilov,

Woods “Two Wheels - Twin Wheel is Better Than One,” published in ABOK Magazine No. 5, 2014, p. 52-54 and on the website http://www.abok.ru/for_spec/articles.php?nid=5896. The article is attached.

In fig. Section 2 of this article shows a schematic diagram of the existing Twin Wheel System, which shows the supply and exhaust air parameters in various zones of the ventilation unit (temperature t _i , ° С; moisture content d _i , g / kg dry air; relative humidity φ _i ,% ) when cooling the supply air to a final temperature of t ₄ = 15 ° C at an outdoor temperature of t ₁ = 32 ° C. In this case, the supply and exhaust air at the inlet and outlet of the adsorption rotor had the following parameters:

a) supply air at the inlet to the adsorption rotor:

t ₁ = 32 ° C, d ₁ = 15 g / kg dry. air .; φ ₁ = 50%;

b) exhaust air at the entrance to the adsorption rotor:

t ₆ = 19.8 ° C, d ₆ = 9.3 g / kg dry air .; φ ₆ = 64.7%;

c) supply air at the outlet of the adsorption rotor:

t ₂ = 22.7 ° C, d ₂ = 10.6 g / kg dry. air .; φ ₂ = 61.6%.

и

адсорбционного ротора

Woods по известным формулам.Based on the article S.A. For the Panfilov values of the supply air parameters at the inlet and outlet of the adsorption rotor and inlet of the exhaust air to the adsorption rotor, the energy efficiencies were calculated

and

adsorption rotor

Woods according to well-known formulas.

Woods по температуре составилаEnergy Efficiency of the Adsorption Rotor

Woods in temperature amounted to

Woods по влагосодержанию составилаEnergy Efficiency of the Adsorption Rotor

Woods moisture content amounted to

и

для адсорбционного ротора были приняты для расчета заявляемой вентиляционной установки.Values obtained

and

for the adsorption rotor were taken to calculate the inventive ventilation installation.

Zero energy consumption for heating the supply air at an extract air temperature _tout = 60 ° C and a moisture content of _dout = 0 to a final temperature of t ₄ = 15 ° C and its relative humidity φ ₄ = 0.726 ÷ 0.69 with a change in the outdoor temperature in the range t ₁ = 10 ÷ (-26) ° C is provided in the inventive ventilation installation with the following advantages:

1. The main exhaust chamber inventive ventilation system, having an exhaust inlet air temperature t = t _{8 stretch} = 60 ° C and a moisture content of zero _draw d = d ₈ = 60 ° C, provides a supply of exhaust air directly to the recuperator dehydrator without passage through heat exchanger - cooler and does not need a regenerative air heater, designed in the prototype for additional heating of the exhaust air and its additional drying.

(см. табл. 10), необходимых для получения расчетных температур приточного воздуха на выходе из рекуператора-охладителя, равных t₃=30,7÷32,1°С, обеспечивающих после адиабатического увлажнения приточного воздуха его косвенное адиабатическое охлаждение до конечной температуры t₄=15°С.2. The installation has an additional exhaust chamber, which allows, in the cold season, when the outside temperature changes in the range t ₁ = 10 ÷ 0 ° C, to supply external air with a temperature t ₅ = t ₁ = 10 ÷ 0 ° C to the additional exhaust chamber entrance to the recuperator-cooler with the adiabatic humidifier turned off, which provides technically achievable energy efficiency values for the recuperator-cooler equal to

(see table 10), necessary to obtain the calculated supply air temperatures at the outlet of the recuperator-cooler, equal to t ₃ = 30.7 ÷ 32.1 ° С, providing after adiabatic humidification of the supply air its indirect adiabatic cooling to a final temperature t ₄ = 15 ° C.

(см. табл. 10), необходимых для получения расчетных температур приточного воздуха на выходе из рекуператора-охладителя, равных t₃=32,2÷32,9°С, обеспечивающих после адиабатического увлажнения приточного воздуха его косвенное адиабатическое охлаждение до конечной температуры t₄=15°С.3. In the installation, the end of the main exhaust line is connected to the beginning of the additional exhaust line by means of a recirculated exhaust air duct. This allows in the cold season, when the outdoor temperature changes in the range t ₁ = (- 1) ÷ (-26) ° С, extract air after the heat exchanger-dryer with a temperature t ₉ = 13.5 ÷ (-5.5) ° C and feed it through a recirculation duct into an additional exhaust chamber at the entrance to the recuperator-cooler, which provides technically achievable values of the energy efficiency of the recuperator-cooler, equal to

(see table 10), necessary to obtain the calculated supply air temperatures at the outlet of the recuperator-cooler, equal to t ₃ = 32.2 ÷ 32.9 ° C, providing after adiabatic humidification of the supply air its indirect adiabatic cooling to a final temperature t ₄ = 15 ° C.

