CN113950605A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
CN113950605A
CN113950605A CN202080042618.8A CN202080042618A CN113950605A CN 113950605 A CN113950605 A CN 113950605A CN 202080042618 A CN202080042618 A CN 202080042618A CN 113950605 A CN113950605 A CN 113950605A
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CN
China
Prior art keywords
heat exchanger
offset
fin
medium
ltoreq
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
CN202080042618.8A
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Chinese (zh)
Inventor
川村威一郎
坂井耐事
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.)
T Rad Co Ltd
Original Assignee
Toyo Radiator 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 Toyo Radiator Co Ltd filed Critical Toyo Radiator Co Ltd
Publication of CN113950605A publication Critical patent/CN113950605A/en
Pending legal-status Critical Current

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    • 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
    • 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
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • 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
    • 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

Abstract

In a heat exchanger having a planar square plate-like plate with offset fins interposed therebetween and having refrigerant inlet and outlet ports arranged at diagonal positions thereof, variation in flow rate distribution in the width direction of the offset fins is suppressed. In a heat exchanger having an aspect ratio b/a of 0.12 to 0.33 between the inlet and outlet of a refrigerant arranged at diagonal positions, a fin pitch Pf is set to 2mm to 5mm, and a groove length SL is set to 1 to 3 mm.

