Nothing Special   »   [go: up one dir, main page]

WO2009088517A1 - Use of an adjustable expansion valve to control dehumidification - Google Patents

Use of an adjustable expansion valve to control dehumidification Download PDF

Info

Publication number
WO2009088517A1
WO2009088517A1 PCT/US2008/050832 US2008050832W WO2009088517A1 WO 2009088517 A1 WO2009088517 A1 WO 2009088517A1 US 2008050832 W US2008050832 W US 2008050832W WO 2009088517 A1 WO2009088517 A1 WO 2009088517A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
set forth
superheat
control
refrigerant system
Prior art date
Application number
PCT/US2008/050832
Other languages
French (fr)
Inventor
Alexander Lifson
Michael F. Taras
Original Assignee
Carrier Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corporation filed Critical Carrier Corporation
Priority to CN2008801248736A priority Critical patent/CN101910762A/en
Priority to PCT/US2008/050832 priority patent/WO2009088517A1/en
Priority to US12/741,392 priority patent/US20100242508A1/en
Publication of WO2009088517A1 publication Critical patent/WO2009088517A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/1405—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification in which the humidity of the air is exclusively affected by contact with the evaporator of a closed-circuit cooling system or heat pump circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • This application relates to a refrigerant system incorporating an adjustable expansion valve, and more particularly, to a refrigerant system wherein this adjustable expansion valve is controlled to achieve desired dehumidif ⁇ cation within a climate- controlled environment.
  • a typical example of such an adjustable expansion device is an electronic expansion valve.
  • Refrigerant systems are known in the HVAC&R (heating, ventilation, air conditioning and refrigeration) art, and operate to compress and circulate a refrigerant throughout a closed-loop refrigerant circuit, connecting a plurality of components, to condition a secondary fluid to be delivered to a climate-controlled space.
  • refrigerant is compressed in a compressor from a lower to a higher pressure and delivered to a heat rejection heat exchanger (condenser or gas cooler). From the heat rejection heat exchanger, where heat is typically transferred from the refrigerant to an ambient environment, a high-pressure refrigerant flows to an expansion device where it is expanded to a lower pressure and temperature and then is routed to a heat accepting heat exchanger (evaporator), where refrigerant cools a secondary fluid to be delivered to the conditioned environment. From the evaporator, refrigerant is returned to the compressor.
  • evaporator heat accepting heat exchanger
  • refrigerant is returned to the compressor.
  • refrigerant systems is an air conditioning system, which operates to condition (cool and often dehumidify) air to be delivered into a climate- controlled zone or space.
  • Refrigerant systems are utilized to provide temperature control, and often humidity control, for air supplied into an occupied environment.
  • One feature that is important to the reliable and efficient operation of a refrigerant system is the amount of superheat of the refrigerant leaving the evaporator and moving to the compressor.
  • the superheat which is defined as a difference between the actual temperature and the saturation temperature of the refrigerant, must be kept within a tight band for most efficient and reliable operation of the refrigerant system.
  • a refrigerant system operates most efficiently with the lowest safe superheat amount that can be accurately sensed and maintained over a wide range of environmental and operating conditions. For various reasons, the superheat needs to be kept several degrees above zero, and it is typically maintained in the low range from 6 to 12° F.
  • Control of the evaporator superheat has been provided for a variety of functions, however, the evaporator superheat has not been controlled to control dehumidification of the air being delivered into an environment to be conditioned.
  • a control for an electronic expansion valve achieves a desired refrigerant superheat at the evaporator exit such that the dehumidification provided by the refrigerant system to the air delivered into a conditioned environment can be controlled.
  • the "dehumidification" mode of superheat control is only entered if a reduced cooling load provided by the refrigerant system is desired.
  • various conditions for reliable operation of the refrigerant system such as discharge temperature and saturation suction temperature being within specified respective ranges, have to be satisfied while entering into the
  • Figure 1 is a schematic view of the basic refrigerant system incorporating the present invention.
  • FIG. 2 is an example of simplified flowchart of one embodiment of the present invention.
  • FIG. 1 shows a refrigerant system 20 incorporating a compressor 22 for compressing a refrigerant and delivering it downstream to a heat rejection heat exchanger 24. From the heat rejection heat exchanger 24, the refrigerant passes through an electronic expansion valve 26, and then to an evaporator 30. As shown, air moving over the evaporator 30 is delivered into an environment to be conditioned 32.
