EP2198215B1 - Dispositif échangeur de chaleur et procédé pour un circuit de réfrigération - Google Patents

Dispositif échangeur de chaleur et procédé pour un circuit de réfrigération Download PDF

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Publication number
EP2198215B1
EP2198215B1 EP07838285.0A EP07838285A EP2198215B1 EP 2198215 B1 EP2198215 B1 EP 2198215B1 EP 07838285 A EP07838285 A EP 07838285A EP 2198215 B1 EP2198215 B1 EP 2198215B1
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EP
European Patent Office
Prior art keywords
manifold
system charge
heat
return manifold
tank
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EP07838285.0A
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German (de)
English (en)
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EP2198215A4 (fr
EP2198215A1 (fr
Inventor
Salvatore Macri
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Carrier Corp
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Carrier Corp
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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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible 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
    • 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
    • F25B2400/16—Receivers
    • 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
    • F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/06—Damage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0063—Condensers

Definitions

  • the present disclosure is related to a refrigeration circuit. More particularly, the present disclosure is related to a refrigeration circuit having a mini-channel heat-exchanger and a system charge tank.
  • Refrigeration circuits are typically used in a number of devices in order to condition (e.g., cool, dehumidify, etc) ambient air within a predefined space such as, but not limited to, a house, a building, a car, a refrigerator, a freezer, and other conditioned spaces.
  • a typical refrigeration circuit contains at least a compressor, a condenser, a receiver, a series of valves, at least one evaporator, and a system charge of refrigerant, which circulates throughout the circuit.
  • a second method commonly used to prepare a circuit for servicing involves a "system pumpdown".
  • the compressor is used to compress all of the system charge into a designated area within the circuit. This is advantageous in that it avoids having to remove and dispose of the system charge thereby, avoiding disposal costs and costs associated with new system charge.
  • the designated storage area In order for a system pumpdown to be effective, the designated storage area must have sufficient volume in which to store the compressed charge. Problems arise, however, when modifications to the circuit are made within the designated area, that reduce the volume available for storage.
  • the condenser is included in the designated storage area. Round tube and fin condenser (“RTF”) coils are frequently used in condensers. RTF coils have large internal volumes and provide sufficient space so that the compressed system charge can be stored within the storage area.
  • RTF Round tube and fin condenser
  • MCHX mini-channel heat-exchanger
  • the heat transfer coefficient is higher for MCHX type construction than for RTF, so whenever this type of replacement is made for coils of equal capacity the internal volume (storage area) will be reduced. Problems will, therefore, arise during a system pumpdown as there is not sufficient space to store the compressed system charge.
  • US 5224358 A discloses a modulator in a coolant recirculation line for a refrigerating apparatus, wherein the modulator is used for storing an excess amount of the coolant recirculated in the system.
  • EP 1150076 A2 discloses a condenser comprising a gas-liquid separator between first and second heat exchange units.
  • JP 2003 014336 A discloses a heat exchanger for a refrigerant circuit comprising a storage tank for storing an excess amount of coolant in the circuit.
  • the invention provides a mini-channel heat-exchanger for a refrigeration circuit, comprising: an inlet manifold; a first return manifold defining a first storage area; a first heat exchange pass in fluid communication between said inlet manifold and said first return manifold, said first heat exchange pass including a plurality of mini-channels; a system charge tank in direct fluid communication with said first return manifold, said system charge tank defining a second storage area; a first conduit at or near the top of the first return manifold placing top portions of said first return manifold and said system charge tank in direct fluid communication with one another; and a second conduit at or near the bottom of the first return manifold placing bottom portions of said first return manifold and said system charge tank in direct fluid communication with one another; wherein the heat exchanger further comprises a second return manifold, a third return manifold, an outlet manifold, a second heat exchange pass between the first return manifold and the second return manifold; a third heat
  • This heat exchanger is used in a method of performing a system pumpdown in another aspect of the invention.
  • the invention provides a refrigeration system, comprising: the above disclosed heat exchanger, wherein the heat exchanger is a condenser a compressor; and an evaporator.
  • Refrigeration circuit 10 includes a system charge tank (“tank”) 12 that can be used to store system charge during a system pump down.
  • tank 12 is shown in use with a mini-channel heat-exchanger, which for purposes of clarity is illustrated as a condenser 14.
  • tank 12 is full of flowing refrigerant in a gaseous state.
  • tank 12 is configured to be filled with refrigerant in a liquid state during the system pump down.
  • Refrigeration circuit 10 includes tank 12, condenser 14, a compressor 18, an evaporator 20, a first valve 22, a second valve 24, a system charge of refrigerant 30, and an expansion device 40. During operation, refrigeration circuit 10 operates in a known manner. Operation of refrigeration circuit 10 is made with reference to FIGS. 1 , 2 , and 3 .
  • Compressor 18 compresses system charge 30, which flows uninterrupted from the compressor to condenser 14.
  • Condensor 14 includes a plurality of mini-channels 16 arranged in a plurality of heat-exchange passes.
  • Compressed system charge 30 in a gaseous state flows into condenser 14 through first inlet 32 into an inlet manifold 32-1.
  • Inlet manifold 32-1 distributes the flow of charge 30 into a first pass 16-1.
  • Circuit 10 includes at least one condenser fan (not shown) that propels ambient outside air over condenser 14 enabling a heat-exchange between system charge 30 and the ambient outside air.
