CN115038924A - Tube heat exchanger with spacers - Google Patents
Tube heat exchanger with spacers Download PDFInfo
- Publication number
- CN115038924A CN115038924A CN202080095530.2A CN202080095530A CN115038924A CN 115038924 A CN115038924 A CN 115038924A CN 202080095530 A CN202080095530 A CN 202080095530A CN 115038924 A CN115038924 A CN 115038924A
- Authority
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- China
- Prior art keywords
- tubes
- heat exchanger
- corrugations
- tube
- profile
- 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
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
-
- 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
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
Landscapes
- 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)
Abstract
The invention relates to a heat exchanger (1) comprising a bundle of tubes (2) arranged parallel to each other, a first heat transfer fluid being intended to flow inside the tubes, a second fluid being intended to pass through the bundle of tubes (2) between the tubes (2), the bundle of tubes (2) comprising a spacer (6) provided between the tubes (2), the spacer (6) having a corrugation (60) extending in the longitudinal direction of the tubes (2), the corrugation (60) having a ridge (61) in contact with the tubes (2) and a side wall (62) connecting the ridge (61), the spacer (6) comprising a first portion (6A) and a second portion (6B), the first portion (6A) being arranged upstream of the second portion (6B) in the flow direction of the second heat transfer fluid, wherein the first portion (6A) protrudes from a front edge of the tubes (2), the ridges (61) of the first portion (6A) have a profile with a flat portion (64), and the ridges (61) of the second portion (6B) have a rounded profile (65), so that the corrugations (60) have a sinusoidal profile.
Description
Technical Field
The present invention relates to a heat exchanger, and more particularly, to a tube type heat exchanger having fins in the field of automobiles.
Background
A tube heat exchanger generally has a bundle of tubes arranged parallel to one another, inside which a first heat transfer fluid circulates. The second heat transfer fluid is used to traverse the tube bundle by passing between the tubes. To improve the heat exchange between the two heat transfer fluids, fins are provided between the tubes in the channels of the second heat transfer fluid.
However, with heat exchangers such as evaporators or evaporator/condensers, when the first refrigerant fluid circulating in the heat exchanger is cold and the second heat transfer fluid is also cold, there is a risk of frost formation on the surfaces of the heat exchanger. The formation of frost reduces the amount of the second heat transfer fluid that can traverse the heat exchanger, thereby reducing the efficiency of the heat exchanger. This phenomenon occurs in particular in evaporators/condensers located in the front face of motor vehicles, when they are used in heat pumps.
One known solution is to periodically circulate a hot first heat transfer fluid in the tubes of the heat exchanger in order to melt any frost. However, this solution may not be suitable because it requires a temporary interruption of the operating mode used. This then reduces the comfort of the passengers.
Disclosure of Invention
It is therefore an object of the present invention to overcome at least some of the disadvantages of the prior art and to propose an improved heat exchanger which reduces the risk of frost formation on its surface.
The invention therefore relates to a heat exchanger having a bundle of tubes arranged parallel to one another, inside which a first heat transfer fluid is intended to flow, a second fluid is intended to pass through the bundle between the tubes, the bundle having fins arranged between the tubes, the fins having corrugations extending in the direction of the length of the tubes, the corrugations having peaks in contact with the tubes and flanks connecting the peaks, the fins having a first portion arranged upstream of a second portion in the direction of flow of the second heat transfer fluid, the first portion projecting beyond the front edges of the tubes, the peaks of the first portion having a profile that presents a flat portion, the peaks of the second portion having a rounded profile, so that the corrugations have a sinusoidal profile.
The fact that the first portion of the fin projects beyond the front edge of the tube and its apex has a flat portion makes it possible to prevent the formation of frost. This is because the peaks with flat portions in combination with the protrusions make it possible to better drain off water condensate on the front face of the heat exchanger, i.e. the face of the heat exchanger through which the second heat transfer fluid enters. Therefore, frost is less likely to be formed.
According to one aspect of the invention, the second portion extends over 100% to 66% of the width of the tube.
According to another aspect of the invention, the first portion and the second portion are made of the same piece.
According to another aspect of the invention, the first portion and the second portion are made of two separate parts.
According to another aspect of the invention, the pitch of the corrugations of the first portion and the pitch of the corrugations of the second portion are different.
According to another aspect of the invention, the pitch of the corrugations of the first portion is greater than the pitch of the corrugations of the second portion.
According to another aspect of the invention, the thickness of the first portion is greater than the thickness of the second portion.
According to another aspect of the invention, the first portion has at least two series of slots offset from each other in the width direction of the tube.