Obtaining these advantages in the inventive installation is provided by the totality of the essential features of the proposed solution.

The design of the inventive ventilation system with a forced system of dehumidification and evaporative cooling of the supply air is illustrated in the drawings in FIG. 1-7. In FIG. 1 shows a vertical projection of the installation; in FIG. 2 - view A (in Fig. 1); in FIG. 3 - a vertical projection of the installation with a horizontal intermediate partition with two windows for embedding the recuperators and a vertical transverse partition between the main exhaust and additional exhaust chambers (the projection is presented without recuperators); in FIG. 4 - section AA (in Fig. 2); in FIG. 5 is a view B (in FIG. 4); in FIG. 6 - view C (in Fig. 4); 7 is a schematic diagram of a ventilation unit with numbering of the air flow zones of the lines of the primary and secondary exhaust and supply.

In FIG. 4 and 7 arrows indicate

- основная и дополнительная линии вытяжки вентиляционной установки

- primary and secondary exhaust lines of the ventilation unit

- линия притока вентиляционной установки.

- inflow line of the ventilation unit.

In FIG. 7 zones 1-4 belong to the inflow line, zones 5-7 to the additional exhaust line, and zones 8-9 to the main exhaust line of the ventilation unit.

The ventilation installation (Fig. 4) contains a supply 1 and exhaust 2 chambers separated by a horizontal intermediate partition 3 with a main 4 and an additional 5 windows (Fig. 3), a supply air cooler 6, made in the form of a forced system of dehumidification and evaporative cooling, consisting of two rotary recuperators - a recuperator-dryer 7 and a recuperator-cooler 8, an adiabatic supply air humidifier 9 and an adiabatic extract air humidifier 10 with supply pipelines demineralization water tank 11, one of which is placed in the supply chamber 1 at the outlet of the recuperator-cooler 8. In this case, the recuperator-dryer 7 is made in the form of a rotary adsorber-type regenerator, which is built into the main window 4 of the horizontal intermediate partition 3 and has oppositely directed supply lines external air and extracts of air removed from the production room, and recuperator-cooler 8 - in the form of a rotary heat exchanger, which is built into an additional window 5 of the horizontal intermediate partition and 3 and has a line of outdoor air. The supply chamber 1 has an inlet 12 and an outlet 13 nozzles, an air cleaner 14 installed at the inlet to the chamber, and a fan unit 15 installed at the outlet of the chamber. The exhaust chamber 2 of the air removed from the production room (hereinafter referred to as the main exhaust chamber) has an inlet 16 and an outlet 17 nozzles, an air purifier 18 installed at the inlet to the chamber and a fan unit 19 installed at the outlet of the chamber.

The ventilation unit is equipped with an additional exhaust chamber 20 for external air, located above the horizontal intermediate partition 3 and divided with the main exhaust chamber 2 of the vertical transverse partition 21 removed from the production room, sealed between the heat exchanger-dryer 7 and heat exchanger-cooler 8. Additional exhaust chamber 20 contains inlet 22, additional inlet 23 and outlet 24 nozzles, an air purifier 25 and a fan unit 26. In this case, the input cartridge ubock 16 of the main exhaust chamber 2 is placed on its upper panel 27 between the vertical transverse partition 21 and the air cleaner 18 of the main exhaust chamber 2, and its outlet pipe 17 is on the upper panel 27 above the fan unit 19. The main inlet pipe 22 of the additional exhaust chamber 20 is located on one end panel 29 with an outlet pipe 13 of the supply chamber 1, an additional inlet pipe 23 of an additional exhaust chamber 20 is placed on the top panel 28 of the chamber 20 between its end panel 29 and the air cleaner 25, and the outlet second nozzle 24 further exhaust chamber 20 - of the top panel 28, the chamber 20 above the fan unit 26.