  • the environment to be conditioned 32 is provided with a control 43 that allows an occupant to select desired temperature and/or humidity levels to be provided by the air being delivered into the environment.
  • a control 28 is shown for the electronic expansion device 26.
  • transducers or other sensors 34 and 36 are shown in various locations within the refrigerant system 20. As shown, a transducer 34 is provided downstream of the compressor and may sense the pressure and/or temperature at the discharge of the compressor 22. Similarly, a sensor 36 may sense the pressure and/or temperature downstream of the evaporator 30. The sensors 34 and 36 signals are provided to the control 28. It should be noted that some of these sensors are optional and may not be required for certain system configurations.
  • Controls are known which operate to control electronic expansion devices to achieve desired superheat values downstream of the evaporator 30.
  • desired performance total capacity and efficiency
  • the evaporator superheat to low positive values, typically in the range from 6 to 12°F.
  • the inventors have recognized that by increasing superheat under certain circumstances, could lead to increased dehumidification capability of the evaporator 30 and in turn lower humidity of the air being delivered into the conditioned environment 32.
  • the present invention utilizes its control of the expansion device 26 to achieve increased dehumidification, at least under certain circumstances. It should be noted that total capacity of the evaporator 30 decreases when superheat is increased, while a simultaneous capacity shift from the sensible component to the latent component is taking place. As a result, a sensible heat ratio (the ratio of the sensible capacity to the total capacity) provided by the evaporator 30 is reduced.
  • the sensible heat ratio of the evaporator 30 can be controlled by controlling the electronic expansion valve 26 and consequently adjusting superheat at the exit of the evaporator 30. Therefore, by controlling the electronic expansion valve 26, the total evaporator capacity as well its sensible and latent components can be controlled.
  • the desired superheat range may be defined by a lower limit and a higher limit, with the lower limit restricted by a minimum value of the evaporator pressure (or saturation temperature) and the higher limit constrained by a discharge temperature threshold.
  • evaporator pressure or saturation temperature
  • discharge temperature threshold a minimum value of the evaporator pressure (or saturation temperature)
  • abnormally low evaporator pressure may cause the evaporator freeze-up and excessively high discharge temperature may lead to the compressor damage.
  • the control 28 may normally operate to achieve a desired optimal superheat in a conventional cooling mode, for instance, to provide maximum performance (capacity and efficiency) for the refrigerant system 20 to cool the air delivered to the conditioned environment 32.
  • a reduced sensible cooling load is demanded, such as, for instance, when the ambient temperature is sufficiently low or/and sensible cooling load demands in the conditioned space 32 are not significant, the control 28 enters a "dehumidification" mode of superheat control.
  • control 28 may control the expansion device 26, such that superheat is adjusted so that the capacity of the evaporator 30 is shifted from cooling to dehumidification (to lower sensible heat ratios) to reduce humidity of the air being delivered into the zone to be conditioned 32.
  • a worker of ordinary skill in the art would recognize how to control the electronic expansion device 26, given the goals of this application as described above, including maintaining the operation of the refrigerant system 20 within safety and reliability limits.
  • superheat control may be executed at the compressor suction or compressor discharge.
  • the compressor suction it can be executed at the location toward the compressor suction instead of the evaporator exit.
  • superheat control can be executed at the compressor discharge, if the relationship between suction superheat and discharge superheat is known. Further, even under circumstances when the desired humidity level cannot be precisely achieved by the evaporator superheat control, it still can be noticeably reduced towards the desired value providing a higher degree of comfort for an occupant of the conditioned space.
  • compressors could be used in this invention.
  • scroll, screw, rotary, or reciprocating compressors can be employed.
  • the refrigerant systems that utilize this invention can be used in many different applications, including, but not limited to, stationary and mobile air conditioning systems as well as heat pump systems.
  • the refrigerant system can also employ vapor injection, liquid injection, multiple circuits, as well as compressors connected in parallel in a tandem fashion.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

A refrigerant system is provided with a control for its expansion device. The control operates the expansion device to adjust the superheat of the refrigerant leaving an evaporator to have desired dehumidification for air being delivered into an environment to be conditioned.