According to another aspect of the invention, the first portion extends along a straight line profile in the width direction of the tube.
According to another aspect of the invention, the first portion extends along the corrugated profile in the width direction of the tube.
Drawings
Other characteristics and advantages of the present invention will become more apparent from reading the following description, given by way of illustrative and non-limiting example, and the accompanying drawings, in which:
figure 1 is a schematic view of a heat exchanger,
figure 2 is a schematic partial perspective view of a tube bundle of a heat exchanger,
figure 3 is a schematic partial cross-sectional view of a first fin portion,
figure 4 is a schematic partial cross-sectional view of a second fin portion,
figure 5 is a schematic partial perspective view of a fin according to a first embodiment,
figure 6 is a schematic partial perspective view of a fin according to a second embodiment,
figure 7 is a schematic partial perspective view of a fin according to a third embodiment,
fig. 8 is a schematic partial perspective view of a fin according to a fourth embodiment.
Like elements in different figures have like reference numerals.
Detailed Description
The following embodiments are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference refers to the same embodiment, or that a feature only applies to a single embodiment. Various features of the different embodiments may also be combined and/or interchanged to provide further embodiments.
In this specification, some elements or parameters may be indexed, such as a first element or a second element and a first parameter and a second parameter or a first criterion and a second criterion, and so on. In this case, this is a simple index used to distinguish and represent similar but not identical elements or parameters or criteria. Such indexing does not imply that one element, parameter or criterion is prioritized over another element, parameter or criterion, and such representations may be readily interchanged without departing from the scope of this specification.
In the present description, "placed upstream" is understood to mean that one element is placed before another element with respect to the direction of circulation of the fluid. In contrast, "placed downstream" is understood to mean that one element is placed after another element with respect to the direction of flow of the fluid.
Fig. 1 shows a heat exchanger 1 having a general parallelepiped shape, this heat exchanger 1 comprising a tube bundle formed by a plurality of tubes 2 inside which a first heat transfer fluid, for example a refrigerant fluid circulating in a reversible cooling circuit, is intended to circulate. The tubes 2 have a circular rectangular cross section defined by a major axis and a minor axis, and are arranged parallel to each other. The tubes 2 are flat tubes, that is to say they have two large sides with plane surfaces and parallel to the long axis and two small sides with curved surfaces which form the edges of the tubes 2 and connect the edges of the large sides. Fins 6 connecting the large sides of two adjacent tubes 2 are arranged between the tubes 2. These fins 6 act as turbulators and increase the surface area for heat exchange with the second heat transfer fluid intended to traverse the bundle of tubes 2 by passing between the tubes 2. For example, the second heat transfer fluid may be an air stream.
The fins 6 are, for example, corrugated or serrated strips, placed between the tubes 2 and fixed to said tubes 2. The tubes 2 and fins 6 are typically made of metal, such as aluminum or an aluminum alloy. The tubes 2 and fins 6 forming the tube bundle are then fixed to one another, typically by brazing. The braze bundle is then referenced.
The heat exchanger 1 also has two manifolds 3 or headers, the manifolds 3 being arranged at each end of the tubes 2. These manifolds 3 each have a header plate 4 and a cover 8 that covers the header plate 4 and closes the manifold 3. These manifolds 3 make it possible to collect and/or distribute the first heat transfer fluid so that it flows in the tubes 2.
Header plate 4 sealingly connects manifold 3 and the bundle of tubes 2. Further, the header plate 4 may have a rectangular overall shape. The header plate 4 also has a plurality of apertures, the shape of which corresponds to the cross-sectional shape of the tubes 2 and which are capable of receiving the ends of the tubes 2. The tubes 2 are sealingly fixed to a header plate 4.
Because the tubes 2, fins 6 and header plate 4 are brazed, the header plate 4 may be made of a metallic material, particularly aluminum or an aluminum alloy. Reference is then made to the brazed heat exchanger 1.
As shown in fig. 2, the fin 6 has a corrugated portion 60 extending in the longitudinal direction of the tube 2. The length of the tube 2 here refers to the axis connecting the ends of the tube 2, to which the manifold 3 is fixed. The corrugations 60 have peaks 61 (visible in fig. 3 and 4) in contact with the tube 2, more specifically with the planar surface of the tube 2, and flanks 62 (visible in fig. 3 and 4) connecting said peaks 61. The peaks 61 and the flanks 62 are arranged perpendicularly to the length axis of the tube 2.
