WO2020145427A1 - Échangeur de chaleur doté de distributeurs à plaques - Google Patents

Échangeur de chaleur doté de distributeurs à plaques Download PDF

Info

Publication number
WO2020145427A1
WO2020145427A1 PCT/KR2019/000299 KR2019000299W WO2020145427A1 WO 2020145427 A1 WO2020145427 A1 WO 2020145427A1 KR 2019000299 W KR2019000299 W KR 2019000299W WO 2020145427 A1 WO2020145427 A1 WO 2020145427A1
Authority
WO
WIPO (PCT)
Prior art keywords
distributors
stacked
refrigerant
heat exchanger
distributor
Prior art date
Application number
PCT/KR2019/000299
Other languages
English (en)
Korean (ko)
Inventor
천성민
이덕희
Original Assignee
두성산업 (주)
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 두성산업 (주) filed Critical 두성산업 (주)
Priority to PCT/KR2019/000299 priority Critical patent/WO2020145427A1/fr
Publication of WO2020145427A1 publication Critical patent/WO2020145427A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • 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

Definitions

  • the present invention relates to a heat exchanger provided with a plate-shaped distributor, and more particularly, to a heat exchanger provided with a plate-shaped distributor to improve heat exchange efficiency by improving the diffusivity of refrigerant flowing between the plate-shaped distributors.
  • the heat exchanger is composed of a pair of header tanks through which heat exchange medium is introduced and discharged, and tubes connecting the header tanks to distribute heat exchange medium therein, thereby performing heat exchange.
  • the heat exchanger can be roughly divided into two types for each type, a fin-tube type heat exchanger made of a plurality of tubes inserted into a tank, and a plate type heat exchanger in which a plurality of plates are stacked to form a tube part and a tank part. It can be classified as a plate heat exchanger.
  • the plate type heat exchanger is widely used because it is easy to assemble and has a small number of required parts, which is more productive than the fin-tube type heat exchanger, and has the advantage of securing a space in the engine room by reducing the volume.
  • the plate-type heat exchanger can design a more complicated and diversified flow path than the fin-tube type heat exchanger by changing the shape of the plate, so it is applied when two types of fluids flow and exchange heat with each other, such as a water-cooled oil cooler. It is desirable to be.
  • the heat exchange efficiency was determined by considering only the area and pitch of the severon formed in the distributor, and the direction or pressure loss of the fluid flowing in the plate heat exchanger was not largely considered.
  • Korean Patent Registration No. 10-1206858 hereinafter referred to as'prior art document'
  • a fluid path is formed by constructing a sebron portion and a fluid distribution guide. It describes how to improve the flow.
  • the fluid in the process of flowing the fluid to be heated flowing through the fluid inlet to the fluid outlet through the severon part, the fluid passes through the severon part and flows its own heat energy to another layer. It is exchanged with a heat medium (refrigerant).
  • a heat medium refrigerant
  • Patent Document 1 Korean Patent No. 10-1206858
  • the present invention was devised to solve the problems of the prior art as described above, and provided with a plurality of plate-shaped distributors in the heat exchanger, and a plurality of entrance holes in the inlet of the plate-shaped distributor through which the refrigerant flows, thereby forming a refrigerant.
  • the purpose of the present invention is to provide a heat exchanger equipped with a plate-shaped distributor capable of improving the diffusibility of the refrigerant, since the refrigerant can be rapidly diffused and spread between the stacked plate-shaped distributors by flowing into the entrance hole through the inlet of each layer. .
  • asymmetric regions are formed in a flow path of a refrigerant flowing through different layers and a fluid to be heated to improve heat exchange efficiency. It is to provide a heat exchanger provided with a plate-shaped distributor.
  • the heat exchanger provided with the plate-shaped distributor of the present invention for achieving the above object the inlet portion and the outlet portion are respectively formed so that the refrigerant and the fluid to be heated enter and exit, respectively, and the surface thereof is made of a convex and concave-shaped severon portion continuously.
  • the inclined portion includes a plurality of entrance holes through which refrigerant enters and exits, and refrigerant flowing into the entrance holes is vaporized to be diffused and supplied to a flow path between upper and lower distributors.
  • the entrance hole may be formed in a larger number on the other side of the inclined portion facing the edge portion than one side of the inclined portion facing the central portion of the distributor, and the multiple distributors stacked alternately so that the elongated sebron portions face each other in the opposite direction.
  • the stacked distributor may be provided to be stacked by asymmetrically contacting a flat portion that is bent outwardly from each sebron portion and extends flat.
  • an extended extension region is formed in a flow path between both sebron portions of the stacked distributor to generate a vortex flow in a fluid flowing through the flow path, and the flat portions of the stacked upper and lower distributors are formed with different lengths. Can be joined.