Description

USE OF AN ADJUSTABLE EXPANSION VALVE TO CONTROL DEHUMIDIFICATION
BACKGROUND OF THE INVENTION This application relates to a refrigerant system incorporating an adjustable expansion valve, and more particularly, to a refrigerant system wherein this adjustable expansion valve is controlled to achieve desired dehumidifϊcation within a climate- controlled environment. A typical example of such an adjustable expansion device is an electronic expansion valve. Refrigerant systems are known in the HVAC&R (heating, ventilation, air conditioning and refrigeration) art, and operate to compress and circulate a refrigerant throughout a closed-loop refrigerant circuit, connecting a plurality of components, to condition a secondary fluid to be delivered to a climate-controlled space. In a basic refrigerant system, refrigerant is compressed in a compressor from a lower to a higher pressure and delivered to a heat rejection heat exchanger (condenser or gas cooler). From the heat rejection heat exchanger, where heat is typically transferred from the refrigerant to an ambient environment, a high-pressure refrigerant flows to an expansion device where it is expanded to a lower pressure and temperature and then is routed to a heat accepting heat exchanger (evaporator), where refrigerant cools a secondary fluid to be delivered to the conditioned environment. From the evaporator, refrigerant is returned to the compressor. One common example of refrigerant systems is an air conditioning system, which operates to condition (cool and often dehumidify) air to be delivered into a climate- controlled zone or space.
Refrigerant systems are utilized to provide temperature control, and often humidity control, for air supplied into an occupied environment. One feature that is important to the reliable and efficient operation of a refrigerant system is the amount of superheat of the refrigerant leaving the evaporator and moving to the compressor. Typically, the superheat, which is defined as a difference between the actual temperature and the saturation temperature of the refrigerant, must be kept within a tight band for most efficient and reliable operation of the refrigerant system. Moreover, it is also typical that for pure temperature control, a refrigerant system operates most efficiently with the lowest safe superheat amount that can be accurately sensed and maintained over a wide range of environmental and operating conditions. For various reasons, the superheat needs to be kept several degrees above zero, and it is typically maintained in the low range from 6 to 12° F.
Control of the evaporator superheat has been provided for a variety of functions, however, the evaporator superheat has not been controlled to control dehumidification of the air being delivered into an environment to be conditioned.
SUMMARY OF THE INVENTION
In a disclosed embodiment of this invention, a control for an electronic expansion valve (EXV) achieves a desired refrigerant superheat at the evaporator exit such that the dehumidification provided by the refrigerant system to the air delivered into a conditioned environment can be controlled. In one embodiment, the "dehumidification" mode of superheat control is only entered if a reduced cooling load provided by the refrigerant system is desired. In another embodiment, various conditions for reliable operation of the refrigerant system, such as discharge temperature and saturation suction temperature being within specified respective ranges, have to be satisfied while entering into the
"dehumidification" mode of superheat control or continuously operating in the
"dehumidification" mode of superheat control.
These and other features of the present invention can be best understood from the following specification and drawings, the following of which is a brief description.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 is a schematic view of the basic refrigerant system incorporating the present invention.
Figure 2 is an example of simplified flowchart of one embodiment of the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Figure 1 shows a refrigerant system 20 incorporating a compressor 22 for compressing a refrigerant and delivering it downstream to a heat rejection heat exchanger 24. From the heat rejection heat exchanger 24, the refrigerant passes through an electronic expansion valve 26, and then to an evaporator 30. As shown, air moving over the evaporator 30 is delivered into an environment to be conditioned 32. The environment to be conditioned 32 is provided with a control 43 that allows an occupant to select desired temperature and/or humidity levels to be provided by the air being delivered into the environment.
A control 28 is shown for the electronic expansion device 26. Moreover, transducers or other sensors 34 and 36 are shown in various locations within the refrigerant system 20. As shown, a transducer 34 is provided downstream of the compressor and may sense the pressure and/or temperature at the discharge of the compressor 22. Similarly, a sensor 36 may sense the pressure and/or temperature downstream of the evaporator 30. The sensors 34 and 36 signals are provided to the control 28. It should be noted that some of these sensors are optional and may not be required for certain system configurations.
