US20130048260A1 - Vehicle Interior Heat Exchanger - Google Patents

Vehicle Interior Heat Exchanger Download PDF

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Publication number
US20130048260A1
US20130048260A1 US13/695,612 US201113695612A US2013048260A1 US 20130048260 A1 US20130048260 A1 US 20130048260A1 US 201113695612 A US201113695612 A US 201113695612A US 2013048260 A1 US2013048260 A1 US 2013048260A1
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US
United States
Prior art keywords
cooling medium
circulation tubes
header tank
medium circulation
vehicle interior
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
US13/695,612
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English (en)
Inventor
Yuuichi Matsumoto
Yusuke Iino
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
Individual
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 Individual filed Critical Individual
Assigned to SANDEN CORPORATION reassignment SANDEN CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IINO, YUSUKE, MATSUMOTO, YUUICHI
Publication of US20130048260A1 publication Critical patent/US20130048260A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—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
    • 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
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0084—Condensers

Definitions

  • the present invention relates to a vehicle interior heat exchanger in a vehicle heat pump apparatus.
  • a heat pump apparatus (air-conditioning apparatus) of a vehicle with an engine is of a counterflow type in which a cooling medium in a mixed gas-liquid state is circulated from the inlet side of an evaporator in one direction that intersects a blowing direction and is thereafter reversed to be circulated in the reverse direction so as to flow out from the outlet side on the same side as the inlet side as a gaseous cooling medium, and suppresses temperature distribution unevenness of cooling air that is blown into the vehicle interior.
  • the temperature difference between the cooling medium inlet side through which a gaseous cooling medium at high temperature and high pressure flows in and the cooling medium outlet side through which a condensed liquid cooling medium at low temperature flows out is increased to about 30° C. (about 10° C. in the evaporator).
  • the present invention has been made focusing on the problems of the related art, and an object thereof is to suppress heat exchange between the inlet side and the outlet side of a heat exchanger while making the temperature distribution of a heating air from a vehicle interior heat exchanger that is operated as a condenser uniform, thereby maintaining favorable thermal efficiency.
  • the present invention has first to third aspects, and a heat exchanger of a vehicle heat pump apparatus, which is disposed on a blowing path in a vehicle interior and functions at least as a condenser, has the following configuration which is common in the first to third aspects.
  • an inlet side header tank which has a cooling medium inlet and to which each of the cooling medium circulation tubes of the tube group on one side is connected for communication
  • an outlet side header tank which has a cooling medium outlet and to which each of the cooling medium circulation tubes of the tube group on the other side is connected for communication.
  • the inlet side header tank and the outlet side header tank are arranged separately with a space therebetween.
  • the inlet side header tank and the outlet side header tank of the inlet and outlet side header tank are arranged in one body via a heat insulation layer.
  • the inlet side header tank and the outlet side header tank of the inlet and outlet side header tank are arranged in one body.
  • the cooling medium inlet and the cooling medium outlet are formed at end portions on the sides opposite to each other in a stacking direction of the cooling medium circulation tubes of the corresponding tanks.
  • cooling medium flow paths in which the cooling medium introduced to the inlet side header tank from the cooling medium inlet reaches the inside of the intermediate header tank through the cooling medium circulation tubes of the tube group on the inlet side, reaches the inside of the outlet side header tank through the cooling medium circulation tubes of the tube group on the outlet side from the intermediate header tank, and flows out from the cooling medium outlet.
  • the average temperature of the temperature of the inlet side tube group and the temperature of the outlet side tube group is made uniform in the entire region of the cross-section of the blowing path of the heat exchanger, and thus the temperature distribution of the heating air after passing through the heat exchanger is made uniform.
  • the inlet side header tank and the outlet side header tank are separately formed and are arranged with a space therebetween, heat exchange between the high-temperature cooling medium in the vicinity of the inlet side header tank and the low-temperature cooling medium in the vicinity of the outlet side header tank is suppressed, thereby maintaining favorable thermal efficiency.