The fin 6 has in particular a first portion 6A and a second portion 6B. The first portion 6A is disposed upstream of the second portion 6B in the direction of passage of the second heat transfer fluid (indicated by arrow 100 in fig. 2). The first portion 6A projects beyond the tube 2, more specifically beyond the front edge of the tube 2. The leading edge of the tubes 2 here refers to the edge of the tubes 2 facing the flow of the second heat transfer fluid.
The second portion 6B stops at the rear edge of the tube 2. The rear edge of the tube 2 here refers to the edge of the tube 2 opposite the front edge.
As shown in fig. 3 and 4, the peaks 61 of the first portion 6A have a profile presenting a flat portion 64 and the peaks 61 of the second portion 6B have a rounded profile 65, so that the corrugations 60 have a sinusoidal profile.
The first portion 6A of the fin 6 protrudes beyond the front edge of the tube 2 and the peak 61 thereof has a flat portion 64, which makes it possible to prevent the formation of frost. This is because the peaks 61 with flat portions 64, in combination with the protrusions, make it possible to better drain the water condensed on the front face of the heat exchanger 1, i.e. the face of the heat exchanger through which the second heat transfer fluid enters. Therefore, frost is less likely to be formed.
The second portion 6B may in particular extend over 100% to 66% of the width of the tube 2. The width here refers to the distance between the front edge and the rear edge of the tube 2. When the second portion 6B extends over 100% of the width, the first portion 6A is limited to the portion of the fin 6 that protrudes outside the tube 2.
The first portion 6A preferably has smooth flanks 62. These smooth flanks 62 likewise make it possible to suitably drain off condensate. The second portion 6B may have louvers 63 on its lateral wings 62. By louver 63 is here meant a deflecting wall in one piece with the lateral wing 62, inclined with respect to said lateral wing 62 and projecting on both sides of the lateral wing 62. The deflector walls define openings on either side of the flap 62 so that the second heat transfer fluid can flow from one side of the flap 62 to the other.
As shown in fig. 5, but also in fig. 2, the louvers 63 of the same wing 62 may all be oriented in the same direction. This means that their openings on the same side of the same flank 62 all face in the same direction. This arrangement makes it possible to appropriately swirl the second heat transfer fluid and improve the heat exchange.
According to the variant shown in fig. 6, one and the same flank 62 with corrugations 60 may have louvers 63 oriented in different directions. In the example shown in fig. 6, one and the same wing 62 has, on the same side, a first series of louvers 63 oriented towards the front edge of tube 2 and a second series of louvers 63 oriented towards the rear edge of tube 2.
The louvers 63 of both flanks 62 may have the same orientation within the same corrugation 60. It is also contemplated that the orientation of louvers 63 is reversed from one wing 62 to the other.
According to a first embodiment, shown in particular in fig. 2, 5 and 6, the first portion 6A and the second portion 6B are made of two separate parts. The first portion 6A and the second portion 6B then correspond to two corrugated strips arranged side by side in the length direction of the tube 2.
A corrugation 60 having peaks 61 with flat portions 64 is more difficult to manufacture than a corrugation 60 having peaks 61 with rounded profiles 65 and it is more difficult to control the pitch of the corrugation 60. Therefore, these corrugations 60 having the peaks 61 with the flat portions 64 can be limited to the first portion 6A in order to limit the manufacturing cost of the heat exchanger 1.
The first portion 6A and the second portion 6B are preferably arranged edge-to-edge and do not match each other (fit). For this reason, the corrugations 60 of the first portion 6A and the second portion 6B are preferably offset from each other. As shown in fig. 5, the pitch of the corrugations 60 of the first portion 6A and the pitch of the corrugations 60 of the second portion 6B may be different. More specifically, the pitch of the corrugations 60 of the first portion 6A may be greater than the pitch of the corrugations 60 of the second portion 6B.
The thickness e (visible in fig. 3) of the first portion 6A may likewise be greater than the thickness e' (visible in fig. 4) of the second portion 6B. This makes it possible for the two parts likewise not to be matched to one another, but it also makes it possible to better protect the heat exchanger 1 against impacts. This is because, since the first portion 6A projects beyond the front edge of the tube 2, the latter is more likely to be subjected to impacts from factors such as gravel, in particular if it is an evaporator/condenser placed on the front face of the motor vehicle. Therefore, the greater thickness e makes it possible to absorb these impacts more effectively and to protect the heat exchanger 1, in particular the tubes 2 thereof.