Controls are known which operate to control electronic expansion devices to achieve desired superheat values downstream of the evaporator 30. Typically, to achieve desirable performance (total capacity and efficiency) for the refrigerant system 20 while preserving reliability of the compressor 22, it would be desirable to control the evaporator superheat to low positive values, typically in the range from 6 to 12°F.
In this invention, however, the inventors have recognized that by increasing superheat under certain circumstances, could lead to increased dehumidification capability of the evaporator 30 and in turn lower humidity of the air being delivered into the conditioned environment 32. Thus, the present invention utilizes its control of the expansion device 26 to achieve increased dehumidification, at least under certain circumstances. It should be noted that total capacity of the evaporator 30 decreases when superheat is increased, while a simultaneous capacity shift from the sensible component to the latent component is taking place. As a result, a sensible heat ratio (the ratio of the sensible capacity to the total capacity) provided by the evaporator 30 is reduced. Therefore, by increasing evaporator superheat, operation of the refrigerant system 20 can be focused more on providing dehumidification, if desired, while full cooling sensible capacity is not required. In other words, the sensible heat ratio of the evaporator 30 can be controlled by controlling the electronic expansion valve 26 and consequently adjusting superheat at the exit of the evaporator 30. Therefore, by controlling the electronic expansion valve 26, the total evaporator capacity as well its sensible and latent components can be controlled.
Feedback from the sensors 34 and 36 may be used to ensure that the increased superheat is provided to ensure desired dehumidifϊcation while, at the same time, any unreliable or unsafe operational limits are not being approached. For instance, the desired superheat range may be defined by a lower limit and a higher limit, with the lower limit restricted by a minimum value of the evaporator pressure (or saturation temperature) and the higher limit constrained by a discharge temperature threshold. As known, abnormally low evaporator pressure may cause the evaporator freeze-up and excessively high discharge temperature may lead to the compressor damage.
As shown in Figure 2, the control 28 may normally operate to achieve a desired optimal superheat in a conventional cooling mode, for instance, to provide maximum performance (capacity and efficiency) for the refrigerant system 20 to cool the air delivered to the conditioned environment 32. However, at least under circumstances where a reduced sensible cooling load is demanded, such as, for instance, when the ambient temperature is sufficiently low or/and sensible cooling load demands in the conditioned space 32 are not significant, the control 28 enters a "dehumidification" mode of superheat control. In this "dehumidification" mode, the control 28 may control the expansion device 26, such that superheat is adjusted so that the capacity of the evaporator 30 is shifted from cooling to dehumidification (to lower sensible heat ratios) to reduce humidity of the air being delivered into the zone to be conditioned 32. A worker of ordinary skill in the art would recognize how to control the electronic expansion device 26, given the goals of this application as described above, including maintaining the operation of the refrigerant system 20 within safety and reliability limits.
It should be noted that superheat control may be executed at the compressor suction or compressor discharge. In case of the compressor suction, it can be executed at the location toward the compressor suction instead of the evaporator exit. Further, superheat control can be executed at the compressor discharge, if the relationship between suction superheat and discharge superheat is known. Further, even under circumstances when the desired humidity level cannot be precisely achieved by the evaporator superheat control, it still can be noticeably reduced towards the desired value providing a higher degree of comfort for an occupant of the conditioned space.
It should be pointed out that many different compressor types could be used in this invention. For example, scroll, screw, rotary, or reciprocating compressors can be employed. The refrigerant systems that utilize this invention can be used in many different applications, including, but not limited to, stationary and mobile air conditioning systems as well as heat pump systems. The refrigerant system can also employ vapor injection, liquid injection, multiple circuits, as well as compressors connected in parallel in a tandem fashion. Although embodiments of this invention have been disclosed a worker of ordinary skill in the art would recognize that certain modifications would come within the scope of this invention. For that reason the following claims should be studied to determine the true scope and content of this invention.

