EP2198215B1 - Wärmetauscher und verfahren für einen kältekreislauf - Google Patents
Wärmetauscher und verfahren für einen kältekreislauf Download PDFInfo
- 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
- Authority
- EP
- European Patent Office
- Prior art keywords
- manifold
- system charge
- heat
- return manifold
- tank
- 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.)
- Active
Links
- 238000005057 refrigeration Methods 0.000 title claims description 23
- 238000000034 method Methods 0.000 title claims description 9
- 239000007788 liquid Substances 0.000 claims description 21
- 239000012530 fluid Substances 0.000 claims description 17
- 238000004891 communication Methods 0.000 claims description 15
- 238000004378 air conditioning Methods 0.000 claims 1
- 239000003507 refrigerant Substances 0.000 description 5
- 239000003570 air Substances 0.000 description 4
- 239000002826 coolant Substances 0.000 description 3
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 239000012080 ambient air Substances 0.000 description 1
- 230000001143 conditioned effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000003607 modifier Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
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- 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)
- Thermal Sciences (AREA)
- Mechanical Engineering (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)
- Minikanal-Wärmetauscher (14) für einen Kältekreislauf (10), umfassend:eine erste Einlasssammelleitung (32-1);eine erste Rücklaufsammelleitung (36-1), die einen ersten Speicherbereich definiert;einen ersten Wärmetauscherdurchgang (16-1) in Fluidverbindung zwischen der Einlasssammelleitung und der ersten Rücklaufsammelleitung, wobei der erste Wärmetauscherdurchgang eine Vielzahl von Minikanälen umfasst;einen Systemladetank (12) in direkter Fluidverbindung mit der ersten Rücklaufsammelleitung, wobei der Systemladetank einen zweiten Speicherbereich definiert;eine erste Leitung (38-1) an oder nahe der Oberseite der ersten Rücklaufsammelleitung, die die oberen Abschnitte der ersten Rücklaufsammelleitung und den Systemladetank in direkte Fluidverbindung miteinander setzt; undeine zweite Leitung (38-2) an oder nahe der Unterseite der ersten Rücklaufsammelleitung, die die unteren Abschnitte der ersten Rücklaufsammelleitung und den Systemladetank in direkte Fluidverbindung miteinander setzt; wobei der Wärmetauscher ferner Folgendes umfasst:eine zweite Rücklaufsammelleitung (36-2),eine dritte Rücklaufsammelleitung (36-3),eine Auslasssammelleitung (34-1),einen zweiten Wärmetauscherdurchgang (16-2) zwischen der ersten Rücklaufsammelleitung (36-1) und der zweiten Rücklaufsammelleitung (36-2);einen dritten Wärmetauscherdurchgang (16-3) zwischen der zweiten Rücklaufsammelleitung (36-2) und der dritten Rücklaufsammelleitung (36-3); undeinen vierten Wärmetauscherdurchgang (16-4), der in Fluidverbindung zwischen der dritten Rücklaufsammelleitung (36-3) und der Auslasssammelleitung (34-1) steht.
- Wärmetauscher (14) nach Anspruch 1, wobei der Systemladetank (12) an der ersten Rücklaufsammelleitung (36-1) so angeordnet ist, dass die erste (38-1) und die zweite (38-2) Leitung zur Strömung in einer horizontalen Richtung konfiguriert sind.
- Wärmetauscher (14) nach Anspruch 1, wobei der Systemladetank (12) an der ersten Rücklaufsammelleitung (36-1) so angeordnet ist, dass die erste (38-1) und die zweite (38-2) Leitung zur Strömung in einer vertikalen Richtung konfiguriert sind.
- Wärmetauscher (14) nach Anspruch 1, wobei die erste Rücklaufsammelleitung (36-1) und der Systemladetank (12) einteilig miteinander ausgebildet sind und die erste (38-1) und die zweite (38-2) Leitung Löcher umfassen.
- Wärmetauscher (14) nach Anspruch 4, wobei der Systemladetank (12) einen Tankboden (FT) aufweist und die erste Rücklaufsammelleitung (36-1) einen Sammelleitungsboden (FM) aufweist, wobei die zweite Leitung (38-2) im Wesentlichen mit dem Tank- und dem Sammelleitungsboden in derselben Ebene liegt.
- Wärmetauscher (14) nach Anspruch 1, wobei die erste Rücklaufsammelleitung (36-1) und der Systemladetank (12) voneinander entfernt sind und die erste (38-1) und die zweite Leitung (38-2) Rohre umfassen.
- Wärmetauscher (14) nach Anspruch 1, wobei der Systemladetank (12) eine Tanklänge (LT) aufweist und die erste Rücklaufsammelleitung (36-1) eine Sammelleitungslänge (LM) aufweist, wobei die Tanklänge im Wesentlichen mit der Sammelleitungslänge identisch ist.
- Wärmetauscher (14) nach Anspruch 1, wobei der Systemladetank (12) einen Tankboden (FT) aufweist und die erste Rücklaufsammelleitung (36-1) einen Sammelleitungsboden (FM) aufweist, wobei der Tankboden mit dem Sammelleitungsboden in einer Ebene liegt oder leicht höher als dieser ist.
