EP3907459A1 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP3907459A1
EP3907459A1 EP20461532.2A EP20461532A EP3907459A1 EP 3907459 A1 EP3907459 A1 EP 3907459A1 EP 20461532 A EP20461532 A EP 20461532A EP 3907459 A1 EP3907459 A1 EP 3907459A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
header
thickness
manifold
tubes
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.)
Pending
Application number
EP20461532.2A
Other languages
English (en)
French (fr)
Inventor
Michal BELZOWSKI
Dawid Szostek
Tomasz Stramecki
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.)
Valeo Autosystemy Sp zoo
Original Assignee
Valeo Autosystemy Sp zoo
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 Valeo Autosystemy Sp zoo filed Critical Valeo Autosystemy Sp zoo
Priority to EP20461532.2A priority Critical patent/EP3907459A1/de
Priority to PCT/EP2021/058586 priority patent/WO2021223944A1/en
Priority to CN202180039054.7A priority patent/CN115698621A/zh
Priority to US17/997,451 priority patent/US20230168048A1/en
Publication of EP3907459A1 publication Critical patent/EP3907459A1/de
Pending legal-status Critical Current

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Classifications

    • 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
    • F28F9/0221—Header boxes or end plates formed by stacked 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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section

Definitions

  • the invention relates to a heat exchanger, especially to a high pressure heat exchanger for automotive industry.
  • heat exchangers configured to exchange heat between two fluids
  • One of the fluids is guided between said manifolds via these tubes, while the second fluid is guided around and in a space between the tubes to enable heat exchange.
  • the tubes can be for example a flat tubes.
  • the tubes are secured in the manifolds in a fluid-tight manner.
  • the heat exchanger When the fluid traveling between the manifolds and in the tubes is a high pressure fluid, like R744 ( CO 2 ), the heat exchanger has to be adapted accordingly.
  • high pressure fluid imposes additional design constrains on the heat exchanger, as the pressure of the fluid necessitates higher mechanical resistance of its components. This pressure can exceed 120 bars.
  • the manifolds In case of heat exchangers comprising flat tubes, the manifolds have slots with shape corresponding to the cross-section of the tubes.
  • the flat tubes are mounted in these slots.
  • the number of tubes is linked to the efficiency of the heat exchange, it is generally preferable to increase the number of tubes to improve the heat exchange between fluids.
  • the distance between the consecutive slots in the manifold decreases. At some point, the distance becomes too small to ensure a proper mechanical resistance of the manifold, given that the fluid which travels through the tubes and which enters said manifold operates at high pressure.
  • the object of the invention is a high pressure heat exchanger comprising a first manifold and a second manifold connected fluidly by a plurality of tube sets arranged in a spaced manner along the manifolds, wherein at least one of the manifold comprises a rear cover, a header with slots receiving tube end sections of the tube sets and at least one internal plate interposed between the header and the rear cover and configured to create a flow path within the manifold, this flow path being in fluid connection with the tubes to allow a circulation of a refrigerant in the tubes and the manifold, and wherein the header has preferably at least a first area adjacent to at least one of the slots and having a first thickness w1 and at least a second area surrounding at least partially the first area and having a second thickness w2, first thickness w1 being smaller than second thickness w2.
  • each slot of the header is adjacent to first areas with first thickness so that that the thickness of the header is locally smaller, around the slots, than in the rest of the header.
  • the thickness in the first area, has a minimum value w1 min on the side adjacent with the slot.
  • first thickness w1 may be variable from a minimum value w1 min at the contact with the tube in the slot up to the second thickness w2. This may be advantageous to form the tapered guiding shape.
  • the heat exchanger has the following ratios: 3 ⁇ h/w1 ⁇ h/(c ⁇ 60%), in particular 3 ⁇ h/w1 ⁇ h/c where h is the height of the distribution channel of the manifold and w1 is the wall thickness of the header in the first zone, where thickness w1 is minimum in the first area, and c is smallest wall thickness in tubes.
  • the manifold comprises a plurality of internal pates stacked together, which may be in number of 2, 3, 4 or 5 or even more plates.
  • At least some of the internal plates have slots extending in different directions, in particular perpendicular directions so as to create U form flow paths.
  • At least one plate has parallel longitudinal slots in particular forming group of two slots, these two slots being aligned.
  • two of the internal plates have parallel slots and one of the internal plate has slots perpendicular to slots of the two other plates.
  • internal plates are flat stamped plates.
  • internal pates create internal channels for distribution of refrigerant.
  • the plates may have different shapes in order to create manifolds with more sophisticated flow paths for instance for more than two passes.
  • each rear plate is working like a closing plate, preventing from leak of refrigerant outside manifold region.
  • the rear plate is configured to close the slots of the adjacent internal plate.
  • the header is configured to stick together all internal plates in position before and during brazing process.
