EP1571407B1 - Echangeur de chaleur à plaques - Google Patents

Echangeur de chaleur à plaques Download PDF

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Publication number
EP1571407B1
EP1571407B1 EP05003752.2A EP05003752A EP1571407B1 EP 1571407 B1 EP1571407 B1 EP 1571407B1 EP 05003752 A EP05003752 A EP 05003752A EP 1571407 B1 EP1571407 B1 EP 1571407B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
plate
furrows
plates
surface side
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.)
Expired - Fee Related
Application number
EP05003752.2A
Other languages
German (de)
English (en)
Other versions
EP1571407A2 (fr
EP1571407A3 (fr
Inventor
Roland Dipl.-Ing. Strähle (FH)
Daniel Dipl.-Ing. Borst (FH)
Frank Dr. Rer.Nat. Vetter
Herbert Marschner
Daniela Welchner
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.)
Modine Manufacturing Co
Original Assignee
Modine Manufacturing Co
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 Modine Manufacturing Co filed Critical Modine Manufacturing Co
Publication of EP1571407A2 publication Critical patent/EP1571407A2/fr
Publication of EP1571407A3 publication Critical patent/EP1571407A3/fr
Application granted granted Critical
Publication of EP1571407B1 publication Critical patent/EP1571407B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28D9/0012—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 apparatus having an annular form
    • 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
    • F28F3/048—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 ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/10—Particular layout, e.g. for uniform temperature distribution