  • heat exchange between the high-temperature cooling medium in the vicinity of the inlet side header tank and the low-temperature cooling medium in the vicinity of the outlet side header tank is suppressed due to the interposition of the heat insulation layer and thus favorable thermal efficiency is able to be maintained.
  • the strength is enhanced and the assembly characteristics of the heat exchanger are also enhanced.
  • the cooling medium inlet which has the highest temperature and the cooling medium outlet which has the lowest temperature are formed at positions farthest from each other between the two tanks. Therefore, heat exchange between regions having a high temperature difference is suppressed and thus favorable thermal efficiency is able to be maintained.
  • the strength is enhanced and the assembly characteristics of the heat exchanger are also enhanced.
  • FIG. 1 is a diagram illustrating the summary of a cooling medium circuit in a vehicle air-conditioning apparatus having a vehicle interior heat exchanger according to the present invention.
  • FIG. 2 is a perspective view of the vehicle interior heat exchanger according to a first embodiment.
  • FIG. 3 is a transverse sectional view of the main part of the vehicle interior heat exchanger according to the first embodiment.
  • FIG. 4 is a perspective view of the vehicle interior heat exchanger according to a second embodiment.
  • FIG. 5 is a transverse sectional view of the main part of the vehicle interior heat exchanger according to the second embodiment.
  • FIG. 6 is a perspective view of the vehicle interior heat exchanger according to a third embodiment.
  • FIG. 7 is a transverse sectional view of the main part of the vehicle interior heat exchanger according to the third embodiment.
  • FIG. 1 illustrates the outline of a cooling medium circuit in a vehicle heat pump apparatus (air-conditioning apparatus) having a vehicle interior heat exchanger according to the present invention.
  • the air-conditioning apparatus is configured by connecting a vehicle interior heat exchanger 1 disposed on a blowing path 51 in the vehicle interior, a vehicle exterior heat exchanger 2 disposed on the vehicle exterior, a four-way switching valve 3 , a compressor 4 , and expansion valves 5 A and 5 B and check valves 6 A and 6 B which are respectively connected in parallel so as to form a circulation passage via a cooling medium pipe 7 .
  • a fan 52 is disposed on the blowing path 51 in the vehicle interior, and vehicle interior air is blown by the fan 52 so as to be circulated via the vehicle interior heat exchanger 1 , thereby performing cooling or heating.
  • the four-way valve 3 is switched to a state indicated by a solid line as illustrated, and a cooling medium pressurized by the compressor 4 flows into the vehicle interior heat exchanger 1 via the four-way valve 3 and is condensed and liquefied through heat exchange (heat dissipation) with the vehicle interior air. Due to the heat exchange, the vehicle interior air is heated. The heated vehicle interior air is blown by the fan 52 into the vehicle interior so as to heat the vehicle interior.
  • liquid cooling medium reaches the expansion valve 5 B through the check valve 6 A, is depressurized into a mist state, flows into the vehicle exterior heat exchange 2 , is vaporized (gasified) through heat exchange (heat absorption) with outside air, and is thereafter returned to the intake port of the compressor 4 and is pressurized again. This cycle is repeated.
  • the cooling medium which is pressurized by driving the compressor 4 flows into the vehicle exterior heat exchanger 2 via the four-way valve 3 in a state indicated by a dotted line as illustrated, and the gas cooling medium is condensed and liquefied through heat exchange (heat dissipation) with outside air.
  • the liquid cooling medium reaches the expansion valve 5 A through the check valve 6 B, is depressurized into a mist state, and flows into the vehicle interior heat exchanger 1 .
  • the cooling medium in the mist state is vaporized through heat exchange (heat absorption) with the vehicle interior air into a gaseous state and thus cools the vehicle interior air.
  • the cooled vehicle interior air is blown by the fan 52 into the vehicle interior and cools the vehicle interior.
  • the gaseous cooling medium is returned to the intake port of the compressor 4 and is pressurized again. This cycle is repeated.
  • the vehicle interior heat exchanger 1 that operates as a condenser during heating is configured as described below.
  • the cooling medium circulation direction is reversed between when the heat exchanger 1 operates as a condenser during heating and when the heat exchanger 1 operates as an evaporator during cooling.
  • the cooling medium circulation direction at the time of operation as a condenser will be described.
  • FIGS. 2 to 4 illustrate a first embodiment of the vehicle interior heat exchanger 1 .
  • a pair of tube groups 13 A and 13 B is formed by stacking a plurality of cooling medium circulation tubes 11 having flat passage cross-sections in the vertical direction via corrugated fins, and the pair of tube groups 13 A and 13 B face each other and are arranged in two rows so as to be spaced apart in the blowing direction of the blowing path 51 .
  • Each of the cooling medium circulation tubes 11 and the corrugated fins are fixed by brazing or the like.