  • the header comprises two lateral walls, in particular two lateral folded walls, to stack the internal plates and the rear cover all together.
  • the slots are formed on a main wall of the header, said main wall being flat.
  • the lateral walls are connected to this main wall.
  • each header forms a part with an accurate shape wit slots in order to create a brazing connection with the tubes.
  • the header is configured with a shape ensuring proper guiding of tubes into the slots during assembly of core.
  • each slot having a tapered shape to guide the tubes during their insertion.
  • the guiding shape may rectilinear or rounded.
  • An advantage of the invention is to use a header with globally small thickness in order to easier bend it around other plates and to have as small radiuses in the corners as possible.
  • the invention makes it possible not to increase the thickness of the manifold too much in order to cut the slots precisely without creating major deformations.
  • the headers are made in stamping process.
  • the distance between slots on the header is sufficient, for instance above 7 mm, and the size of the slots is relatively small, so that it is possible to punch slots in a way to create drafted angles whose are guiding tubes during assembly of the tubes.
  • the internal plates which are added are configured to support the structure between the slots.
  • an internal plate is brazed with the header.
  • the internal plates enable to withstand high pressure despite limited thickness of header in order to create the guiding surfaces in the first area of small thickness.
  • the internal plates have slots to form flow paths within the manifold, these slots communicating each with another in a certain manner to form the flow paths.
  • the invention in particular thanks to internal plates, enables to create a robust structure of manifold, for instance which is able to withstand pressure up to 26 MPa or even bigger for other applications.
  • the invention also enables to use an assembly of parts made in reasonably cheap for serial processes such as stamped components instead of machining components.
  • Each manifold is assembled for instance from few internal plates together with a header.
  • the heat exchanger comprises rows of tubes connecting the manifolds forming an inlet row and an outlet row for refrigerant.
  • the refrigerant is flowing from an inlet through the manifold to first row of the tubes. Then the refrigerant is flowing through the tubes to opposite manifold where the refrigerant is transferred from first row of the tubes to the second row of the tubes. Then the refrigerant is flowing through the second row to the manifold forming IN/OUT and to the connecting block 30 ensuring tight hydraulic connection with the rest of the system.
  • the heat exchanger for cooling a heat source of a motor vehicle has coolant channels forming a coolant flow path and refrigerant channels forming a refrigerant flow path.
  • the refrigerant flow path is deviated at least once in the shape of a U.
  • the refrigerant channels in the tubes have a ratio of at least 0.3 between their wall thickness and the diameter.
  • a web is placed between two refrigerant channels in the tubes and has a width b equal to at least 40% of the diameter of the refrigerant channel.
  • the heat exchanger is a chiller.
  • the refrigerant is CO 2 , also called R744.
  • the invention is not limited to such a refrigerant.
  • the connecting block is attached to one the manifolds.
  • each tube set comprises a first tube and a second tube, wherein each of the first and the second tubes comprises an intermediate tube section between two opposing tube end sections, and the manifolds comprise slots receiving the tube end sections in a fluid-tight manner.
  • At least the first tube comprises a bent tube section between the tube end section and the intermediate tube section, so that the intermediate tube sections of the first and second tubes run substantially in a parallel and spaced manner to each other, while the tube end tube sections are stacked on each other within a single slot.
  • the bent tube section comprises two opposing turns.
  • both the first tube and the second tube comprise bent tube sections.
  • the spaces between the tubes in a tube set have equal height to the spaces between the tube sets.
  • a flow disruptor is arranged in a space between the first tube and the second tube in the tube set.
  • a flow disruptor is arranged in a space between the tube sets.
  • a tube height h1 of flat tubes is between 2 mm and 3 mm
  • a flow disruptor height h2 is between 1,7mm and 2,5 mm
  • a material height h3 between consecutive slots is (2 ⁇ h2)-a, a being between 0,4 and 0,8 mm.
  • a third tube is located between the first tube and the second tube, so that the end sections of the tubes 11, 12, 16 are stacked on each other within a single slot
  • a tube height h1 of flat tubes is between 2 mm and 3 mm
  • a flow disruptor height h2 is between 1,7mm and 2,5 mm
  • a material height h3 between consecutive slots is (3 ⁇ h2)-a, a being between 0,4 and 0,8 mm.
  • Fig. 1 shows a known heat exchanger with flat tubes 11 in partial cross-section.
  • the heat exchanger 1 comprises a plurality of flat tubes 11 for guiding the first fluid, in particular a fluid operating at high pressure, for example R744. These tubes 11 are connected at their end portions with manifolds 10a, 10b.
  • the flat tubes 11 are arranged in horizontally parallel rows so that the first fluid can enter through the block 30 into the first manifold 10a, travel through the first column of tubes 11, reach the second manifold 10b and make a U-turn, returning to the first manifold 10a via second column of tubes 11, and then exit through outlet channel in the manifold 10a and the connecting block 30.