The specified location of the main inlet 22 and outlet 24 nozzles in the additional exhaust chamber 20 provides the formation of an additional line for extracting external air through the recuperator-cooler 8, having the opposite direction with the inflow line. The exhaust pipe 17 of the main exhaust chamber 2 and the additional inlet pipe 23 of the additional exhaust chamber 20 are located on one longitudinal axis that is offset from the longitudinal axis of the inlet pipe 16 of the main exhaust chamber 2 and the exhaust pipe 24 with an additional exhaust chamber 20.

In addition, the ventilation unit is additionally equipped with a recirculated exhaust air duct 30, the exhaust pipe 17 of the main exhaust chamber 2 is equipped with a distribution tee 31, at the direct outlet of which a controlled normally open insulated multi-leaf air valve 32 is installed, and at the lateral output of the distribution tee 31 it is controlled normally closed air valve 33. The main inlet pipe 22 of the additional exhaust chamber 20 is provided with a controlled, insulated multi-leaf normally open air valve 34, and an additional inlet pipe 23 of an additional exhaust chamber 20 - by branch 35 with a rotation angle of 90 °. The controlled air valve 33 of the lateral outlet of the distributing tee 31 and the controlled insulated multi-leaf air valves 32 and 34 with are blocked between each other, and the controlled air valve 33 of the lateral outlet of the distributing tee 31 and the outlet 35 of the additional inlet pipe 23 of the additional exhaust chamber 20 are connected by a recirculating exhaust 30 of the exhaust exhaust air, which together with the controlled insulated multi-leaf air valves 32 and 34 and the controlled air valve 33, allows inenia of the end of the main exhaust line with the beginning of the additional exhaust line, and allowing the heat of exhaust exhaust air to be reused at the outlet of the heat exchanger-dryer 7 in the additional exhaust chamber 20 to be fed to the heat exchanger-cooler 8 in the cold season at an outdoor temperature that varies in the range t ₁ = (- 1) ÷ (-25) ° С. The second adiabatic extract air humidifier 10 is installed in an additional exhaust chamber 20 between the air purifier 25 and the recuperator-cooler 8. The rotary recuperator-cooler 8 is equipped with an inverter and a controller (not shown in Fig.).

To service the ventilation unit during its operation, the unit is equipped with eight service doors: service door 37 for the heat exchanger-dryer, service door 38 for the heat exchanger-cooler, service door 39 for the air cleaner of the main exhaust chamber, service door 40 for the fan unit of the main exhaust chamber; service door 41 for the air purifier of the supply chamber, service door 42 for the adiabatic humidifier and supply unit fan unit, service door 43 for the air purifier and adiabatic humidifier of the auxiliary exhaust chamber, service door 44 for the fan unit of the additional exhaust chamber.

The inventive fan installation can operate in five modes.

Mode 1. Air conditioning in the warm season with cooling of the supply air in the forced system of dehumidification and evaporative cooling of the fan unit to a final supply air temperature t ₄ = 18 ° C and relative humidity φ ₄ = 0.7 ÷ 0.758 in the range of outdoor temperature t ₁ = 11 ÷ 27 ° C at an extract air temperature of t ₈ = 60 ° C and a moisture content of d ₈ = 0 without using an adiabatic humidifier in an additional exhaust chamber.

Mode 2. Air conditioning in the warm season with fresh air cooling in the forced system of dehumidification and evaporative cooling of the ventilation unit to a final fresh air temperature t ₄ = 18 ° C and relative humidity φ ₄ = 0.763 ÷ 0.776 in the range of outdoor temperature t ₁ = 28 ÷ 30 ° C at an extract air temperature of t ₈ = 60 ° C and a moisture content of d ₈ = 0 using an adiabatic humidifier in an additional exhaust chamber.

Mode 3. Air conditioning in the cold season with heating of the supply air in the forced system of dehumidification and evaporative cooling of the ventilation unit to a final supply air temperature t ₄ = 15 ° C and relative humidity φ ₄ = 0.726 ÷ 0.707 in the range of outdoor temperature t ₁ = 10 ÷ 0 ° С at an extract air temperature of t ₈ = 60 ° С and a moisture content of d ₈ = 0 without using an adiabatic humidifier in an additional exhaust chamber.