Description

Heat exchanger
Technical Field
The present invention relates to a heat exchanger in which a plurality of plate-shaped plates are stacked, first flow paths and second flow paths are alternately arranged in a stacking direction, and offset fins are interposed between the first flow paths, and more particularly, to a heat exchanger most suitable for heat exchange in an evaporator or a condenser.
Background
As an example, a plate-laminated heat exchanger is known in which a first flow path and a second flow path are formed between rectangular plate-shaped plates that are laminated, inner fins are interposed between the first flow paths, and inlet/outlet ports of the respective flow paths are provided at diagonal positions of the plates.
An example of the inner fin is an offset type inner fin in which fluid flows and diffuses in the width direction of the fin through a gap of an offset portion, but when the flow and diffusion are insufficient, a flow rate distribution may be deviated, and a pressure loss may be increased.
Disclosure of Invention
Problems to be solved by the invention
Currently, it is desired to uniformize the flow rate distribution of the fluid flowing through the heat exchanger having the offset inner fin and reduce the pressure loss.
Accordingly, an object of the present invention is to provide a heat exchanger having offset inner fins capable of uniformizing the flow rate distribution of a fluid and reducing pressure loss.
Means for solving the problems
The present invention described in claim 1 is a heat exchanger including a plurality of plates 3a, 3b, the plurality of plates 3a, 3b having a pair of opposed long sides L and a pair of opposed short sides M on an outer periphery thereof and being formed in a plate shape having a rectangular plane, a pair of first medium flow holes 1 being arranged at a first pair of angular positions of the plane, and a second medium flow hole 2 being arranged at a second pair of angular positions, the heat exchanger being configured such that the plates 3a, 3b are stacked to alternately form a first flow path 4 for a first medium and a second flow path 5 for a second medium in a stacking direction, offset fins 6 are incorporated in the first flow path 4, the plates are joined liquid-tightly, and heat exchange is performed between the two media,
the heat exchanger is characterized in that it is provided with,
the offset fin 6 is formed by bending a metal plate into a plurality of wave-like shapes 6a running in the short side M direction, each wave-like shape 6a adjacent to each other so as to be separated in the long side L direction is shifted in position in the short side M direction, a ridge line 6b of each wave-like shape is arranged in parallel with the long side L direction,
the aspect ratio b/a, i.e., the dimension ratio, between the inlet and outlet of the first medium of the plates 3a and 3b and the offset fin 6 is 0.12. ltoreq. b/a. ltoreq.0.33,
the fin pitch Pf of each waveform 6a of the offset fin 6 is 2mm or more and Pf or less and 5mm or less,
the slot length SL of each waveform 6a of the offset fin 6 is 1mm or more and 3mm or less.
The present invention according to claim 2 is the present invention according to claim 1,
the heat exchanger is an evaporator and the heat exchanger is,
the fin pitch Pf is more than or equal to 3mm and less than or equal to 5 mm.
The present invention according to claim 3 is the present invention according to claim 1,
the heat exchanger is a condenser and the heat exchanger is,
the fin pitch Pf is more than or equal to 2mm and less than or equal to 3 mm.
Effects of the invention
The invention described in claim 1 is characterized in that, in the heat exchanger in which the aspect ratio b/a (dimension ratio) between the inlet and outlet of the first medium is 0.12. ltoreq. b/a. ltoreq.0.33, the fin pitch Pf of each of the undulations 6a of the offset fin 6 is 2 mm. ltoreq. Pf.ltoreq.5 mm, and the groove length SL of each of the undulations 6a of the offset fin 6 is 1 mm. ltoreq. SL. 3 mm.
This ensures the flow path (gap) of the offset portion and the reinforcing effect by the inner fin, and suppresses the variation in the flow rate distribution in the width direction orthogonal to the ridge line direction of the wave, thereby making it possible to uniformize the flow rate distribution of the fluid in the heat exchanger.
The invention of the heat exchanger according to claim 2 is characterized in that, in the evaporator in which the aspect ratio b/a (dimension ratio) between the inlet and outlet of the first medium is 0.12. ltoreq. b/a. ltoreq.0.33, the fin pitch Pf of each waveform of the offset fins is 3 mm. ltoreq. Pf.ltoreq.5 mm, and the groove length SL of each waveform 6a is 1 mm. ltoreq. SL. ltoreq.3 mm.
Thus, in the evaporator, it is possible to secure a sufficient heat exchange amount while suppressing variation in flow rate distribution in the width direction orthogonal to the ridge line direction of the wave.
The invention of the heat exchanger according to claim 3 is characterized in that, in the condenser in which the aspect ratio b/a (dimension ratio) between the inlet and outlet of the first medium is 0.12. ltoreq. b/a. ltoreq.0.33, the fin pitch Pf of each waveform of the offset fins is 2 mm. ltoreq. Pf.ltoreq.3 mm, and the groove length SL of each waveform 6a is 1 mm. ltoreq. SL. ltoreq.3 mm.
Thus, in the condenser, it is possible to secure a sufficient heat exchange amount while suppressing variation in flow rate distribution in the width direction orthogonal to the ridge line direction of the wave.