Claims

CLAIMSWhat is claimed is:
1. A refrigerant system including: a compressor for compressing a refrigerant and delivering it downstream into a heat rejection heat exchanger, the refrigerant from said heat rejection heat exchanger passing through an adjustable expansion device, and then through an evaporator, before being returned to the compressor; and a control for said adjustable expansion device, said control being operable to control dehumidification in an environment to be conditioned by controlling said adjustable expansion device.
2. The refrigerant system as set forth in Claim 1, wherein said dehumidification control consists of changing refrigerant superheat.
3. The refrigerant system as set forth in Claim 2, wherein said superheat is at least one of suction superheat and discharge superheat.
4. The refrigerant system as set forth in Claim 1, wherein said dehumidification control has a limit on the maximum acceptable superheat.
5. The refrigerant system as set forth in Claim 1, wherein said adjustable expansion device is an electronic expansion valve.
6. The refrigerant system as set forth in Claim 1, wherein said control being provided with feedback of at least one measurement within said refrigerant system.
7. The refrigerant system as set forth in Claim 6, wherein said feedback includes feedback from at least one of the pressure and temperature measurement at the discharge of said compressor.
8. The refrigerant system as set forth in Claim 6, wherein said feedback includes feedback from at least one of the pressure and temperature measurement in at least one location selected from the following locations: the evaporator, the compressor or between the evaporator and the compressor.
9. The refrigerant system as set forth in Claim 1, wherein said control has a dehumidifϊcation mode at which it increases the superheat of the refrigerant leaving the evaporator, when full sensible cooling capacity of the refrigerant system is not required, to provide desired dehumidifϊcation.
10. The refrigerant system as set forth in Claim 1, wherein said control has a dehumidifϊcation mode at which it increases the superheat of the refrigerant leaving the evaporator, when full sensible cooling capacity of the refrigerant system is not required, to provide the desired sensible heat ratio.
11. The refrigerant system as set forth in Claim 1, wherein said control has a dehumidifϊcation mode at which it increases the superheat of the refrigerant leaving the evaporator, when full sensible cooling capacity of the refrigerant system is not required, to provide the desired latent capacity and the desired sensible capacity.
12. A method of operating a refrigerant system including the steps of:
(a) compressing a refrigerant and delivering it downstream into a heat rejection heat exchanger, the refrigerant from said heat rejection heat exchanger passing through an adjustable expansion device, and then through an evaporator, before being returned to the compressor; and
(b) controlling said adjustable expansion device to control dehumidifϊcation in an environment to be conditioned by controlling said adjustable expansion device.
13. The method as set forth in Claim 12, wherein said control being provided with feedback of at least one measurement within said refrigerant system.
14. The method as set forth in Claim 13, wherein said feedback includes feedback from at least one of the pressure and temperature measurement at the discharge of said compressor.
15. The method as set forth in Claim 13, wherein said feedback includes feedback from at least one of the pressure and temperature measurement in at least one location selected from the following locations: the evaporator, the compressor or between the evaporator and the compressor.
16. The method as set forth in Claim 12, wherein said control moving into a dehumidifϊcation mode at which it increases the superheat of the refrigerant leaving the evaporator, when full sensible cooling capacity of the refrigerant system is not required, to provide desired dehumidifϊcation.
17. The method as set forth in Claim 12, wherein said control moving into a dehumidifϊcation mode at which it increases the superheat of the refrigerant leaving the evaporator, when full sensible cooling capacity of the refrigerant system is not required, to provide the desired sensible heat ratio.
18. The method as set forth in Claim 12, wherein said control moving into a dehumidifϊcation mode at which it increases the superheat of the refrigerant leaving the evaporator, when full sensible cooling capacity of the refrigerant system is not required, to provide the desired latent capacity and the desired sensible capacity.
19. The method as set forth in Claim 12, wherein said dehumidifϊcation control consists of changing refrigerant superheat.
20. The method as set forth in Claim 13, wherein said superheat is at least one of suction superheat and discharge superheat.
21. The method as set forth in Claim 12, wherein said dehumidifϊcation control has a limit on the maximum acceptable superheat.
2. The method as set forth in Claim 12, wherein the said adjustable expansion device an electronic expansion valve.
PCT/US2008/050832 2008-01-11 2008-01-11 Use of an adjustable expansion valve to control dehumidification WO2009088517A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN2008801248736A CN101910762A (en) 2008-01-11 2008-01-11 Use of an adjustable expansion valve to control dehumidification
PCT/US2008/050832 WO2009088517A1 (en) 2008-01-11 2008-01-11 Use of an adjustable expansion valve to control dehumidification
US12/741,392 US20100242508A1 (en) 2008-01-11 2008-01-11 Use of an adjustable expansion vavle to control dehumidification