  • a plurality of plate-shaped distributors are stacked in a heat exchanger, and a plurality of entrance holes are formed around each inlet of a stacked plate-shaped distributor through which refrigerant flows, thereby flowing through the inlet.
  • the refrigerant diffuses quickly and spreads in a space between vaporized and stacked plate-shaped distributors, thereby improving the diffusivity of the refrigerant and increasing heat exchange efficiency.
  • an extended region of an asymmetrical structure is further formed in each flow path through which the refrigerant and the fluid to be heated flow, thereby flowing each layer. Since the refrigerant to be heated and the fluid to be heated flow in the vortex flow in the extended region of each flow path, the heat exchange efficiency between the refrigerant and the fluid to be heated is improved, thereby improving the heat exchange performance of the heat exchanger.
  • FIG. 1 is a combined view of a heat exchanger according to the present invention.
  • FIG. 2 is an exploded view of a heat exchanger according to the present invention.
  • Figure 3 is an enlarged view of the separation of the plate-shaped distributor configured in the heat exchanger according to the present invention.
  • FIG. 4 is a cross-sectional view taken along line A-A in FIG. 1.
  • FIG. 5 is a cross-sectional view taken along line B-B in FIG. 1.
  • FIG. 6 is a cross-sectional view taken along line C-C in FIG. 1.
  • FIG. 7 is a view showing the diffusivity of the refrigerant introduced through the entrance hole formed in each inlet of the laminated plate-shaped distributor according to the present invention.
  • FIG. 8 is a cross-sectional view taken along line A-A of FIG. 1 according to another embodiment of the present invention.
  • FIG. 9 is an enlarged view of a main portion of a portion D of FIG. 8.
  • FIG. 10 is a view showing a flow of fluid generated at the inlet of a plate-shaped distributor stacked in an asymmetric structure according to another embodiment of the present invention.
  • FIG. 1 to 10 are views showing a heat exchanger according to the present invention and a plate-shaped distributor provided in the heat exchanger, respectively.
  • first and second cover plates 110 and 120 and the first and second cover plates 110 provided on the outermost sides, respectively, as shown in FIGS. 1 and 2. It includes a plurality of distributors 130 and 140 are provided to be stacked between (120).
  • the reference numerals of the distributor 130 positioned at the top and the distributor 140 positioned at the bottom among the plurality of distributors are differently assigned to distinguish them.
  • the first and second cover plates 110 and 120 are generally rectangular flat plates, and a plurality of inlet portions 170 through which refrigerant and a heated fluid are respectively introduced and discharged at each corner of the first cover plate 110 ( 180) and the outlet portions 171 and 181 are formed, and the inlet portion and the outlet portion are not formed in the second cover plate 120.
  • the refrigerant flowing into the inlet parts 170 and 180 of the first cover plate 110 and the fluid to be heated flow into and flow into different layers of the stacked distributor, respectively, and then exit the first cover plate 110. It is discharged through the parts 171 and 181, respectively.
  • the inlet portions 170 and 180 formed in the first cover plate 110 are formed to be spaced apart in the diagonal direction, and the outlet portions 171 and 181 are also spaced apart in the diagonal direction.
  • the flow paths 150 and 160 between the plate-shaped distributors 130 and 140 to be described later (herein referred to as "flow paths") refer to the refrigerant flow path through which the refrigerant flows and the fluid flow path through which the fluid to be heated flows. In the following, the fluid flowing through the refrigerant flow path and the fluid flow path to be heated) will be moved along the direction of the sebron portions 131 and 141 of the distributors 130 and 140. It is prepared to match.
  • the flow paths 150 and 160 between each of the stacked distributors 130 and 140 are closed flow paths that do not communicate with each other, and the refrigerant flowing through the flow paths 150 and 160 of each layer and the fluid to be heated are flown. By allowing them to flow in directions facing each other, it is possible to maximize heat exchange efficiency.
  • a separate reinforcement plate for reinforcing the strength of the first and second cover plates 110 and 120 is provided on the inner surface of the first and second cover plates 110 and 120 facing the distributors 130 and 140. Each may be provided.
  • the reinforcing plate may be formed of the same rectangular flat plate as the first and second cover plates 110 and 120, and the first cover plate 110 may be provided in the reinforcing plate provided on the first cover plate 110 side of the reinforcing plate. ), the inlet portion 170, 180 and the outlet portion 171, 181 are formed in the same way, and the reinforcing plate provided on the second cover plate 120 side is the same as the second cover plate 120. It is preferable that the part and the outlet part are not formed.
  • the refrigerant flowing through each of the inlets 170 and 180 of the first cover plate 110 and the fluid to be heated are each distributor 130 stacked between the first and second cover plates 110 and 120.
