EP1795835A2 - Système de réfrigération à compression de vapeur - Google Patents

Système de réfrigération à compression de vapeur Download PDF

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Publication number
EP1795835A2
EP1795835A2 EP06125847A EP06125847A EP1795835A2 EP 1795835 A2 EP1795835 A2 EP 1795835A2 EP 06125847 A EP06125847 A EP 06125847A EP 06125847 A EP06125847 A EP 06125847A EP 1795835 A2 EP1795835 A2 EP 1795835A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
separator
reducing mechanism
pressure reducing
tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP06125847A
Other languages
German (de)
English (en)
Other versions
EP1795835A3 (fr
Inventor
Kenichi Suzuki
Masato Tsuboi
Yuuichi Matsumoto
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.)
Sanden Corp
Original Assignee
Sanden 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 Sanden Corp filed Critical Sanden Corp
Publication of EP1795835A2 publication Critical patent/EP1795835A2/fr
Publication of EP1795835A3 publication Critical patent/EP1795835A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/053—Compression system with heat exchange between particular parts of the system between the storage receiver and another part of the system
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/23—Separators

Definitions

  • the present invention relates generally to vapor compression refrigerating systems.
  • the present invention relates to vapor compression refrigerating systems in which a separator includes an oil separator integrated with a gas and liquid separator to form a single separator, and a gas portion of a refrigerant and an oil separated from the refrigerant flows from the separator to a compressor via the same tube, such that the size and the weight of the vapor compression refrigerating systems is reduced.
  • Fleon group refrigerants have been used in known air conditioning systems, Nevertheless, the use such fleon group refrigerants has begun to be restricted due to environmental concerns. In Europe, it has been proposed that carbon dioxide be used as a refrigerant in place of fleon. Carbon dioxide refrigerant is poisonless and incombustible, however, the theoretical energy efficiency of carbon dioxide as a refrigerant is relatively low, there are problems associated with improving the efficiency of carbon dioxide as a refrigerant. Moreover, when carbon dioxide is used as a refrigerant, because a highpressure side may reach a supercritical condition which exceeds a critical pressure, it is necessary to use materials that may bear this pressure. Consequently, the thickness of the materials increases, which increases the weight of the air conditioner system.
  • a technical advantage of the present invention is that a separator may comprise an oil separator integrated with a gas and liquid separator to form a single separator, and a gas portion of the refrigerant and an oil separated from the refrigerant may flow from the separator to a compressor via the same tube, such that the size and the weight of the vapor compression refrigerating system may be reduced relative to the known vapor compression refrigerating systems.
  • a vapor compression refrigerating system comprises a compressor configured to compress a refrigerant, and a radiator connected to the compressor via a first tube.
  • the radiator is configured to receive the refrigerant from the compressor and to radiate the refrigerant.
  • the system also comprises a first pressure reducing mechanism connected to the radiator via a second tube, and the first pressure reducing mechanism is configured to receive the refrigerant from the radiator and to reduce a pressure of the refrigerant.
  • the system comprises a separator connected to the first pressure reducing mechanism via a third tube and the compressor via a fourth tube, and the separator is configured to receive the refrigerant from the first pressure reducing mechanism.
  • the separator comprises an oil separator which is configured to separate an oil from the refrigerant, and a liquid and gas separator formed integral with the oil separator.
  • the liquid and gas separator is configured to separate a liquid portion and a gas portion from the refrigerant, and the separator is further configured to transmit the oil and the gas portion to the compressor via the fourth tube.
  • the system also comprises a second pressure reducing mechanism connected to the separator via a fifth tube, and the second pressure reducing mechanism is configured to receive the liquid portion from the separator and to reduce a pressure of the liquid portion.
  • the system comprises an evaporator connected to the second pressure reducing mechanism via a sixth tube and operationally coupled to the compressor via at least a seventh tube. The evaporator is configured to receive the liquid portion from the second pressure reducing mechanism and to evaporate the liquid portion.
  • Fig. 1 depicts a vapor compression refrigerating system according to an embodiment of the present invention.
  • the vapor compression refrigerating system may comprise a compressor 1, a radiator 2 connected to compressor 1, a first pressure reducing mechanism 3 connected to radiator 2, and a separator 4 connected to compressor 1 and to first pressure reducing mechanism 3.
  • separator 4 may comprise an oil separator integrated with a gas and liquid separator to form a single separator, and the radiator 2 may be a gas cooler.
  • the vapor compression refrigerating system also may comprise a second pressure reducing mechanism 5 connected to separator 4, and an evaporator 6 connected to compressor I and to second pressure reducing mechanism 5.
  • Each of the connections between the elements of the vapor compression refrigerating system may be made via a tube 7.
  • a refrigerant such as a carbon dioxide refrigerant
  • compressor 1 contracts the refrigerant and increases the temperature of the refrigerant.
  • the refrigerant then may flow from compressor 1 to radiator 2, and radiator 2 may radiate the refrigerant to decrease the temperature of the refrigerant.
  • the refrigerant then may flow from radiator 2 to first pressure reducing mechanism 3, and first pressure reducing mechanism 3 may expand the refrigerant and may reduce the pressure of the refrigerant.
  • the refrigerant then may flow from first pressure reducing mechanism 3 to separator 4, and separator 4 may separate the refrigerant into a gas portion and a liquid portion, and may separate an oil from the refrigerant.
  • the oil may be separated from the refrigerant by centrifugal separation or collision separation.
  • the oil and the gas portion then may flow from separator 4 to compressor 1, such that the oil and the gas portion flow from separator 4 to compressor 1 via the same tube 7.
  • the liquid portion may flow from separator 4 to second pressure reducing mechanism 5, and second pressure reducing mechanism 5 may further expand and further reduce the pressure of the liquid portion.
  • the liquid portion then may flow from second pressure reducing mechanism 5 to evaporator 6, and evaporator 6 may evaporate the liquid portion into a gas.
