EP1260776A1 - Echangeur de chaleur pour système de climatisation - Google Patents

Echangeur de chaleur pour système de climatisation Download PDF

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Publication number
EP1260776A1
EP1260776A1 EP01112491A EP01112491A EP1260776A1 EP 1260776 A1 EP1260776 A1 EP 1260776A1 EP 01112491 A EP01112491 A EP 01112491A EP 01112491 A EP01112491 A EP 01112491A EP 1260776 A1 EP1260776 A1 EP 1260776A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
bypass
pathway
flow
heat exchanger
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.)
Granted
Application number
EP01112491A
Other languages
German (de)
English (en)
Other versions
EP1260776B1 (fr
Inventor
Thomas Tiedemann
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 Thermal Systems Japan Corp
Original Assignee
Zexel Valeo Climate Control Corp
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 Zexel Valeo Climate Control Corp filed Critical Zexel Valeo Climate Control Corp
Priority to DE60125146T priority Critical patent/DE60125146T2/de
Priority to EP01112491A priority patent/EP1260776B1/fr
Publication of EP1260776A1 publication Critical patent/EP1260776A1/fr
Application granted granted Critical
Publication of EP1260776B1 publication Critical patent/EP1260776B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
    • 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

Definitions

  • the present invention relates to a heat exchanger for an air conditioning system and in particular for a CO 2 air conditioning system for use in an automotive vehicle.
  • CO 2 carbon dioxide
  • R134a tetrafluoroethane
  • Fig. 1 is a diagram of a conventional cold-vapour refrigeration cycle wherein a refrigerant is circulated in a closed circuit made up of a compressor 1, a first heat exchanger in the form of a condenser 2, an expansion valve 3 and a second heat exchanger in the form of an evaporator 4.
  • the refrigerant which is under low pressure is evaporated into a gaseous phase in the evaporator 4, which typically comprising a coiled pipe.
  • the evaporation lowers the temperature of the air passing over the evaporator 4, for example for use in a vehicle air conditioning system, such air being that which is blown into the passenger compartment of the vehicle.
  • the compressor 2 draws away the refrigerant from the evaporator 4, compresses it and passes it to the condenser 2, where the refrigerant gives up its heat to the environment, and as a result of its increased pressure and loss of heat condenses back to a liquid phase. It may even become supercooled. Finally, the liquid refrigerant is expanded to a lower vaporizing pressure via the expansion valve 3 and returned to the evaporator 4.
  • the refrigeration cycle in this device comprises a compressor 10, a gas cooler 11, a counter-current heat exchanger 12, an expansion valve 13, an evaporator 14, a combination liquid separator and accumulator 16, and a return flow through the internal counter-current hear exchanger 12 to the compressor 10.
  • the internal counter-current heat exchanger 12 improves the process efficiency and substantially increases the available refrigerating capacity, particularly at high ambient temperatures. It operates by transferring heat from the relatively warm refrigerant discharged from the condenser 11 to the colder refrigerant discharged from the evaporator 14 or the accumulator 16. The refrigerant temperature is thereby lowered prior to expansion via the valve 13 so that the wet vapour content after expansion is decreased and the available refrigerating capacity is thereby increased. However, the heat transfer causes the refrigerant temperature at the inlet to the compressor 10 to increase, which results in a proportional increase in the refrigerant temperature leaving the compressor.
  • the design of the heat exchanger is a compromise between the following two requirements.
  • the object of the present invention is to provide an internal heat exchanger for use in a vehicle air conditioning system in which the thermal flow is substantially maximized under all operating conditions of the air conditioning system whilst the final compression temperature is maintained within permitted limits.
  • a heat exchanger for use in a refrigeration system of a vehicle air conditioning system defining a first refrigerant pathway through which refrigerant can flow from a condenser of the system to an expansion valve of the system; and a second refrigerant pathway through which the refrigerant can flow from an evaporator of the system to a compressor of the system, the two pathways being arranged so that a thermal flow can occur between the refrigerant flowing in the first and second pathways, and characterised in that a bypass is provided through which at least a portion of the refrigerant can flow instead of flowing through at least one of the first pathway and the second pathway, and a control valve is provided to control the flow of refrigerant through the bypass whereby the thermal flow can be regulated.
  • the bypass is provided for the first pathway.
  • the bypass is provided for the second pathway.
  • First and second bypasses may also be provided for both the first and the second pathways respectively.
  • control valve is located at a branch-off point in the pathway at either an inlet to the bypass or at an outlet from the bypass whereby refrigerant flow through both the bypass and the pathway provided with the bypass can be controlled.
  • control valve is located in an intermediate position along the length of the bypass so that only refrigerant flow through the bypass can be controlled.
  • a controller is provided to control the opening and closing of the control valves.
  • a plurality of conduits are preferably provided between the bypass and the pathway at spaced intervals along the length of the pathway and a plurality of control valves are provided to control flow independently through each of the conduits respectively and thereby control overall the flow of refrigerant through the bypass in order that the thermal flow can be regulated.
  • control valves may comprise thermostatic expansion valves.
  • the heat exchanger of the present invention can thus be used in a refrigeration system for a vehicle air conditioning system and connected in series with a compressor, a condenser, an expansion valve, and an evaporator to form an integral closed circuit.
  • the refrigerant used is preferably carbon dioxide.