  • Fig. 2 shows the heat exchanger of Fig. 1 in greater detail.
  • the flat tubes 11 are placed in slots 13 of the manifold 10b (in a consecutive manner along the vertical direction).
  • the other ends of the tubes 11 are situated in manifold 10a in an analogous manner.
  • the heat exchanger further comprises flow disruptors 15, which disrupt the flow of the second fluid, in order to improve the heat exchange with the first fluid.
  • the tube height h1 is slightly smaller than manifold material height h3 between consecutive slots 13.
  • the flow disruptor 15 has a height h2. As the height of the disruptor 15 approaches the h1 value, h3 also decreases, which is detrimental to the manifolds strength. The following embodiments propose avoiding this negative dependency.
  • Fig. 3 shows a heat exchanger according to the invention in a first embodiment.
  • the invention differs from the heat exchanger discussed in relation to Figs. 1 and 2 in The example is explained relative to manifold 10b, but this description applies to manifold 10a in an analogous manner.
  • a plurality of tube sets 20, each comprising a first tube 11 and a second tube 12, is arranged along the manifold 10b in a spaced manner.
  • Each of the first and the second tubes 11, 12 comprises an intermediate tube section 11a between two opposing tube end sections 11b.
  • the manifolds 10a, 10b comprise slots 13, in which the tube end sections 11b of tubes 11, 12 are mounted in a fluid-tight manner.
  • the first tube 11 comprises a bent tube section 11c between the tube end section 11b and the intermediate tube section 11a.
  • the intermediate tube sections 11a of the first and second tubes 11, 12 then run substantially in a parallel and spaced manner to each other, while the tube end sections 11b are stacked on each other within a single slot 13. Because at least one of the tubes 11, 12 is bent in this manner, the distance between the consecutive slots 12 is enlarged. It is therefore clear that by the term 'bent' it is understood any shape which allows providing two sections of the tube, preceding the bend and following the bend, which would run in parallel but in shifted relation, as shown in the drawings. For example, the first tube 11 is bent so that it has two opposing bends (i.e. forms a chicane).
  • the tube bent section 11c is located close to the tube end section 11b. Consequently, the disruptors 15 can occupy most of the space between the tubes and prevent excessive by-passing of the second fluid.
  • the second tube 12 is a straight (i.e. non bent) flat tube, which nevertheless comprises an intermediate portion 11a and a tube end section 11b, the tube end section 10b being placed in the slot 13.
  • the arrangement according to the invention improves mechanical resistance of the header, and at the same time allows application of known, standard flow disrupters 15.
  • the number of tubes applied along the manifold consequently can also be greater.
  • Fig. 4 shows a heat exchanger according to the invention in a second embodiment.
  • This embodiment differs from the first embodiment in that a third tube 16 is present in the tube set 20. It has the same shape as the first tube 11, but is arranged inversely and stacked below the second tube 12.
  • the tube he i ght h1 is preferably between 3 mm and 4,5 mm
  • the flow disruptor height h2 is between 1,7mm and 2,5 mm
  • the material height h3 between the consecutive tube slots 13 is (3 ⁇ h2)-a, which is between 0,4 and 0,8 mm.
  • Fig. 5 shows a heat exchanger according to the invention in a third embodiment. It differs from the previous embodiments in that both the first tube 11 and the second tube 12 comprise tube bent sections 11c, and there is no flat tube between them.
  • the disruptors 15 can be located between the tubes 11, 12 and/or between the consecutive tube sets 20.
  • the tube height h1 is preferably between 2 mm and 3 mm
  • the flow disruptor height h2 is between 1,7mm and 2,5 mm
  • the material he i ght h3 between the consecutive tube slots 13 is (2 ⁇ h2)-a, which is between 0,4 and 0,8 mm.
  • the spaces between the tubes in a tube set 20 can have equal height to the spaces between the tube sets 20. This can enable applying identical flow distributors 15.
  • FIGS 6 to 8 discloses an embodiment of the invention.
  • a high pressure heat exchanger 100 is shown on Figures 6 to 8 which comprises a first manifold 101 and a second manifold connected fluidly by a plurality of tube sets 20 arranged in a spaced manner along the manifolds, wherein the manifold 101 comprises a rear cover 102, a header 103 with slots 104 receiving tube end sections 11b of the tube sets and internal plates 105 interposed between the header 103 and the rear cover 102 and configured to create a flow path 106 within the manifold, this flow path being in fluid connection with the tubes 11 to allow a circulation of a refrigerant in the tubes and the manifold 101.
  • the header 103 has preferably a first area 110 adjacent to each slot 104 and having a first thickness w1 and at a second area 111 surrounding the first area 110 and having a second thickness w2, first thickness w1 being smaller than second thickness w2.
  • Each slot 104 of the header 103 is adjacent to first areas 110 with first thickness so that that the thickness of the header is locally smaller, around the slots, than in the rest of the header 103.
  • the thickness has a minimum value w1min on the side adjacent with the slot 104.
  • First thickness w1 may be variable from a minimum value w1min at the contact with the tube in the slot up to the second thickness w2. This may be advantageous to form the tapered guiding shape 125.