  • header tanks that extend in the stacking direction of the cooling medium circulation tubes 11 are respectively arranged.
  • inlet side header tank 14 A and outlet side header tank 14 B are separately formed and are arranged with a space therebetween.
  • the inlet side header tank 14 A and the outlet side header tank 14 B have a shape in which, for example, the upper and lower end surfaces of circular pipe members are blocked by lid members and as described later, a plurality of holes through which the end portions of the cooling medium circulation tubes 11 are inserted are open.
  • each of the cooling medium circulation tubes 11 of the tube group 13 A on the downstream side in the blowing direction is inserted into the corresponding hole so as to communicate with the inside of the tank and is fixed by brazing or the like.
  • a cooling medium inlet tube 14 a which is connected to the external upstream side cooling medium pipe 7 communicates with the inside of the tank and is connected thereto by brazing.
  • each of the cooling medium circulation tubes 11 of the tube group 13 B on the upstream side in the blowing direction is inserted into the corresponding hole so as to communicate with the inside of the tank and is fixed by brazing or the like.
  • a cooling medium outlet tube 14 b which is connected to the external downstream side cooling medium pipe 7 communicates with the inside of the tank and is connected thereto by brazing.
  • the cooling medium inlet tube 14 a and the cooling medium outlet tube 14 b are formed so that the front end portions thereof airtightly penetrate through the passage wall of the blowing path 51 in the vehicle interior and are connected to the external upstream side cooling medium pipe 7 and downstream side cooling medium pipe 7 on the vehicle exterior, respectively.
  • an intermediate header tank 15 arranged on the other side (on the right in the figure) in the axial direction of the tubes is formed of a single tank so that the end portions of all the cooling medium circulation tubes 11 of both the tube groups 13 A and 13 B are inserted into corresponding holes for communication and are fixed by brazing or the like.
  • the gaseous cooling medium at high pressure and high temperature which flows into the inlet side header tank 14 A from the upstream side cooling medium pipe 7 via the cooling medium inlet tube 14 a is diffused in the inlet side header tank 14 A and at the same time reaches the inside of the intermediate header tank 15 on the opposite side through each of the cooling medium circulation tubes 11 of the tube group 13 A.
  • the cooling medium After joining together in the inside of the intermediate header tank 15 , the cooling medium is turned in the reverse direction, reaches the inside of the outlet tank 14 B through each of the cooling medium circulation tubes 11 of the tube group 13 B on the upstream side in the blowing direction, and flows out to the downstream side cooling medium pipe 7 from the cooling medium outlet tube 14 b.
  • the cooling medium passes through each of the cooling medium circulation tubes 11 of the two tube groups 13 A and 13 B as described above, the cooling medium dissipates heat through heat exchange with the blown air that is circulated while coming into contact with the outer surface of each of the tubes 11 and dissipates heat through heat exchange with the corrugated fins cooled by the blown air that comes into contact with the outer surface thereof, thereby being efficiently cooled, condensed, and liquefied.
  • a region close to the cooling medium inlet, through which the gaseous cooling medium at high temperature is circulated at high density in the tube group 13 A on the downstream side in the blowing direction overlaps a region close to the cooling medium outlet, through which the liquid cooling medium at low temperature condensed in the tube group 13 B on the upstream side in the blowing direction is circulated, in the blowing direction.
  • the difference between the temperatures of the cooling medium (or gas-to-liquid ratio) that is circulated through the tube groups 13 A and 13 B on the downstream side and on the upstream side in the blowing direction is reduced as the cooling medium is close to the intermediate header tank 15 on the opposite side.
  • the average value (average temperature or average gas-to-liquid ratio) of the cooling medium temperature (gas-to-liquid ratio) of the tube group 13 A on the downstream side in the blowing direction and the cooling medium temperature (gas-to-liquid ratio) of the tube group 13 B on the upstream side is made uniform. Accordingly, the temperature of the heating air that is blown into the vehicle interior while passing through the vehicle interior heat exchanger 1 for heat exchange is made uniform, and thus comfortable heating is able to be achieved.
  • the temperature difference between the vicinity of the cooling medium inlet and the vicinity of the cooling medium outlet is particularly large.
  • the temperature difference between the outlet and the inlet due to heat exchange with air is about 10° C. (sensible heat change).
  • the temperature difference between the outlet and the inlet is about 10° C. (latent heat change).