Drawings
Fig. 1 (a) is a plan view of a main part of the heat exchanger of the present invention, fig. 1 (B) is a perspective view of a main part of the offset fin 6 of the heat exchanger of the present invention, and fig. 1 (C) is a view from C-C of fig. 1 (B).
Fig. 2 is an exploded perspective view of the heat exchanger.
FIG. 3 is a schematic sectional view from III-III in FIG. 1A.
Fig. 4 is a diagram showing the pressure-loss ratio of the heat exchanger of the present invention, fig. 4 (a) shows a characteristic curve of the evaporator at each fin pitch Pf and groove length SL, and fig. 4 (B) shows a characteristic curve of the pressure-loss ratio of the condenser.
Fig. 5 is a diagram showing the heat exchange amount ratio of the heat exchanger, and is a characteristic curve for each fin pitch Pf and each groove length SL, fig. 5 (a) is a characteristic curve for an evaporator, and fig. 5 (B) is a characteristic curve for a condenser.
Detailed Description
Next, embodiments of the present invention will be described based on the drawings.
The heat exchanger of the present invention has offset fins (offset fins) in a flow passage through which a fluid flows, and is suitable for use as an evaporator or a condenser.
Fig. 1 (a) is a plan view of the plates 3a and 3b of the heat exchanger and the offset fins 6 interposed between the plates 3a and 3 b. Fig. 1 (B) is an enlarged perspective view of the offset fin 6, and fig. 1 (C) is a view along line C-C of fig. 1 (B). Fig. 2 is an exploded perspective view of the heat exchanger. FIG. 3 is a sectional view taken along line III-III in FIG. 1A.
As shown in fig. 2 and 3, the core of the heat exchanger includes a stacked body of plates 3a and 3b, in which a first flow path 4 and a second flow path 5 are formed in every other plate, and offset fins 6 are interposed in the first flow path 4. The plates 3a and 3b are formed in a disc shape so that the plane is substantially square, and a pair of first medium flow holes 1 are formed at a first pair of angular positions, and a pair of second medium flow holes 2 are formed at a second pair of angular positions. An annular bulge 9 is provided on the plate 3a side at the hole edge of the second medium flow hole 2, and an annular bulge 9 is provided on the plate 3b side at the hole edge of the first medium flow hole 1. The offset fin 6 interposed in the first flow channel 4 has an opening 10 formed therethrough so as to match the first medium flow hole 1 and the second medium flow hole 2 of each plate. When these are stacked, the offset fin 6 has communication holes formed between adjacent plates.
As shown in fig. 2, the top plate 12 is fitted to the upper end of the heat exchanger in the stacking direction of the cores via an end plate 15, and the tubes 13 are provided in the top plate 12. These components are arranged on the substrate 11, and are soldered and fixed integrally with each other.
The first medium 7 flows through the first flow paths 4 from one of the first medium tubes 13 and flows out from the other first medium tube 13. The second medium 8 flows through the second flow paths 5 from one of the second medium tubes 13 and flows out from the other second medium tube 13.
In this example, a refrigerant that changes into a gas-liquid two-phase state is supplied as the first medium 7, and cooling water is supplied as the second medium 8, and heat exchange is performed between both media.
The offset fin 6 interposed in the first flow channel 4 may be formed of an aluminum material (an alloy including aluminum) or the like, and as shown in fig. 1 (B) and (C), the offset fin 6 is bent so that waves travel at a constant fin pitch Pf in the direction of the short side M of the plate 3a, thereby forming a wave shape 6 a. The ridge line 6b of the waveform 6a is shifted in phase by several pitches with respect to the direction of the long side L, thereby forming an offset gap. The interval of the offset gaps can be, for example, about 1/4 of the fin pitch Pf.
The height H of the waveform 6a can be about 1/2 of the fin pitch Pf, for example, and the plate thickness of the offset fin 6 can be 0.1mm to 0.3mm, for example.
The present inventors have found that the conditions of the aspect ratio (dimension ratio) b/a between the inlet and outlet of the heat exchanger, the fin pitch Pf of the offset fin 6, and the slot (slit) length SL of the offset fin 6 affect the flow resistance (pressure loss ratio, pressure loss) of the refrigerant flowing through the offset fin 6 of the first flow channel 4 and the heat exchange amount (heat exchange amount).
Here, a of the dimension ratio b/a is a distance between centers of the entrances and exits measured in parallel to the long side L of each plate 3 in fig. 1 (a), and b is a distance between centers of the entrances and exits measured in parallel to the short side M. The slot length SL is the length of the ridge line 6B of each waveform 6a in fig. 1 (B).
Experimental conditions for the heat exchanger with offset fins 6 are as follows.
The dimension ratio (b/a) is set to 0.12. ltoreq. b/a. ltoreq.0.33, the fin pitch Pf is set to 2mm, 3mm, 4mm, 5mm, and the slot length SL is set to 1mm to 7 mm.
The first medium 7 flowing through the first flow path 4 is a fluorocarbon refrigerant, and the second medium 8 flowing through the second flow path 5 is cooling water.