  • the right-to-be-heated fluid flow path 160 (or even-numbered and odd-numbered flow paths) are formed so as not to communicate with each other, so that the refrigerant and the heated fluid do not mix with each other and each flow path 150 and 160 between the distributors 130 and 140 And heat exchange while flowing.
  • the distributors 130 and 140 provided to be stacked between the first and second cover plates 110 and 120 like the first and second cover plates 110 and 120, have a regular rectangular flat plate. It is formed, and the inlet portion and the outlet portion corresponding to the inlet portion 170, 180 and the outlet portion 171, 181 of the first cover plate 110 are formed in each corner portion.
  • the inlet portions 170 and 180 and the outlet portions 171 formed on the first cover plate 110 will be described below. It will be described by giving the same drawing number as (181).
  • each distributor 130 is provided at the inlet 170 and outlet 171 through which refrigerant flows among the inlet and outlet of the distributors 130 and 140 provided to be stacked as described above.
  • the inclined portions 133 and 143 respectively inclined in the vertical direction from the flat portions 132 and 142 of the 140 are formed, and the inner peripheral portions of the inclined portions 133 and 143 are formed to be flat and bonded to each other.
  • the joints 134 and 144 to be formed are formed.
  • the inner periphery of the junction 134 and 144 is formed as an inlet and an outlet, and the inclined portions 133 and 143 have a plurality of entrance holes 170a and 171a, which are the circumferences of the inclined portions 133 and 143. It can be formed at regular intervals in the direction.
  • the inclined portion (133) (143) from the central portion of the distributor 130, 140 that is, from one side toward the sevron portion (131) (141)
  • the refrigerant is supplied in a liquefied state due to the pressure and temperature rising due to the supply pressure by the pressurization of the pump, and the refrigerant supplied in this way is a stacked distributor 130, 140 in the conventional case where there is no access hole 170a ) Is calculated and supplied as the required amount of input from the inlet portion 170, and thus, when such a liquefied refrigerant flows into the inlet portion 170 of the stacked distributors 130 and 140, a large area of the inlet portion 170 It is vaporized under reduced pressure.
  • the refrigerant vaporized at the inlet 170 flows differently in pressure and flow rate for each layer, so that the diffusion rate of the refrigerant flowing through the refrigerant passage 150 of each layer decreases, resulting in low heat exchange efficiency. Moreover, since most of the refrigerant supplied to the refrigerant passage 150 flows only to the central portion and only a relatively small amount flows to the edge side, an imbalance of heat exchange is caused.
  • a plurality of entrance holes 170a are formed in the inclined portions 133 and 143 of each inlet portion 170 of the stacked distributors 130 and 140 to be stacked.
  • the refrigerant in the liquefied state is the distributor 130 and 140 It is supplied as it is in a liquefied state without phase change to the inlet part 170 of the, and the refrigerant in the liquefied state thus supplied is of each layer through the entrance hole 170a formed in the inlet part of each layer due to the supply pressure of the pump. It is supplied to the refrigerant passage 150, and after being supplied to the refrigerant passage 150, a reduced pressure is generated due to the large area of the refrigerant passage 150 and is vaporized at the same time as the supply.
  • the vaporized refrigerant is rapidly diffused and spread throughout the refrigerant flow path 150 as a vaporized state, as shown in FIG. 7, thereby improving heat exchange efficiency, and a relatively large amount of refrigerant is supplied to the edge portion to exchange heat.
  • the imbalance can be resolved.
  • the refrigerant in the vaporized state flowing through the refrigerant flow path 150 is discharged through the exit hole 171a on the side of the outlet portion 171 to the outside through the outlet portion 171 of the stacked distributors 130 and 140. Is discharged.
  • the inlet portion 170 and the outlet portion 171 through which the fluid to be heated flows may be formed as the inlet and outlet portions through which the refrigerant flows, the fluid to be heated flows in this embodiment due to the characteristics of the fluid to be heated. 6, the inlet 180 and the outlet 181 will be described by exemplifying a structure in which an entrance hole is not formed.
  • the refrigerant flows only through the refrigerant passage 150 through the inlet portion 170 and the entrance hole 170a formed in the distributor 130 and 140 stacked as in FIGS. 4 and 5, and then in FIG. 5.
  • the fluid to be heated is discharged to the outlet 171 through the entrance hole 171a, and the fluid to be heated is heated through the inlet 180 of the distributor 130, 140 as shown in FIGS. 4 and 6. ), while being heat exchanged with the vaporized refrigerant while flowing only, is discharged to the outlet 181 as shown in FIG. 6.
