US20080066488A1 - Heat Exchanger, Intermediate Heat Exchanger, and Refrigeration Cycle - Google Patents

Heat Exchanger, Intermediate Heat Exchanger, and Refrigeration Cycle Download PDF

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Publication number
US20080066488A1
US20080066488A1 US11/571,893 US57189305A US2008066488A1 US 20080066488 A1 US20080066488 A1 US 20080066488A1 US 57189305 A US57189305 A US 57189305A US 2008066488 A1 US2008066488 A1 US 2008066488A1
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US
United States
Prior art keywords
inner tube
heat exchanger
pressure refrigerant
fins
refrigerant
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
US11/571,893
Other languages
English (en)
Inventor
Koichiro Take
Shigeharu Ichiyanagi
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.)
Resonac Holdings Corp
Original Assignee
Showa Denko KK
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 Showa Denko KK filed Critical Showa Denko KK
Priority to US11/571,893 priority Critical patent/US20080066488A1/en
Publication of US20080066488A1 publication Critical patent/US20080066488A1/en
Assigned to SHOWA DENKO K.K. reassignment SHOWA DENKO K.K. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ICHIYANAGI, SHIGEHARU, TAKE, KOICHIRO
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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element
    • 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

Definitions

  • the present invention relates to a refrigeration cycle to be employed, for example, in an automobile air-conditioning refrigeration cycle, and also relates to an intermediate heat exchanger and a heat exchanger for use in such a cycle.
  • Freon series refrigerant has been used. In recent years, however, it is getting to draw the attention of a refrigeration cycle using natural refrigerant such as carbon dioxide (CO 2 ).
  • refrigerant circulates such that high pressure refrigerant from a compressor and a gas cooler (condenser) passes through a decompressor and an evaporator into low pressure refrigerant and returns to the compressor.
  • a gas cooler condenser
  • tubular structure intermediate heat exchangers disclosed in, for example, the following patent documents have been known.
  • Patent Document 1 Japanese Unexamined Laid-open Patent Document No. 2001-56188
  • Patent Document 2 Japanese Unexamined Laid-open Patent Document No. 2002-181466
  • Patent Document 3 In a heat exchanger as disclosed in International Publication No. WO 03/085344 (hereinafter, “Patent Document 3”), it is constituted by a tubular element in which an inner tube provided with a plurality of fins on an external periphery of the inner tube is inserted in an outer tube. In this heat exchanger, high pressure refrigerant passes through the inner tube and low pressure refrigerant passes in between both tubes to exchange the heat therebetween.
  • the preferred embodiments of the present invention have been developed in view of the above-mentioned and/or other problems in the related art.
  • the preferred embodiments of the present invention can significantly improve upon existing methods and/or apparatuses.
  • some embodiments can provide a heat exchanger capable of improving heat exchanging performance and excellent in bending workability.
  • some embodiments can provide an intermediate heat exchanger capable of improving heat exchanging performance and excellent in bending workability.
  • some embodiments can provide a refrigeration cycle using the aforementioned heat exchanger or intermediate heat exchanger.
  • the heat exchanger according to the present invention has the following structure as recited in the following Items [1] to [20].
  • a heat exchanger comprising:
  • an inner tube having a plurality of fins formed on an external periphery of the inner tube, the inner tube being disposed in the outer tube;
  • heat exchanger exchanges heat between the first fluid and the second fluid
  • a gap is formed between an internal periphery of the outer tube and a tip end of each of the plurality of fins of the inner tube.
  • the intermediate heat exchanger comprising:
  • the intermediate heat exchanger comprising:
  • the refrigerant cycle comprising:
  • an intermediate heat exchanger for exchanging heat between high pressure refrigerant passing through a high pressure circuit from the compressor to the decompressor and low pressure refrigerant passing through a low pressure circuit from the decompressor toward the compressor
  • intermediate heat exchanger includes:
  • a refrigerant cycle in which refrigerant circulates such that the refrigerant passes through a compressor, a condenser, a decompressor and an evaporator, and then returns to the compressor,
  • the refrigerant cycle comprising:
  • an intermediate heat exchanger for exchanging heat between high pressure refrigerant passing through a circuit located between the condenser and the decompressor and low pressure passing through a circuit located between the evaporator and the compressor
  • intermediate heat exchanger includes:
  • the heat exchanger can be formed by combining the inner tube having fins and the outer tube. Therefore, as compared with the case in which a heat exchanging multi-bored tube is formed by a single extrusion procedure, the fin and tube can be decreased in thickness, and minute structure thereof can be formed. Accordingly, the heat exchanging performance can be improved.
  • the heat exchanger can be bent easily and accurately into a desired configuration.
  • the heat exchanger is excellent in bending performance.
  • the second fluid can be mixed via the gaps, which can prevent deflection of the refrigerant temperature distribution.
  • the heat exchanging efficiency can be further improved.
  • the heat exchanging efficiency can be improved.
  • the heat exchanging efficiency can be further improved.
  • FIG. 1 is a refrigeration circuit diagram of an automobile air-conditioning refrigeration system in which an intermediate heat exchanger according to an embodiment of this invention is employed;
  • FIG. 2 is a cross-sectional view showing the intermediate heat exchanger of the embodiment.
  • FIG. 1 shows a refrigerant circuit diagram showing an automobile air-conditioning refrigeration system in which a heat exchanger according to an embodiment of this invention is employed.
  • this refrigeration cycle uses carbon dioxide as refrigerant and includes a compressor 1 , a gas cooler (condenser 2 ), a decompressor such as an expansion valve 3 , an evaporator 4 , and an intermediate heat exchanger 10 which will be detailed.
  • a refrigerant circulation circuit is formed. That is, the refrigerant compressed by the compressor 1 is cooled by the gas cooler 2 , and then decompressed by the expansion valve 3 . Thereafter, the refrigerant is evaporated by the evaporator 4 and then returns to the compressor 1 .
  • the high pressure refrigerant (forwarding refrigerant) flowing from the gas cooler 2 toward the expansion valve 3 passes through a high pressure refrigerant heat exchanging passage 25 in the intermediate heat exchanger 10