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2008/050832 WO2009088517A1 (en) 2008-01-11 2008-01-11 Use of an adjustable expansion valve to control dehumidification

Publications (1)

Publication Number Publication Date
WO2009088517A1 true WO2009088517A1 (en) 2009-07-16

Family

ID=40853353

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2008/050832 WO2009088517A1 (en) 2008-01-11 2008-01-11 Use of an adjustable expansion valve to control dehumidification

Country Status (3)

Country Link
US (1) US20100242508A1 (en)
CN (1) CN101910762A (en)
WO (1) WO2009088517A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011046803A2 (en) 2009-10-14 2011-04-21 Carrier Corporation Dehumidification control in refrigerant vapor compression systems

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103512145B (en) * 2012-06-19 2016-08-31 珠海格力电器股份有限公司 Adjusting method and adjusting device of electronic expansion valve for air conditioning unit
US10556484B2 (en) * 2015-10-28 2020-02-11 Ford Global Technologies, Llc Vehicle climate control valve and operating method
US10488083B2 (en) * 2015-12-18 2019-11-26 Friedrich Air Conditioning Co., Ltd. Variable refrigerant package
JP6332537B2 (en) * 2016-09-30 2018-05-30 ダイキン工業株式会社 Air conditioner
US10415856B2 (en) * 2017-04-05 2019-09-17 Lennox Industries Inc. Method and apparatus for part-load optimized refrigeration system with integrated intertwined row split condenser coil
US10274213B2 (en) * 2017-05-01 2019-04-30 Haier Us Appliance Solutions, Inc. Air conditioning system including a hybrid reheat loop

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5615560A (en) * 1995-04-17 1997-04-01 Sanden Corporation Automotive air conditioner system
US5664425A (en) * 1991-03-08 1997-09-09 Hyde; Robert E. Process for dehumidifying air in an air-conditioned environment with climate control system
US6427454B1 (en) * 2000-02-05 2002-08-06 Michael K. West Air conditioner and controller for active dehumidification while using ambient air to prevent overcooling

