EP2551626A1 - Échangeur thermique à plaques, procédé de fabrication d'un échangeur thermique à plaques, et appareil de pompe à chaleur - Google Patents

Échangeur thermique à plaques, procédé de fabrication d'un échangeur thermique à plaques, et appareil de pompe à chaleur Download PDF

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Publication number
EP2551626A1
EP2551626A1 EP10848381A EP10848381A EP2551626A1 EP 2551626 A1 EP2551626 A1 EP 2551626A1 EP 10848381 A EP10848381 A EP 10848381A EP 10848381 A EP10848381 A EP 10848381A EP 2551626 A1 EP2551626 A1 EP 2551626A1
Authority
EP
European Patent Office
Prior art keywords
plate
nozzle
heat exchanger
fluid
hole
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Withdrawn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
EP10848381A
Other languages
German (de)
English (en)
Other versions
EP2551626A4 (fr
Inventor
Shinichi Uchino
Takehiro Hayashi
Daisuke Ito
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric 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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP2551626A1 publication Critical patent/EP2551626A1/fr
Publication of EP2551626A4 publication Critical patent/EP2551626A4/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the present invention relates to a plate heat exchanger which exchanges heat between a refrigerant and a heat absorbing fluid.
  • the present invention also relates to a plate heat exchanger producing method, and a heat pump apparatus.
  • Plate heat exchangers are generally known to exchange heat between two flow channels which are formed by stacking and brazing a plurality of plates together. Plate heat exchangers are characterized in that a heat-exchanger body can be reduced in size because components therein are joined together by brazing.
  • Plate heat exchangers are small in size, and therefore used in heat pump apparatuses. Plate heat exchangers, which exchange heat between a liquid fluid and a refrigerant, are used for water heating, sterilization, or the like. In a plate heat exchanger, pressure differs between a refrigerant side where the pressure becomes relatively high, and a fluid side (heat-absorbing medium side) where the pressure does not change much. Therefore, it is important to improve the bearing capacity of a plate heat exchanger to withstand the inner pressure thereof.
  • Patent Document 1 discloses a technology to improve the bearing capacity of a plate heat exchanger to withstand the inner pressure thereof.
  • a plate heat exchanger is assembled and fixed almost permanently by a brazing filler material. Therefore, if a heat transfer plate therein is damaged, the damaged heat transfer plate cannot be replaced alone. For this reason, damage on a heat transfer plate results in a failure in the function of the whole plate heat exchanger.
  • a plate heat exchanger is used in a heat pump unit mainly for heating air or water, if a heat transfer plate is damaged, water and R410A as a typical refrigerant therein are mixed together. This results in an adverse effect both on environment and human health. Therefore, it is essential to improve the reliability of plate heat exchangers, not for the longevity of individual plate heat exchangers, but for all products that use the plate heat exchangers.
  • An object of the present invention is to improve the strength of a plate heat exchanger against pressure damage or pressure fatigue damage.
  • a plate heat exchanger includes a plurality of stacked plates in which adjacent plates in a stacking direction are joined together by brazing, the plate heat exchanger exchanging heat between a first fluid being a refrigerant and a second fluid with which the first fluid exchanges heat, the first and second fluids passing through a flow channel for the first fluid and a flow channel for the second fluid which are formed in the plurality of plates.
  • the plate heat exchanger comprises: a nozzle serving as one of an inlet port and an outlet port of one of the first fluid and the second fluid, the nozzle having a hollow center; an outer plate arranged on an outermost side, the outer plate including a nozzle-corresponding hole which has a shape corresponding to a shape of a nozzle end so that the nozzle end passes through the nozzle-corresponding hole, the nozzle end being one of ends of the nozzle; and a first plate arranged adjacent to a bottom surface side of the outer plate, the first plate including a recessed area which, in conjunction with the nozzle end and the bottom surface of the outer plate, defines an enclosed space which substantially seals a periphery of the nozzle end when the nozzle end is inserted through the nozzle-corresponding hole in the outer plate, the recessed area having, at a central portion thereof, a first hole which is aligned with the nozzle-corresponding hole in the stacking direction, The enclosed space is filled with a brazing filler material.
  • This invention allows a plate heat exchanger to improve the strength against pressure damage or pressure fatigue damage.
  • a plate heat exchanger 100 is described below according to a first embodiment.