The fact that the first portion 6A and the second portion 6B are separate parts also makes it possible to vary their shape with respect to each other in order to limit the risk of frost formation. Thus, as shown in fig. 1, 5 and 6, the first portion 6A may extend along a straight line profile in the width direction of the tube 2. According to another example shown in fig. 7, the first portion 6A may extend along a corrugated profile in the width direction of the tube 2.
Even more complex first portions 6A are equally conceivable, for example as shown in fig. 8. Thus, the first portion 6A may have at least two series of grooves 601, 602, 603, 604 offset from each other in the width direction of the tube 2. In the example shown in fig. 8, the first portion 6A has four series of slots 601, 602, 603, 604.
Thus, the first portion 6A and the second portion 6B of the fin 6 can be manufactured separately, for example by shaping two different metal plates with rollers exhibiting different patterns, so as to form discrete peaks 61 between the first portion 6A and the second portion 6B. The two parts 6A, 6B are then arranged side by side during the manufacture of the heat exchanger 1 and fixed to the tube 2, for example by brazing.
According to a second embodiment, not shown, the first portion 6A and the second portion 6B can be made of one and the same piece. In this case, the corrugations 60 of the first portion 6A and the second portion 6B have a similar pitch and are aligned. The first portion 6A may have smooth flanks 62 or corrugated flanks 62, as long as the corrugations 60 meet at the junction with the second portion 6B.
Still according to this second embodiment, the first portion 6A and the second portion 6B of the fin 6 can be made simultaneously, for example by shaping the metal sheet by means of rollers exhibiting different patterns, so as to form different peaks 61 between the first portion 6A and the second portion 6B.
It is therefore evident that the heat exchanger 1 makes it possible to reduce the risk of frost formation when said heat exchanger 1 is in use, thanks to the presence of the two separate portions 6A, 6B of the fins 6.
Claims (10)
1. A heat exchanger (1) having a bundle of tubes (2) arranged parallel to each other, inside which a first heat transfer fluid is intended to circulate, a second fluid is intended to traverse the bundle of tubes (2) between the tubes (2), the bundle of tubes (2) having fins (6) arranged between the tubes (2), the fins (6) having corrugations (60) extending in the length direction of the tubes (2), the corrugations (60) having peaks (61) in contact with the tubes (2) and flanks (62) connecting the peaks (61), characterized in that the fins (6) have a first portion (6A) and a second portion (6B), the first portion (6A) being arranged upstream of the second portion (6B) in the direction of passage of the second heat transfer fluid, the first portion (6A) projecting beyond the front edge of the tubes (2), the peaks (61) of the first portions (6A) have a profile presenting flat portions (64), the peaks (61) of the second portions (6B) have a rounded profile (65), so that the corrugations (60) have a sinusoidal profile.
2. Heat exchanger (1) according to claim 1, characterized in that said second portion (6B) extends over 100% to 66% of the width of said tubes (2).
3. Heat exchanger (1) according to claim 1 or 2, characterized in that said first portion (6A) and second portion (6B) are made of one and the same piece.
4. Heat exchanger (1) according to claim 1 or 2, characterized in that said first portion (6A) and second portion (6B) are made of two separate parts.
5. Heat exchanger (1) according to claim 4, characterized in that the pitch of the corrugations (60) of said first portion (6A) and the pitch of the corrugations (60) of said second portion (6B) are different.
6. Heat exchanger (1) according to claim 5, characterized in that the pitch of the corrugations (60) of said first portion (6A) is greater than the pitch of the corrugations (60) of said second portion (6B).
7. The heat exchanger (1) according to any of claims 4 to 6, wherein the thickness (e) of the first portion (6A) is greater than the thickness (e') of the second portion (6B).
8. Heat exchanger (1) according to any of claims 4 to 7, characterized in that said first portion (6A) has at least two series of grooves (601, 602, 603, 604) offset from each other in the width direction of said tubes (2).
9. The heat exchanger (1) according to any one of claims 1 to 7, wherein the first portion (6A) extends along a rectilinear profile in the width direction of the tubes (2).