Definitions

  • the invention relates to a plate heat exchanger, consisting of first and second heat exchanger plates with at least four openings for two media, the heat exchanger plates being alternately stacked between a base plate and a cover plate in such a way that the openings form collecting or distribution channels which pass through the stack of heat exchanger plates. wherein there are inlets or outlets from the collecting or distribution channels to flow channels between the heat exchanger plates in which the heat transfer takes place, and wherein the flow channels for the one medium from one surface side of the first heat exchanger plate and from the spaced one surface side of the second heat exchanger plate are limited.
  • Such a plate heat exchanger is based on the unpublished European application with the publication number EP 14 00 772 A2 which belongs to the same applicant.
  • This plate-type heat exchanger is suitable for heat transfer between media under relatively high pressure, as is the case, for example, in an air conditioning circuit on the refrigerant side.
  • a suitable, in particular pressure-stable, design of the collecting and distribution channels for the refrigerant, for example for CO 2 was described in the document specified. However, the formation of the flow channels for the CO 2 gas was neither shown nor described there.
  • the preamble of claim 1 also goes from WO 01 / 88454A1 forth.
  • the heat exchanger plates of one type are provided with deep-drawn knobs in order to generate turbulence.
  • the knobs are formed on the entire bottom of the plates, also around the four openings.
  • the one from the WO 03/054468 A1 Known heat transfer device is also part of an air conditioning circuit. All heat exchanger plates of this device are provided with a structure, which could be assessed as too complex from a manufacturing point of view. In addition, this known device could be regarded as spatially too large (large building).
  • the object of the invention is to propose a plate heat exchanger which can be used and is inexpensive to produce for media under high pressure, for example for heat exchange between the refrigerant in air conditioning systems and a liquid.
  • the flow channels for the one medium are formed by the connection of the first heat exchanger plate embossed on one surface side and a surface side of an unembossed or likewise embossed second heat exchanger plate, and the flow channels for the other medium are through the other unembossed surface side of the embossed first heat exchanger plate and through that spaced other surface side of the unembossed or also embossed second heat exchanger plate.
  • the plate heat exchanger preferably consists of one-sided embossed and non-embossed heat exchanger plates.
  • This particularly preferred embodiment also ensures that the plate thicknesses of the two types of heat exchanger plates can be significantly different from one another, ie the non-embossed heat exchanger plates are preferably designed to be considerably thinner than the embossed heat exchanger plates, which leads to material and weight savings.
  • This advantage was not necessarily to be expected for plate heat exchangers for media under high pressure.
  • the stamping of the flow channels permits their arbitrarily shaped design to achieve the desired heat exchange effects, which cannot be achieved with extrusion processes known in the prior art.
  • the impressions are preferably made using a Stamping tool made on a press. They are preferably created by cold forming, which is quite possible, especially if the plates are made from a suitable aluminum sheet. Production using embossing rollers is fundamentally not excluded.
  • the two heat exchanger plates to one another and between them to form the flow channels for one medium, preferably for the high-pressure medium, in the form of impressions and on the other hand to arrange the two heat exchanger plates at a distance from one another, the flow channels for the other medium are formed.
  • the impressions represent structures made of groove-like furrows, which are provided in a surface side of one type of heat exchanger plate and which are formed by flat contact with a heat exchanger plate of the other type to form flow channels for the one medium.
  • the groove-like furrows provide a hydraulic connection from one opening of the one medium to the other opening of the same medium.
  • the openings, or the collection and distribution channels thus formed in the stack of heat exchanger plates are arranged within an essential section of the heat exchanger plate provided with the groove-like furrows (structures).
  • the plate heat exchanger according to the invention is advantageously also suitable for use as a water / oil heat exchanger.
  • the cross-sectional size or the hydraulic diameter of the flow channels can be changed for the respective application.
  • Preferred hydraulic diameters of the flow channels for the refrigerant are approximately between 0.5 and 1.0 mm.
  • the hydraulic diameter of the flow channels is above these values when used as a water / oil heat exchanger.
  • the plate heat exchanger shown is used for heat exchange between the refrigerant CO 2 (or another refrigerant) and the coolant of a motor vehicle engine and is integrated in the refrigerant circuit of the air conditioning system and in the coolant circuit in a known and therefore not shown manner.
  • Trough-shaped heat exchanger plates 4a and 4b were produced from the aluminum sheets, which have a simply beveled edge 24 and which are each provided with four openings 5 .
  • the same shape was also provided for the cover plate 3 and for the base plate 2 .
  • the base plate 2 is designed without openings 5 , since the CO 2 gas and the cooling liquid are provided on and off the cover plate 3 .
  • the heat exchanger plates 4a, 4b are assembled into a stack.
  • fins 13 through which the coolant can flow were inserted in the flow channels 11 in a known manner, which ensure efficient heat exchange.
  • the lamellae 13 also contribute to greater compressive strength, since they are soldered to the surface sides mentioned.
  • the slats 13 were only hinted at.
  • the edge 24 of the plates 4a, 4b points upwards.
  • the four openings 5 of the heat exchanger plates 4a, 4b stacked one on top of the other form four collecting or distribution channels 6 , 7 , 8 , 9 which pass vertically through the stack.
  • connection stub 6.1 show that the cooling liquid in the distribution channel 6 of the plate heat exchanger via the Connection stub 6.1 flows in and leaves the same via the collecting duct 7 and the connection stub 7.1 after flowing through the flow ducts 11 .