  • Fig. 1 illustrates a configuration of the plate heat exchanger 100 according to the first embodiment.
  • a configuration of the plate heat exchanger 100 is described with reference to Fig. 1 .
  • a heat pump unit 10 heat pump apparatus
  • the compressor 1 to the evaporator 4 form a refrigeration cycle through which the refrigerant 11 circulates.
  • the plate heat exchanger 100 is used as the condenser 2.
  • the heat of the external heat source (absorbed heat by the evaporator 4) is radiated by the plate heat exchanger 100, thereby heating water introduced into the plate heat exchanger 100.
  • media such as air and geothermal heat, used as the external heat source (whose heat is exchanged by the evaporator 4).
  • the plate heat exchanger 100 can be used in all the water heater type heat pump units that use the external heat source.
  • the plate heat exchanger 100 may not be limited to be used only as the condenser (first heat exchanger), but also used as the evaporator (second heat exchanger).
  • Outlet hot water 12 (also referred to as water 12) circulates through a water circuit 14.
  • Fig. 1 illustrates an indirect heating system.
  • the water 12 flows into the plate heat exchanger 100 as the condenser 2, absorbs heat from the refrigerant 11, and flows out from the plate heat exchanger 100.
  • the outlet hot water 12 discharged from the plate heat exchanger 100 flows into a heater 5, such as a radiator or a floor heater, connected by pipes in the water circuit 14, to be used for room temperature regulation.
  • a water-water heat exchanger tank 6 in which heat is exchanged between the outlet hot water 12 and clean water 13 is also included in the water circuit 14. This allows the clean water 13 heated by the outlet hot water 12 to be used as household water for bath, shower, and the like.
  • the plate heat exchanger 100 includes a first flow channel, into which the refrigerant 11 is introduced through a nozzle 114-2 as a refrigerant inlet port, and from which the refrigerant 11 is discharged through a nozzle 114-4 as a refrigerant outlet port.
  • the plate heat exchanger 100 also includes a second flow channel, into which the water 12 is introduced through a nozzle 114-3 as a water inlet port, and from which the water 12 is discharged through a nozzle 114-1 as a water outlet port.
  • the plate heat exchanger 100 includes the reinforcing plate 113a to which nozzles 114-1 to 114-4 are attached, the side plate 110a, a heat transfer plate 109b, a heat transfer plate 109a ... a heat transfer plate 109b, a heat transfer plate 109a, a side plate 110b, and a reinforcing plate 113b, which are arranged in that order in a stacked assembly.
  • the front view (from the arrow A direction of Fig. 3 ) illustrates four nozzles 114-1 to 114-4 attached to the reinforcing plate 113a.
  • the back view (from the arrow B direction of Fig. 3 ) illustrates a surface of the reinforcing plate 113b.
  • FIG. 6 illustrates a section corresponding to an X-X section shown in Fig. 4 .
  • a term "corresponding" is used here for the following reason.
  • the heat transfer plates 109a, 109b shown in Fig. 6 for ease of explanation.
  • the nozzle 114a (corresponding to the nozzle 114-1) is a nozzle at an inlet port for the refrigerant 11.
  • Fig. 6 and Fig. 4 do not illustrate the same, and therefore the term "corresponding" is used.
  • FIG. 7 Views (a) and (b) of Fig. 7 illustrate the heat transfer plate 109a (third plate) and the heat transfer plate 109b (second plate) of the plate heat exchanger 100 shown in Fig. 6 when viewed from a direction indicated by an arrow C.
  • the heat transfer plate 109b is arranged immediately below the side plate 110a, and immediately above the heat transfer plate 109a.
  • flow openings 115a to 115d (second holes) in the heat transfer plate 109b are aligned with flow openings 115a to 115d (third holes) in the heat transfer plate 109a to form the flow channels.
  • FIG. 8 A view (a) of Fig. 8 illustrates the side plate 110a (first plate) of the plate heat exchanger 100 shown in Fig. 6 when viewed from the arrow C direction.
  • Flow openings 115a to 115d (first holes) in the side plate 110a are aligned with the flow openings 115a to 115d in the heat transfer plate 109b and the flow openings 115a to 115d in the heat transfer plate 109a to form the flow channels.
  • a Y-Y section shown in (a) of Fig. 8 is illustrated in (b).
  • Fig. 9 is an enlarged view of a portion D shown in Fig. 6 .
  • the plate heat exchanger 100 of the first embodiment includes a heat transfer portion 111 as a main structure in which the heat transfer plates 109a, 109b are stacked together to form the flow channels for exchanging heat between the first fluid and the second fluid.
  • a plate heat exchanger core portion 112 (hereinafter, referred to as core portion 112) includes the heat transfer portion 111, the side plate 110a arranged above the heat transfer portion 111, and the side plate 110b arranged below the heat transfer portion 111.