  • the low pressure refrigerant (returning refrigerant) flowing from the evaporator 4 toward the compressor 1 passes through a low pressure refrigerant heat exchanger passage 35 to exchange the heat therebetween.
  • the intermediate heat exchanger 10 has a double-tube structure including an inner tube 20 which is an aluminum (including its alloy) extruded member and an outer tube 30 which is an aluminum (including its alloy) extruded member.
  • the inner tube 20 is provided a plurality of fins 21 integrally formed on the external periphery of the inner tube.
  • the fins 21 extend along the longitudinal direction of the tube and arranged on the external periphery at certain equal intervals in the circumferential direction.
  • a plurality of inner fins 22 extending along the longitudinal direction of the inner tube and arranged at certain equal intervals in the circumferential direction are integrally provided.
  • the outer tube 30 has a tube aperture having an internal diameter larger than the external diameter of the fins 21 of the inner tube 20 , and the inner tube 20 is inserted in the tube aperture of the outer tube in a manner such that the axial center of the inner tube 20 coincides with that of the outer tube 30 .
  • the inside of the inner tube 20 constitutes a first heat exchanging passage 25 through which high pressure refrigerant (first fluid) passes, and the space between the inner tube 20 and the outer tube 30 constitutes a second heat exchanging passage 35 through which low pressure refrigerant (second fluid) passes.
  • the inner tube 20 is disposed in the outer tube 30 so as to form a gap S between the tip end of the fin 21 and the internal periphery of the outer tube 30 so that the inner tube 20 is not restrained by the outer tube 30 .
  • the size Ls of the gap S is adjusted to 0.2 to 1 mm.
  • the difference between the inner diameter of the outer tube 30 and the external diameter of the inner tube 20 including the fins 21 is adjusted to 0.4 to 2 mm.
  • the gap S is smaller than the lower limit, the inner tube 20 may be restrained by the outer tube 30 , and therefore external force applied to the outer tube 30 greatly acts on the inner tube 20 . Therefore, when the intermediate heat exchanger 10 constituted by both the tubes 20 and 30 is subjected to bending work, the bending stress will concentrate on the outside of the bending portion of the fins 21 of the inner tube 20 , which may cause cracks in fins 21 .
  • the gap S is larger than the upper limit, the size (height) of the fin 21 becomes small (low), which may cause deteriorated heat transfer property, resulting in deteriorated heat exchanging performance.
  • the number of fins 21 is set to 13 to 18, more preferably 15 to 17. If the number of fins is smaller than the lower limit, the heat transfer property may deteriorate, which in turn may cause a deterioration of heat exchanging performance. On the other hand, if the number of fins exceeds the upper limit, the fin pitch becomes small, decreasing the width between adjacent fins, which results in deteriorated heat exchanging performance due to the increased flow resistance of the refrigerant passing threrethrough.
  • the thickness T of the fin 21 is set to 0.3 to 1.3 mm, more preferably 0.5 to 1.1 mm. If the fin thickness T is smaller than the lower limit, it becomes difficult to secure sufficient strength. To the contrary, if the fin thickness T exceeds the upper limit, the heat transfer property deteriorates and the flow resistance increases, resulting in deteriorated heat exchanging performance.
  • the opening angle ⁇ of the adjacent fins 21 and 21 is preferably set to 15 to 30°, more preferably 18 to 26°. If the opening angle ⁇ is smaller than the lower limit, the width between the adjacent fins 21 and 21 becomes small, causing increased flow resistance of the refrigerant passing therethrough, which in turn results in deteriorated heat exchanging performance. To the contrary, if the opening angle ⁇ exceeds the upper limit, the number of fins 21 decreases, causing deteriorated heat transfer performance, which in turn results in deteriorated heat exchanging performance.
  • the inner tube 20 with fins is inserted and disposed in the outer tube 30 as mentioned above. Therefore, the heat exchanger can be manufactured by forming both the tubes 20 and 30 separately and then combining them. Accordingly, as compared with the case in which a heat exchanging multi-bored tube is formed by a single extrusion procedure, the fin and tube can be decreased in thickness, and minute structure thereof can be formed. Accordingly, desired heat transfer performance and heat exchanging performance can be attained more assuredly.
  • the heat exchanger can be bent easily and accurately into a desired configuration because of the excellent bending performance.
  • the heat exchanger can be bent into a desired configuration in accordance with the limited available installing space in the automobile, which dramatically improves the degree of design freedom.
  • the gap S is formed at the tip end of each fin 21 in the second heat exchanging passage 35 , the refrigerant in the heat exchanging passage 35 will be mixed via the gaps S. Therefore, deflection of the refrigerant temperature distribution can be effectively prevented, which further improves the heat exchanging efficiency.
  • the conditions were set as follows: the length of the intermediate heat exchanger (length of the outer tube) was set to 500 mm, the external diameter of the outer tube 30 was set to 21.0 mm, the internal diameter of the outer tube 30 was set to 15.0 mm, the external diameter of the inner tube 20 including the outer fins 21 was set to 14.0 mm, the external diameter of the inner tube 20 excluding the outer fins 21 was set to 7.0 mm, the internal diameter of the tubular portion of the inner tube 20 excluding the inner fins 22 was set to 4.0 mm, and the inner diameter of the inner tube 20 including the inner fins 22 was set to 3.5 mm.
  • the heat exchanger, intermediate heat exchanger and refrigeration cycle according to the present invention can be employed in a refrigeration system for use in, example, automobile air-conditioners.
  • the term “preferably” is non-exclusive and means “preferably, but not limited to.”
  • means-plus-function or step-plus-function limitations will only be employed where for a specific claim limitation all of the following conditions are present in that limitation: a) “means for” or “step for” is expressly recited; b) a corresponding function is expressly recited; and c) structure, material or acts that support that structure are not recited.
  • the terminology “present invention” or “invention” may be used as a reference to one or more aspect within the present disclosure.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US11/571,893 2004-08-06 2005-08-05 Heat Exchanger, Intermediate Heat Exchanger, and Refrigeration Cycle Abandoned US20080066488A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/571,893 US20080066488A1 (en) 2004-08-06 2005-08-05 Heat Exchanger, Intermediate Heat Exchanger, and Refrigeration Cycle