  • the connecting pieces 8.1 and 9.1 for the refrigerant are special high-pressure fittings.
  • every second flow channel 10 is hydraulically connected to the distributor - and to the collecting channel 8 , 9 . Since the flow channels 10 and 11 formed by the heat exchanger plates 4a , 4b alternate, the first flow channels 11 are hydraulically connected to the distributor and to the collecting channel 6 , 7 . It is from the Fig. 3 It can be seen that the heat exchanger plates 4a are formed around the openings 5 with passages 15 which are produced by shaping and block the hydraulic connection from the distribution channel 8 and the collecting channel 9 into the flow channel 11 . Instead of the passages 15 , rings could also be inserted.
  • the connecting flanges have been formed from the cover plate 3 by forming.
  • the flange plate on the base plate 2 likewise, the flange plate also having a reducer 31 , in which the lower end 32 of a body 12 is soldered, which provides the required pressure stability.
  • a body 12 which in this case relates only to a preferred exemplary embodiment , is located both in the distribution channel 8 and in the collecting channel 9 , wherein in the Fig.
  • the body 12 can be dispensed with because the substantially lower pressures there allow this.
  • Fig. 1 and 3rd show that the flow channels 10 for the CO 2 through the connection of the one surface side of an embossed heat exchanger plate 4a with the one surface side of an unembossed heat exchanger plate 4b are formed, and that the flow channels 11 for the cooling liquid are delimited by the other surface side of the embossed heat exchanger plate 4a and by the other spaced surface side of the unembossed heat exchanger plate 4b .
  • the Fig. 2 shows a view of an embossed heat exchanger plate 4a , which (in this exemplary embodiment) is the thicker of the two heat exchanger plates 4a , 4b .
  • Structures 20 can be seen in the surface side of the embossed heat exchanger plates 4a that are formed as groove-like furrows 20 .
  • This surface side lies in the Fig. 1 Embodiment shown flat on the surface side of an embossed and essentially also flat heat exchanger plate 4b , whereby the groove-like furrows 20 form the flow channels 10 for the CO 2 .
  • the embossed surface side of the plates 4a points upwards and the second heat exchanger plate 4b lies flat against it with its one surface side. In the Fig. 4 the foothills of the flow channels 10 are clearly visible.
  • Fig. 2 ostensibly gives the impression of an ornamental design. However, this is aimed at achieving intended technical effects.
  • the section 21 of the heat exchanger plates 4a covered with the structures 20 should be as large as possible, and on the other hand, this entire section 21 should be used as much as possible for heat exchange.
  • the best possible heat exchange is achieved in that the same pressure loss should always be present in all flow channels 10 through a clever choice of the design and the length of each flow channel. It is also a uniform distribution of the flow channels 10 intended over the entire section 21, which is why one has been provided both to a vertical symmetrical VA as well as to a horizontal axis HA of the design portion 21st As a result, the length of all flow channels 10 is approximately the same.
  • the flow channels 10 are of a discrete type.
  • the parallel flow channels 10 should preferably not be in a short-circuit-like hydraulic connection with one another.
  • the additional metallic connections described above are provided on regions 22 and regions 25 .
  • a hexagonal shape of the heat exchanger plates 4a , 4b was selected. From the Fig. 2 it can be seen that this special shape is related to the required size of the regions 25 and the larger openings 5 for the cooling liquid, or has its causes therein.
  • the openings 5 for the cooling liquid lie outside the essential section 21 , whereas the openings 5 for the CO 2 are arranged inside the latter.
  • edges 24 on the thicker heat exchanger plates 4a are significantly shorter than the edges 24 on the thinner heat exchanger plates 4b . This could be done because, on the one hand, there are pressures on the coolant side that allow this construction and, on the other hand, the high-pressure CO 2 gas flows on the side on which there is a durable flat metallic connection between the thin heat exchanger plate 4b and the thicker one Heat exchanger plate 4a is present. This leads to an extremely compact design of the Plate heat exchanger and for further material and weight savings, which should not go unmentioned with a large number of such plates 4a , 4b .
  • the 7 and 8 show a view of the two surface sides of the heat transfer plates 104a and 104b , which are metallically connected to form the flow channels 110 in a second exemplary embodiment.
  • one of the plates 104a or 104b is rotated through 180 ° about the axis HA , so that the surface sides shown come to lie against one another.
  • FIG. 2 shows an example of two connected heat exchanger plates 104a , 104b , which illustrates the above.
  • the structures 120 lying on the left or right of the vertical axis of symmetry VA were divided between the two heat exchanger plates 104a and 104b .
  • both plates 104a , 104b can have the same sheet thickness.
  • the symmetry only relates to the arrangement of the structures 120 and the two openings 105 .
  • the outer shape of the plates shown is not symmetrical in the two representations, but should preferably be symmetrical.
  • the walls 230 between the furrows of one plate 204a are metallically connected to the walls 230 of the other plate 204b . Further modifications, not shown, of such exemplary embodiments can be made.
  • Fig. 9 it is shown how the shape of the groove-like furrows 20 , which form the flow channels 10 , has changed after the soldering process has been completed.
  • the illustration shows the preferred embodiment with the different thickness heat exchanger plates 4a and 4b .
  • the embossing produces groove-like furrows 20 with a width of approximately 0.8 mm and a depth of approximately 1.0 mm.
  • the solder flows into the grooves 50 , so that an approximately elliptical or circular cross section is formed in each groove-like groove 20 .
  • This ideal cross-sectional shape ensures the lowest possible pressure loss along each flow channel 10 .
  • the depth and the width of the groove-like furrows 20 can be adapted to the required conditions.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (15)

  1. Échangeur de chaleur à plaques, constitué de premières et deuxièmes plaques échangeuses de chaleur (4a, 4b) dotées d'au moins quatre orifices (5) pour deux fluides, les plaques échangeuses de chaleur (4a, 4b) étant empilées en alternance entre une plaque de base (3) et une plaque de recouvrement (2), de telle sorte que les orifices (5) forment des canaux collecteurs ou distributeurs (6, 7, 8, 9) traversant l'empilage de plaques échangeuses de chaleur (4), des entrées et des sorties étant prévues entre les plaques échangeuses de chaleur (4), depuis les canaux collecteurs ou distributeurs (6, 7, 8, 9) vers des canaux d'écoulement (10, 11), dans lesquels s'effectue le transfert de chaleur, et les canaux d'écoulement (11) pour l'un des fluides étant limités par un côté de surface de la première plaque échangeuse de chaleur (4a) ainsi que par un côté de surface espacé de la deuxième plaque échangeuse de chaleur (4b),
    caractérisé en ce que
    les canaux d'écoulement (10, 110) pour l'autre fluide sont de type distinct, de sorte que ces canaux d'écoulement ne sont pas en liaison hydraulique de type court-circuit les uns avec les autres et sont formés par appui plan et liaison métallique de l'autre côté de surface de la première plaque échangeuse de chaleur (4a, 104a) avec l'autre côté de surface de la deuxième plaque échangeuse de chaleur (4b, 104b), l'autre côté de surface de la première plaque échangeuse de chaleur (4a, 104a) comprenant des structures (20, 120) sous forme de sillons de type rainures et l'autre côté de surface de la deuxième plaque échangeuse de chaleur (4b, 104b) étant formé soit avec soit sans de telles structures (20, 120), des lamelles (13) étant insérées entre les plaques échangeuses de chaleur (4a, 4b) dans les canaux d'écoulement (11) pour l'un des fluides et les structures (20) étant produites par estampage des plaques échangeuses de chaleur (4a ou 4a et 4b).
  2. Échangeur de chaleur à plaques selon la revendication 1, caractérisé en ce que les structures ou les sillons (20) de type rainures fournissent une liaison hydraulique de l'un des orifices (5) de l'autre fluide à l'autre orifice (5) du même fluide, ce pour quoi les orifices (5) ou les canaux collecteurs et distributeurs (8, 9) formés avec ceux-ci sont disposés à l'intérieur d'une partie principale (21) de la plaque échangeuse de chaleur (4a), laquelle partie est dotée des sillons (20) de type rainures.
  3. Échangeur de chaleur à plaques selon la revendication 3, caractérisé en ce que les structures (20) ou les sillons (20) de type rainures disposés dans la partie principale (21) de la plaque échangeuse de chaleur (4a) forment une image à symétrie miroir, de sorte que des canaux d'écoulement (10) approximativement de même longueur soient présents sur les deux côtés d'image.
  4. Échangeur de chaleur à plaques selon la revendication 1, caractérisé en ce que les premières plaques échangeuses de chaleur (4a) présentent une épaisseur de plaque significativement supérieure à celle des deuxièmes plaques échangeuses de chaleur (4b).
  5. Échangeur de chaleur à plaques selon la revendication 1, caractérisé en ce que les premières et deuxièmes plaques échangeuses de chaleur (4a, 4b) présentent la même épaisseur de plaque.
  6. Échangeur de chaleur à plaques selon l'une des revendications précédentes, caractérisé en ce que les autres orifices (5) pour l'un des fluides ou les canaux collecteurs et distributeurs (6, 7) formés avec ceux-ci sont disposés à l'extérieur d'une partie (21) des plaques échangeuses de chaleur (4a, 4b), laquelle partie est dotée des structures estampées (20).
  7. Échangeur de chaleur à plaques selon l'une des revendications précédentes, caractérisé en ce que les premières et deuxièmes plaques échangeuses de chaleur (4a, 4b) comprennent un bord recourbé périphérique (24) au niveau duquel des plaques échangeuses de chaleur (4a, 4b) adjacentes sont reliées métalliquement l'une à l'autre.