  • each of the sebron portions 131 and 141 protruding in an uneven shape is formed, and the sebron portions 131 and 141 are the distributors 130 2 and 3 based on the center line of the center of 140, the left and right sides of the severon portions 131 and 141 are formed to be inclined from the center line side to the edge, so that the severon portions 131 and 141 The entire shape is formed in a V-shape.
  • the refrigerant or the fluid to be heated flowing through each of the flow paths 150 and 160 between the upper and lower distributors 130 and 140 flows and moves in the direction of the vertex of the V-shaped sebron parts 131 and 141.
  • flow paths 150 and 160 are formed by the sebron portions 131 and 141, and each flow path 150 and 160 is as shown in FIG.
  • Each of the inlet portion 170, 180 and the outlet portion 171, 181 are formed in communication.
  • the inlet portion 170 and the outlet portion 171 through which the refrigerant flows are formed to communicate with the refrigerant passage 150 through the entrance holes 170a and 171a formed in the inclined portions 133 and 143 thereof.
  • the refrigerant passages 150 on the left and right sides based on the centers of the distributors 130 and 140 are separated so as not to communicate with each other while having a height difference (phase difference). Is formed.
  • the refrigerant flowing into the left inlet 170 of the first cover plate 110 flows only through the refrigerant passage 150 located on the left, and flows into the right inlet 180
  • the fluid to be heated flows only the fluid fluid passage 160 on the right.
  • each distributor 130, 140 As another embodiment of the distributors 130 and 140 stacked as described above, as shown in FIGS. 8 and 9, the inlet 170, 180 and outlet of each distributor 130, 140 ( The flat portions 132 and 142 which are bent outwardly from the 171 and 181 and are flatly extended are joined and provided as an asymmetric structure. 5 and 6, this structure is also configured on both sides of the sebron portion 131, 141 formed between the inlet portion 170 and 180 and the outlet portion 171 and 181. desirable.
  • the inclined portions 133 and 143 and the inclined portions 133 and 143 are formed to be bent upward or downward from both ends of the inlet portions 170 and 180 and the outlet portions 171 and 181.
  • Flat portions 132 and 142 are formed to extend outwardly from the ends of the.
  • the flat portions 132 and 142 are provided with the flat portions 132 and 142 of the distributors 130 and 140 stacked up and down in contact with each other, and the flat portions of the stacked distributors 130 and 140 are stacked ( 132) (142) length (L1) (L2) is formed in a different length as shown in Figure 9 is joined.
  • the flat portions 132 and 142 of the distributors 130 and 140 that are joined in this way will be described in more detail with reference to FIG. 9, the flow path 150 formed by the stacked distributors 130 and 140.
  • the flat portion 142 length L1 of the lower distributor 140 is formed shorter than the length L2 of the flat portion 132 of the upper distributor 130, so that the lower distributor 140 Since the flat portion 142 is provided to protrude toward the flow path 150 and 160, an extended region 135 extending toward the inclined portion 133 of the upper distributor 130 is formed in the flow path 150 and 160.
  • the refrigerant and the fluid to be heated flowing through the flow paths 150 and 160 by the expansion region 135 formed as described above flow through the flow paths 150 and 160 in the vortex flow, respectively, thereby cooling the refrigerant and the fluid to be heated. Is distributed quickly and evenly so that it can flow.
  • the flat portion 142 of the lower distributor 140 as described above and the flat portion 132 of the upper distributor 130 are preferably formed at a ratio of 1:1.1 to 1.3.
  • the flat portion 142 of the lower distributor 140 and the flat portion 132 of the upper distributor 130 are formed in a ratio of 1:1.2.
  • inlet portion 170 and the outlet portion 171 side adjacent to the refrigerant flow path 150 are configured in a symmetrical structure in which the flow path side is turned upside down, as shown in FIG. 9.
  • the refrigerant flowing through the inlet portion 170 and the outlet portion 171 also flows in a vortex flow as in the flow paths 150 and 160, so that the fluid is rapidly and evenly distributed and supplied.
  • the length ratio between the upper and lower flat portions 132 and 142 as in the flow paths 150 and 160 is not described in detail, but the flow path 150 Given the symmetrical relationship with the structure of the flat parts 132 and 142 of 160, the length L1 of the flat parts 132 and 142 forming the extended area 135 in the flow path 150 and 160 ) (L2) ratio and the length ratio between the flat portions 132 and 142 forming the extended area 145 in the inlet portion 170 and the outlet portion 171 can be seen to have an organic relationship.
  • fluid flow path 160 to be heated may also be configured in the same structure as the refrigerant flow path 150 described above.
  • the refrigerant and the fluid to be heated flow into each of the inlets 170 and 180, the refrigerant and the fluid to be heated flow through the inlets 170 and 180, respectively.
  • the refrigerant flowing through the vortex and the fluid to be heated are rapidly and evenly diffused and flow through the entire flow paths 150 and 160 of each layer, thereby balancing heat exchange efficiency over the entire area of the distributors 130 and 140. Heat exchange performance is improved.

