EP1519127A1 - Cycle de refroidissement - Google Patents

Cycle de refroidissement Download PDF

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Publication number
EP1519127A1
EP1519127A1 EP04022914A EP04022914A EP1519127A1 EP 1519127 A1 EP1519127 A1 EP 1519127A1 EP 04022914 A EP04022914 A EP 04022914A EP 04022914 A EP04022914 A EP 04022914A EP 1519127 A1 EP1519127 A1 EP 1519127A1
Authority
EP
European Patent Office
Prior art keywords
coolant
compressor
pressure
heat exchanger
accumulator
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP04022914A
Other languages
German (de)
English (en)
Inventor
Kenji Zexel Valeo Climate Control Corp. Lijima
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Systemes Thermiques SAS
Original Assignee
Valeo Climatisation SA
Valeo Systemes Thermiques SAS
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 Valeo Climatisation SA, Valeo Systemes Thermiques SAS filed Critical Valeo Climatisation SA
Publication of EP1519127A1 publication Critical patent/EP1519127A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2600/2501—Bypass 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
    • F25B2700/21—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

Definitions

  • This invention relates to a cooling cycle which employs a supercritical fluid such as carbon dioxide (CO 2 ) as the coolant.
  • a supercritical fluid such as carbon dioxide (CO 2 ) as the coolant.
  • the durability of the components which make up the cooling cycle can deteriorate significantly.
  • the temperature range within which the durability of rubber or resin parts can be maintained is low compared to other components, and during times of high load the discharge temperature of the coolant can exceed this temperature range leading to potential damage.
  • an internal heat exchanger which exchanges heat between the high-pressure coolant passing through the radiator and the low-pressure coolant introduced into the compressor is provided with the purpose of increasing cooling performance, and also to prevent compression of the liquid by the compressor.
  • the main purpose of the invention is to provide a cooling cycle which, with a structure which prevents a rise of temperature in the coolant discharged from the compressor, avoids increased pressure loss in the internal heat exchanger and enables a reduction in the size, weight and cost of the necessary components which make up the structure in question.
  • the cooling cycle of the invention is characterized in that a recovery path is provided which bypasses said internal heat exchanger, enabling recovery of the liquid coolant or oil inside said accumulator between said internal heat exchanger and compressor, and a regulator valve which enables regulation of the quantity of said liquid coolant or oil recovered via this recovery path.
  • the liquid coolant or oil separated in the accumulator is recovered between the internal heat exchanger and the compressor and mixed with the gas coolant that has passed through the internal heat exchanger, it is possible to reduce the temperature of the coolant introduced into the compressor, and even to reduce the temperature of the coolant discharged from the compressor.
  • the liquid coolant or oil separated in the accumulator is made to bypass the internal heat exchanger and is recovered between the internal heat exchanger and the compressor, it is possible to avoid pressure losses within the internal heat exchanger, and as the liquid coolant or oil are recovered via the recovery path, it is possible to make the diameter of the tubing of the recovery path smaller than with gas coolant passing through, thus enabling reductions in size and weight.
  • the above structure may also be realized by providing a coolant discharge temperature sensor which detects the temperature of the coolant discharged from said compressor, and a control means which controls said regulator valve in accordance with the coolant discharge temperature detected by said coolant discharge temperature sensor, or a control means which controls said regulator valve where it is expected that the discharge temperature will rise with a high cycle load due to the outside temperature, pressure within the cycle, room temperature or the like.
  • the internal heat exchanger and regulator valve may also be built into the accumulator to enable reductions in the size, weight and cost of the cooling cycle.
  • the structure of the above cycle is suited to a supercritical vapour compression cooling cycle which uses carbon dioxide as a coolant, in which the coolant discharge temperature of the compressor becomes extremely high at times of high load.
  • the liquid coolant or oil within the accumulator bypasses the internal heat exchanger via the recovery path, enabling recovery between the internal heat exchanger and the compressor, the quantity of liquid coolant or oil recovered via this recovery path being regulated by a regulator valve, thus enabling the temperature of the coolant introduced to the compressor to be reduced, and even enabling a reduction in the coolant discharge temperature.
  • cooling cycle 1 has a structure comprising compressor 2 which increases the pressure of the coolant, radiator 3 which cools the coolant compressed by compressor 2, expansion device 4 which reduces the pressure of the coolant cooled by radiator 3, evaporator 5 which evaporates coolant whose pressure is reduced in expansion device 4, accumulator 6 which in addition to separating out the gas and liquid in the coolant passing through evaporator 5 separates the oil (lubricating oil) mixed in with the coolant, and internal heat exchanger 7 which exchanges heat between the low-pressure coolant conducted from accumulator 6 to compressor 2 and the high-pressure coolant conducted from radiator 3 to expansion device 4.