Mode 4. Air conditioning in the cold season with heating of the supply air in the forced system of dehumidification and evaporative cooling of the ventilation unit to a final supply air temperature of t ₄ = 15 ° C and relative humidity φ ₄ = 0.707 ÷ 0.69 in the range of outdoor temperature t ₁ = (- 1) ÷ (-25) ° С at an extract air temperature t ₈ = 60 ° С and moisture content d ₈ = 0 without using an adiabatic humidifier in an additional exhaust chamber, but using a recirculated exhaust duct of bright air.

Mode 5. Standby.

All five modes are set on the control panel.

ротора в соответствии с изменением температуры наружного воздуха t₁ на каждый °С в диапазоне t₁, соответствующем номеру режима:The ventilation unit in modes 1-2 works as follows. There are three fan units 15, 19 and 26 of the supply chamber 1, the main exhaust 2 and the additional exhaust 20 chambers, the electric drive of the rotary recuperator-dryer 7 at a constant rotational speed of the adsorption rotor. An electric drive of a rotary recuperator-cooler 8 with an inverter and a controller (not indicated in the drawings) and an adiabatic supply air humidifier 9 with an inverter and a controller (not indicated in the drawings). In this case, the controlled insulated air valves 32 and 34 are open, and the controlled air valve 33 is closed. Fan blocks 15, 19 and 26 operate at 100% performance. The controller with the inverter of the rotary recuperator-cooler 8 individually controls the rotational speed of the electric motor of the drive of the rotary recuperator 8, providing a change in dry energy efficiency

rotor in accordance with a change in outdoor temperature t ₁ for every ° C in the range t ₁ corresponding to the mode number:

- mode 1 t ₁ = 11 ÷ 27 ° C;

- mode 2 t ₁ = 28 ÷ 30 ° C.

In mode 2, the adiabatic humidifier 10 is turned on.

и

, t₂, t₃ и t₆, рассчитанные для режимов 1-2 для диапазона изменения температур t₁=11÷30°С с шагом в 1°С, приведены в табл. 2.Values

and

, t ₂ , t ₃ and t ₆ , calculated for modes 1-2 for the temperature range t ₁ = 11 ÷ 30 ° C in increments of 1 ° C, are given in table. 2.

The adiabatic humidifier of the supply air 9 operates in the range of outdoor temperatures t ₁ = 11 ÷ 30 ° C with a variable capacity G _yв , kg / h, provided by an inverter with a controller, and calculated by the formula (53).

Consider the operation of the main exhaust line of the inventive ventilation unit in modes 1-2.

The air removed from the production room with a temperature of t ₈ = 60 ° C and a moisture content of d ₈ = 0 enters through the inlet pipe 16 of the main exhaust chamber 2 into the chamber, is drawn by the fan unit 19 through the air cleaner 18 and the adsorption heat exchanger-dryer 7, and then through the exhaust pipe 17 is thrown into the distributing tee 31 with a temperature of t ₉ , ° C, a moisture content of d ₉ , g / kg dry. air and relative humidity φ ₉ (in fractions of units), determined by the formulas

- эффективность рекуператора-осушителя 7 по влагосодержанию

Where

- the efficiency of the heat exchanger-desiccant 7

where P _n9 , P _p9 are the partial pressures of saturated and unsaturated water vapor, Pa.

The values of the parameters t ₉ , d ₉ , P _n9 , P _p9 and φ ₉ for t ₁ = 11 ÷ 30 ° C in increments of one ° C are given in table. 3.

From the dispensing tee 31, exhaust air when the air valve 33 is closed is discharged through the open air valve 32 into the atmosphere.

Consider the operation of an additional line for extracting outdoor air of the inventive ventilation unit in modes 1-2

An additional exhaust chamber 20 is designed to supply external air to its main inlet pipe 22, which has a lower temperature t ₅ = t ₁ = 11 ÷ 30 ° C during the warm season than temperature t ₅ = 60 ° C, which occurs in the air conditioner prototype.