  • the gas then may flow from evaporator 6 to compressor 7.
  • separator 4 may comprise an oil separator integrated with a gas and liquid separator to form a single separator, and/or because the gas portion of the refrigerant and the oil may flow from separator 4 to compressor 1 via the same tube 7, the size and/or the weight of the vapor compression refrigerating system may be reduced.
  • Fig. 2 is a Mollier chart of carbon dioxide refrigerant in the vapor compression refrigerating system of Fig. 1.
  • state points of the respective components are connected to each other by lines.
  • a curve 11 represents a saturated liquid curve and a saturated vapor curve of carbon dioxide refrigerant, and a curve connecting both lines is referred to as a saturation curve.
  • a curve 12 represents an isothermal line passing through a critical point of carbon dioxide refrigerant.
  • numerals labeled in Fig. 2 express the respective components depicted in Fig. 1, and they show operations of the respective components.
  • Fig. 3 depicts a vapor compression refrigerating system according to another embodiment of the present invention.
  • a refrigerant heat exchanging means e.g., a heat exchanging tube 8
  • a heat exchanging tube 8 is provided for exchanging heat between the liquid refrigerant in separator 4 or/and the refrigerant which flows out of separator 4, and the refrigerant which flows out of evaporator 6.
  • super cooling is possible by lowering the temperature of the refrigerant immediately before the refrigerant flows to second pressure reducing mechanism 5.
  • super heating is possible for preventing liquid compression in compressor 1, and the refrigerating ability and the reliability of the vapor compression refrigerating system may be increased.
  • Fig. 4 is a Mollier chart of carbon dioxide refrigerant in the vapor compression refrigerating system depicted in Fig. 3.
  • state points of the respective components are connected to each other by lines.
  • curve 11 represents a saturated liquid curve and a saturated vapor curve of carbon dioxide refrigerant, and a curve connecting both lines is referred to as a saturation curve.
  • a curve 12 represents an isothermal line passing through a critical point of carbon dioxide refrigerant.
  • the separation of the refrigerant and the oil is performed by a centrifugal separation system.
  • the gas and liquid portion of the refrigerant may flow from first pressure reducing mechanism 3 into the separator from a refrigerant flow passage 22, and the refrigerant rotates in the circumferential direction around a gas refrigerant and oil flow passage 22 to compressor 1. Refrigerant and oil then are separated from each other by the centrifugal force (centrifugal flow: 31).
  • the pressure of the refrigerant has been reduced to a pressure which is less than the critical pressure, the refrigerant and the oil are not dissolved in each other, and because the density of oil is greater than the density of refrigerant, the oil is stored in the lowest layer, which is an oil layer 29.
  • the liquid portion of the refrigerant has a greater density and is stored as a liquid refrigerant layer 28 at a position above the oil layer 29, and the gas portion of the refrigerant is present in a gas refrigerant layer 27, which is a space above the liquid refrigerant layer 28, together with a small amount of liquid refrigerant at a condition of gas/liquid mixture.
  • a refrigerant flow passage 23 to second pressure reducing mechanism 5 is positioned lower than oil layer 29, and an oil flowing out prevention plate 30 is positioned above refrigerant flow passage 23, such that a fine amount of oil existing in liquid refrigerant layer 28 does not flaw out together with the liquid portion of the refrigerant.
  • the gas portion of the refrigerant in gas refrigerant layer 27 passes through a diffuser or tube support 26, and liquid present in the gas portion of the refrigerant is removed, such that only gas refrigerant flows into oil flow passage 24 to compressor 1. At the same time, oil is sucked through an oil returning hole 25, and the sucked oil flows out together with the gas refrigerant.
  • Such a structure is contained in a container 21.
  • the separation of the refrigerant and the oil is performed by a collision separation system.
  • the gas and liquid portion of the refrigerant may flow from first pressure reducing mechanism into the separator from refrigerant flow passage 22, and the refrigerant and the oil are separated from each other by collision with diffuser or tube support 26 (collision flow for separation: 32).
  • diffuser or tube support 26 also is provided in Figs. 5A and 58, and refrigerant and oil are separated from each other by diffuser or tube support 26, the structure depicted in Figs. 5A and 5B is a structure in which the centrifugal separation system is mainly employed and the collision separation system is added thereto.
  • Figs. 7A-7C show an example of a structure configured to be employed in the system of Fig. 3, in which a heat exchanging tube 41, e.g.. a flat tube, is provided at a storage part of liquid refrigerant of separator 4 for exchanging heat between the refrigerant present in separator 4 and the refrigerant which flows from evaporator 6.
  • Heat exchanging tube 41 may be wound at a tight contact condition at the position and its vicinity of liquid refrigerant layer 28 of separator 4, and heat exchange may be performed.
  • heat exchanging tube 41 may be wound at a tight contact condition at the position and its vicinity of liquid refrigerant layer 28 of separator 4, and heat exchange may be performed.
  • heat exchanging tube 41 by forming heat exchanging tube 41 as a parallel multi-hole flat tube 42, the efficiency of the heat exchange may be improved. In such a structure, processing to the container 21 with a pressure resistance may not be necessary.
  • Fig. 8 shows an example of another structure configured to be employed in the system of Fig. 3, in which a heat exchanging tube 51 having a double-pipe structure is used for heat exchanging between the liquid portion of the refrigerant flowing into second pressure reducing mechanism 5 from separator 4 and the refrigerant which flows from evaporator 6.
  • a heat exchanging tube 51 in order to efficiently perform the heat exchange between the liquid refrigerant portion flowing into second pressure reducing mechanism 5 from separator 4 and the refrigerant which flows from evaporator 6, both flows may be set as a counter flow or a parallel flow.
  • the vapor compression refrigerating system according to the present invention may be particularly suitable for an air conditioning system of a vehicle, such as an air conditioning system which uses carbon dioxide as a refrigerant.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP06125847A 2005-12-12 2006-12-11 Système de réfrigération à compression de vapeur Withdrawn EP1795835A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2005357701A JP2007162988A (ja) 2005-12-12 2005-12-12 蒸気圧縮式冷凍サイクル