  • the system charge begins to change from a gaseous state to a liquid state.
  • system charge 30 is collected in a first return manifold 36-1.
  • Tank 12 is in fluid communication with first return manifold 36-1 through a plurality of conduits 38-1, 38-2.
  • plurality of conduits 38 is a set of holes so that tank 12 is integral with condenser 14.
  • plurality of conduits 38 may be pipes so that tank 12 can be remote from condenser 14.
  • Tank 12 has a length (L T ) that is substantially equal to the length of first return manifold 36-1 (L M ). In this manner, the upper conduit 38-1 is positioned at or near the top of the first return manifold, while the lower conduit 38-2 is positioned at or near the bottom of the first return manifold. Moreover, it is preferred that a floor (F T ) of tank 12 is co-planar with or slightly higher than a floor (F M ) of manifold 36-1.
  • condenser 14 is configured for arrangement in a substantially vertical position in refrigeration circuit 10.
  • Return manifold 36-1 distributes the flow of charge 30 into a second pass 16-2. After passing through the second pass 16-2, system charge 30 is collected in a second return manifold 36-2, which distributes the flow of charge 30 into a third pass 16-3. After passing through the third pass 16-3, system charge 30 is collected in a third return manifold 36-3, which distributes the flow of charge 30 into a fourth pass 16-4. After passing through the fourth pass 16-4, system charge 30 is collected in an outlet manifold 34-1, which passes the collected system charge out of condenser 14 at an outlet 34.
  • condenser 14 is illustrated by way of example as a four-pass mini-channel heat-exchanger. However, it is contemplated by the present disclosure for condenser 14 to have as many passes as desired for the proper operation of circuit 10.
  • Condenser 14 is fluidly connected to expansion device 40 such that system charge 30 flows from the condenser uninterrupted to the expansion device.
  • the position of expansion device 40 can be changed from a fully open position to a fully closed position, and any position therebetween. When expansion device 40 is in a fully closed position, system charge 30, in a liquid state, will collect at the expansion device until such time that the expansion device is opened.
  • Expansion device 40 can be any known expansion device such as, but not limited to, a fixed expansion device (e.g., an orifice) or a controllable expansion device (e.g., a thermal expansion valve).
  • first valve 22 can be opened or closed either manually or by means of electrical communication from a controller (not shown). During normal operation of refrigeration circuit 10, first valve 22 is open such that system charge 30 can flow continuously to evaporator 20. As system charge 30 flows through evaporator 20, system charge 30 is in heat-exchange communication with a working fluid (not shown) to condition the working fluid. It is contemplated by the present disclosure that the working fluid can be ambient indoor air or a secondary loop fluid such as, but not limited to, chilled water or glycol.
  • Second valve 24 can be in either an open or closed position and its position can be changed either manually or via electrical communication from a controller (not shown). When second valve 24 is opened, system charge 30 flows uninterrupted from evaporator 20 to compressor 18.
  • first valve 22 is closed and compressor 18 is run.
  • compressed system charge 30 flows through condenser 14 wherein the system charge is changed from a gaseous to liquid state.
  • Liquid system charge 30 will then collect at first valve 22 and will then be collected in the condenser.
  • the liquid system charge will flow through and be collected in the condenser in a reverse order to the normal direction of flow of the system charge. For example, the liquid system charge 30 will first be collected in outlet manifold 34-1, fourth pass 16-4, and third return manifold 36-3. The collection of liquid system charge 30 will continue until the liquid level reaches the bottom conduit 38-2. Once the fluid level reaches the bottom conduit 38-2, the liquid system charge 30 is collected in tank 12, as well as in the remaining portions of condenser 14.
  • tank 12 is positioned on first return manifold 36-1 so that flow of system charge 30 through first and second conduits 38-1, 38-2 is in a horizontal direction.
  • Compressor 18 will continue to run until all of system charge 30 has been compressed at which time second valve 24 will be closed. Upon completion of the pumpdown, all of compressed system charge 30 will be stored in outside portion 28 of refrigeration circuit 10 between first and second valves 22, 24.
  • outside portion 28 can be dissociated from inside portion 26 allowing for the inside portion to be serviced without replacing any of system charge 30.
  • first and second valves 22, 24 can be either fully opened or partially opened either manually or through electrical communication from a controller (not shown). As such, system charge 30 can now flow freely throughout refrigeration circuit 10. Compressor 18 is turned on and system charge 30 circulates throughout circuit 10.
  • condenser 14 is configured for arrangement in a substantially horizontal position in refrigeration circuit 10. More particularly, tank 12 is arranged with respect to a flow direction through mini-channels 16 so that there is an approximately ninety-degree angle between the tank and the mini-channels.
  • liquid system charge 30 collects at first valve 22 and will then be collected in condenser 14. As the level of liquid system charge 30 increases in condenser 14, the liquid system charge will flow through and be collected in the condenser in a reverse order to the normal direction of flow of the system charge. For example, liquid system charge 30 will first be collected in outlet manifold 34-1, fourth pass 16-4, and third return manifold 36-3. The collection of liquid system charge 30 continues until the liquid level reaches bottom conduit 38-2. Once the fluid level reaches bottom conduit 38-2, the liquid system charge 30 is collected in tank 12, as well as the remaining portions of condenser 14.
  • tank 12 is positioned on first return manifold 36-1 so that the flow of system charge 30 through first and second conduits 38-1, 38-2 is in a vertical direction.
  • tank 12 is positioned on first return manifold 36-1 so that flow of system charge 30 through first and second conduits 38-1, 38-2 is in a vertical direction.
  • tank 12 is described in use with condenser 14. However, it is contemplated by the present disclosure for tank 12 to find equal use with evaporator 20.

