EP2420791A2 - Échangeur thermique à plaques - Google Patents

Échangeur thermique à plaques Download PDF

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Publication number
EP2420791A2
EP2420791A2 EP10764664A EP10764664A EP2420791A2 EP 2420791 A2 EP2420791 A2 EP 2420791A2 EP 10764664 A EP10764664 A EP 10764664A EP 10764664 A EP10764664 A EP 10764664A EP 2420791 A2 EP2420791 A2 EP 2420791A2
Authority
EP
European Patent Office
Prior art keywords
plate
flow
heat exchange
fluid
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP10764664A
Other languages
German (de)
English (en)
Other versions
EP2420791A4 (fr
Inventor
Sang Chul Han
Sin Ii Choi
Rak Gyun Kim
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.)
Estra Automotive Systems Co Ltd
Original Assignee
Estra Automotive Systems Co Ltd
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 Estra Automotive Systems Co Ltd filed Critical Estra Automotive Systems Co Ltd
Publication of EP2420791A2 publication Critical patent/EP2420791A2/fr
Publication of EP2420791A4 publication Critical patent/EP2420791A4/fr
Withdrawn legal-status Critical Current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
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits

Definitions

  • the present invention relates, in general, to a plate heat exchanger and, more particularly, to a plate heat exchanger which can increase the fluidity of a fluid, thereby realizing improved heat exchange efficiency.
  • a heat exchanger is a device for transferring heat from a higher temperature fluid to a lower temperature fluid through a heat transfer wall, and is used in an air conditioning system, a transmission oil cooler, etc. of an automobile. To be accommodated in a limited space in which the heat exchanger is installed, it is required to realize compactness of the heat exchanger and, accordingly, a plate heat exchanger has been widely used.
  • the plate heat exchanger includes a plurality of heat exchange elements that are stacked to define a flow channel between neighboring plates of the elements.
  • the flow channel includes at least two flow channels through which different heat exchange medium can flow.
  • the different heat exchange medium exchange heat with each other through the heat exchange elements when the medium pass through the respective flow channels.
  • each of the respective plates of the heat exchange elements has an inlet port and an outlet port in opposite ends thereof, wherein the inlet ports and the outlet ports of the respective plates communicate with each other.
  • An inlet cap and an outlet cap are mounted to the inlet and outlet ports of the uppermost plate by brazing, etc.
  • a heat exchange element of a conventional plate heat exchanger is fabricated by assembling a pair of plates 1 and 2 with each other.
  • a plurality of diagonal grooves 1a and 2a are formed by embossing the plates 1 and 2 in such a way that the grooves 1a and 2a extend diagonally.
  • the grooves 1a and 2a form a flow channel.
  • opposite ends of the respective plates 1 and 2 are provided with respective through holes 1b and 2b for forming an inlet port and an outlet port. Depressed edges 1c and 2c are formed around the respective through holes 1b and 2b.
  • a fluid in the flow channel flows along the grooves 1a and 2a of the respective plates 1 and 2, so that the fluid flows in an diagonal direction. Therefore, the flow of fluid may easily stagnate on the depressed edges 1c and 2c around the through holes 1b and 2b, so that the conventional plate heat exchanger excessively reduces the fluidity of the fluid and, accordingly, reduces the heat exchange efficiency.
  • the present invention has been made keeping in mind the above problems occurring in the related art, and is intended to provide a plate heat exchanger which can increase the fluidity of a fluid, thereby realizing improved heat exchange efficiency.
  • the present invention provides a plate heat exchanger, including:
  • the upper flow grooves may extend to the areas around the upper flanges of the upper plate, with at least one upper subsidiary groove being formed in each of the upper flanges of the upper plate, wherein the at least one upper subsidiary groove intersects with the upper flow grooves.
  • the lower flow grooves may extend to the areas around the lower flanges of the lower plate, with at least one lower subsidiary groove being formed in each of the lower flanges of the lower plate, wherein the at least one lower subsidiary groove intersects with the lower flow grooves.