10. The heat exchanger (1) according to any one of claims 1 to 7, wherein the first portion (6A) extends along a corrugated profile in the width direction of the tubes (2).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FRFR2000040 | 2020-01-03 | ||
| FR2000040A FR3106000B1 (en) | 2020-01-03 | 2020-01-03 | Tube heat exchanger with spacers |
| PCT/FR2020/052481 WO2021136896A1 (en) | 2020-01-03 | 2020-12-16 | Tube heat exchanger having spacers |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115038924A true CN115038924A (en) | 2022-09-09 |
Family
ID=69811379
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202080095530.2A Pending CN115038924A (en) | 2020-01-03 | 2020-12-16 | Tube heat exchanger with spacers |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20230042424A1 (en) |
| CN (1) | CN115038924A (en) |
| FR (1) | FR3106000B1 (en) |
| WO (1) | WO2021136896A1 (en) |
Family Cites Families (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002090082A (en) * | 2000-09-19 | 2002-03-27 | Japan Climate Systems Corp | Heat exchanger |
| ATE380324T1 (en) * | 2002-03-09 | 2007-12-15 | Behr Gmbh & Co Kg | HEAT EXCHANGER |
| JP2005283019A (en) * | 2004-03-30 | 2005-10-13 | Calsonic Kansei Corp | Louver fin |
| KR100668806B1 (en) * | 2005-06-17 | 2007-01-16 | 한국과학기술연구원 | Louver fin type heat exchanger having improved heat exchange efficiency by controlling water blockage |
| JP2007232246A (en) * | 2006-02-28 | 2007-09-13 | Denso Corp | Heat exchanger |
| JP4674602B2 (en) * | 2007-11-22 | 2011-04-20 | 株式会社デンソー | Heat exchanger |
| US8167028B2 (en) * | 2008-01-03 | 2012-05-01 | Denso Corporation | Heat exchanger fin with planar crests and troughs having slits |
| US7913750B2 (en) * | 2008-01-09 | 2011-03-29 | Delphi Technologies, Inc. | Louvered air center with vortex generating extensions for compact heat exchanger |
| CN101619950B (en) * | 2009-08-13 | 2011-05-04 | 三花丹佛斯（杭州）微通道换热器有限公司 | Fin and heat exchanger with same |
| US20110139414A1 (en) * | 2009-12-14 | 2011-06-16 | Delphi Technologies, Inc. | Low Pressure Drop Fin with Selective Micro Surface Enhancement |
| WO2012098912A1 (en) * | 2011-01-21 | 2012-07-26 | ダイキン工業株式会社 | Heat exchanger and air conditioner |
| EP2653819A4 (en) * | 2011-01-21 | 2014-07-02 | Daikin Ind Ltd | Heat exchanger and air conditioner |
| WO2013160950A1 (en) * | 2012-04-26 | 2013-10-31 | 三菱電機株式会社 | Heat exchanger and air conditioner |
| FR2991034B1 (en) * | 2012-05-25 | 2014-06-06 | Valeo Systemes Thermiques | INTERCALAR FOR THERMAL EXCHANGER AND THERMAL EXCHANGER |
| FR2995397B1 (en) * | 2012-09-10 | 2014-08-22 | Valeo Systemes Thermiques | INTERCALAR OF HEAT EXCHANGER. |
| MX2016013418A (en) * | 2014-04-16 | 2017-05-04 | Sanhua (Hangzhou) Micro Channel Heat Exchanger Co Ltd | Fins and bent heat exchanger with same. |
| CN106643263B (en) * | 2015-07-29 | 2019-02-15 | 丹佛斯微通道换热器（嘉兴）有限公司 | Fin component for heat exchanger and the heat exchanger with the fin component |
| FR3040478B1 (en) * | 2015-08-25 | 2017-12-15 | Valeo Systemes Thermiques | HEAT EXCHANGER |
| CN205352165U (en) * | 2015-12-16 | 2016-06-29 | 杭州三花微通道换热器有限公司 | Heat exchanger core and heat exchanger that has it |
| US11073342B2 (en) * | 2016-06-01 | 2021-07-27 | Denso Corporation | Regenerative heat exchanger |
| CN110300879B (en) * | 2017-02-21 | 2020-11-03 | 三菱电机株式会社 | Heat exchanger and air conditioner |
| JP2020034184A (en) * | 2018-08-27 | 2020-03-05 | 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． | Heat exchanger and air conditioner |
| WO2021234964A1 (en) * | 2020-05-22 | 2021-11-25 | 三菱電機株式会社 | Heat exchanger and air conditioner |
-
2020
- 2020-01-03 FR FR2000040A patent/FR3106000B1/en active Active
- 2020-12-16 WO PCT/FR2020/052481 patent/WO2021136896A1/en active Application Filing
- 2020-12-16 US US17/790,595 patent/US20230042424A1/en active Pending
- 2020-12-16 CN CN202080095530.2A patent/CN115038924A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| US20230042424A1 (en) | 2023-02-09 |
| FR3106000A1 (en) | 2021-07-09 |
| WO2021136896A1 (en) | 2021-07-08 |
| FR3106000B1 (en) | 2022-01-14 |
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