  • the cooling medium flows into the inlet side in a completely gasified state at high temperature and flows out from the outlet side in a low-temperature liquid state of being condensed by heat dissipation. Therefore, the temperature difference between the outlet and the inlet is as large as about 30° C. (latent heat change).
  • the inlet and outlet side header tank is separately formed into the inlet side header tank 14 A and the outlet side header tank 14 B and are arranged with a space therebetween.
  • heat exchange between the high-temperature gaseous cooling medium in the inlet side header tank 14 A and the low-temperature liquid cooling medium cooled in the outlet side header tank 14 B is able to be effectively suppressed, thereby sufficiently suppressing a reduction in thermal efficiency.
  • cooling medium outlet tube 14 b is arranged at the lower end portion of the outlet tank 14 B, the liquid cooling medium and an oil contained in the cooling medium smoothly flow out from the cooling medium outlet tube 14 b and is prevented from staying at the lower portion of the outlet tank 14 B, thereby maintaining favorable thermal efficiency.
  • FIGS. 4 and 5 illustrate a second embodiment in which an inlet and outlet side header tank 21 for the cooling medium is integrated.
  • an inlet side header tank member 21 A and an outlet side header tank member 21 B are connected by a pair of plates 21 C and 21 D that circumscribe the circular cross-sections thereof and are integrated into a shape in which the entire outer cross-sections of the upper and lower ends are blocked by lid members.
  • Other configurations are the same as those of the first embodiment, and a cooling medium inlet tube 21 a and a cooling medium outlet tube 21 b are connected to corresponding positions of the integrated inlet and outlet side header tank 21 .
  • both the tube groups 13 A and 13 B are connected to and supported by the integrated tanks on both sides in the tube axis direction, and thus the strength of the entire heat exchanger 1 is increased.
  • the integrated tank enables the cooling medium circulation tubes 11 of both the tube groups 13 A and 13 B to be simultaneously assembled to the inlet side header tank 21 A and the outlet side header tank 21 B, and thus the manufacturing efficiency of the heat exchanger is increased.
  • FIGS. 6 and 7 illustrate a third embodiment, in which inlet and outlet side header tanks for the cooling medium are integrated in another form.
  • An inlet and outlet side header tank 31 is integrally formed in a box shape having the same outer shape as the intermediate header tank 15 , and the tank internal space is partitioned into an inlet side header tank 31 A to which the inlet side tube group 13 A is connected for communication and an outlet side header tank 31 B to which the outlet side tube group 13 B is connected for communication by a partition wall 32 .
  • a cooling medium inlet tube 31 a is connected to the upper end portion of the inlet side header tank 31 A, and a cooling medium outlet tube 31 b is connected to the lower end portion of the outlet side header tank 31 B.
  • the region in the vicinity of the cooling medium inlet tube 31 a is a part where the high-temperature gaseous cooling medium directly flows in and thus has the highest temperature.
  • the region in the vicinity of the cooling medium outlet tube 31 b is a part where the cooled liquid cooling media flowing out from the cooling medium circulation tubes 11 of the tube group 13 B join together and thus has the lowest temperature.
  • cooling medium inlet tube 31 a and the cooling medium outlet tube 31 b are disposed at diagonal positions which are farthest from each other in the inlet and outlet side header tank 31 , and thus the region which has the highest temperature is able to be located away from the region which has the lowest temperature in the heat exchanger as far as possible. Therefore, heat exchange between the high-temperature region and the low-temperature region is suppressed, thereby maintaining favorable thermal efficiency.
  • an increase in the strength of the tank as a result of the integration as the inlet and outlet side header tank 31 , an increase in the strength of the entire heat exchanger 1 as a result of connecting and supporting both of the tube groups 13 A and 13 B to the integrated tanks on both sides in the tube axis direction, and an increase in the manufacturing efficiency of the heat exchanger as a result of enabling the cooling medium circulation tubes 11 of the tube groups 13 A and 13 B to be simultaneously assembled to the integrated tanks are the same as those in the second embodiment.
  • the inlet and outlet side header tank 31 and the intermediate header tank 15 are generalized by using members having the same outer shape, and the partition wall 32 is formed by connecting a partition plate as a separate member, thereby achieving a reduction in cost.
  • the embodiments described above have a configuration in which the vehicle interior heat exchanger 1 is switched between the operations of a condenser and an evaporator.
  • the configuration according to the present invention may be applied to a condenser of a system having a configuration in which a condenser and an evaporator are provided separately on the blowing path in the vehicle interior so as to be switched depending on heating and cooling.