Publications (2)

Publication Number Publication Date
EP1795835A2 true EP1795835A2 (fr) 2007-06-13
EP1795835A3 EP1795835A3 (fr) 2008-10-08

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EP06125847A Withdrawn EP1795835A3 (fr) 2005-12-12 2006-12-11 Système de réfrigération à compression de vapeur

Country Status (3)

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US (1) US20070130988A1 (fr)
EP (1) EP1795835A3 (fr)
JP (1) JP2007162988A (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2340406A2 (fr) * 2008-10-01 2011-07-06 Carrier Corporation Separation de liquide et de vapeur dans un cycle de refrigerant transcritique
EP2530409A2 (fr) * 2011-06-03 2012-12-05 Glen Dimplex Deutschland GmbH Installation de pompe à chaleur et procédé de fonctionnement dýune installation de pompe à chaleur
WO2012176072A3 (fr) * 2011-06-16 2013-07-18 Advansor A/S Système de réfrigération
EP2690376A1 (fr) * 2012-07-24 2014-01-29 LG Electronics, Inc. Circuit de réfrigération et réfrigérateur en disposant
CN103836856A (zh) * 2012-11-22 2014-06-04 浙江三花制冷集团有限公司 一种油分离器及应用该油分离器的制冷设备
FR3030700A1 (fr) * 2014-12-18 2016-06-24 Valeo Systemes Thermiques Circuit de climatisation de vehicule automobile
CN111546852A (zh) * 2020-04-30 2020-08-18 西安交通大学 一种跨临界二氧化碳电动汽车热管理系统及其控制方法
US11162721B2 (en) * 2019-05-31 2021-11-02 Hyundai Motor Company Gas-liquid separation device for vehicle
US11255580B2 (en) 2015-08-20 2022-02-22 Lennox Industries Inc. Carbon dioxide cooling system with subcooling