Landscapes

  • 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)

Abstract

La présente invention concerne un échangeur de chaleur doté de distributeurs à plaques. L'échangeur de chaleur comporte une pluralité de distributeurs empilés entre des première et seconde plaques-couvercle. Chaque distributeur, parmi la pluralité de distributeurs, comporte une partie d'entrée et une partie de sortie permettant qu'un fluide frigorigène et qu'un fluide à chauffer puissent entrer et sortir, respectivement, et comporte, formées en continu sur sa surface, des parties en chevron formées à partir d'une concavité et d'une convexité en V. Une partie inclinée est formée sur la partie d'entrée, d'un distributeur, à travers laquelle un fluide frigorigène entre, de façon à être fixée à des parties d'entrée des distributeurs supérieur et inférieur empilés. Une pluralité de trous d'entrée-sortie, à travers lesquels le fluide frigorigène entre et sort, sont formés sur la partie inclinée. Par conséquent, le fluide frigorigène entrant à travers les trous d'entrée/sortie est vaporisé et alimenté de manière diffuse aux circuits d'écoulement entre les distributeurs supérieur et inférieur.
PCT/KR2019/000299 2019-01-08 2019-01-08 Échangeur de chaleur doté de distributeurs à plaques WO2020145427A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/KR2019/000299 WO2020145427A1 (fr) 2019-01-08 2019-01-08 Échangeur de chaleur doté de distributeurs à plaques