  • the reinforcing plate 113a is arranged above the core portion 112 and the reinforcing plate 113b is arranged below the core portion 112 to sandwich the core portion 112 between the reinforcing plates 113a and 113b.
  • the reinforcing plate 113a is formed with nozzle attachment openings (nozzle-corresponding holes). The nozzles 114a to 114d are attached to the nozzle attachment openings.
  • the heat transfer plate 109a and the heat transfer plate 109b shown in Fig. 7 have the same size, and the plate thickness is the same.
  • the heat transfer plate 109a and the heat transfer plate 109b each have the flow openings 115a to 115d at the four corners.
  • the heat transfer plate 109a and the heat transfer plate 109b have corrugated shapes 116a and 116b for disturbing the fluid between the flow openings 115a, 115b and the flow openings 115c, 115d in the long-side direction.
  • the corrugated shape 116a of the heat transfer plate 109a and the corrugated shape 116b of the heat transfer plate 109b are 180-degree inverted to each other.
  • the corrugated shape 116b is obtained by rotating the corrugated shape 116a by 180 degrees about a point P in an arrow's direction shown.
  • a ridge line 122 of the heat transfer plate 109b indicates a ridge line, i.e., the top of a wave in the corrugation.
  • the "top of a wave” means the top of a wave in the direction opposite to the C direction in Fig. 6 .
  • the corrugated shape 116b is formed by a series of V-shaped waves with the vertex of each V (bent position of a V) being aligned on a center line 121 of the heat transfer plate 109b. The same is applied to the corrugated shape 116a.
  • an area around the periphery of the flow opening 115a of the heat transfer plate 109b is lower than an area around the periphery of the flow opening 115b of the heat transfer plate 109b, when the direction opposite to the C direction is the higher direction. That is, the heat transfer plate 109b has a step 123 with the center line 121 as a boarder in the short-side direction. The step 123 serves as the flow channels when the heat transfer plates are stacked together. The same is applied to the heat transfer plates 109a.
  • the corrugated shape 116a and the corrugated shape 116b meet by point contact.
  • the point-contact portions are brazed to serve as "pillars" to form the flow channels.
  • the heat transfer plates 109a form the flow channel for water (pure water, tap water, mixed water with antifreeze solution, etc.) and the heat transfer plates 109b form the flow channel for the refrigerant 11 (e.g., a refrigerant used in an air-conditioner, such as R410A as a typical refrigerant).
  • the water flow channel is formed by stacking the heat transfer plate 109a and the heat transfer plate 109b alternately.
  • water-refrigerant layers are formed by stacking an additional heat transfer plate 109a.
  • alternate flow channels such as “water-refrigerant-water-refrigerant"
  • the stacked heat transfer plates constitute the heat transfer portion 111 shown in Fig. 6 .
  • the side plate 110a and the side plate 110b which sandwich the heat transfer potion 111 at the top and bottom portions thereof, have the same size and thickness as those of the heat transfer plate 109.
  • the side plates 110a and 110b are flat plates without the corrugated shape 116, and have the flow openings 115a to 115d at the four corners.
  • the side plate 110a is arranged above the heat transfer portion 111 and the side plate 110b is arranged below the heat transfer portion 111 to form the core portion 112.
  • a recessed portion 117 is formed on the periphery of the flow opening 115a, 115c of the side plate 110a, 110b. The recessed portion 117 is in contact with the flow opening 115a, 115c of the heat transfer plate 109a, 109b.
  • the side plate 110a has the recessed portion 117 (recessed area) formed by drawing on the periphery of the flow opening 115a, 115c.
  • the recessed portion 117 serves to prevent the refrigerant from flowing into a non-heat transfer space 118, which is defined by the side plate 110a and the side plate 110b.
  • the non-heat transfer space 118 is a space which is defined by a flat surface and the corrugated shape 116b, and in which effective heat transfer performance cannot be expected. For this reason, preventing the refrigerant from flowing into the non-heat transfer space 118 can avoid excessive radiation and a reduction in the flow speed of the refrigerant.
  • the reinforcing plate 113a (outer plate) is arranged above the core portion 112, and the reinforcing plate 113b is arranged below the core portion 112.
  • the reinforcing plate 113 is substantially five times thicker than the heat transfer plate 109 or the side plate 110.
  • the reinforcing plate 113a has four flow openings as shown in Fig. 2 , Fig. 4 , etc.
  • the reinforcing plate 113b has no flow opening 115, as shown in Fig. 5 .
  • the reinforcing plates 113a and 113b allow the plate heat exchanger 100 to withstand pressure fluctuation fatigue caused by the fluids flowing through the core portion 112, and force caused by differences between the atmospheric pressure and the pressure of the plate heat exchanger 100.