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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)
  • Other Air-Conditioning Systems (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (12)

  1. Échangeur de chaleur à mini-canaux (14) pour un circuit de réfrigération (10), comprenant :
    un collecteur d'entrée (32-1) ;
    un premier collecteur de retour (36-1) définissant une première zone de stockage ;
    un premier passage d'échange de chaleur (16-1) en communication fluidique entre ledit colleteur d'entrée et ledit premier collecteur de retour, ledit premier passage d'échange de chaleur comportant une pluralité de mini-canaux ;
    un réservoir de charge de système (12) en communication fluidique directe avec ledit premier collecteur de retour, ledit réservoir de charge de système définissant une seconde zone de stockage ;
    une première conduite (38-1) au niveau ou près du dessus du premier collecteur de retour plaçant des portions de dessus dudit premier collecteur de retour et dudit réservoir de charge de système en communication fluidique directe les unes avec les autres ; et
    une seconde conduite (38-2) au niveau ou près du dessous du premier collecteur de retour plaçant des portions de dessous dudit premier collecteur de retour et dudit réservoir de charge de système en communication fluidique directe les unes avec les autres ; dans lequel l'échangeur de chaleur comprend en outre :
    un deuxième collecteur de retour (36-2),
    un troisième collecteur de retour (36-3),
    un collecteur de sortie (34-1),
    un deuxième passage d'échange de chaleur (16-2) entre le premier collecteur de retour (36-1) et le deuxième collecteur de retour (36-2) ;
    un troisième passage d'échange de chaleur (16-3) entre le deuxième collecteur de retour (36-2) et le troisième collecteur de retour (36-3) ; et
    un quatrième passage d'échange de chaleur (16-4) étant en communication fluidique entre ledit troisième collecteur de retour (36-3) et ledit collecteur de sortie (34-1).
  2. Échangeur de chaleur (14) selon la revendication 1, dans lequel ledit réservoir de charge de système (12) est positionné sur ledit premier collecteur de retour (36-1) de sorte que lesdites première (38-1) et seconde (38-2) conduites sont configurées pour un écoulement dans une direction horizontale.
  3. Échangeur de chaleur (14) selon la revendication 1, dans lequel ledit réservoir de charge de système (12) est positionné sur ledit premier collecteur de retour (36-1) de sorte que lesdites première (38-1) et seconde (38-2) conduites sont configurées pour un écoulement dans une direction verticale.
  4. Échangeur de chaleur (14) selon la revendication 1, dans lequel ledit premier collecteur de retour (36-1) et ledit réservoir de charge de système (12) sont formés d'un seul tenant l'un avec l'autre et lesdites première (38-1) et seconde (38-2) conduites comprennent des trous.
  5. Échangeur de chaleur (14) selon la revendication 4, dans lequel ledit réservoir de charge de système (12) a un fond de réservoir (FT) et ledit premier collecteur de retour (36-1) a un fond de collecteur (FM), ladite seconde conduite (38-2) étant sensiblement coplanaire avec ledit réservoir et lesdits fonds de collecteur.
  6. Échangeur de chaleur (14) selon la revendication 1, dans lequel ledit premier collecteur de retour (36-1) et ledit réservoir de charge de système (12) sont éloignés l'un de l'autre et lesdites première (38-1) et seconde (38-2) conduites comprennent des tubes.
  7. Échangeur de chaleur (14) selon la revendication 1, dans lequel ledit réservoir de charge de système (12) a une longueur de réservoir (LT) et ledit premier collecteur de retour (36-1) a une longueur de collecteur (LM), ladite longueur de réservoir étant sensiblement égale à ladite longueur de collecteur.
  8. Échangeur de chaleur (14) selon la revendication 1, dans lequel ledit réservoir de charge de système (12) a un fond de réservoir (FT) et ledit premier collecteur de retour (36-1) a un fond de collecteur (FM), ledit fond de réservoir étant coplanaire avec ou légèrement plus élevé que ledit fond de collecteur.
  9. Procédé de réalisation d'une évacuation de système dans un système de climatisation ayant un circuit de réfrigération (10) comprenant l'échangeur de chaleur selon la revendication 1, le procédé comprenant les étapes de :
    fermeture d'un premier clapet (22) ;
    fonctionnement d'un compresseur (18) jusqu'à ce que la totalité d'une charge de système (30) ait été comprimée en un liquide entre ledit compresseur et ledit premier clapet et que ledit liquide remplisse une portion dudit échangeur de chaleur (14) et du réservoir de charge de système (12), ledit réservoir de charge de système étant raccordé fluidiquement audit échangeur de chaleur.
  10. Procédé selon la revendication 9, comprenant en outre la fermeture d'un second clapet (24) après que ledit compresseur (18) est désactivé.
  11. Procédé selon la revendication 10, comprenant en outre l'ouverture desdits premier (22) et second (24) clapets de sorte que ladite charge de système (30) peut être recirculée dans tout le circuit de réfrigération (10).
  12. Système de réfrigération (10), comprenant :
    un échangeur de chaleur (14) selon la revendication 1, dans lequel l'échangeur de chaleur est un condenseur (14) ;
    un compresseur (18) ; et
    un évaporateur (20).
EP07838285.0A 2007-09-14 2007-09-14 Dispositif échangeur de chaleur et procédé pour un circuit de réfrigération Active EP2198215B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2007/020057 WO2009035440A1 (fr) 2007-09-14 2007-09-14 Procédés et systèmes pour utiliser un dispositif d'échangeurs de chaleur à mini canaux dans un circuit de réfrigération