The pressure loss in the case of using the heat exchanger as an evaporator and the pressure loss in the case of using the heat exchanger as a condenser were measured for each offset fin 6. The heat exchange amount in the case of using the heat exchanger as the evaporator and the heat exchange amount in the case of using the heat exchanger as the condenser were measured.
The minimum value (lower limit) of the slot length SL is set to 1mm, which is the limit of the press working by the offset fin.
The lower limit of the fin pitch Pf is set to 2mm, which is the minimum limit of the offset clearance in consideration of the offset fins. The reason why the upper limit of the fin pitch Pf is 5mm is that if the offset fin Pf is too large, the pressure resistance by the inner fins between the plates of the heat exchanger cannot be sufficiently obtained.
As a result, the following is clarified.
Fig. 4 (a) shows a pressure loss ratio (pressure loss ratio) in the case of using the evaporator. The vertical axis represents the pressure loss ratio, and the horizontal axis represents the groove length SL. Here, the pressure loss is based on a pressure loss of 2mm in fin pitch Pf and 2mm in slot length SL (100%). Fig. 4 (B) shows a pressure loss ratio (pressure loss ratio) when the condenser is used. The vertical axis, horizontal axis, and reference are taken in the same manner as in fig. 4 (a).
In both cases of fig. 4 a and 4B, the pressure loss ratio is reduced in a range where the groove length is short (a range of SL from 1mm to 3 mm).
This is because, basically, the shorter the groove length becomes, the more uniform the flow velocity distribution in the width direction (fig. 1 (a) M) of the refrigerant becomes. That is, this is because, as the groove length is short, the refrigerant passing through the groove easily flows not only in the longitudinal direction of the plate but also in the width direction, and the pressure loss is reduced. This tendency is also the same when the aspect ratio (dimension ratio) between the entrance and the exit is 0.12 or 0.33.
Next, fig. 5 (a) shows the exchange heat ratio in the case of using as an evaporator. The vertical axis represents the exchange heat ratio, and the horizontal axis represents the slot length SL. The heat exchange amount was calculated based on the fin pitch Pf of 2mm and the slot length SL of 2mm (100%).
The optimum range of the heat exchange ratio when used as an evaporator is a range of a shaded portion (Pf is 3mm to 5mm), and the larger the fin pitch Pf is, the larger the heat exchange amount is.
This is because the operating pressure of the refrigerant in the evaporator is as low as about 200KPaG, and the saturation temperature greatly changes due to the pressure loss. Further, the lower the pressure loss, the smaller the change in saturation temperature, and the larger the temperature difference with the cooling water, the larger the heat exchange amount.
Next, fig. 5 (B) shows the exchange heat ratio in the case of using as a condenser. The vertical axis, horizontal axis, and reference are taken in the same manner as in fig. 5 (a).
The optimum range of the heat exchange rate when the condenser is used is a range of a shaded portion (Pf is 2mm to 3mm), and the smaller the fin pitch, the larger the heat exchange amount.
This is because the operating pressure of the condenser is as high as about 2000KPaG, and the change in saturation temperature due to pressure loss is small. In addition, unlike the evaporator, the condenser has a large proportion of the gas phase state in the heat exchanger. Therefore, as the fin pitch Pf is reduced and the heat exchange area is increased, the heat exchange of the gas phase progresses, and the entire heat exchange amount increases.
From the above, when the heat exchanger having offset fins is used as an evaporator, it is preferable that the aspect ratio b/a (dimension ratio) between the inlet and outlet of the first medium is in the range of 0.12. ltoreq. b/a. ltoreq.0.33, the groove length SL of the offset fins 6 is in the range of 1 mm. ltoreq. SL. ltoreq.3 mm, and the fin pitch Pf of the offset fins 6 is in the range of 3 mm. ltoreq. Pf. ltoreq.5 mm.
Next, when the heat exchanger is used as a condenser, it is preferable that the aspect ratio b/a (dimension ratio) between the inlet and outlet of the first medium is in the range of 0.12. ltoreq. b/a. ltoreq.0.33, the groove length SL of the offset fin 6 is in the range of 1 mm. ltoreq. SL. ltoreq.3 mm, and the fin pitch Pf of the offset fin 6 is in the range of 2 mm. ltoreq. Pf. ltoreq.3 mm.
When the plate-stacked heat exchanger having offset fins is used in a heat exchanger other than an evaporator or a condenser, such as an oil cooler (the first medium is oil), for example, the aspect ratio b/a (dimension ratio) between the inlet and outlet of the first medium can be set to a range of 0.12. ltoreq. b/a. ltoreq.0.33, the groove length SL of the offset fins 6 can be set to a range of 1 mm. ltoreq. SL. ltoreq.3 mm, and the fin pitch Pf of the offset fins 6 can be set to a range of 2 mm. ltoreq. Pf. ltoreq.5 mm.
Description of the reference numerals
1 first Medium flow hole
2 second Medium circulation hole
3a, 3b plate
4 first flow path
5 second flow path
6 offset fin
6a waveform
6b ridge
7 first Medium
8 second Medium
9 annular bulge
10 opening
11 substrate
12 Top plate
13 pipe
14 recess
15 end plate
Aspect ratio (dimension ratio) between b/a ports
Pf fin pitch
Length of SL slot
L Long side
M short side
And H height.