  • the heat exchanger has the following ratios: 3 ⁇ h/w1 ⁇ h/(c ⁇ 60%), in particular 3 ⁇ h/w1 ⁇ h/c where h is the height of the distribution channel of the manifold and w1 is the wall thickness of the header in the first zone, where thickness w1 is minimum in the first area, and c is smallest wall thickness in tubes 11.
  • Dimensions h and w1 and w2 are measured relatively to the same axis perpendicular to the plane of the internal plates 105.
  • the manifold 101 comprises a plurality of internal pates stacked together, which may be in number of 3.
  • Internal plates 105 have slots 115 extending in different directions, in particular perpendicular directions so as to create U form flow paths.
  • Some plates 105 has parallel longitudinal slots 115 in particular forming group of two slots, these two slots 115 being aligned.
  • Two of the internal plates 105 have parallel slots 115 and one of the internal plate 105 has slots 115 perpendicular to slots of the two other plates.
  • Internal plates 105 are flat stamped plates.
  • Internal pates 105 create internal channels for distribution of refrigerant.
  • Rear plate or rear cover 102 is working like a closing plate, preventing from leak of refrigerant outside manifold region.
  • the rear plate 102 is configured to close the slots 115 of the adjacent internal plate 105.
  • the header 103 is configured to stick together all internal plates 105 in position before and during brazing process.
  • the header 103 comprises two folded lateral walls 117, to stack the internal plates 105 and the rear cover 102 all together.
  • the slots are formed on a flat main wall 118 of the header, said main wall being flat.
  • the lateral walls 117 are connected to this main wall 118.
  • the header 103 forms a part with an accurate shape wit slots 104 in order to create a brazing connection with the tubes.
  • the header 103 is configured with a shape ensuring proper guiding of tubes 11 into the slots during assembly of core.
  • Each slot 104 having a tapered shape 125 to guide the tubes 11 during their insertion.
  • the guiding shape may rectilinear shape 126 on the bottom of figure 9 , or rounded as shape 125 on the top of Figure 9 .
  • An advantage of the invention is to use a header 103 with globally small thickness in order to easier bend it around other plates and to have as small radiuses in the corners as possible.
  • the invention makes it possible not to increase the thickness of the manifold too much in order to cut the slots 104 precisely without creating major deformations.
  • the header 103 are made in stamping process.
  • the distance between slots 104 on the header 103 is sufficient, for instance above 7 mm, and the size of the slots is relatively small, so that it is possible to punch slots in a way to create drafted angles whose are guiding tubes during assembly of the tubes.
  • the internal plates 105 which are added are configured to support the structure between the slots.
  • An internal plate 105 is brazed with the header 103.
  • the internal plates 105 enable to withstand high pressure despite limited thickness of header in order to create the guiding surfaces in the first area of small thickness.
  • the internal plates 105 have slots 115 to form flow paths within the manifold, these slots 115 communicating each with another in a certain manner to form the flow paths.
  • the invention in particular thanks to internal plates 105, enables to create a robust structure of manifold 101, for instance which is able to withstand pressure up to 26 MPa or even bigger for other applications.
  • the invention also enables to use an assembly of parts made in reasonably cheap for serial processes such as stamped components instead of machining components.
  • the heat exchanger 100 comprises rows of tubes connecting the manifolds forming an inlet row and an outlet row for refrigerant.
  • the refrigerant is flowing from an inlet through the manifold to first row of the tubes. Then the refrigerant is flowing through the tubes to opposite manifold where the refrigerant is transferred from first row of the tubes to the second row of the tubes. Then the refrigerant is flowing through the second row to the manifold forming IN/OUT and to the connecting block 30 ensuring tight hydraulic connection with the rest of the system.
  • the heat exchanger 100 for cooling a heat source of a motor vehicle has coolant channels forming a coolant flow path and refrigerant channels forming a refrigerant flow path.
  • the refrigerant flow path is deviated at least once in the shape of a U.
  • the refrigerant channels 120 in the tubes 11 have a ratio of at least 0.3 between their wall thickness and the diameter.
  • a web 121 is placed between two refrigerant channels in the tubes and has a width b equal to at least 40% of the diameter of the refrigerant channel.
  • header and rear cover can be made of metal.
  • the heat exchanger is a chiller.
  • the refrigerant is CO 2 .
  • the invention is not limited to such a refrigerant.
  • the connecting block 30 is attached to one the manifolds 101.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP20461532.2A 2020-05-04 2020-05-04 Wärmetauscher Pending EP3907459A1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP20461532.2A EP3907459A1 (de) 2020-05-04 2020-05-04 Wärmetauscher
PCT/EP2021/058586 WO2021223944A1 (en) 2020-05-04 2021-04-01 A heat exchanger
CN202180039054.7A CN115698621A (zh) 2020-05-04 2021-04-01 热交换器
US17/997,451 US20230168048A1 (en) 2020-05-04 2021-04-01 Heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20461532.2A EP3907459A1 (de) 2020-05-04 2020-05-04 Wärmetauscher