  • the nozzles 114a to 114d are attached to four flow openings in the reinforcing plate 113a to direct the refrigerant and water passing into the core portion 112. Positions where the nozzles 114 are attached (attachment positions) are determined by the number of flow openings in the reinforcing plate 113a, 113b. If each reinforcing plate has a maximum of four flow openings, a total of eight nozzles 114 are attached per unit of the plate heat exchanger 100. As shown in Fig. 9 , the nozzle 114a has the insertion portion 131 at an end portion thereof, which fits into the flow opening of the reinforcing plate 113a.
  • the insertion portion 131 is formed so that a tip portion thereof protrudes by 1 mm or more from a bottom surface 133 of the reinforcing plate 113a.
  • Fig. 9 shows a length H, which is 1 mm or more.
  • the temporarily assembled plate heat exchanger 100 strips of copper as the brazing filler material are inserted between the heat transfer plates 109a and the heat transfer plates 109b, between the heat transfer portion 111 and the side plate 110a, 110b, and between the core portion 112 and the reinforcing plate 113a, 113b.
  • the brazing filler copper is also inserted between the reinforcing plate 113a and the nozzles 114.
  • the temporarily assembled plate heat exchanger 100 with the brazing filler material inserted therein is put in a vacuum furnace for vacuum brazing. During the brazing process, the copper melts and penetrates into the joint surfaces of each component. When the penetrated copper is cooled, the components are joined together almost permanently. The plate heat exchanger 100 is thus produced.
  • Molten copper by brazing penetrates through the joint surfaces of the components (plates, nozzles, etc.). Surplus copper remaining after molten copper having penetrated through the entire joint surfaces accumulates inside the plate heat exchanger 100. The surplus copper under surface tension tends to flow into narrower gaps.
  • the tip portion of the insertion portion 131 of the nozzle 114a is positioned closely to the recessed portion 117 of the side plate 110a to create the gap 132.
  • the inner space 19 is filled with the brazing filler copper.
  • the gap 132 is designed so that molten copper under surface tension penetrates through the gap, and does not flow out through the gap while the copper is cooled in the brazing process.
  • the gap 132 is between several ⁇ m and several dozen ⁇ m.
  • the plate heat exchanger 100 is configured as follows: the side plates 110a, 110b and the reinforcing plates 113a, 113b are arranged above and below, respectively, the heat transfer portion 111 where the plurality of heat transfer plates 109a, 109b are stacked together.
  • the heat transfer portion 111 sandwiched between the side plates 110a, 110b and the reinforcing plates 113a, 113b is brazed all together by vacuum brazing.
  • the recess is formed on the periphery of the refrigerant side flow channel opening in the side plate 110a.
  • the heat transfer plates 109 and the side plates 110 are joined together on the periphery of the flow openings 15, respectively.
  • the entire inner space 19 can serve as a pillar to support the inside of the plate heat exchanger.
  • the "pillar” made of three components, i.e., the nozzle 114a, the reinforcing plate 113a, and the side plate 110a, is formed as a result of the filling of the inner space 119 with copper.
  • the "pillar” based on the joint area of the recessed portion 117 of the side plate 110a and the heat transfer portion 111 can be thus obtained. Therefore, a pressure receiving area is increased and stress is reduced, which improves the reliability against internal pressure fatigue damage caused by refrigerant pressure fluctuations and pressure damage caused by differences between the internal pressure of the plate heat exchanger and the atmospheric pressure.
  • the plate heat exchanger 100 of the first embodiment allows large-sized "pillars” to be obtained in the vicinity of the nozzles without adding a "pillar” which blocks a fluid flow. Therefore, the reliability of the strength is improved.
  • Filling the inner space 119 with copper can prevent a corrosive fluid such as water from flowing into the inner space 119.
  • a corrosive fluid such as water
  • it is effective in terms of corrosion to eliminate an empty space such as the inner space 119.
  • the reinforcing plate (pressure resistance plate), the side plate, and the nozzle constitute the solid "pillar", by filling the inner space, which is defined by the reinforcing plate (pressure resistance plate), the side plate, and the nozzle, with the brazing filler material for joining each plate together and each nozzle and plate together, in brazing using a vacuum furnace.
  • the "pillar" can improve the strength of the plate heat exchanger 100 against the inner pressure fluctuations thereof.
  • the strength can be improved by forming the "pillar" at a nozzle as a refrigerant inlet port, if there are differences between atmospheric pressure and refrigerant pressure, and there are refrigerant pressure fluctuations in the heat pump unit.