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2004230778 2004-08-06
JP2004-230778 2004-08-06
US60035704P 2004-08-11 2004-08-11
US11/571,893 US20080066488A1 (en) 2004-08-06 2005-08-05 Heat Exchanger, Intermediate Heat Exchanger, and Refrigeration Cycle
PCT/JP2005/014810 WO2006014032A1 (en) 2004-08-06 2005-08-05 Heat exchanger, intermediate heat exchanger, and regrigeration cycle

Publications (1)

Publication Number Publication Date
US20080066488A1 true US20080066488A1 (en) 2008-03-20

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ID=38126333

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Application Number Title Priority Date Filing Date
US11/571,893 Abandoned US20080066488A1 (en) 2004-08-06 2005-08-05 Heat Exchanger, Intermediate Heat Exchanger, and Refrigeration Cycle

Country Status (5)

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US (1) US20080066488A1 (zh)
JP (1) JP2006071270A (zh)
CN (1) CN1977139A (zh)
DE (1) DE112005001885T5 (zh)
WO (1) WO2006014032A1 (zh)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090166019A1 (en) * 2007-12-28 2009-07-02 Showa Denko K.K. Double-wall-tube heat exchanger
US20100313589A1 (en) * 2009-06-13 2010-12-16 Brent Alden Junge Tubular element
US20110252783A1 (en) * 2008-12-22 2011-10-20 Ingvast Haakan Energy cell
US20160334149A1 (en) * 2014-01-17 2016-11-17 Siemens Aktiengesellschaft Method For Configuring The Size Of A Heat Transfer Surface
US20170356692A1 (en) * 2016-06-08 2017-12-14 Savannah River Nuclear Solutions, Llc Finned Heat Exchanger
US20210278137A1 (en) * 2020-03-03 2021-09-09 Daikin Applied Americas, Inc. System and Method for Manufacturing and Operating a Coaxial Tube Heat Exchanger