Publications (1)

Publication Number Publication Date
EP3907459A1 true EP3907459A1 (de) 2021-11-10

Family

ID=70553994

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20461532.2A Pending EP3907459A1 (de) 2020-05-04 2020-05-04 Wärmetauscher

Country Status (4)

Country Link
US (1) US20230168048A1 (de)
EP (1) EP3907459A1 (de)
CN (1) CN115698621A (de)
WO (1) WO2021223944A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023126075A1 (en) * 2022-01-03 2023-07-06 Huawei Technologies Co., Ltd. Heat exchange arrangement

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003054467A1 (de) * 2001-12-21 2003-07-03 Behr Gmbh & Co. Wärmeübertrager, insbesondere für ein kraftfahrzeug
EP2090851A1 (de) * 2008-02-15 2009-08-19 Delphi Technologies, Inc. Wärmetauscher mit Mischkammer
EP2372283A1 (de) * 2010-03-23 2011-10-05 Delphi Technologies, Inc. Wärmetauscher mit Verteilerplatte
EP3534104A1 (de) * 2018-02-28 2019-09-04 Valeo Autosystemy SP. Z.O.O. Wärmetauscher

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003054467A1 (de) * 2001-12-21 2003-07-03 Behr Gmbh & Co. Wärmeübertrager, insbesondere für ein kraftfahrzeug
EP2090851A1 (de) * 2008-02-15 2009-08-19 Delphi Technologies, Inc. Wärmetauscher mit Mischkammer
EP2372283A1 (de) * 2010-03-23 2011-10-05 Delphi Technologies, Inc. Wärmetauscher mit Verteilerplatte
EP3534104A1 (de) * 2018-02-28 2019-09-04 Valeo Autosystemy SP. Z.O.O. Wärmetauscher

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023126075A1 (en) * 2022-01-03 2023-07-06 Huawei Technologies Co., Ltd. Heat exchange arrangement

Also Published As

Publication number Publication date
US20230168048A1 (en) 2023-06-01
CN115698621A (zh) 2023-02-03
WO2021223944A1 (en) 2021-11-11

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