  • compressor 2 which increases the pressure of the coolant
  • radiator 3 which cools the coolant compressed by compressor 2
  • expansion device 4 which reduces the pressure of the coolant cooled by radiator 3
  • evaporator 5 which evaporates coolant whose pressure is reduced in expansion device 4
  • accumulator 6 which in addition to separating out the gas and liquid in the coolant passing through evaporator 5 separates the oil (lubricating
  • the above described cooling cycle 1 uses carbon dioxide (CO 2 ) as the coolant, and the coolant whose pressure is increased in compressor 2 is introduced into radiator 3 as a high-temperature and high-pressure supercritical coolant, being cooled here by radiation. Thereafter it enters high-pressure duct 7a of internal heat exchanger 7 where it is further cooled by heat exchange with the low-temperature gas coolant flowing out from accumulator 6, and sent on without being liquefied to expansion device 4. In this expansion device 4 the pressure is then reduced, creating a low-temperature low-pressure wet vapour, which is vaporized by heat exchange with the air passing through evaporator 5, before flowing into accumulator 6 as a two-phase coolant in which gas and liquid are mixed.
  • CO 2 carbon dioxide
  • cooling cycle 1 is provided with recovery path 10, one end of which has an opening at the bottom of accumulator 6, the other end being connected between low-pressure duct 7b of internal heat exchanger 7 and the inlet side of compressor 2, the degree of opening of this recovery path 10 being regulated by regulator valve 11, which comprises an electromagnetic valve.
  • the reference 12 is a temperature sensor for the coolant discharge which detects temperature Td of the coolant discharged from compressor 2, and the temperature signal output from this coolant discharge temperature sensor 12 is input to control unit 13, said control unit 13 being part of the control means.
  • This control unit 13 has a structure comprising a central processing unit (CPU), a read-only memory (ROM), a random access memory (RAM), an input/output port and the like, and in addition a drive circuit which controls regulator valve 11, it being arranged that regulator valve 11 is controlled using the control routine shown in Figure 3 which is executed at prescribed intervals.
  • the coolant discharge temperature Td is input at prescribed intervals (step 50), it is determined whether the coolant discharge temperature Td thus input is above a fixed temperature (step 52) and where determined that it is above the prescribed temperature, the degree of opening of regulator valve 11 is adjusted in accordance with the coolant discharge temperature Td (step 54) so that regulator valve 11 opens up more with rises in coolant discharge temperature Td (and a greater quantity of oil or liquid coolant is recovered via recovery path 10).
  • oil 20a separated within accumulator 6, as shown in Figure 2 sinks to a lower level than liquid coolant 20b as it has a higher specific gravity than liquid coolant 20b, and when recovery path 10 is opened up using regulator valve 11, recovery takes place between internal heat exchanger 7 and compressor 2 via recovery path 10 starting with the liquid coolant.
  • liquid coolant 20b is recovered between internal heat exchanger 7 and compressor 2 via recovery path 10, mixed in with the gas coolant passing through internal heat exchanger 7 and recovered to compressor 2.
  • the liquid flowing through recovery path 10 is oil or liquid coolant, enabling the diameter of the tubing which makes up recovery path 10 to be made smaller than in the case of tubing through which a gas coolant flows, and also enabling the diameter of regulator valve 11 provided in recovery path 10 to be made smaller. For this reason a reduction in the size, weight and cost of components is feasible.
  • the tubing which forms recovery path 10 may be inserted within the accumulator, and the regulator valve provided for recovering the oil or liquid coolant may be positioned within this inserted portion.
  • internal heat exchanger 7 may be built into accumulator 6, and the regulator valve, which regulates the quantity recovered and the recovery path for oil or liquid coolant, may also be provided within accumulator 6.
  • the regulator valve which regulates the quantity recovered and the recovery path for oil or liquid coolant, may also be provided within accumulator 6.
  • the quantity recovered is regulated where the coolant discharge temperature is above a prescribed value, but where it is expected that a high coolant discharge temperature will result from a high cycle load due to external temperature, internal cycle pressure, room temperature or the like, said regulator valve may be controlled to allow the quantity recovered to be regulated.
  • the quantity recovered may be regulated where the room temperature, the external temperature or the air temperature at the inlet of radiator 3 exceeds a prescribed temperature, where the air temperature at the exit of the evaporator 5 or the pressure of the low-pressure line is above a prescribed value, or where the flow of air blown from the air-conditioning unit is above a prescribed level.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Compressor (AREA)
EP04022914A 2003-09-26 2004-09-27 Cycle de refroidissement Withdrawn EP1519127A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003334770A JP2005098635A (ja) 2003-09-26 2003-09-26 冷凍サイクル
JP2003334770 2003-09-26

Publications (1)

Publication Number Publication Date
EP1519127A1 true EP1519127A1 (fr) 2005-03-30

Family

ID=34191511

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04022914A Withdrawn EP1519127A1 (fr) 2003-09-26 2004-09-27 Cycle de refroidissement

Country Status (2)