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/KR2019/000299 WO2020145427A1 (fr) 2019-01-08 2019-01-08 Échangeur de chaleur doté de distributeurs à plaques

Publications (1)

Publication Number Publication Date
WO2020145427A1 true WO2020145427A1 (fr) 2020-07-16

Family

ID=71520459

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2019/000299 WO2020145427A1 (fr) 2019-01-08 2019-01-08 Échangeur de chaleur doté de distributeurs à plaques

Country Status (1)

Country Link
WO (1) WO2020145427A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005106412A (ja) * 2003-09-30 2005-04-21 Hisaka Works Ltd 接合型プレート式熱交換器
KR101206858B1 (ko) * 2011-09-22 2012-12-03 주식회사 한국쿨러 판형 열교환부 및 이의 적층으로 구성되는 판형 열교환기
JP2014109388A (ja) * 2012-11-30 2014-06-12 T Rad Co Ltd 積層型熱交換器
KR20150030234A (ko) * 2012-06-14 2015-03-19 알파 라발 코포레이트 에이비 분사 수단을 갖는 판형 열교환기
KR101952938B1 (ko) * 2017-09-29 2019-02-28 두성산업(주) 판형 디스트리뷰터가 구비되는 열교환기

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005106412A (ja) * 2003-09-30 2005-04-21 Hisaka Works Ltd 接合型プレート式熱交換器
KR101206858B1 (ko) * 2011-09-22 2012-12-03 주식회사 한국쿨러 판형 열교환부 및 이의 적층으로 구성되는 판형 열교환기
KR20150030234A (ko) * 2012-06-14 2015-03-19 알파 라발 코포레이트 에이비 분사 수단을 갖는 판형 열교환기
JP2014109388A (ja) * 2012-11-30 2014-06-12 T Rad Co Ltd 積層型熱交換器
KR101952938B1 (ko) * 2017-09-29 2019-02-28 두성산업(주) 판형 디스트리뷰터가 구비되는 열교환기

Similar Documents

Publication Publication Date Title
US6142221A (en) Three-circuit plate heat exchanger
KR101952938B1 (ko) 판형 디스트리뷰터가 구비되는 열교환기
WO2018079978A1 (fr) Échangeur thermique à plaques de type à faisceau de disques
US6250380B1 (en) Heat exchanger, especially for gases and fluids
EP1484567B1 (fr) Echangeur de chaleur avec écoulements parallèles de fluides
WO2010120125A2 (fr) Échangeur thermique à plaques
JP2605035Y2 (ja) 積層型熱交換器
KR101108069B1 (ko) 열교환기 코어
CN111316057B (zh) 多流体热交换器
EP2929273B1 (fr) Échangeur de chaleur à plaques
PT1299681E (pt) Conjunto de permutação de calor
FR2773875B1 (fr) Echangeur de chaleur a plaques sans carter
US6128920A (en) Dephlegmator
US5584341A (en) Plate bundle for a heat exchanger
CN104755869B (zh) 具有单块板设计的堆叠板式换热器
WO2013073814A1 (fr) Échangeur thermique à eau chaude
WO2020145427A1 (fr) Échangeur de chaleur doté de distributeurs à plaques
US20130081794A1 (en) Layered core heat exchanger
WO2015105261A1 (fr) Échangeur de chaleur modulaire et procédé d'échange de chaleur ayant recours à celui-ci
JP2000356483A (ja) 熱交換器
CN1875235B (zh) 热交换器，特别是增压空气/冷却液冷却器
WO2019124847A1 (fr) Échangeur de chaleur
JPS6186590A (ja) 熱交換器
WO2013048021A1 (fr) Échangeur thermique à plaques soudé
WO2021082618A1 (fr) Échangeur de chaleur

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19908658

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19908658

Country of ref document: EP

Kind code of ref document: A1