US20110005243A1 - Methods and systems for utilizing a micro-channel heat-exchanger device in a refrigeration circuit - Google Patents

Methods and systems for utilizing a micro-channel heat-exchanger device in a refrigeration circuit Download PDF

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Publication number
US20110005243A1
US20110005243A1 US12/677,427 US67742710A US2011005243A1 US 20110005243 A1 US20110005243 A1 US 20110005243A1 US 67742710 A US67742710 A US 67742710A US 2011005243 A1 US2011005243 A1 US 2011005243A1
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United States
Prior art keywords
manifold
system charge
tank
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.)
Abandoned
Application number
US12/677,427
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English (en)
Inventor
Salvatore Macri
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Carrier Corp
Original Assignee
Carrier Corp
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Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of US20110005243A1 publication Critical patent/US20110005243A1/en
Assigned to CARRIER CORPORATION reassignment CARRIER CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MACRI, SALVATORE
Abandoned 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
    • 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 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.
  • a mini-channel heat-exchanger for a refrigeration circuit having an inlet manifold; a first return manifold; a first heat exchange pass in fluid communication between the inlet manifold and the first return manifold, the first heat exchange pass including a plurality of mini-channels; and a system charge tank in direct fluid communication with the first return manifold.
  • a method of performing a system pumpdown in an air conditioning system having a refrigeration circuit includes closing a first valve; running a compressor until all of a system charge has been compressed between the compressor and the first valve and liquid system charge fills a portion of a mini-channel heat-exchanger and a system charge tank, the system charge tank being fluidly connected to the mini-channel heat-exchanger.
  • FIG. 1 is a schematic representation of an exemplary embodiment of a refrigeration circuit according to the present disclosure.
  • FIG. 2 is a side view of a mini-channel heat-exchanger with an integrated system charge tank in vertical orientation according to the present disclosure.
  • FIG. 3 is a top view of a first exemplary embodiment of the heat-exchanger of FIG. 2 configured for use in a vertical orientation according to the present disclosure.
  • FIG. 4 is a side view of a second exemplary embodiment of the heat-exchanger of FIG. 2 configured for use in a horizontal orientation according to the present disclosure.
  • 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 .
  • 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 .
  • 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 .
  • 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 few as one pass and 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 .
  • 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 .
  • 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.
  • 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)
US12/677,427 2007-09-14 2007-09-14 Methods and systems for utilizing a micro-channel heat-exchanger device in a refrigeration circuit Abandoned US20110005243A1 (en)

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 (1)

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US20110005243A1 true US20110005243A1 (en) 2011-01-13

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US12/677,427 Abandoned US20110005243A1 (en) 2007-09-14 2007-09-14 Methods and systems for utilizing a micro-channel heat-exchanger device in a refrigeration circuit

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US (1) US20110005243A1 (zh)
EP (1) EP2198215B1 (zh)
CN (1) CN102016455B (zh)
ES (1) ES2728398T3 (zh)
HK (1) HK1156390A1 (zh)
WO (1) WO2009035440A1 (zh)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US20180253126A1 (en) * 2017-03-01 2018-09-06 Auras Technology Co., Ltd. Water-cooling heat dissipation module
US10619901B2 (en) 2015-06-29 2020-04-14 Trane International Inc. Heat exchanger with refrigerant storage volume
US20200400357A1 (en) * 2015-02-24 2020-12-24 Walmart Apollo, Llc Refrigeration heat reclaim

Families Citing this family (1)

* Cited by examiner, † Cited by third party
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

Citations (6)

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Publication number Priority date Publication date Assignee Title
JPH05157382A (ja) * 1991-12-09 1993-06-22 Mitsubishi Heavy Ind Ltd 空気調和機
US5224358A (en) * 1990-10-04 1993-07-06 Nippondenso Co., Ltd. Refrigerating apparatus and modulator
US5277032A (en) * 1992-07-17 1994-01-11 Cfc Reclamation And Recycling Service, Inc. Apparatus for recovering and recycling refrigerants
US5765633A (en) * 1996-03-25 1998-06-16 Valeo Thermique Moteur Condenser for a refrigerating circuit
US20010004935A1 (en) * 1999-12-09 2001-06-28 Ryouichi Sanada Refrigerant condenser used for automotive air conditioner
US6397627B1 (en) * 1999-03-05 2002-06-04 Denso Corporation Receiver-integrated condenser

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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
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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
JP4078812B2 (ja) * 2000-04-26 2008-04-23 株式会社デンソー 冷凍サイクル装置
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
CN2606005Y (zh) * 2003-02-20 2004-03-10 上海德尔福汽车空调系统有限公司 汽车空调过冷式冷凝器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US5765633A (en) * 1996-03-25 1998-06-16 Valeo Thermique Moteur Condenser for a refrigerating circuit
US6397627B1 (en) * 1999-03-05 2002-06-04 Denso Corporation Receiver-integrated condenser
US20010004935A1 (en) * 1999-12-09 2001-06-28 Ryouichi Sanada Refrigerant condenser used for automotive air conditioner

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US20200400357A1 (en) * 2015-02-24 2020-12-24 Walmart Apollo, Llc Refrigeration heat reclaim
US12025357B2 (en) * 2015-02-24 2024-07-02 Walmart Apollo, Llc Refrigeration heat reclaim
US10619901B2 (en) 2015-06-29 2020-04-14 Trane International Inc. Heat exchanger with refrigerant storage volume
US11365920B2 (en) 2015-06-29 2022-06-21 Trane International Inc. Heat exchanger with refrigerant storage volume
US20180253126A1 (en) * 2017-03-01 2018-09-06 Auras Technology Co., Ltd. Water-cooling heat dissipation module
CN108541183A (zh) * 2017-03-01 2018-09-14 双鸿科技股份有限公司 水冷式散热模块
US10303229B2 (en) * 2017-03-01 2019-05-28 Auras Technology Co., Ltd. Water-cooling heat dissipation module

Also Published As

Publication number Publication date
EP2198215A1 (en) 2010-06-23
CN102016455B (zh) 2013-08-21
CN102016455A (zh) 2011-04-13
ES2728398T3 (es) 2019-10-24
HK1156390A1 (en) 2012-06-08
WO2009035440A1 (en) 2009-03-19
EP2198215B1 (en) 2019-05-22
EP2198215A4 (en) 2013-12-11

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Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:MACRI, SALVATORE;REEL/FRAME:030727/0928

Effective date: 20070903

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION