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EP1054225A1 - Plattenwärmetauscher für drei fluide und verfahren zu dessen herstellung - Google Patents

Plattenwärmetauscher für drei fluide und verfahren zu dessen herstellung Download PDF

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Publication number
EP1054225A1
EP1054225A1 EP99959689A EP99959689A EP1054225A1 EP 1054225 A1 EP1054225 A1 EP 1054225A1 EP 99959689 A EP99959689 A EP 99959689A EP 99959689 A EP99959689 A EP 99959689A EP 1054225 A1 EP1054225 A1 EP 1054225A1
Authority
EP
European Patent Office
Prior art keywords
fluid
interplate
heat exchange
exchange section
plates
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.)
Granted
Application number
EP99959689A
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English (en)
French (fr)
Other versions
EP1054225A4 (de
EP1054225B1 (de
Inventor
Yasunari Furukawa
Norio Uedono
Naoyuki Inoue
Akiyoshi Suzuki
Kaoru Watanabe
Hidemitsu Hideshima
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.)
Ebara Corp
Original Assignee
Ebara 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 Ebara Corp filed Critical Ebara Corp
Publication of EP1054225A1 publication Critical patent/EP1054225A1/de
Publication of EP1054225A4 publication Critical patent/EP1054225A4/de
Application granted granted Critical
Publication of EP1054225B1 publication Critical patent/EP1054225B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/008—Sorption machines, plants or systems, operating continuously, e.g. absorption type with multi-stage operation
    • 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
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/02—Sorption machines, plants or systems, operating continuously, e.g. absorption type without inert gas
    • F25B15/06—Sorption machines, plants or systems, operating continuously, e.g. absorption type without inert gas the refrigerant being water vapour evaporated from a salt solution, e.g. lithium bromide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling
    • F28F2270/02—Thermal insulation; Thermal decoupling by using blind conduits

Definitions

  • the present invention relates to a plate beat exchanger for three fluids, and more particularly to a plate heat exchanger for three fluids, which allows a first fluid to exchange heat with a second fluid, and then with a third fluid, and also to a method for producing the heat exchanger.
  • a preceding-stage heat exchange section 13A having interplate first fluid paths f1 for passing a first fluid La between the plates 15 and interplate second fluid paths f2 for passing a second fluid Lc between the plates 15 is formed at one side in a plate longitudinal direction of a plate laminate composed of many plates 15 laminated one on another.
  • the interplate first fluid paths f1 and the interplate second fluid paths f2 are positioned alternately in a plate laminating direction.
  • a succeeding-stage heat exchange section 13B having interplate first fluid paths f1 continued from the interplate first fluid paths f1 in the preceding-stage heat exchange section 13A and adapted to pass the first fluid La between the plates 15 and interplate third fluid paths f3 for passing a third fluid Lb between the plates 15 is formed at the other side in the plate longitudinal direction of the plate laminate.
  • the interplate first fluid paths f1 and the interplate third fluid paths f3 are positioned alternately in the plate laminating direction (see Japanese laid-open Patent Publication No. 9-60996).
  • the heat exchanger has a structure in which the preceding-stage heat exchange section 13A for exchanging heat between the first fluid La and the second fluid Lc, and the succeeding-stage heat exchange section 13B for exchanging heat between the first fluid La and the third fluid Lb are located parallel in the longitudinal direction of the plates 15 and integrated together.
  • Such a conventional structure can make the entire heat exchanger considerably compact in comparison with the preceding-stage heat exchange section 13A and the succeeding-stage heat exchange section 13B being composed of separate plate heat exchangers.
  • the conventional heat exchanger still has room for improvement in view of the fact that further downsizing of the equipments and further energy saving have been demanded in recent years.
  • the present invention has been made in view of the above drawbacks. It is therefore an object of the present invention mainly to ensure further compactness and achieve a further decrease in a heat loss, by adopting a rational structure in integrating the preceding-stage heat exchange section and the succeeding-stage heat exchange section.
  • FIG. 1 shows a schematic structure of an absorption refrigerating machine, in which the reference numeral 1 denotes a high temperature regenerator, 2 a low temperature regenerator, 3 a condenser, 4 an evaporator, and 5 an absorber.
  • a low concentration absorption solution La e.g., an aqueous solution of lithium bromide
  • a refrigerant R e.g., water
  • An intermediate concentration absorption solution Lb from which the refrigerant R has been separated in the high temperature regenerator 1 is sent to the low temperature regenerator 2 via a passage r1.
  • a refrigerant vapor R' generated in the high temperature regenerator 1 is sent as a heat source to a low temperature heater 7 in the low temperature regenerator 2 via a passage r2.
  • the intermediate concentration absorption solution Lb is heated by the refrigerant vapor R' as a heat source which has been generated in the high temperature regenerator 1, for thereby further evaporating and separating the refrigerant R from the intermediate concentration absorption solution Lb.
  • the refrigerant vapor R' generated in the low temperature regenerator 2 and the refrigerant vapor R' which has been used as a heat source in the low temperature heater 7 are cooled by a cooler 8 in the condenser 3 to be condensed.
  • the condensed refrigerant R i.e., a liquid refrigerant
  • the condensed refrigerant R sent from the condenser 3 is sprayed onto an interior heat exchanger 11 by a sprayer 10, while the refrigerant R is being circulated by a refrigerant pump 9A, for thereby cooling a fluid C to be cooled (e.g., water or brine) flowing in the interior heat exchanger 11 by evaporating the refrigerant R and utilizing the heat of vaporization thereof.
  • a fluid C to be cooled e.g., water or brine
  • a high concentration absorption solution Lc from which the refrigerant R has been separated in the low temperature regenerator 2 is sent to the absorber 5 via a passage r4.
  • the high concentration absorption solution Lc sent from the low temperature regenerator 2 is sprayed by a sprayer 12, and hence absorbs the refrigerant vapor R' generated in the evaporator 4, forming a low pressure atmosphere for evaporating the sprayed refrigerant R at a low temperature in the evaporator 4.
  • the low concentration absorption solution La which has absorbed the refrigerant vapor R' in the absorber 5 is returned to the high temperature regenerator 1 via a passage r5 by a solution pump 9B, and the step of separating the refrigerant R from the low concentration absorption solution La is conducted again.
  • the reference numeral 13 denotes a heat recovery type heat exchanger for allowing the low concentration absorption solution La having a low temperature which is to be returned to the high temperature regenerator 1 to exchange heat with the high concentration absorption solution Lc having an intermediate temperature which is to be sent from the low temperature regenerator 2 to the absorber 5, and then to exchange heat with the intermediate concentration absorption solution Lb having a high temperature which is to be sent from the high temperature regenerator 1 to the low temperature regenerator 2, for thereby recovering the heat that the high concentration absorption solution Lc and the intermediate concentration absorption solution Lb hold.
  • the heat recovery type heat exchanger 13 is shown only schematically to describe the order of heat exchange of the low concentration absorption solution La with the high concentration absorption solution Lc and the intermediate concentration absorption solution Lb, and does not correspond with its concrete structure to be described later on.
  • the reference numeral 14 denotes a cooler for removing the heat of absorption generated at the time when the sprayed absorption solution Lc in the absorber 5 absorbs the refrigerant.
  • a cooling fluid W e.g., cooling water circulated into a cooling tower
  • W is supplied to the cooler 14 in the absorber 5 and the cooler 8 in the condenser 3.
  • the heat recovery type heat exchanger 13 for exchanging heat among three fluids i.e., the low concentration absorption solution La, the high concentration absorption solution Lc, and the intermediate concentration absorption solution Lb (hereinafter respectively referred to as a first fluid, a second fluid, and a third fluid), is constructed in the following manner:
  • a plate 15 has a corrugated cross-sectional shape, except its portions near both ends thereof, and has holes p1 to p4 for inlet and outlet path at corners thereof.
  • a plurality of the plates 15 are laminated in such a state that the ridges of the corrugations of the plates 15 are contacted with those of the facing plates.
  • FIG. 1 the low concentration absorption solution La
  • Lc high concentration absorption solution
  • Lb intermediate concentration absorption solution Lb
  • a preceding-stage heat exchange section 13A for exchanging heat between the first fluid La and the second fluid Lc is formed at one side of the plate laminate in a plate laminating direction.
  • a succeeding-stage heat exchange section 13B for exchanging heat between the first fluid La which has exchanged heat with the second fluid Lc in the preceding-stage heat exchange section 13A and the third fluid Lb is formed at the other side of the plate laminate in the plate laminating direction.
  • interplate first fluid paths f1 for passing the first fluid La between the adjacent plates 15 and interplate second fluid paths f2 for passing the second fluid Lc between the adjacent plates 15 are positioned alternately in the plate laminating direction. While these fluids are passing through these interplate fluid paths f1 and f2, heat is exchanged between the first fluid La and the second fluid Lc via the plates 15 serving as heat transfer walls.
  • interplate first fluid paths f1 for passing the first fluid La between the adjacent plates 15 and interplate third fluid paths f3 for passing the third fluid Lb between the adjacent plates 15 are positioned alternately in the plate laminating direction. While these fluids are passing through these interplate fluid paths f1 and f3, heat is exchanged between the first fluid La and the third fluid Lb via the plates 15 serving as heat transfer walls.
  • the interplate fluid paths f1 to f3 are finely divided into many segments in the plate width direction perpendicular to the fluid flowing direction. Thus, a larger area of heat transfer can be ensured, and high strength can be obtained.
  • each plate 15 near both ends thereof are in the form of a flat plate without corrugations, headers for the passages finely divided in the plate width direction are formed at both end portions of the interplate fluid paths f1 to f3.
  • the holes p1 among the holes p1 to p4 for inlet and outlet path formed at the four corners of the respective plates 15 constitute a first fluid crossover path m which extends between the headers beside one end of the interplate first fluid paths f1 in the preceding-stage heat exchange section 13A and the headers beside one end of the interplate first fluid paths f1 in the succeeding-stage heat exchange section 13B inside the plate laminate.
  • FIG. 2 represents a vertical cross-sectional view of the heat exchanger 13 with overlaps of these flow paths being developed.
  • the hole p4 located at a diagonal position to the hole p1 forming the first fluid crossover path m constitutes a first fluid inlet path i1 which extends between the headers beside the other end of the interplate first fluid paths f1 in the preceding-stage heat exchange section 13A inside the plate laminate.
  • the hole p4 further constitutes a first fluid outlet path o1 which extends between the headers beside the other end of the interplate first fluid paths f1 in the succeeding-stage heat exchange section 13B inside the plate laminate.
  • the hole p2 located adjacent, in the plate width direction, to the hole p1 forming the first fluid crossover path m constitutes a second fluid inlet path i2 which extends between the headers beside the one end of the interplate second fluid paths f2 in the preceding-stage heat exchange section 13A inside the plate laminate.
  • the hole p2 further constitutes a third fluid outlet path o3 which extends between headers beside the one end of the interplate third fluid paths f3 in the succeeding-stage heat exchange section 13B inside the plate laminate.
  • the neck d of the hole p2 extends to the corresponding hole p2 of the next plate 15 in the lamination of the plates 15, and hence each of communications is blocked between the second fluid inlet path i2 and the interplate first fluid paths f1, and between the third fluid outlet path o3 and the interplate first fluid paths f1.
  • the remaining hole p3 constitutes a second fluid outlet path o2 which extends between the headers beside the other end of the interplate second fluid paths f2 in the preceding-stage heat exchange section 13A inside the plate laminate, and constitutes a third fluid inlet path i3 which extends between the headers beside the other end of the interplate third fluid paths f3 in the succeeding-stage heat exchange section 13B inside the plate laminate.
  • the neck d of the hole p3 of the plate 15 extends to the corresponding hole p3 of the next plate 15 in the lamination of the plates 15, as in the case of the other inlet and outlet paths, and hence each of communications is blocked between the second fluid outlet path o2 and the interplate first fluid paths f1, and between the third fluid inlet path i3 and the interplate first fluid paths f1.
  • the first fluid La flows as parallel streams from the first fluid inlet path i1 into a plurality of the interplate first fluid paths f1 in the preceding-stage heat exchange section 13A. Subsequently, the first fluid La having passed as parallel streams through a plurality of the interplate first fluid paths f1 in the preceding-stage heat exchange section 13A is gathered at the first fluid crossover path m, and then flows as parallel streams into a plurality of the interplate first fluid paths f1 in the succeeding-stage heat exchange section 13B. Then, the first fluid La having passed as parallel streams through a plurality of the interplate first fluid paths f1 in the succeeding-stage heat exchange section 13B is discharged in a gathered state from the first fluid outlet path o1.
  • the second fluid Lc flows from the second fluid inlet path i2 into a plurality of the interplate second fluid paths f2 as parallel streams in the preceding-stage heat exchange section 13A.
  • the second fluid Lc having passed through a plurality of the interplate second fluid paths f2 as parallel streams is discharged in a gathered state from the second fluid outlet path o2, and hence the first fluid La (low concentration absorption solution) exchanges heat with the second fluid Lc (high concentration absorption solution) as countercurrent flows at a plurality of the paths in the preceding-stage heat exchange section 13A.
  • the third fluid Lb flows from the third fluid inlet path i3 into a plurality of the interplate third fluid paths f3 as parallel streams.
  • the third fluid Lb having passed through a plurality of the interplate third fluid paths f3 as parallel streams is discharged in a gathered state from the third fluid outlet path o3, and hence the first fluid La (low concentration absorption solution) which has exchanged heat with the second fluid Lc (high concentration absorption solution) in the preceding-stage heat exchange section 13A exchanges heat with the third fluid Lb (intermediate concentration absorption solution) as countercurrent flows at a plurality of the paths in the succeeding-stage heat exchange section 13B.
  • the holes p1 constituting the first fluid crossover path m are blocked by the plates 15 located at both ends in the plate laminating direction of the plate laminate.
  • the plate laminate described above has a structure in which the preceding-stage heat exchange section 13A and the succeeding-stage heat exchange section 13B are arranged parallel in the plate laminating direction, and integrated.
  • the two adjacent plates 15 located at the boundary between the preceding-stage heat exchange section 13A and the succeeding-stage heat exchange section 13B block the holes p2 to p4 except the holes p1 constituting the first fluid crossover path m.
  • the neck d of one of the holes p1 constituting the first fluid crossover path m in these two adjacent plates 15 extends to the other corresponding hole p1.
  • the two adjacent plates 15 located at the boundary form an airtight space under vacuum state.
  • this interplate airtight space under vacuum serves as a vacuum heat insulating layer 16, for thereby preventing a heat loss due to heat transfer between the preceding-stage heat exchange section 13A and the succeeding-stage heat exchange section 13B.
  • the plates 15 are laminated in such a state that a brazing material is put between bonding-required portions, such as the portions between folded-back peripheral edges of the adjacent plates 15, the portions between the neck d of each of the holes p1 to p4 and each of the corresponding holes p1 to p4 to which the neck d extends, and the like.
  • bonding-required portions such as the portions between folded-back peripheral edges of the adjacent plates 15, the portions between the neck d of each of the holes p1 to p4 and each of the corresponding holes p1 to p4 to which the neck d extends, and the like.
  • this brazing under vacuum results in the bonding of the plates 15 and the formation of the above-mentioned airtight space under vacuum as the vacuum heat insulating layer 16 between the adjacent plates 15 located at the boundary between the preceding-stage heat exchange section 13A and the succeeding-stage heat exchange section 13B, at the same time.
  • each of the portions between three or more of the adjacent plates 15 located at the boundary between the preceding-stage heat exchange section 13A and the succeeding-stage heat exchange section 13B may form the vacuum heat insulating layer 16.
  • vacuum brazing was used for bonding the plates 15 and forming the vacuum heat insulating layer 16 at the same time.
  • an airtight space may be formed between the plates 15 located at the boundary between the two heat exchange sections 13A and 13B by bonding the plates 15, and then a vacuum heat insulating layer 16 may be formed by bleeding air from this airtight space.
  • the higher effect of insulating heat can be obtained, as the degree of vacuum in the vacuum heat insulating layer 16 is higher.
  • the proper degree of vacuum in the vacuum heat insulating layer 16 may be concretely determined depending on various conditions. A high degree of vacuum is not always necessary for the vacuum heat insulating layer 16.
  • a heat insulating material or a gas may be filled between the plates 15 located at the boundary between the preceding-stage heat exchange section 13A and the succeeding-stage heat exchange section 13B to form a heat insulating layer between the plates 15, instead of providing the vacuum heat insulating layer 16.
  • the number of the interplate fluid paths f1, f2 arranged parallel in the preceding-stage heat exchange section 13A, and the number of the interplate fluid paths f1, f3 arranged parallel in the succeeding-stage heat exchange section 13B may be determined by the required amount of heat exchange, respectively, and is not restricted to the number of them that was shown in the above embodiment.
  • various method can be applied as concrete methods for brazing the plates 15 in a vacuum atmosphere.
  • the degree of vacuum and a rarefied gas during brazing may also be determined depending on various conditions.
  • the plate heat exchanger for three fluids according to the present invention can be applied not only to exchange heat between absorption solutions in an absorption refrigerating machine, but also to exchange heat between various fluids.
  • the present invention relates to a plate heat exchanger for three fluids, which flows two fluids alternately between plates in a laminate of plates, whereby a first fluid exchanges heat with a second fluid, and then the first fluid further exchanges heat with a third fluid.
  • the present invention can be used for a refrigerator such as an absorption refrigerating machine.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP99959689A 1998-12-08 1999-12-08 Plattenwärmetauscher für drei fluide und verfahren zu dessen herstellung Expired - Lifetime EP1054225B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP34827798 1998-12-08
JP34827798A JP3936088B2 (ja) 1998-12-08 1998-12-08 三流体用プレート式熱交換器、及び、その製造方法
PCT/JP1999/006864 WO2000034729A1 (fr) 1998-12-08 1999-12-08 Echangeur thermique du type a plaques pour trois fluides et procede de fabrication

Publications (3)

Publication Number Publication Date
EP1054225A1 true EP1054225A1 (de) 2000-11-22
EP1054225A4 EP1054225A4 (de) 2005-01-12
EP1054225B1 EP1054225B1 (de) 2007-06-13

Family

ID=18395962

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99959689A Expired - Lifetime EP1054225B1 (de) 1998-12-08 1999-12-08 Plattenwärmetauscher für drei fluide und verfahren zu dessen herstellung

Country Status (5)

Country Link
EP (1) EP1054225B1 (de)
JP (1) JP3936088B2 (de)
CN (1) CN1172158C (de)
DE (1) DE69936288D1 (de)
WO (1) WO2000034729A1 (de)

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WO2003046461A1 (es) * 2001-11-23 2003-06-05 Rotartica, S.A. Termocambiador compacto de placas
FR2846733A1 (fr) * 2002-10-31 2004-05-07 Valeo Thermique Moteur Sa Condenseur, notamment pour un circuit de cimatisation de vehicule automobile, et circuit comprenant ce condenseur
FR2846736A1 (fr) * 2002-10-31 2004-05-07 Valeo Thermique Moteur Sa Module d'echange de chaleur a plaques empilees, notamment pour un vehicule automobile
WO2004092663A1 (en) * 2003-04-17 2004-10-28 Ep Technology Ab Evaporator and heat exchanger with external loop, as well as heat pump system and air conditioning system comprising said evaporator or heat exchanger
WO2004113815A1 (de) * 2003-06-25 2004-12-29 Behr Gmbh & Co. Kg Vorrichtung zum mehrstufigen wärmeaustausch und verfahren zur herstellung einer derartigen vorrichtung
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DE102016101677B4 (de) 2016-01-29 2022-02-17 TTZ GmbH & Co. KG Plattenwärmeübertragervorrichtung und Vorrichtung zur Nutzung von Abwärme
JP6993862B2 (ja) * 2017-12-14 2022-01-14 株式会社マーレ フィルターシステムズ オイルクーラ
JP6865934B2 (ja) * 2018-07-18 2021-04-28 オリオン機械株式会社 プレート式熱交換器
CN110567297B (zh) * 2019-09-20 2021-04-23 安徽普泛能源技术有限公司 一种三相换热器及其吸收式制冷系统
KR102723560B1 (ko) 2022-03-11 2024-10-29 에스트라오토모티브시스템 주식회사 차량용 통합 열교환기
JP2024132223A (ja) * 2023-03-17 2024-09-30 三菱重工サーマルシステムズ株式会社 車両用温調システムおよび熱交換器

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ES2188415A1 (es) * 2001-11-23 2003-06-16 Rotartica S A Termocambiador compacto de placas.
WO2003046461A1 (es) * 2001-11-23 2003-06-05 Rotartica, S.A. Termocambiador compacto de placas
US7469554B2 (en) 2002-10-31 2008-12-30 Valeo Systeme Thermiques Condenser, in particular for a motor vehicle air conditioning circuit, and circuit comprising same
FR2846733A1 (fr) * 2002-10-31 2004-05-07 Valeo Thermique Moteur Sa Condenseur, notamment pour un circuit de cimatisation de vehicule automobile, et circuit comprenant ce condenseur
FR2846736A1 (fr) * 2002-10-31 2004-05-07 Valeo Thermique Moteur Sa Module d'echange de chaleur a plaques empilees, notamment pour un vehicule automobile
WO2004042293A1 (fr) * 2002-10-31 2004-05-21 Valeo Thermique Moteur Condenseur, notamment pour un circuit de climatisation de vehicule automobile, et circuit comprenant ce condenseur
WO2004042312A1 (fr) * 2002-10-31 2004-05-21 Valeo Thermique Moteur Module d'echange a plaque empilees, notamment pour un vehicule automobile
US8122736B2 (en) 2002-10-31 2012-02-28 Valeo Systemes Thermiques Condenser for a motor vehicle air conditioning circuit, and circuit comprising same
WO2004092663A1 (en) * 2003-04-17 2004-10-28 Ep Technology Ab Evaporator and heat exchanger with external loop, as well as heat pump system and air conditioning system comprising said evaporator or heat exchanger
US7334431B2 (en) 2003-04-17 2008-02-26 Ep Technology Ab Evaporator and heat exchanger with external loop, as well as heat pump system and air conditioning system comprising said evaporator or heat exchanger
JP2007506928A (ja) * 2003-06-25 2007-03-22 ベール ゲーエムベーハー ウント コー カーゲー 多段熱交換装置およびこのような装置を製造するための方法
WO2004113815A1 (de) * 2003-06-25 2004-12-29 Behr Gmbh & Co. Kg Vorrichtung zum mehrstufigen wärmeaustausch und verfahren zur herstellung einer derartigen vorrichtung
DE102004020602A1 (de) * 2004-04-27 2005-12-01 Mahle Filtersysteme Gmbh Plattenwärmetauscher mit Strömungswegen für drei Wärmetauschfluide
EP2080976A1 (de) * 2008-01-15 2009-07-22 KIOTO Clear Energy AG Wärmetauscher
US20130146246A1 (en) * 2011-12-07 2013-06-13 Hyundai Motor Company Heat exchanger for lpi vehicle
DE102012105604B4 (de) * 2011-12-07 2021-05-06 Hyundai Motor Company Wärmetauscher für ein Fahrzeug
JP2015207535A (ja) * 2014-04-23 2015-11-19 京セラ株式会社 燃料電池装置
EP3388772A4 (de) * 2015-12-11 2019-01-02 Mitsubishi Electric Corporation Plattenförmiger wärmetauscher und kühlzyklusvorrichtung
US10697677B2 (en) 2015-12-11 2020-06-30 Mitsubishi Electric Corporation Plate type heat exchanger and refrigeration cycle apparatus
WO2018013054A1 (en) * 2016-07-11 2018-01-18 National University Of Singapore A multi-fluid heat exchanger
US10883767B2 (en) 2016-07-11 2021-01-05 National University Of Singapore Multi-fluid heat exchanger
EP3511666A4 (de) * 2016-09-09 2019-09-25 Mitsubishi Electric Corporation Plattenartiger wärmetauscher und kühlzyklusvorrichtung
EP3524913A4 (de) * 2016-10-07 2019-10-16 Sumitomo Precision Products Co., Ltd. Wärmetauscher
US11022376B2 (en) 2016-10-07 2021-06-01 Sumitomo Precision Products Co., Ltd. Heat exchanger
WO2020136092A3 (en) * 2018-12-28 2020-08-13 Mahle Filter Systems Japan Corporation Heat exchanger and vehicle heat exchange system

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DE69936288D1 (de) 2007-07-26
EP1054225A4 (de) 2005-01-12
JP2000171177A (ja) 2000-06-23
JP3936088B2 (ja) 2007-06-27
CN1290338A (zh) 2001-04-04
CN1172158C (zh) 2004-10-20
EP1054225B1 (de) 2007-06-13
WO2000034729A1 (fr) 2000-06-15

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