на входах в рекуператор-охладитель 8, и как следствие, охлаждение приточного воздуха до расчетного значения температуры t₃=37,4÷33,2°С на выходе из рекуператора-охладителя 8 без применения адиабатического увлажнителя 10 вытяжного наружного воздуха в дополнительной вытяжной камере 20.This allows you to provide at t ₁ = 11 ÷ 27 ° C, t ₂ = 48.3 ÷ 52.1 ° C the required temperature difference

at the inlet to the recuperator-cooler 8, and as a result, cooling of the supply air to the calculated temperature t ₃ = 37.4 ÷ 33.2 ° С at the outlet of the recuperator-cooler 8 without the use of an adiabatic humidifier 10 of the extract air in the additional exhaust chamber twenty.

When the outdoor temperature varies in the range t ₁ = 28 ÷ 30 ° C, the adiabatic humidifier 10 of the additional exhaust chamber 20 is activated.

External air is drawn in an additional exhaust chamber 20 by a fan unit 26 through an air cleaner 25 and is supplied to a heat exchanger-cooler 8:

a) at an outdoor temperature that varies in the range t ₁ = 11 ÷ 27 ° C and an idle adiabatic humidifier 10 with a temperature t ₆ = t ₁ ;

(где

- величина косвенного адиабатического охлаждения вытяжного наружного воздуха, обеспечиваемая адиабатическим увлажнением. Определяется по формуле (28) табл. 1.b) at an outdoor temperature that varies in the range t ₁ = 28 ÷ 30 ° C and a working adiabatic humidifier 10 with a temperature

(Where

- the value of indirect adiabatic cooling of the exhaust outdoor air provided by adiabatic humidification. It is determined by the formula (28) of the table. one.

After the exhaust air passes through the recuperator-cooler 8, the exhaust air is emitted by the fan unit 26 through the exhaust pipe 24 of the additional exhaust chamber 20 into the atmosphere.

The temperature at the outlet of the exhaust air recuperator-cooler 8 t ₇ , its moisture content d ₇ and relative humidity φ _{7 are} determined by the following formulas:

where R _n7 , R _p7 - partial pressure of saturated and unsaturated water vapor, Pa. The values of P _{n7 are} determined by reference tables on temperature t ₇ .

The values of P _{p7 are} determined by the formula 40

where P _p1 is the partial pressure of unsaturated water vapor, Pa.

It is determined by the formula (2) of the table. one.

where P _bar - barometric pressure, Pa, P _bar = 101000 Pa, adopted for the climatic conditions of St. Petersburg.

The values of the parameters t ₇ , d ₇ , P _p7 and φ ₇ calculated for the range t ₁ = 11 ÷ 30 ° C in increments of one ° C are given in table. four.

Consider the operation of the inflow line of the inventive ventilation unit in modes 1-2

The line of outdoor air inflow during the warm season when working together with the main exhaust line and the additional exhaust line at an air temperature t ₈ = 60 ° C removed from the production room and its moisture content d ₈ = 0 ensures the supply air is cooled to the specified values of the final temperature t ₄ in accordance with the number of operation mode of the air conditioner.

- mode 1 (t ₄ = 18 ° C and φ ₄ = 0.7 ÷ 0.758 in the range t ₁ = 11 ÷ 27 ° C);

- mode 2 (t ₄ = 18 ° C and φ ₄ = 0.763 ÷ 0.776 in the range t ₁ = 28 ÷ 30 ° C).

Outside air is drawn through the inlet pipe 12 by the fan unit 15 into the supply chamber 1, in which the air to be processed passes sequentially through the air purifier 14, the recuperator-dryer 7, the recuperator-cooler 8 and the adiabatic humidifier of the supply air 9, after which it is supplied through the outlet pipe 13 to the air distributor (not indicated on the drawings) located in the production room.

Woods, который имеет постоянную частоту вращения, обеспечивающую получение двух энергетических эффективностей:The recuperator-dryer 7 is equipped with an adsorption rotor

Woods, which has a constant rotational speed, providing two energy efficiency:

;- energy efficiency in temperature equal to

;

.- energy efficiency in moisture content equal to

.

и

обеспечивают при изменении температуры наружного воздуха в диапазоне t₁=11÷30°С и его влагосодержании в диапазоне d₁=5,87÷19,41 г/кг сух. возд. на выходе из рекуператора осушителя повышение температуры приточного воздуха до значения t₂ и уменьшение влагосодержания до значения d₂, которые при t₈=60°С и d₈=0 определяются по формуламIndicated Values

and

provide when the outside temperature changes in the range t ₁ = 11 ÷ 30 ° C and its moisture content in the range d ₁ = 5.87 ÷ 19.41 g / kg dry. air at the outlet of the desiccant recuperator, an increase in the supply air temperature to a value of t ₂ and a decrease in moisture content to a value of d ₂ , which at t ₈ = 60 ° C and d ₈ = 0 are determined by the formulas

The relative humidity of the supply air at the outlet of the recuperator-dryer 7 is determined by the formula

where P _H2, P _n2 - the partial pressures of saturated and unsaturated steam, Pa.