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JP2009008349A (ja) * 2007-06-29 2009-01-15 Daikin Ind Ltd 気液分離器
JP5119060B2 (ja) * 2008-06-27 2013-01-16 サンデン株式会社 冷凍サイクル
EP2169332A3 (fr) * 2008-09-29 2014-12-03 Sanyo Electric Co., Ltd. Séparateur d'huile pour séparer un réfrigérant et l'huile
JP2010078262A (ja) * 2008-09-29 2010-04-08 Sanyo Electric Co Ltd オイルセパレータ
JP5143040B2 (ja) * 2009-02-05 2013-02-13 三菱電機株式会社 気液分離器及びこの気液分離器を搭載した冷凍サイクル装置
US8596080B2 (en) * 2010-05-27 2013-12-03 Delphi Technologies, Inc. Air conditioning system having an improved internal heat exchanger
JP2012002418A (ja) * 2010-06-16 2012-01-05 Hitachi Appliances Inc 空気調和機および気液分離装置
DE102011014955A1 (de) * 2011-03-24 2012-09-27 Airbus Operations Gmbh Kühlsystem und Verfahren zum Betreiben eines Kühlsystems
WO2014097484A1 (fr) * 2012-12-21 2014-06-26 三菱電機株式会社 Dispositif à cycle de réfrigération
JP2014185811A (ja) * 2013-03-22 2014-10-02 Fujitsu General Ltd 冷凍サイクル装置
JP6160502B2 (ja) * 2014-02-17 2017-07-12 株式会社デンソー 冷凍サイクル装置
KR101811957B1 (ko) * 2016-11-09 2017-12-22 한국해양대학교 산학협력단 Co2 냉매를 이용한 2단 팽창 구조를 갖는 다단 열펌프 및 그 순환 방법
KR102126133B1 (ko) * 2018-11-08 2020-06-23 한국해양대학교 산학협력단 예냉 냉동기
CN113432350A (zh) * 2020-03-20 2021-09-24 青岛海尔空调电子有限公司 用于空调系统的管路清油装置及空调系统

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JP2000035251A (ja) * 1998-07-17 2000-02-02 Zexel Corp 冷却サイクルの三層分離器
EP0976991A2 (fr) * 1998-07-31 2000-02-02 Zexel Corporation Cycle frigorifique
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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2340406A2 (fr) * 2008-10-01 2011-07-06 Carrier Corporation Separation de liquide et de vapeur dans un cycle de refrigerant transcritique
EP2340406A4 (fr) * 2008-10-01 2014-11-19 Carrier Corp Separation de liquide et de vapeur dans un cycle de refrigerant transcritique
EP2530409A3 (fr) * 2011-06-03 2013-09-04 Glen Dimplex Deutschland GmbH Installation de pompe à chaleur et procédé de fonctionnement dýune installation de pompe à chaleur
EP2530409A2 (fr) * 2011-06-03 2012-12-05 Glen Dimplex Deutschland GmbH Installation de pompe à chaleur et procédé de fonctionnement dýune installation de pompe à chaleur
WO2012176072A3 (fr) * 2011-06-16 2013-07-18 Advansor A/S Système de réfrigération
US8966934B2 (en) 2011-06-16 2015-03-03 Hill Phoenix, Inc. Refrigeration system
EP2690376A1 (fr) * 2012-07-24 2014-01-29 LG Electronics, Inc. Circuit de réfrigération et réfrigérateur en disposant
US9625181B2 (en) 2012-07-24 2017-04-18 Lg Electronics Inc. Refrigerator cycle system and refrigerator having the same including a gas-liquid separator and a liquid refrigerant remover
CN103836856A (zh) * 2012-11-22 2014-06-04 浙江三花制冷集团有限公司 一种油分离器及应用该油分离器的制冷设备
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