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2350408A (en) * 1941-05-28 1944-06-06 Honeywell Regulator Co Direct expansion air conditioning control system
US3385349A (en) * 1966-03-01 1968-05-28 Carrier Corp Control arrangement for an air conditioning system
US4523435A (en) * 1983-12-19 1985-06-18 Carrier Corporation Method and apparatus for controlling a refrigerant expansion valve in a refrigeration system
US4787211A (en) * 1984-07-30 1988-11-29 Copeland Corporation Refrigeration system
USRE33775E (en) * 1984-08-22 1991-12-24 Emerson Electric Co. Pulse controlled expansion valve for multiple evaporators and method of controlling same
US4835976A (en) * 1988-03-14 1989-06-06 Eaton Corporation Controlling superheat in a refrigeration system
DE69732206T2 (en) * 1996-08-22 2005-12-22 Denso Corp., Kariya Refrigeration system of the vapor compression type
US5996360A (en) * 1997-11-27 1999-12-07 Denso Corporation Refrigerant cycle system
US6141981A (en) * 1999-03-26 2000-11-07 Carrier Corporation Superheat control for optimum capacity under power limitation and using a suction modulation valve
US6321549B1 (en) * 2000-04-14 2001-11-27 Carrier Corporation Electronic expansion valve control system
JP2002061922A (en) * 2000-08-14 2002-02-28 Fujitsu General Ltd Method for contorlling air conditioner
ITTO20030792A1 (en) * 2002-10-08 2004-04-09 Danfoss As VALVE CONTROL DEVICE AND PROCEDURE
KR100540808B1 (en) * 2003-10-17 2006-01-10 엘지전자 주식회사 Control method for Superheating of heat pump system
US7096679B2 (en) * 2003-12-23 2006-08-29 Tecumseh Products Company Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
US7290402B1 (en) * 2003-12-29 2007-11-06 Heatcraft Refrigeration Products Llc Expansion valve control system and method and refrigeration unit employing the same
US7234313B2 (en) * 2004-11-02 2007-06-26 Stargate International, Inc. HVAC monitor and superheat calculator system
JP3852015B1 (en) * 2005-05-30 2006-11-29 ダイキン工業株式会社 Humidity control device
EP2488796B1 (en) * 2009-10-14 2018-12-12 Carrier Corporation Dehumidification control in refrigerant vapor compression systems

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5664425A (en) * 1991-03-08 1997-09-09 Hyde; Robert E. Process for dehumidifying air in an air-conditioned environment with climate control system
US5615560A (en) * 1995-04-17 1997-04-01 Sanden Corporation Automotive air conditioner system
US6427454B1 (en) * 2000-02-05 2002-08-06 Michael K. West Air conditioner and controller for active dehumidification while using ambient air to prevent overcooling

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011046803A2 (en) 2009-10-14 2011-04-21 Carrier Corporation Dehumidification control in refrigerant vapor compression systems
EP2488796A4 (en) * 2009-10-14 2015-11-25 Carrier Corp Dehumidification control in refrigerant vapor compression systems

Also Published As

Publication number Publication date
US20100242508A1 (en) 2010-09-30
CN101910762A (en) 2010-12-08

Similar Documents

Publication Publication Date Title
US9353980B2 (en) Climate-control system having multiple compressors
US9151522B2 (en) Air conditioner and control method thereof
US8522568B2 (en) Refrigeration system
US20100242508A1 (en) Use of an adjustable expansion vavle to control dehumidification
EP2270405A1 (en) Refrigerating device
US20110100035A1 (en) Two-phase single circuit reheat cycle and method of operation
JP4779791B2 (en) Air conditioner
EP2068098A1 (en) Air conditioner
US7380411B2 (en) Heat source unit with switching means between heating and cooling
JP2016003848A (en) Air conditioning system and control method for the same
US12018867B2 (en) Refrigeration apparatus
EP2321593B1 (en) Improved operation of a refrigerant system
US11112151B2 (en) Heat source unit for refrigeration apparatus including a heat-source-side heat exchanger having a heat exchange region of variable size
US11448433B2 (en) Refrigeration apparatus
CN114110739B (en) One-driving-multiple refrigerating and heating air conditioner
US20180363961A1 (en) Air conditioner
US7854136B2 (en) Automated drive for fan and refrigerant system
US11959676B2 (en) Method for controlling a vapour compression system at a reduced suction pressure
CN110573810A (en) vapor compression system with suction line liquid separator
US6966193B2 (en) Control of multi-circuit economized system
US20080250812A1 (en) Multi-Circuit Refrigerant System Utilizing Pulse Width Modulation Techniques
US11788759B2 (en) Refrigeration system and heat source unit
JPS63297784A (en) Protecting device for refrigeration device
US20240247845A1 (en) Heating, ventilation, and air-conditioning systems and methods with bypass line
EP1235043A1 (en) Refrigerating device

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 200880124873.6

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 08727580

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 12741392

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 08727580

Country of ref document: EP

Kind code of ref document: A1