  8. Échangeur de chaleur à plaques selon la revendication 8, caractérisé en ce que le bord (13) de l'une des plaques échangeuses de chaleur (4b) est plus long que le bord des autres plaques échangeuses de chaleur (4a).
  9. Échangeur de chaleur à plaques selon la revendication 1, 3 ou 4, caractérisé en ce que la partie principale (21) dotée de structures (20) ou des sillons (20) de type rainures de la plaque échangeuse de chaleur (4a) est encadrée par une pluralité de sillons sensiblement parallèles, et en ce qu'une autre pluralité de sillons (20) de type rainures est formée à l'intérieur de la partie encadrée (23) dans laquelle des régions (22) non estampées sont présentes.
  10. Échangeur de chaleur à plaques selon la revendication 9, caractérisé en ce que respectivement une première plaque échangeuse de chaleur (4a) est reliée métalliquement à plat à une deuxième plaque échangeuse de chaleur (4b) à l'extérieur de la partie principale (21) et au niveau des régions (22) à l'intérieur de la partie (21), et en ce qu'également une liaison métallique est présente au niveau des sillons (20) de type rainures, de sorte que les canaux d'écoulement (10) sont réalisés de manière résistante à la pression et sont de types distincts.
  11. Échangeur de chaleur à plaques selon la revendication 11, caractérisé en ce que les sillons (20) de type rainures à l'intérieur de la partie encadrée (23) présentent une allure sinueuse qui comprend partiellement plusieurs sillons parallèles et des sillons individuels (20) qui sont disposés autour des régions (22).
  12. Échangeur de chaleur à plaques selon la revendication 4, caractérisé en ce que des zones (25) de préférence planes sont présentes à l'extérieur de la partie principale (21), zones dans lesquelles la plaque échangeuse de chaleur (4a) est reliée métalliquement à plat à la plaque échangeuse de chaleur (4b).
  13. Échangeur de chaleur à plaques selon l'une des revendications précédentes, caractérisé en ce que les canaux d'écoulement (10), qui sont formés par un côté de surface estampé de la première plaque échangeuse de chaleur (4a) et par un côté de surface non estampé de la deuxième plaque échangeuse de chaleur (4b), sont prévus pour du CO2 en tant que fluide frigorigène de systèmes de climatisation dans des véhicules automobiles, tandis que les autres canaux d'écoulement (11) sont configurés de telle sorte que du liquide de refroidissement d'un moteur peut s'écouler à travers les autres canaux d'écoulement (11).
  14. Échangeur de chaleur à plaques selon la revendication 15, caractérisé en ce qu'un corps (12) de type barre est disposé dans les canaux collecteurs ou distributeurs (8, 9) pour le fluide frigorigène, lequel corps augmente la stabilité en pression de l'échangeur de chaleur à plaques.
  15. Utilisation d'un échangeur de chaleur à plaques selon l'une des revendications précédentes, en tant qu'échangeur de chaleur eau/huile.
EP05003752.2A 2004-03-05 2005-02-22 Echangeur de chaleur à plaques Expired - Fee Related EP1571407B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004010640 2004-03-05
DE102004010640A DE102004010640A1 (de) 2004-03-05 2004-03-05 Plattenwärmeübertrager

Publications (3)

Publication Number Publication Date
EP1571407A2 EP1571407A2 (fr) 2005-09-07
EP1571407A3 EP1571407A3 (fr) 2010-09-29
EP1571407B1 true EP1571407B1 (fr) 2020-04-08

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EP05003752.2A Expired - Fee Related EP1571407B1 (fr) 2004-03-05 2005-02-22 Echangeur de chaleur à plaques

Country Status (3)

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US (1) US7600559B2 (fr)
EP (1) EP1571407B1 (fr)
DE (1) DE102004010640A1 (fr)

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EP1571407A2 (fr) 2005-09-07
US7600559B2 (en) 2009-10-13
EP1571407A3 (fr) 2010-09-29
US20050194123A1 (en) 2005-09-08

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