Country Link
EP (1) EP1519127A1 (fr)
JP (1) JP2005098635A (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104075493A (zh) * 2013-03-27 2014-10-01 特灵空调系统(中国)有限公司 排气温度可控制的压缩系统及其排气温度控制方法
GB2539911A (en) * 2015-06-30 2017-01-04 Arctic Circle Ltd Refrigeration apparatus
US20210010733A1 (en) * 2018-09-25 2021-01-14 Hangzhou Sanhua Research Institute Co., Ltd. Air conditioning system and control method therefor
DE102020126579A1 (de) 2020-10-09 2022-04-14 Viessmann Climate Solutions Se Verfahren zum Betrieb einer Kältekreislaufvorrichtung
US12078397B2 (en) 2020-12-04 2024-09-03 Honeywell International Inc. Surge control subcooling circuit

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5046895B2 (ja) * 2007-12-06 2012-10-10 三菱電機株式会社 空気調和装置およびその運転制御方法
JP2017101897A (ja) * 2015-12-03 2017-06-08 東芝キヤリア株式会社 冷凍サイクル装置
JP7236606B2 (ja) * 2018-11-16 2023-03-10 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1990007683A1 (fr) * 1989-01-09 1990-07-12 Sinvent As Dispositif a cycle de carnot renverse en conditions transcritiques
JPH1019421A (ja) * 1996-07-05 1998-01-23 Nippon Soken Inc 冷凍サイクルおよびこのサイクルに用いるアキュムレータ
EP0915306A2 (fr) * 1997-11-06 1999-05-12 Denso Corporation Appareil frigorifigue supercritique
EP1043550A1 (fr) * 1997-12-26 2000-10-11 Zexel Corporation Cycle de refrigeration
JP2001235239A (ja) * 2000-02-23 2001-08-31 Seiko Seiki Co Ltd 超臨界蒸気圧縮サイクル装置
US6370896B1 (en) * 1998-11-18 2002-04-16 Denso Corporation Hot water supply system
US20020078698A1 (en) * 2000-12-16 2002-06-27 Bert Leisenheimer Cooling device with a controlled coolant phase upstream of the compressor
JP2002228282A (ja) * 2001-01-29 2002-08-14 Matsushita Electric Ind Co Ltd 冷凍装置
EP1367344A2 (fr) * 2002-05-30 2003-12-03 Praxair Technology, Inc. Procédé pour faire fonctionner un système frigorifique transcritique

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1990007683A1 (fr) * 1989-01-09 1990-07-12 Sinvent As Dispositif a cycle de carnot renverse en conditions transcritiques
JPH1019421A (ja) * 1996-07-05 1998-01-23 Nippon Soken Inc 冷凍サイクルおよびこのサイクルに用いるアキュムレータ
EP0915306A2 (fr) * 1997-11-06 1999-05-12 Denso Corporation Appareil frigorifigue supercritique
EP1043550A1 (fr) * 1997-12-26 2000-10-11 Zexel Corporation Cycle de refrigeration
US6370896B1 (en) * 1998-11-18 2002-04-16 Denso Corporation Hot water supply system
JP2001235239A (ja) * 2000-02-23 2001-08-31 Seiko Seiki Co Ltd 超臨界蒸気圧縮サイクル装置
US20020078698A1 (en) * 2000-12-16 2002-06-27 Bert Leisenheimer Cooling device with a controlled coolant phase upstream of the compressor
JP2002228282A (ja) * 2001-01-29 2002-08-14 Matsushita Electric Ind Co Ltd 冷凍装置
EP1367344A2 (fr) * 2002-05-30 2003-12-03 Praxair Technology, Inc. Procédé pour faire fonctionner un système frigorifique transcritique

Non-Patent Citations (4)

* Cited by examiner, † Cited by third party
Title
NEKSA P ET AL: "CO2-heat pump water heater: characteristics, system design and experimental results", INTERNATIONAL JOURNAL OF REFRIGERATION, OXFORD, GB, vol. 21, no. 3, May 1998 (1998-05-01), pages 172 - 179, XP004287240, ISSN: 0140-7007 *
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 05 30 April 1998 (1998-04-30) *
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 25 12 April 2001 (2001-04-12) *
PATENT ABSTRACTS OF JAPAN vol. 2002, no. 12 12 December 2002 (2002-12-12) *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104075493A (zh) * 2013-03-27 2014-10-01 特灵空调系统(中国)有限公司 排气温度可控制的压缩系统及其排气温度控制方法
GB2539911A (en) * 2015-06-30 2017-01-04 Arctic Circle Ltd Refrigeration apparatus
US20210010733A1 (en) * 2018-09-25 2021-01-14 Hangzhou Sanhua Research Institute Co., Ltd. Air conditioning system and control method therefor
US11828507B2 (en) * 2018-09-25 2023-11-28 Hangzhou Sanhua Research Institute Co., Ltd. Air conditioning system and control method therefor
DE102020126579A1 (de) 2020-10-09 2022-04-14 Viessmann Climate Solutions Se Verfahren zum Betrieb einer Kältekreislaufvorrichtung
WO2022073556A1 (fr) 2020-10-09 2022-04-14 Viessmann Climate Solutions Se Procédé de fonctionnement d'un appareil à cycle frigorifique
US12078397B2 (en) 2020-12-04 2024-09-03 Honeywell International Inc. Surge control subcooling circuit

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Publication number Publication date
JP2005098635A (ja) 2005-04-14

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