The values of P _{n2 are} determined by reference tables for t ₂ , the values of P _{p2 are} determined by the formula

The temperature values t ₂ calculated by the formula (8) for the range t ₁ = 11 ÷ 30 ° C are given in table. 2.

The values of the parameters d ₂ , P _p2 and φ ₂ calculated for the range t ₁ = 11 ÷ 30 ° C in increments of one ° C are given in table. 5.

Supply air cooling in the heat exchanger-cooler 8 from temperature t ₂ to temperature t ₃ according to the id diagram is carried out at a constant moisture content d ₃ = d ₂ for each given value of the outdoor temperature t ₁ . The value of d ₃ increases with increasing temperature t ₁ . The supply air temperature t ₃ at the outlet of the recuperator-cooler 8 is a variable value, which depends on the moisture content d ₃ and a given final cooling temperature t ₄ .

Supply air cooling in the range of outdoor temperatures t ₁ = 11 ÷ 30 ° C is provided by two operating modes of the ventilation unit, in which the final temperature of the cooled supply air t ₄ is set by the designer, and its implementation is checked by the formula

- величина косвенного адиабатического охлаждения приточного воздуха, обеспечиваемого адиабатическим охлаждением воздухаWhere

- the value of indirect adiabatic cooling of the supply air provided by adiabatic air cooling

where t _m3 is the temperature according to the wet supply air thermometer at the outlet of the heat exchanger-cooler 8. It is determined by the formula (9) of the table. one; E is the efficiency of the adiabatic humidifier for air cooling, E = 0.85.

Temperature t _{3 is} determined on the basis of a joint solution of 3 equations (43) ÷ (45):

получимWe make the replacement in (47)

we get

Equating (46) and (48) and solving a system of 2 equations with respect to t _m3 , we obtain the temperature using a wet thermometer

. Коэффициент K_м3 имеет индивидуальные значения в каждом режиме работы кондиционера, которые составляют:K _m3 - coefficient characterizing the number of t _m3 values in the specific enthalpy of saturated air

. The coefficient K _m3 has unique values in each operation mode, which are:

- for mode 1 (t ₁ = 11 ÷ 27 ° С, t ₄ = 18 ° С) K _m3 = 2,807

- for mode 2 (t ₁ = 28 ÷ 30 ° С, t ₄ = 20 ° С) K _m3 = 2.82.

, i₃, t₃,

и t₄, рассчитанные для диапазона t₁=11÷27°С в двух режимах заявляемой вентиляционной установки, приведены в табл. 6.The values of the parameters t _m3 , d _n3 ,

, i ₃ , t ₃ ,

and t ₄ calculated for the range t ₁ = 11 ÷ 27 ° C in two modes of the inventive ventilation unit are shown in table. 6.

, которые обеспечиваются инвертором с контроллером и определяются с шагом в один °С по формуле (30) табл. 1:Maintenance of the supply air temperature t ₃ obtained by the formula (48) at the outlet of the heat exchanger-cooler 8 is carried out by controlling the values of the dry energy efficiency of the heat exchanger-cooler

, which are provided by an inverter with a controller and are determined in increments of one ° C according to the formula (30) of the table. one:

In this case, obtaining temperature values of 7 _{3 is} checked from the expression

, рассчитанные для диапазона t₁=11÷27°С, при изменении t₁ с шагом в один °С, приведены в табл. 2.Values

calculated for the range t ₁ = 11 ÷ 27 ° C, when t ₁ changes in increments of one ° C, are given in table. 2.