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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)
EP10848381.9A 2010-03-25 2010-03-25 Échangeur thermique à plaques, procédé de fabrication d'un échangeur thermique à plaques, et appareil de pompe à chaleur Withdrawn EP2551626A4 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/055166 WO2011117988A1 (fr) 2010-03-25 2010-03-25 Échangeur thermique à plaques, procédé de fabrication d'un échangeur thermique à plaques, et appareil de pompe à chaleur

Publications (2)

Publication Number Publication Date
EP2551626A1 true EP2551626A1 (fr) 2013-01-30
EP2551626A4 EP2551626A4 (fr) 2018-02-21

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EP10848381.9A Withdrawn EP2551626A4 (fr) 2010-03-25 2010-03-25 Échangeur thermique à plaques, procédé de fabrication d'un échangeur thermique à plaques, et appareil de pompe à chaleur

Country Status (3)

Country Link
EP (1) EP2551626A4 (fr)
JP (1) JP5496321B2 (fr)
WO (1) WO2011117988A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3203171A1 (fr) * 2016-02-04 2017-08-09 Mahle International GmbH Échangeur thermique à plaques, en particulier pour un véhicule automobile
WO2021020749A1 (fr) * 2019-07-29 2021-02-04 엘지전자 주식회사 Échangeur de chaleur à plaques
WO2021259762A1 (fr) * 2020-06-24 2021-12-30 Valeo Systemes Thermiques Échangeur de chaleur.

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5881515B2 (ja) * 2012-04-12 2016-03-09 三菱電機株式会社 プレート式熱交換器およびその製造方法並びにヒートポンプ装置
WO2013183113A1 (fr) * 2012-06-05 2013-12-12 三菱電機株式会社 Échangeur de chaleur du type à plaques et dispositif à cycle frigorifique le comprenant
JP5940152B2 (ja) * 2012-06-05 2016-06-29 三菱電機株式会社 プレート式熱交換器及びそれを備えた冷凍サイクル装置
EP2977704B1 (fr) * 2013-03-22 2020-06-17 Mitsubishi Electric Corporation Échangeur de chaleur du type à plaques et dispositif de cycle de réfrigération le comportant
JP7181271B2 (ja) * 2020-12-10 2022-11-30 株式会社日阪製作所 プレート式熱交換器

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3203171A1 (fr) * 2016-02-04 2017-08-09 Mahle International GmbH Échangeur thermique à plaques, en particulier pour un véhicule automobile
DE102016201712A1 (de) * 2016-02-04 2017-08-10 Mahle International Gmbh Stapelscheibenwärmetauscher, insbesondere für ein Kraftfahrzeug
WO2021020749A1 (fr) * 2019-07-29 2021-02-04 엘지전자 주식회사 Échangeur de chaleur à plaques
US11353268B2 (en) 2019-07-29 2022-06-07 Lg Electronics Inc. Plate type heat exchanger
EP4006477A4 (fr) * 2019-07-29 2023-08-02 LG Electronics Inc. Échangeur de chaleur à plaques
WO2021259762A1 (fr) * 2020-06-24 2021-12-30 Valeo Systemes Thermiques Échangeur de chaleur.
FR3111976A1 (fr) * 2020-06-24 2021-12-31 Valeo Systemes Thermiques Échangeur de chaleur.

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JPWO2011117988A1 (ja) 2013-07-04
EP2551626A4 (fr) 2018-02-21
JP5496321B2 (ja) 2014-05-21
WO2011117988A1 (fr) 2011-09-29

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