  • At least one upper spacing lug may be formed on an upper surface of the upper plate, and at least one lower spacing lug may be formed on a lower surface of the lower plate.
  • the upper spacing lug of each of the heat exchange elements may be in contact with the lower spacing lug of a neighboring heat exchange element, the upper spacing lug and the lower spacing lug having respective through holes on contact surfaces thereof so that the first flow channels of the heat exchange elements communicate with each other.
  • the plate heat exchanger according to the present invention uses a flow guide structure, by which the fluid can be guided in at least two flow directions in the area around the upper flange of the upper plate and/or around the lower flange of the lower plate, so that the present invention prevents stagnation of the fluid in the areas around the inlet ports and the outlet ports of the heat exchange elements and allows the fluid to smoothly and constantly flow for the whole length of the respective plates and, accordingly, increases the fluidity of the fluid and realizes improved heat exchange efficiency.
  • Figs. 1 through 7 show a plate heat exchanger according to an embodiment of the present invention.
  • the plate heat exchanger of the present invention includes a plurality of heat exchange elements 10, wherein the plurality of heat exchange elements 10 is stacked in such a way that one is laid on top of another.
  • each of the heat exchange elements 10 defines therein a first flow channel 18, through which a first fluid, such as oil or refrigerant, passes.
  • a first fluid such as oil or refrigerant
  • Each of the heat exchange elements 10 is formed by assembling an upper plate 11 with a lower plate 12 into a single structure.
  • the upper plate 11 and the lower plate 12 are made of a metal material having excellent heat conductivity, such as aluminum, and are joined together along the edges 11a and 12a by brazing.
  • the upper plate 11 and the lower plate 12 are provided on facing surfaces thereof with a plurality of flow grooves 11b and 12b. Described in detail, the lower surface of the upper plate 11 is provided with a plurality of upper flow grooves 11b and the upper surface of the lower plate 12 is provided with a plurality of lower flow grooves 12b.
  • the upper flow grooves 11b of the upper plate 11 and the lower flow grooves 12b of the lower plate 12 diagonally extend on a flat plane.
  • the upper plate 11 and the lower plate 12 are stacked in such a way that the upper flow grooves 11b of the upper plate 11 intersect with the lower flow grooves 12b of the lower plate 12.
  • the first flow channel 18 is defined in the heat exchange element 10. Therefore, in the heat exchange element 10, the first fluid, for example, oil, can flow zigzag through the first flow channel 18, so that the flow rate of the first fluid can be increased and the contact surface of the first fluid relative to the heat exchange element can be enlarged to realize improved heat exchange efficiency.
  • the first fluid for example, oil
  • the plurality of the flow grooves 11b and 12b may be formed by subjecting the upper and lower plates 11 and 12 to die-casting or pressing, such as stamping. Further, bulging parts 13a and 14a are formed in the heat exchange element 10 at locations opposed to the flow grooves 11b and 12b, with a plurality of depressed parts 13b and 14b defined between the plurality of bulging parts 13a and 14a. Due to the flow grooves 11b and 12b, the upper and lower plates 11 and 12 have respective wave structures 13 and 14.
  • each of the heat exchange elements 10 is provided with an inlet port 43 in one end thereof and with an outlet port 44 in the other end thereof.
  • the inlet port 43 and the outlet port 44 communicate with the first flow channel 18. Further, when the plurality of the heat exchange elements 10 are stacked, the inlet ports 43 and the outlet ports 44 of the elements 10 communicate with each other.
  • the upper plate 11 has an upper flange 23 which is raised upwards from each of the inlet and outlet ports 43 and 44
  • the lower plate 12 has a lower flange 24 which protrudes downwards from each of the inlet and outlet ports 43 and 44.
  • the upper flange 23 and the lower flange 24 are assembled with each other through fitting. Described in detail, the upper flanges 23 of a lower heat exchange element 10 may be fitted over the respective lower flanges 24 of an upper heat exchange element 10 or the lower flanges 24 of an upper heat exchange element 10 may be fitted into the respective upper flanges 23 of a lower heat exchange element 10, so that the desired fluid tightness can be realized.
  • the neighboring upper and lower flanges 23 and 24 may be integrated with each other by brazing in a leak proof manner. Therefore, the inlet ports 43 and the outlet ports 44 of the heat exchange elements 10 are hermetically sealed from a second flow channel 28.
  • an inlet fitting 25 is mounted to the upper flange 23 of the inlet port 43 and an outlet fitting 26 is mounted to the upper flange 23 of the outlet port 44.
  • the inlet fitting 25 has an opening 25a to which an inlet pipe is connected.
  • the outlet fitting 26 has an opening 26a to which an outlet pipe is connected.
  • the upper flow grooves 11b of the upper plate 11 extend to areas around the upper flanges 23 and the lower flow grooves 12b of the lower plate 12 extend to areas around the lower flange 24. Further, in the heat exchange element 10, the upper flow grooves 11bof the upper plate 11 intersect with the lower flow grooves 12b of the lower plate 12, thereby defining the first flow channel 18 having an intersecting structure. Therefore, when the first fluid is introduced from the inlet port 43 into the first flow channel 18, the first fluid flows zigzag both through the upper flow grooves 11b of the upper plate 11 and through the lower flow grooves 12b of the lower plate 12 prior to being discharged through the outlet port 44.
  • the present invention provides a flow guide structure capable of guiding the first fluid in such a way that the fluid can flow in at least two directions, in other words, the fluid can flow in radial directions in the areas around the inlet and outlet ports 43 and 44. Therefore, the present invention can prevent the stagnation of the first fluid and can realize increased fluidity of the first fluid.
  • the upper plate 11 is provided with at least one upper subsidiary groove 63 in an area around each of the upper flanges 23 and the lower plate 12 is provided with at least one lower subsidiary groove 64 in an area around each of the lower flanges 24.
  • the upper subsidiary groove 63 is formed by embossing, etc. in such a way that the upper subsidiary groove 63 can intersect with the upper flow grooves 11b of the upper plate 11 at a predetermined angle of intersection.
  • the upper flow grooves 11b of the upper plate 11 are formed on the rear surfaces of the bulging parts 13a of the wave structure 13, so that the bulging parts 13a and the upper flow grooves 11b are oriented in the same direction and, accordingly, the upper subsidiary groove 63 intersects with the bulging parts 13a at the predetermined angle of intersection. Therefore, in the area around each of the upper flanges 23 of the upper plate 11, the first fluid can flow in main flow directions (the directions designated by arrow K) in which the fluid flows along the upper flow grooves 11b and, at the same time, can flow in at least one subsidiary flow direction (the direction designated by arrow U) in which the fluid flows along at least one upper subsidiary groove 63.
  • the first fluid can cross-flow both in the main flow directions and in the at least one subsidiary flow direction, so that the first fluid can more evenly, smoothly and constantly flow for the whole length of the upper plate 11 with increased fluidity.
  • the lower subsidiary groove 64 is formed by embossing, etc. in such a way that the lower subsidiary groove 64 can intersect with the lower flow grooves 12b of the lower plate 12 at a predetermined angle of intersection.
  • the lower flow grooves 12b of the lower plate 12 are formed on the rear surfaces of the bulging parts 14a of the wave structure 14 and, accordingly, the bulging parts 14a and the lower flow grooves 12b are oriented in the same direction. Therefore, the lower subsidiary groove 64 intersects with the bulging parts 14a at the predetermined angle of intersection.
  • the first fluid can flow in main flow directions (the directions designated by arrow J) in which the fluid flows along the lower flow grooves 12b and, at the same time, can flow in at least one subsidiary flow direction (the direction designated by arrow W) in which the fluid flows along at least one lower subsidiary groove 64.
  • the first fluid can cross-flow both in the main flow directions and in the at least one subsidiary flow direction, so that the first fluid can more evenly, smoothly and constantly flow for the whole length of the lower plate 12 with increased fluidity.
  • At least one upper subsidiary groove 63 is formed in the area around each of the upper flanges 23 of the upper plate 11 and at least one lower subsidiary groove 64 is formed in the area around each of the lower flanges 24 of the lower plate 12, thereby guiding the first fluid to at least two flow directions in the area around each of the inlet and outlet ports 43 and 44 of the heat exchange element 10. Therefore, the present invention can prevent stagnation of the first fluid in the areas and, accordingly, can allow the fluid to smoothly and constantly flow for the whole length of the respective plates 11 and 12. That is, the present invention increases the fluidity of the first fluid and, accordingly, realizes improved heat exchange efficiency.
  • a second flow channel 28 through which a second fluid, such as cooling water, passes is defined between the stacked heat exchange elements 10.
  • the second flow channel 28 is defined because the plurality of heat exchange elements 10 are spaced apart from each other at a predetermined interval.
  • each of the heat exchange elements 10 that is, the upper surface of the upper plate 11 and the lower surface of the lower plate 12 are provided with a plurality of upper and lower spacing lugs 21 and 22.
  • the plurality of upper spacing lugs 21 are formed on the upper surface of each bulging part 13a of the upper plate 11 in such a way that the lugs 21 are spaced apart from each other at regular intervals.
  • the plurality of lower spacing lugs 22 are formed on the lower surface of each bulging part 14a of the lower plate 12 in such a way that the lugs 22 are spaced apart from each other at regular intervals.
  • the lower spacing lugs 22 of the upper heat exchange elements 10 are brought into contact with the upper spacing lugs 21 of the lower heat exchange elements 10. Because the plurality of upper and lower spacing lugs 21 and 22 are brought into contact with each other as described above, the interval between the stacked heat exchange elements 10 is increased and, accordingly, the sectional area of the second flow channel 28 is increased. Further, the spacing lugs 21 and 22 which are in contact with each other may be joined to each other by brazing, etc. The upper spacing lugs 21 and the corresponding lower spacing lugs 22 are located on points at which the upper flow grooves 11b and the lower flow grooves 12b intersect with each other, so that the stacked structure of the heat exchange elements can have a stable structure.
  • the spacing lugs 21 and 22 may be shaped in the form of any one of a trapezoidal cross-section, a curved cross-section, such as a circular or elliptical cross-section, and a square cross-section. Further, the upper surfaces 21a of the respective upper spacing lugs 21 can be brought into close contact with the lower surfaces 22a of the corresponding lower spacing lugs 22, so that the integration of the upper and lower plates 11 and 12 can be more easily accomplished.
  • the contact surfaces 21a and 22a of the upper and lower spacing lugs 21 and 22, that is, the upper surfaces 21a of upper spacing lugs 21 and the lower surfaces 22a of the lower spacing lugs 22 are provided with respective through holes 21c and 22c. Further, the through holes 21c and 22c of neighboring spacing lugs 21 and 22 which are in contact with each other communicate with each other. Therefore, the first flow channels 18 of the respective heat exchange elements 10 communicate with each other by means of the through holes 21c and 22c.
  • the first fluid, such as oil, inside a heat exchange element 10 can freely flow to the first flow channel 18 of a neighboring heat exchange element 10 through the through holes 21c and 22c, so that the first fluid can be mixed in all of the heat exchange elements 10 and, accordingly, desirably improves the heat exchange efficiency.
  • the upper plate 11 and the lower plate 12 have positioning grooves 11c and positioning protrusions 12c on corresponding ends 11a and 12a thereof. Due to the positioning grooves and positioning protrusions, the upper plate 11 and the lower plate 12 can be easily positioned and, accordingly, the preliminary assembly of the upper and lower plates 11 and 12 can be quickly finished during a process of assembling the plates. Therefore, the precise and firm assembly of the upper and lower plates 11 and 12 can be realized.

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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)
EP10764664.8A 2009-04-16 2010-04-15 Échangeur thermique à plaques Withdrawn EP2420791A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020090033219A KR100950689B1 (ko) 2009-04-16 2009-04-16 플레이트 열교환기
PCT/KR2010/002323 WO2010120125A2 (fr) 2009-04-16 2010-04-15 Échangeur thermique à plaques

Publications (2)

Publication Number Publication Date
EP2420791A2 true EP2420791A2 (fr) 2012-02-22
EP2420791A4 EP2420791A4 (fr) 2014-03-05

Family

ID=42184011

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10764664.8A Withdrawn EP2420791A4 (fr) 2009-04-16 2010-04-15 Échangeur thermique à plaques

Country Status (5)

Country Link
US (1) US20120031598A1 (fr)
EP (1) EP2420791A4 (fr)
KR (1) KR100950689B1 (fr)
CN (1) CN102395853B (fr)
WO (1) WO2010120125A2 (fr)

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CN104708293A (zh) * 2015-03-10 2015-06-17 胡桂林 换热器的制造方法
WO2015086343A1 (fr) * 2013-12-10 2015-06-18 Swep International Ab Échangeur thermique avec écoulement amélioré
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US9437905B2 (en) 2014-02-25 2016-09-06 Ford Global Technologies, Llc Traction battery thermal plate manifold
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US9362040B2 (en) 2014-05-15 2016-06-07 Lear Corporation Coldplate with integrated electrical components for cooling thereof
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CN105066751B (zh) * 2015-09-25 2017-04-12 四平市巨元瀚洋板式换热器有限公司 一种板式换热器
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CN105651084B (zh) * 2016-01-13 2018-01-26 宁波市哈雷换热设备有限公司 板式热交换器
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CN108645268A (zh) * 2018-04-30 2018-10-12 南京理工大学 加半圆柱凸起的板式换热器板片
CN108827058A (zh) * 2018-04-30 2018-11-16 南京理工大学 一种加梭形凸起的板式换热器板片
CN109855436A (zh) * 2019-02-27 2019-06-07 西安交通大学 剑鱼梭型-倾斜沟槽仿生微细通道冷凝器
US11280560B1 (en) * 2020-12-08 2022-03-22 Dana Canada Corporation Heat exchanger with two-piece through fittings
FR3122728B1 (fr) * 2021-05-06 2023-06-02 Commissariat A L’Energie Atomique Et Aux Energies Alternatives Module d’échangeur de chaleur à plaques à canaux intégrant au moins une zone d’alimentation et de distribution de fluide formée par des plots.

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0252275A2 (fr) * 1986-07-03 1988-01-13 W. Schmidt GmbH & Co. KG Echangeur de chaleur à plaques
WO1997039301A1 (fr) * 1996-04-16 1997-10-23 Alfa Laval Ab Echangeur de chaleur a plaques
WO2005088223A1 (fr) * 2004-03-11 2005-09-22 Behr Gmbh & Co. Kg Echangeur thermique a empilement de disques
DE102006048305A1 (de) * 2006-10-12 2008-04-17 Modine Manufacturing Co., Racine Plattenwärmetauscher
KR100892109B1 (ko) * 2008-07-10 2009-04-08 한국델파이주식회사 변속기 오일 쿨러

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1376882A (en) * 1919-10-14 1921-05-03 Motor Radiator & Mfg Corp Radiator
US4470455A (en) * 1978-06-19 1984-09-11 General Motors Corporation Plate type heat exchanger tube pass
JPH0666487A (ja) * 1992-08-13 1994-03-08 Showa Alum Corp 積層型熱交換器
DK171957B1 (da) * 1995-06-06 1997-08-25 Apv Baker As Pladevarmeveksler
CN1110682C (zh) * 1996-01-16 2003-06-04 奥里恩机械株式会社 热交换器
JPH09196591A (ja) * 1996-01-23 1997-07-31 Sanden Corp 熱交換チューブエレメント及びそれを用いた熱交換器
JP2002022374A (ja) * 2000-07-07 2002-01-23 Hitachi Ltd プレート式熱交換器および冷凍空調装置
KR100718262B1 (ko) * 2002-12-30 2007-05-15 한라공조주식회사 열교환기용 매니폴드 플레이트
US20070199687A1 (en) * 2004-03-11 2007-08-30 Behr Gmbh & Co. Kg Stacked-Plate Heat Exchanger
SE526831C2 (sv) 2004-03-12 2005-11-08 Alfa Laval Corp Ab Värmeväxlarplatta och plattpaket
CN201163159Y (zh) * 2008-01-18 2008-12-10 江阴博格机械制冷技术有限公司 钎焊板式换热器
CN201199138Y (zh) * 2008-02-05 2009-02-25 王玉辉 新型板式换热器
CN101261057B (zh) * 2008-04-18 2010-07-28 江苏宝得换热设备有限公司 板式换热器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0252275A2 (fr) * 1986-07-03 1988-01-13 W. Schmidt GmbH & Co. KG Echangeur de chaleur à plaques
WO1997039301A1 (fr) * 1996-04-16 1997-10-23 Alfa Laval Ab Echangeur de chaleur a plaques
WO2005088223A1 (fr) * 2004-03-11 2005-09-22 Behr Gmbh & Co. Kg Echangeur thermique a empilement de disques
DE102006048305A1 (de) * 2006-10-12 2008-04-17 Modine Manufacturing Co., Racine Plattenwärmetauscher
KR100892109B1 (ko) * 2008-07-10 2009-04-08 한국델파이주식회사 변속기 오일 쿨러

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2010120125A2 *

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103278035B (zh) * 2013-05-31 2015-07-15 浙江尔格科技股份有限公司 一种换热板片
CN103278035A (zh) * 2013-05-31 2013-09-04 浙江尔格科技有限公司 一种换热板片
CN103486729A (zh) * 2013-10-14 2014-01-01 胡桂林 板翅式热交换器
CN105793662B (zh) * 2013-12-10 2020-03-10 舒瑞普国际股份公司 具有改进的流动的热交换器
WO2015086343A1 (fr) * 2013-12-10 2015-06-18 Swep International Ab Échangeur thermique avec écoulement amélioré
CN105793662A (zh) * 2013-12-10 2016-07-20 舒瑞普国际股份公司 具有改进的流动的热交换器
US10837717B2 (en) 2013-12-10 2020-11-17 Swep International Ab Heat exchanger with improved flow
EP3002536A1 (fr) * 2014-10-02 2016-04-06 Valeo Systemes Thermiques Ensemble comprenant au moins une première et une deuxième plaque permettant de former un faisceau d'echange d'un échangeur de chaleur et un échangeur de chaleur comprenant cet ensemble
FR3026834A1 (fr) * 2014-10-02 2016-04-08 Valeo Systemes Thermiques Ensemble comprenant au moins une premiere et une deuxieme plaque permettant de former un faisceau d'echange d'un echangeur de chaleur et un echangeur de chaleur comprenant cet ensemble
CN104708293A (zh) * 2015-03-10 2015-06-17 胡桂林 换热器的制造方法
US10914532B2 (en) 2015-09-04 2021-02-09 Kyungdong Navien Co., Ltd. Curved plate heat exchanger
EP3346208A4 (fr) * 2015-09-04 2019-06-05 Kyungdong Navien Co., Ltd. Échangeur de chaleur à plaque incurvée
EP3354998A4 (fr) * 2015-09-25 2019-06-05 Kyungdong Navien Co., Ltd. Échangeur de chaleur à plaques rondes
US11454453B2 (en) 2015-09-25 2022-09-27 Kyungdong Navien Co., Ltd. Round plate heat exchanger
FR3100058A1 (fr) * 2019-08-23 2021-02-26 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d’un tel échangeur de chaleur
WO2021038152A1 (fr) * 2019-08-23 2021-03-04 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d'un tel échangeur de chaleur

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US20120031598A1 (en) 2012-02-09
WO2010120125A3 (fr) 2011-03-10
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WO2010120125A2 (fr) 2010-10-21
CN102395853B (zh) 2014-04-02
EP2420791A4 (fr) 2014-03-05

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