The moisture content of the supply air at the outlet of the recuperator-cooler 8 d _{3 was} determined from the condition

The relative humidity of the supply air at the outlet of the heat exchanger-cooler 8 at a temperature of t ₃ is determined from the expression

where R _n3 , R _p3 - partial pressure of saturated and unsaturated water vapor, Pa. The values of P _{n3 are} determined for t ₃ according to the reference tables. The values of P _{p3 are} determined from the expression

The values of d ₃ , t ₃ , P _n3 , P _p3 and φ ₃ calculated for the temperature range t ₁ = 11 ÷ 30 ° C and modes 1-2 of the inventive ventilation unit are given in table. 7.

After passing through the recuperator-cooler 8, the supply air enters the adiabatic humidifier 9, which provides indirect adiabatic cooling of the supply air by an amount determined from expression (13) of the table. one

where E is the effectiveness of the adiabatic humidifier; E = 0.85.

The adiabatic humidifier of the supply air 9 operates with a variable capacity of the water pump G _SW , kg / h, provided by the inverter and calculated by the formula

- массовый поток сухого приточного воздуха, кг/ч; Δd_i - перепад влагосодержания приточного воздуха, обеспечиваемый адиабатическим увлажнителем при изменении температуры наружного воздуха с шагом в один °С в диапазоне изменения температуры наружного воздуха t₁=11÷30°С; d₃, d₄ - влагосодержание приточного воздуха на выходе из рекуператора-охладителя и после адиабатического увлажнителя, г/кг сух. возд.; 10^-3 - коэффициент перевода граммов в килограммы.Where

- mass flow of dry supply air, kg / h; Δd _i - difference in moisture content of the supply air provided by adiabatic humidifier when the outdoor temperature is changed in increments of one ° C in the range of outdoor temperature changes t ₁ = 11 ÷ 30 ° C; d ₃ , d ₄ - moisture content of the supply air at the outlet of the heat exchanger-cooler and after an adiabatic humidifier, g / kg dry. air .; 10 ^-3 is the conversion rate of grams to kilograms.

In addition to the frequency control of the water pump performance when using a humi Fog humidifier, an on / off system of solenoid valves is connected, which connects up to three additional spray circuits with nozzles to one main circuit that is constantly on. In general, humi Fog atomizers, in the presence of the full composition of the spray circuits (4 pcs.), Provide a change in the amount of water supplied to the nozzles in the range of 20-100% of the nominal capacity.

The values of Δd _i calculated for modes 1-2 for the temperature range t ₁ = 11 ÷ 30 ° C in increments of 1 ° C are given in table. 8.

In order to get a clear picture of changes in air parameters in zones 1–9 of the supply lines, the main and additional exhaust of the forced DEC system of the inventive ventilation unit in modes 1-2 of supply air cooling, all calculated values of the parameters t _i , φ _i , d _i and i _i are summarized in table. 9.

Air handling unit operation in modes 3 and 4

The ventilation unit in modes 3 and 4 works as follows. There are three fan units 15, 19 and 26 of the supply chamber 1, the main exhaust 2 and the additional exhaust 20 chambers, an electric drive of an adsorption rotary heat exchanger-dryer 7 at a constant rotor speed, an electric drive of a rotary heat exchanger-cooler 8 with an inverter and a controller (not shown in the drawings ) and an adiabatic supply air humidifier 9 with an inverter and a controller (not shown in the drawings). Fan blocks 15, 19 and 26 operate at 100% performance.

In mode 3, the controlled warm air valves 32, 34 and 36 are open, and the controlled air valve 33 is closed. In mode 4, the controlled warm air valves 32 and 34 are closed, and the controlled air valve 33 and the warmed air valve 36 are open.

In modes 3 and 4, the adiabatic extract air humidifier 10 does not work.

в соответствии с изменением температуры наружного воздуха t₁ на каждый °С в диапазоне t₁, соответствующем номеру режима:The controller with the inverter of the rotary recuperator-cooler 8 individually controls the frequency of rotation of the electric motor of the drive of the rotary recuperator 8, providing a change in the dry energy efficiency of the rotor

in accordance with the change in the outdoor temperature t ₁ for each ° C in the range t ₁ corresponding to the mode number:

- mode 3 = ₁ t 0 ÷ 10 ° C;

- mode 4 t ₁ = (- 1) ÷ (-25) ° C;

, рассчитанные для диапазона температур t₁=(10)÷(-26)°С (климатические условия Санкт-Петербурга), приведены в табл. 10.Values

calculated for the temperature range t ₁ = (10) ÷ (-26) ° С (climatic conditions of St. Petersburg) are given in table. 10.