- Verfahren zum Durchführen einer Systemevakuierung in einer Klimaanlage, die einen Kühlkreislauf (10) aufweist, der den Wärmetauscher nach Anspruch 1 umfasst, wobei das Verfahren die folgenden Schritte umfasst:Schließen eines ersten Ventils (22);Betreiben eines Kompressors (18), bis eine gesamte Systemladung (30) zu einer Flüssigkeit zwischen dem Kompressor und dem ersten Ventil komprimiert wurde und die Flüssigkeit einen Abschnitt des Wärmetauschers (14) und den Systemladetank (12) füllt, wobei der Systemladetank in Fluidverbindung mit dem Wärmetauscher steht.
- Verfahren nach Anspruch 9, ferner umfassend das Schließen eines zweiten Ventils (24), nachdem der Kompressor (18) abgeschaltet wurde.
- Verfahren nach Anspruch 10, ferner umfassend das Öffnen des ersten (22) und des zweiten (24) Ventils, so dass die Systemladung (30) wieder durch den Kältekreislauf (10) zirkuliert werden kann.
- Kältesystem (10), umfassend:einen Wärmetauscher (14) nach Anspruch 1, wobei der Wärmetauscher ein Kondensator (14) ist;einen Kompressor (18); undeinen Verdampfer (20).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/US2007/020057 WO2009035440A1 (en) | 2007-09-14 | 2007-09-14 | Methods and systems for utilizing a mini-channel heat-exchanger device in a refrigeration circuit |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2198215A1 EP2198215A1 (de) | 2010-06-23 |
EP2198215A4 EP2198215A4 (de) | 2013-12-11 |
EP2198215B1 true EP2198215B1 (de) | 2019-05-22 |
Family
ID=40452276
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07838285.0A Active EP2198215B1 (de) | 2007-09-14 | 2007-09-14 | Wärmetauscher und verfahren für einen kältekreislauf |
Country Status (6)
Country | Link |
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US (1) | US20110005243A1 (de) |
EP (1) | EP2198215B1 (de) |
CN (1) | CN102016455B (de) |
ES (1) | ES2728398T3 (de) |
HK (1) | HK1156390A1 (de) |
WO (1) | WO2009035440A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5536420B2 (ja) * | 2009-11-10 | 2014-07-02 | シャープ株式会社 | セパレート型空気調和機 |
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 (de) | 2015-06-29 | 2022-03-30 | Trane International Inc. | Wärmetauscher mit kältemittelaufbewahrungsvolumen |
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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EP1150076A2 (de) * | 2000-04-26 | 2001-10-31 | Denso Corporation | Kältemittelkreislaufanlage |
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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US5224358A (en) * | 1990-10-04 | 1993-07-06 | Nippondenso Co., Ltd. | Refrigerating apparatus and modulator |
JPH05157382A (ja) * | 1991-12-09 | 1993-06-22 | Mitsubishi Heavy Ind Ltd | 空気調和機 |
US5277032A (en) * | 1992-07-17 | 1994-01-11 | Cfc Reclamation And Recycling Service, Inc. | Apparatus for recovering and recycling refrigerants |
FR2735845B1 (fr) * | 1995-06-22 | 1997-08-29 | Valeo Thermique Moteur Sa | Raccord coude pour boite collectrice tubulaire d'un condenseur de climatisation de vehicule |
FR2742531B1 (fr) * | 1995-12-13 | 1998-01-30 | Valeo Thermique Moteur Sa | Plaque collectrice d'echangeur de chaleur, procede pour sa fabrication et echangeur de chaleur comprenant une telle plaque collectrice |
FR2746490B1 (fr) * | 1996-03-25 | 1998-04-30 | Valeo Thermique Moteur Sa | Condenseur a reservoir integre pour circuit de refrigeration |
CN1162537A (zh) * | 1996-03-25 | 1997-10-22 | 瓦莱奥热机公司 | 用于冷却回路的具有一体化容器的冷凝器 |
FR2747768B1 (fr) * | 1996-04-18 | 1998-12-24 | Valeo Thermique Moteur Sa | Condenseur pour circuit de refrigeration, en particulier pour la climatisation d'un vehicule automobile |
JP4147709B2 (ja) * | 1999-03-05 | 2008-09-10 | 株式会社デンソー | 冷媒凝縮器 |
JP2001165532A (ja) * | 1999-12-09 | 2001-06-22 | Denso Corp | 冷媒凝縮器 |
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 |
-
2007
- 2007-09-14 EP EP07838285.0A patent/EP2198215B1/de active Active
- 2007-09-14 WO PCT/US2007/020057 patent/WO2009035440A1/en active Application Filing
- 2007-09-14 ES ES07838285T patent/ES2728398T3/es active Active
- 2007-09-14 CN CN2007801006361A patent/CN102016455B/zh active Active
- 2007-09-14 US US12/677,427 patent/US20110005243A1/en not_active Abandoned
-
2011
- 2011-10-07 HK HK11110651.6A patent/HK1156390A1/xx not_active IP Right Cessation
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1150076A2 (de) * | 2000-04-26 | 2001-10-31 | Denso Corporation | Kältemittelkreislaufanlage |
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 |
Also Published As
Publication number | Publication date |
---|---|
ES2728398T3 (es) | 2019-10-24 |
HK1156390A1 (en) | 2012-06-08 |
WO2009035440A1 (en) | 2009-03-19 |
US20110005243A1 (en) | 2011-01-13 |
EP2198215A4 (de) | 2013-12-11 |
CN102016455A (zh) | 2011-04-13 |
CN102016455B (zh) | 2013-08-21 |
EP2198215A1 (de) | 2010-06-23 |
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