Claims (3)

1. A heat exchanger having a plurality of plates (3a, 3b) which have a pair of long sides (L) facing each other and a pair of short sides (M) facing each other on the outer periphery, are formed in a plate shape having a rectangular plane, are provided with a pair of first medium flow holes (1) at a first pair of corners of the plane, and are provided with a second medium flow hole (2) at a second pair of corners, wherein the plates (3a, 3b) are stacked to alternately form a first flow path (4) for a first medium and a second flow path (5) for a second medium in the stacking direction, offset fins (6) are incorporated in the first flow path (4), and the plates are joined together in a liquid-tight manner to perform heat exchange between the two media,
the heat exchanger is characterized in that it is provided with,
the offset fin (6) is formed by bending a metal plate into a plurality of waves (6a) running in the short side (M) direction, wherein each wave (6a) adjacent to each other while being separated in the long side (L) direction is shifted in position in the short side (M) direction, and a ridge line (6b) of each wave is arranged in parallel to the long side (L) direction,
the aspect ratio b/a, i.e., the dimension ratio, between the inlet and outlet of the first medium of the plates (3a, 3b) and the offset fin (6) is 0.12-0.33,
the fin pitch Pf of each wave form (6a) of the offset fin (6) is 2mm ≤ Pf ≤ 5mm,
the slot length SL of each waveform (6a) of the offset fin (6) is more than or equal to 1mm and less than or equal to 3 mm.
2. The heat exchanger of claim 1,
the heat exchanger is an evaporator and the heat exchanger is,
the fin pitch Pf is more than or equal to 3mm and less than or equal to 5 mm.
3. The heat exchanger of claim 1,
the heat exchanger is a condenser and the heat exchanger is,
the fin pitch Pf is more than or equal to 2mm and less than or equal to 3 mm.
CN202080042618.8A 2019-07-02 2020-06-29 Heat exchanger Pending CN113950605A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2019123984 2019-07-02
JP2019-123984 2019-07-02
PCT/JP2020/026313 WO2021002474A1 (en) 2019-07-02 2020-06-29 Heat exchanger

Publications (1)

Publication Number Publication Date
CN113950605A true CN113950605A (en) 2022-01-18

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ID=74100396

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202080042618.8A Pending CN113950605A (en) 2019-07-02 2020-06-29 Heat exchanger

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JP (1) JPWO2021002474A1 (en)
CN (1) CN113950605A (en)
DE (1) DE112020003195T5 (en)
WO (1) WO2021002474A1 (en)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008039380A (en) * 2006-07-11 2008-02-21 Denso Corp Exhaust gas heat exchanger
KR20120002075A (en) * 2010-06-30 2012-01-05 한라공조주식회사 Plate-type heat exchanger
WO2014048228A1 (en) * 2012-09-26 2014-04-03 杭州三花研究院有限公司 Fin of heat exchanger and heat exchanger
WO2014132602A1 (en) * 2013-02-27 2014-09-04 株式会社デンソー Stacked heat exchanger
US20170051982A1 (en) * 2014-05-09 2017-02-23 Panasonic Intellectual Property Management Co., Ltd. Offset fin and heat exchanger having same

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005147572A (en) * 2003-11-18 2005-06-09 Calsonic Kansei Corp Fin for heat exchanger
JP2007183071A (en) * 2006-01-10 2007-07-19 Tokyo Bureizu Kk High-pressure-resistant compact heat exchanger and manufacturing method of the same
JP6420140B2 (en) * 2014-12-26 2018-11-07 株式会社マーレ フィルターシステムズ Oil cooler
FR3049644B1 (en) * 2016-04-01 2018-04-13 Safran Aircraft Engines AIRBORNE TURBOMACHINE EXIT OUTPUT AUBE, HAVING AN IMPROVED LUBRICANT COOLING FUNCTION USING A THERMAL CONDUCTION MATRIX OCCURRING IN AN INTERIOR PASSAGE OF THE DAWN

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008039380A (en) * 2006-07-11 2008-02-21 Denso Corp Exhaust gas heat exchanger
KR20120002075A (en) * 2010-06-30 2012-01-05 한라공조주식회사 Plate-type heat exchanger
WO2014048228A1 (en) * 2012-09-26 2014-04-03 杭州三花研究院有限公司 Fin of heat exchanger and heat exchanger
WO2014132602A1 (en) * 2013-02-27 2014-09-04 株式会社デンソー Stacked heat exchanger
CN105074375A (en) * 2013-02-27 2015-11-18 株式会社电装 Stacked heat exchanger
US20170051982A1 (en) * 2014-05-09 2017-02-23 Panasonic Intellectual Property Management Co., Ltd. Offset fin and heat exchanger having same

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WO2021002474A1 (en) 2021-01-07
JPWO2021002474A1 (en) 2021-01-07
DE112020003195T5 (en) 2022-04-21

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