The adiabatic humidifier of the supply air 9 operates in a range of outdoor temperatures t ₁ = 10 ÷ (-26) ° C with a variable capacity G _u , kg / h provided by the inverter and controller.

Calculation of the parameters of the outdoor, supply and exhaust air to obtain the final supply air temperature in the cold season t ₄ = 15 ° С for modes 3 and 4 at t ₈ = 60 ° С, d ₈ = 0, Р _bar = 101000 Pa (climatic conditions St. Petersburg) is given in table. 10.

In standby mode (mode 5), the electric drives of all equipment of the ventilation unit are turned off, the controlled air valves 32, 33, 34 and 36 are closed.

All of the above, including a description of the operation of the inventive ventilation unit confirms the possibility of its use in industry with obtaining high technical performance in comparison with the known designs of ventilation units. In addition, both in the sources of patent and scientific and technical information, and in industry, such a design did not occur, which indicates that the claimed invention meets all the criteria of patentability

Claims (1)

A ventilation unit with a forced system of dehumidification and evaporative cooling, containing a supply chamber and a main exhaust chamber of air removed from the production room, separated by a horizontal intermediate partition with main and additional windows, a supply air cooler made in the form of a dehumidification and evaporative cooling system, consisting of two rotary recuperators - recuperator-dryer and recuperator-cooler, and two adiabatic humidifiers in spirit with a supply pipe of demineralized water, one of which is placed in the supply chamber at the outlet of the recuperator-cooler, while the recuperator-dryer is made in the form of a rotary adsorber-type regenerator, which is built into the main window of the horizontal intermediate partition and has oppositely directed lines of outdoor air flow and extracts of air removed from the production room, and the recuperator-cooler - in the form of a rotary heat exchanger with an inverter and a controller, which is built-in an additional window of the horizontal intermediate partition and has a line of external air inflow, the supply and exhaust chambers contain inlet and outlet pipes, air purifiers installed at the inlets of the supply and exhaust chambers, and fan units installed at the outlet of the chambers, characterized in that the ventilation unit is equipped additional exhaust chamber located above the horizontal intermediate partition, and divided with the main exhaust chamber removed from the production room in air with a vertical transverse partition sealed between the recuperator-dryer and recuperator-cooler, and containing the main and additional inlet pipes, exhaust pipe, air cleaner and fan unit, while the second adiabatic humidifier is placed in an additional exhaust chamber between the air cleaner and recuperator-cooler, the main exhaust pipe is located on the upper panel of the chamber between the vertical transverse partition and the air cleaner, and its inlet pipe - on the upper panel of the chamber above the fan unit, the main inlet pipe of the additional exhaust chamber is located on one end panel with the outlet pipe of the supply chamber, the additional inlet pipe of the additional exhaust chamber is located on the upper panel of the chamber between its end panel and the air cleaner, and the exhaust pipe of the additional exhaust chamber - on the upper panel of the chamber above the fan unit with the formation of an additional exhaust line passing through the heat exchanger-cooler having a direction opposite to the inflow line, the exhaust pipe of the main exhaust chamber and the additional inlet pipe of the additional exhaust chamber are located on one longitudinal axis, which is offset from the longitudinal axis of the inlet pipe of the main exhaust chamber and the exhaust pipe with an additional exhaust chamber, in addition, the ventilation unit is additionally equipped with a recirculation the exhaust air duct, the exhaust pipe of the main exhaust chamber is equipped with a supply tee, at the direct exit from which a normally open controlled insulated multi-leaf air valve is installed, and at the lateral output of the distributing tee is a controlled normally closed air valve, the main inlet pipe of the additional exhaust chamber is equipped with a controlled insulated multi-leaf normally open air valve, and an additional inlet pipe of an additional the exhaust chamber - by a branch with a rotation angle of 90 °, a controlled air valve of the lateral outlet of the distributing tee and control Autonomous heated multi-leaf air valves of the main and additional exhaust chambers are interlocked with each other, and the controlled air valve of the lateral outlet of the distributing tee and the outlet of the additional inlet pipe of the additional exhaust chamber are connected by a recirculated exhaust air duct that provides, together with the controlled heated multi-leaf air valves of the main and additional exhaust chambers and air-operated valve novnoy line drawing with the beginning of more line-drawing.

Images