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JP5202030B2 (ja) * 2008-02-26 2013-06-05 株式会社ケーヒン・サーマル・テクノロジー 二重管式熱交換器
JP5202029B2 (ja) * 2008-02-26 2013-06-05 株式会社ケーヒン・サーマル・テクノロジー 二重管式熱交換器
JP2009204271A (ja) * 2008-02-29 2009-09-10 Tgk Co Ltd 冷凍サイクル
WO2010078686A1 (zh) * 2009-01-06 2010-07-15 昆山开思拓空调技术有限公司 一种换热用毛细管
CN101561210B (zh) * 2009-03-16 2012-10-03 黄洪滔 一种波浪形翅片式蓄冷热交换器
EP2659215B1 (en) * 2010-12-29 2019-02-27 ContiTech Kühner GmbH & Cie. KG Internal heat exchanger
CN102425971B (zh) * 2011-11-10 2014-02-19 上海交通大学 带交错翅片的热交换器管、制作方法及其应用
WO2013122508A1 (ru) * 2012-02-17 2013-08-22 Общество С Ограниченной Ответственностью "Прорывные Инновационные Технологии" Теплообменное устройство
JP2014181870A (ja) * 2013-03-21 2014-09-29 Panasonic Corp 冷凍サイクル装置
CN104949540B (zh) * 2014-03-26 2017-02-08 上海福宜真空设备有限公司 气体冷凝装置
CN106907943B (zh) * 2017-03-02 2019-04-23 青岛海尔空调器有限总公司 换热器
CN110871049B (zh) * 2018-09-03 2021-07-27 中国石油化工股份有限公司 高效热交换反应管
CN110030772A (zh) * 2019-04-12 2019-07-19 浙江吉利控股集团有限公司 一种车用空调冷凝器

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US6019168A (en) * 1994-09-02 2000-02-01 Sustainable Engine Systems Limited Heat exchangers
US6098704A (en) * 1997-06-06 2000-08-08 Denso Corporation Heat exchanger having a double pipe construction and method for manufacturing the same

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JPS63129161A (ja) * 1986-11-17 1988-06-01 Toyo Kosan Kk 燃料磁化処理装置
JPH0590175U (ja) * 1991-05-17 1993-12-07 株式会社日本アルミ 二重管式熱交換器
JP3033047B2 (ja) * 1995-11-30 2000-04-17 株式会社小松製作所 流体の温度制御装置
DE19944951B4 (de) * 1999-09-20 2010-06-10 Behr Gmbh & Co. Kg Klimaanlage mit innerem Wärmeübertrager
JP2002156162A (ja) * 2000-11-16 2002-05-31 Mitsubishi Heavy Ind Ltd インタークーラ及び車両用ｃｏ２冷媒空調装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6019168A (en) * 1994-09-02 2000-02-01 Sustainable Engine Systems Limited Heat exchangers
US6098704A (en) * 1997-06-06 2000-08-08 Denso Corporation Heat exchanger having a double pipe construction and method for manufacturing the same

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090166019A1 (en) * 2007-12-28 2009-07-02 Showa Denko K.K. Double-wall-tube heat exchanger
US20110252783A1 (en) * 2008-12-22 2011-10-20 Ingvast Haakan Energy cell
US8919117B2 (en) * 2008-12-22 2014-12-30 Exencotech Ab Energy cell operable to generate a pressurized fluid via bladder means and a phase change material
US20100313589A1 (en) * 2009-06-13 2010-12-16 Brent Alden Junge Tubular element
US20160334149A1 (en) * 2014-01-17 2016-11-17 Siemens Aktiengesellschaft Method For Configuring The Size Of A Heat Transfer Surface
US9885505B2 (en) * 2014-01-17 2018-02-06 Siemens Aktiengesellschaft Method for configuring the size of a heat transfer surface
US20170356692A1 (en) * 2016-06-08 2017-12-14 Savannah River Nuclear Solutions, Llc Finned Heat Exchanger
US20210278137A1 (en) * 2020-03-03 2021-09-09 Daikin Applied Americas, Inc. System and Method for Manufacturing and Operating a Coaxial Tube Heat Exchanger

Also Published As

Publication number Publication date
DE112005001885T5 (de) 2007-06-21
JP2006071270A (ja) 2006-03-16
WO2006014032A1 (en) 2006-02-09
CN1977139A (zh) 2007-06-06

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AS Assignment

Owner name: SHOWA DENKO K.K., JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TAKE, KOICHIRO;ICHIYANAGI, SHIGEHARU;REEL/FRAME:021178/0747

Effective date: 20061011

STCB Information on status: application discontinuation

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