  • a method of regulating thermal flow in a refrigeration system for a vehicle air conditioning system comprising the steps of evaporating a refrigerant into a gaseous phase in an evaporator and passing it to a compressor; compressing a gaseous refrigerant in the compressor; passing the refrigerant to a gas cooler where the refrigerant is permitted to up its heat to the environment expanding the refrigerant to a lower vaporizing pressure via an expansion valve; returning the refrigerant to the evaporator; and inserting an internal heat exchanger into the refrigeration cycle in order that a thermal flow can occur between the refrigerant flowing in a first pathway located intermediate the condenser and the expansion valve and the refrigerant flowing in a second pathway located intermediate the evaporator and the compressor; and characterised in that a bypass is provided through which refrigerant can flow instead of flowing through at least one of the first pathway and the second pathway, and a control valve is provided to control the flow
  • a heat exchanger 12 for use in a refrigeration cycle of a vehicle air conditioning system as described above with reference to Fig. 2 comprises a first refrigerant pathway 20 through which high-pressure refrigerant can flow from the condenser 11 of the refrigeration system to the expansion valve 13 and a second refrigerant pathway 21 through which low-pressure refrigerant can flow from the evaporator 14 or the accumulator 16 to the compressor 10.
  • the two pathways 20, 21 are arranged in a conventional manner so that a thermal flow can occur between the refrigerant flowing in them.
  • the pathways 20, 21 are arranged in a manner which would maximize the thermal flow.
  • a bypass 22 is provided through which refrigerant can flow instead of flowing through at least one of the pathways 20, 21.
  • the first pathway 20 is provided with the bypass but a similar bypass 23 could be provided for the second pathway, as shown in Fig. 4, in addition to or in place of the bypass 22.
  • a control valve V1 is provided in order to control the flow of refrigerant through the bypass 22 or the bypass 23. As shown in Fig. 3, when the control valve V1 closes the bypass 22, all of the refrigerant flows through the pathway 2 and in this case the thermal flow between the pathways 20 and 21 is maximized.
  • control valve V1 When the thermal flow is to be reduced, the control valve V1 is operated to reduce the high-pressure side flow of refrigerant through the pathway 20 by permitting flow through the bypass 22. In extreme cases the flow through the pathway 20 can be completely stopped so that the refrigerant flows solely through the bypass 22. In this case the refrigeration cycle operates in a manner as described with reference to Fig. 1 where no internal heat exchanger is present.
  • the control valve V1 can be installed in a variety of positions as shown in Fig. 4. If the control valve is located at a position V1 or V2 on the high-pressure side of the exchanger in the first pathway 20 at the branch-off points for the bypass 22, or similarly at a position V3 or V4 on the low-pressure side of the exchanger in the second pathway 21 at the branch-off points for the bypass 23, then flow of refrigerant through the pathways 20 and 21 as well as through the bypasses 22 and 23 can be directly controlled.
  • the control valve could be located at positions V5 and V6 at intermediate positions within in the bypasses 22 and 23 respectively.
  • bypasses 22 and 23 can be directly controlled and, owing to the lower pressures losses of the bypasses 22, 23 as compared to the pathways 20 and 21, nearly the full flow through the heat exchanger may be diverted to the bypasses 22, 23.
  • the advantage of positioning the control valve at positions V5 and V6 is that it permits a less complex valve to be used than would be the case for the other positions.
  • FIG. 5 A modification of a heat exchanger 12 according to the present invention for use in a refrigeration cycle of a vehicle air conditioning system as described above with reference to Fig. 2 is shown in Fig. 5.
  • the heat exchanger comprises a bypass 22 for the first pathway 20 and a plurality of conduits 24 are provided between the bypass 22 and the pathway 20 at spaced intervals along the length of the pathway 20.
  • three such conduits 24a, 24b, 24c are provided, each of which is provided with a control valve Z1, Z2, Z3 respectively to control independently the refrigerant flow therethrough.
  • a further control valve Z4 is provided in the inlet to the bypass 22.
  • a first control valve Z1 can be opened to permit refrigerant flow through the conduit 24a so that a major portion of the refrigerant is diverted from the pathway 20 into the bypass 22 through the conduit 24a due to the lower pressure losses, the minor portion of the refrigerant continuing to flow through the pathway 20.
  • the valves Z2 and z£ may be opened in succession to permit flow through the conduits 24b and 24C thus diverting refrigerant from the pathway 20 at successively earlier stages of the refrigerants travel through the heat exchanger 12. By opening the valve z4, the refrigerant will flow wholly through the bypass 22 and the pathway 20 is then completely bypassed.
  • the variable which is used to control operation of the control valves V1-V6 and Z1-Z4 is the temperature of the refrigerant subsequent to its compression in the compressor 10. If this temperature exceeds a predetermined level, then the control valves V1-V6 and Z1-Z4 are set to operate to increase the flow of refrigerant through the bypass 22, 23 so that the thermal flow between the pathways 20 and 21 is reduced. The final compression temperature is thereby also reduced. However, owing to the interrelationship between the temperature of the refrigerant both before and after compression, it is also possible to use the temperature of the refrigerant prior to compression as the control variable.
  • valves V1 to V4 in Fig. 4 may be arranged to correspond with the controller of the cooling water circuit of the vehicle as in both cases a mass flow of fluid is distributed to two circuits dependent on the operating temperature.
  • valves V5 and V6 and of the valves Z1 to Z4 is simpler because only one mass flow of fluid is controlled dependent on the operating temperature.
  • Conventional thermostatic expansion valves as used in air-conditioning and refrigerating engineering, or valves of this type, can be used for these valves.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP01112491A 2001-05-22 2001-05-22 Echangeur de chaleur pour système de climatisation Expired - Lifetime EP1260776B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE60125146T DE60125146T2 (de) 2001-05-22 2001-05-22 Wärmetauscher für Klimaanlage
EP01112491A EP1260776B1 (fr) 2001-05-22 2001-05-22 Echangeur de chaleur pour système de climatisation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP01112491A EP1260776B1 (fr) 2001-05-22 2001-05-22 Echangeur de chaleur pour système de climatisation