Publications (3)

Publication Number Publication Date
EP2198215A1 EP2198215A1 (fr) 2010-06-23
EP2198215A4 EP2198215A4 (fr) 2013-12-11
EP2198215B1 true EP2198215B1 (fr) 2019-05-22

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EP07838285.0A Active EP2198215B1 (fr) 2007-09-14 2007-09-14 Dispositif échangeur de chaleur et procédé pour un circuit de réfrigération

Country Status (6)

Country Link
US (1) US20110005243A1 (fr)
EP (1) EP2198215B1 (fr)
CN (1) CN102016455B (fr)
ES (1) ES2728398T3 (fr)
HK (1) HK1156390A1 (fr)
WO (1) WO2009035440A1 (fr)

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US20110219790A1 (en) * 2010-03-14 2011-09-15 Trane International Inc. System and Method For Charging HVAC System
US20130255294A1 (en) * 2012-03-28 2013-10-03 Trane International Inc. Charge Port For Microchannel Heat Exchanger Systems
MX2017010897A (es) * 2015-02-24 2018-06-05 Walmart Apollo Llc Recuperador de calor de refrigeracion.
EP3929503A3 (fr) 2015-06-29 2022-03-30 Trane International Inc. Échangeur de chaleur comprenant un volume de stockage de réfrigérant
TWM561776U (zh) * 2017-03-01 2018-06-11 雙鴻科技股份有限公司 水冷式散熱模組

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JP2003014336A (ja) * 2001-06-29 2003-01-15 Japan Climate Systems Corp 凝縮器
JP4151345B2 (ja) * 2002-08-09 2008-09-17 株式会社デンソー 冷凍サイクル装置

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CN2606005Y (zh) * 2003-02-20 2004-03-10 上海德尔福汽车空调***有限公司 汽车空调过冷式冷凝器

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ES2728398T3 (es) 2019-10-24
HK1156390A1 (en) 2012-06-08
WO2009035440A1 (fr) 2009-03-19
US20110005243A1 (en) 2011-01-13
EP2198215A4 (fr) 2013-12-11
CN102016455A (zh) 2011-04-13
CN102016455B (zh) 2013-08-21
EP2198215A1 (fr) 2010-06-23

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