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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)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US13/695,612 2010-04-28 2011-04-15 Vehicle Interior Heat Exchanger Abandoned US20130048260A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2010-102876 2010-04-28
JP2010102876A JP2011230655A (ja) 2010-04-28 2010-04-28 車室内熱交換器
PCT/JP2011/059399 WO2011136047A1 (ja) 2010-04-28 2011-04-15 車室内熱交換器

Publications (1)

Publication Number Publication Date
US20130048260A1 true US20130048260A1 (en) 2013-02-28

Family

ID=44861355

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/695,612 Abandoned US20130048260A1 (en) 2010-04-28 2011-04-15 Vehicle Interior Heat Exchanger

Country Status (5)

Country Link
US (1) US20130048260A1 (zh)
EP (1) EP2565571A4 (zh)
JP (1) JP2011230655A (zh)
CN (1) CN102869942A (zh)
WO (1) WO2011136047A1 (zh)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2521113A (en) * 2013-10-11 2015-06-17 Reaction Engines Ltd Heat exchangers
EP3514812A4 (en) * 2016-09-13 2019-09-04 Mitsubishi Electric Corporation TRANSFORMER FOR VEHICLE
US11162424B2 (en) 2013-10-11 2021-11-02 Reaction Engines Ltd Heat exchangers
US11384988B2 (en) 2017-06-13 2022-07-12 Denso Corporation Heat exchanger

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Publication number Priority date Publication date Assignee Title
JP5913913B2 (ja) * 2011-11-07 2016-04-27 サンデンホールディングス株式会社 室内側凝縮器
US9671176B2 (en) * 2012-05-18 2017-06-06 Modine Manufacturing Company Heat exchanger, and method for transferring heat
JP2014055735A (ja) * 2012-09-13 2014-03-27 Denso Corp 冷媒放熱器
JP2015055409A (ja) * 2013-09-11 2015-03-23 ダイキン工業株式会社 熱交換器および空気調和機
DE102017114993A1 (de) 2016-07-27 2018-02-01 Hanon Systems Vorrichtung zur Wärmeübertragung und Verfahren zum Betreiben der Vorrichtung
JP2020100255A (ja) * 2018-12-21 2020-07-02 サンデン・オートモーティブクライメイトシステム株式会社 凝縮器、車両用空気調和装置
JP2020152158A (ja) * 2019-03-18 2020-09-24 サンデンホールディングス株式会社 温度調節装置
CN112880432A (zh) * 2021-02-02 2021-06-01 格力电器（武汉）有限公司 换热管组件、微通道换热器、空调系统及换热器设计方法

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2521113A (en) * 2013-10-11 2015-06-17 Reaction Engines Ltd Heat exchangers
GB2521113B (en) * 2013-10-11 2017-05-24 Reaction Engines Ltd Heat exchangers
US11162424B2 (en) 2013-10-11 2021-11-02 Reaction Engines Ltd Heat exchangers
US11203975B2 (en) 2013-10-11 2021-12-21 Reaction Engines Ltd Heat exchangers
US11661888B2 (en) 2013-10-11 2023-05-30 Reaction Engines Ltd. Heat exchangers
EP3514812A4 (en) * 2016-09-13 2019-09-04 Mitsubishi Electric Corporation TRANSFORMER FOR VEHICLE
US11384988B2 (en) 2017-06-13 2022-07-12 Denso Corporation Heat exchanger

Also Published As

Publication number Publication date
CN102869942A (zh) 2013-01-09
JP2011230655A (ja) 2011-11-17
WO2011136047A1 (ja) 2011-11-03
EP2565571A4 (en) 2014-09-24
EP2565571A1 (en) 2013-03-06

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