Publications (2)

Publication Number Publication Date
EP1260776A1 true EP1260776A1 (fr) 2002-11-27
EP1260776B1 EP1260776B1 (fr) 2006-12-13

Family

ID=8177512

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01112491A Expired - Lifetime EP1260776B1 (fr) 2001-05-22 2001-05-22 Echangeur de chaleur pour système de climatisation

Country Status (2)

Country Link
EP (1) EP1260776B1 (fr)
DE (1) DE60125146T2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006062860A2 (fr) 2004-12-10 2006-06-15 Carrier Corporation Systeme refrigerant comprenant un economiseur et un echangeur thermique a aspiration liquide commun
CN103851853A (zh) * 2014-03-28 2014-06-11 合肥华凌股份有限公司 一种换热器及使用该换热器的冰箱
WO2023098780A1 (fr) * 2021-12-03 2023-06-08 青岛海尔特种电冰柜有限公司 Procédé de commande de dispositif de réfrigération

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5479789A (en) * 1994-12-29 1996-01-02 Aire Solutions, Inc. Heat exchanger for a heat pump
EP0779481A2 (fr) * 1995-12-15 1997-06-18 Showa Aluminum Corporation Système à circuit frigorifique
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
EP1059495A2 (fr) * 1999-06-08 2000-12-13 Mitsubishi Heavy Industries, Ltd. Cycle de compression à vapeur surcritique
DE19944951A1 (de) * 1999-09-20 2001-03-22 Behr Gmbh & Co Klimaanlage mit innerem Wärmeübertrager

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5479789A (en) * 1994-12-29 1996-01-02 Aire Solutions, Inc. Heat exchanger for a heat pump
EP0779481A2 (fr) * 1995-12-15 1997-06-18 Showa Aluminum Corporation Système à circuit frigorifique
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
EP1059495A2 (fr) * 1999-06-08 2000-12-13 Mitsubishi Heavy Industries, Ltd. Cycle de compression à vapeur surcritique
DE19944951A1 (de) * 1999-09-20 2001-03-22 Behr Gmbh & Co Klimaanlage mit innerem Wärmeübertrager

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006062860A2 (fr) 2004-12-10 2006-06-15 Carrier Corporation Systeme refrigerant comprenant un economiseur et un echangeur thermique a aspiration liquide commun
EP1819970A2 (fr) * 2004-12-10 2007-08-22 Carrier Corporation Systeme refrigerant comprenant un economiseur et un echangeur thermique a aspiration liquide commun
EP1819970A4 (fr) * 2004-12-10 2010-07-14 Carrier Corp Systeme refrigerant comprenant un economiseur et un echangeur thermique a aspiration liquide commun
CN103851853A (zh) * 2014-03-28 2014-06-11 合肥华凌股份有限公司 一种换热器及使用该换热器的冰箱
WO2023098780A1 (fr) * 2021-12-03 2023-06-08 青岛海尔特种电冰柜有限公司 Procédé de commande de dispositif de réfrigération

Also Published As

Publication number Publication date
DE60125146T2 (de) 2007-04-12
DE60125146D1 (de) 2007-01-25
EP1260776B1 (fr) 2006-12-13

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