EP1400772B1 - Echangeur de chaleur à plaques - Google Patents

Echangeur de chaleur à plaques Download PDF

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Publication number
EP1400772B1
EP1400772B1 EP03016863A EP03016863A EP1400772B1 EP 1400772 B1 EP1400772 B1 EP 1400772B1 EP 03016863 A EP03016863 A EP 03016863A EP 03016863 A EP03016863 A EP 03016863A EP 1400772 B1 EP1400772 B1 EP 1400772B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
plate
distributor
channel
collector
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 - Lifetime
Application number
EP03016863A
Other languages
German (de)
English (en)
Other versions
EP1400772A3 (fr
EP1400772A2 (fr
Inventor
Roland Dipl.-Ing. Strähle
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 EP1400772A2 publication Critical patent/EP1400772A2/fr
Publication of EP1400772A3 publication Critical patent/EP1400772A3/fr
Application granted granted Critical
Publication of EP1400772B1 publication Critical patent/EP1400772B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/0075—Supports for plates or plate assemblies
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with 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
    • F28F2225/00—Reinforcing means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/906—Reinforcement

Definitions

  • the invention relates to a plate heat exchanger with the features of the preamble of claim 1.
  • the features specified in the preamble characterize plate heat exchangers, which are now referred to in many sources as "caseless" plate heat exchanger.
  • the known plate heat exchanger consists of a separable stack of plates, between which seals are arranged. It is probably intended for use in the food industry.
  • the body arranged in the distribution channel and in the collection channel serves to better divide the inflowing medium into the flow channels so that as far as possible all the flow channels are involved in the heat transfer. This is particularly important if the plate heat exchanger is constructed from a large number of heat exchanger plates, which leads to a large number of mentioned flow channels, whereby not all flow channels are far enough flowed through.
  • the well-known plate heat exchanger is not applicable to media that are under particularly high pressures.
  • the plate heat exchanger equipped with the features of the preamble is known from US 5 307 869. There, the body extending through the manifold and through the collection channel must be inserted and mechanically fastened after soldering.
  • the object of the invention is to propose a plate heat exchanger which can be used for media under high pressure, for example for heat exchange between the refrigerant in air conditioning systems and a cooling liquid.
  • a plurality of openings are formed around the end of the body which provide a hydraulic connection to the flow path and further through the associated flow channels, the cross section of the openings approximately corresponding to the cross section of the flow path.
  • the plate heat exchanger is a brazing construction constructed in particular of solder-coated aluminum sheet, and the body is substantially extends through the entire distributor or collecting channel, wherein it is directly or indirectly connected to the base plate directly at one end and directly or indirectly connected to the cover plate at the other end, the plate heat exchanger receives a very good pressure stability, and is therefore particularly suitable for Heat exchange between the refrigerant, eg. CO 2 , an air conditioner and the coolant of the engine of a motor vehicle suitable.
  • the refrigerant is known to be under a very high pressure of up to about 150 bar working pressure, the plate heat exchanger to withstand a maximum pressure of about 450 bar without losing its function.
  • the pressure stability is achieved in particular by the arrangement of the body in the distributor and in the collection channel for the CO 2 and by the direct or indirect connection of the body to the base plate and to the cover plate.
  • the formation of the plate heat exchanger which is best known per se, from aluminum sheet coated with a solder material or, for example, from stainless steel sheet in a compact soldering construction alone, has proven to be insufficient to ensure the required pressure stability.
  • the base plate and the cover plate are generally formed with a substantially larger sheet thickness than the heat exchanger plates and therefore suitable to absorb forces and even better than before to provide stability.
  • the body which is preferably a closed round bar, also contributes to the excellent distribution of the refrigerant on all the flow channels, whereby a very good heat exchange rate is achieved in particular when a large number of flow channels formed from heat transfer plates is provided.
  • the flow path of the CO 2 in the distributor and in the collecting channel preferably presents itself as an annular channel, and it is bounded by the wall of the body and by the edge of the openings in the heat exchanger plates.
  • the annular flow path passes through the entire stack and thus distributes the CO 2 to those flow channels that the distribution channel and the Are assigned collecting channel. It must be emphasized, however, that the flow path does not have to be of the same size and ring-shaped over the entire stack. In other words, the flow path determining cross section of the body need not be uniform over the entire stack.
  • the accompanying figures show the plate heat exchanger, first, in perspective and partially exploded view and second, in a guided through the connecting piece section through the plate heat exchanger.
  • the plate heat exchanger is used for heat exchange between the refrigerant CO 2 and the cooling liquid of a motor vehicle engine and is integrated in a known and not shown manner in the air conditioning.
  • tub-shaped heat exchanger plates 4 were produced from the aluminum sheets, which have a simply bevelled edge 24 and which are each provided with four openings 5 .
  • the same shape was also provided for the cover plate 3 and the base plate 2 .
  • the base plate 2 is formed in this embodiment without openings 5 , since the supply and discharge of CO 2 and the cooling liquid is provided on the cover plate 3 .
  • the heat exchanger plates 4 are assembled into a stack. Between the heat exchanger plates 4 , or between the spaced heat exchange surfaces were inserted in the flow channels 10 in a known manner by the cooling liquid Oberströmbare lamellae 32 , which provide for efficient heat exchange.
  • the fins 32 also contribute to a greater compressive strength, because they are soldered to the heat exchange surfaces.
  • the fins 32 were merely indicated.
  • the base and cover plates 2 , 3 complete the plate heat exchanger.
  • the edge 24 of the plates 2 , 3 , 4 down.
  • the four apertures 5 of the stacked heat exchanger plates 4 form four collection and distribution channels 6, 7, 8, 9 which pass vertically through the stack.
  • the reference numerals 6, 7, 8, 9 were attached to the flow arrows, which should simultaneously show that 6, the cooling liquid flows into the distribution channel 6 of the plate heat exchanger via the connecting piece 1.2 and leaves the same through the collecting channel 7 and the connecting piece 1.2, after flowing through the flow channels 10 .
  • the refrigerant flows into the plate heat exchanger, which leaves the plate heat exchanger at 8 again after flowing through the flow channels 11 .
  • the heat exchange thus takes place in direct current, but in a non-illustrated embodiment, countercurrent is provided.
  • the connecting pieces 1.1 for the refrigerant are special high-pressure fittings.
  • a body 12th The body 12 extends through the entire distributor channel 9 or through the collecting channel 8 . It is of generally round cross-section shape, whose diameter must be smaller than the diameter of the openings 5, which form the distribution channel 9 and the collecting channel 8 .
  • each second flow channel 11 is hydraulically connected to the distributor and to the collecting channel 8, 9 . Since, in the embodiment shown, the flow channels 10 and 11 formed by the heat exchanger plates 4 alternate, the first flow channels 10 are hydraulically connected to the distributor and to the collecting channel 6 , 7 .
  • the hydraulic connection of the distributor and the collecting channels 6 , 7 , 8 , 9 with the associated flow channels 10 and 11 is not been shown in detail because such training belongs to the prior art. However, it can be seen from FIG.
  • passages 15, which are produced around the apertures 5 by deformation, are arranged, which block the hydraulic connection from the distributor channel 8 and the collecting channel 9 into the flow channel 10 .
  • This and all but two flow channels 10 are hydraulically accessible only from the distribution channel 6 and collecting channel 7 (for coolant), which was not shown in the drawing. There are accordingly missing the mentioned passages 15th Instead of the passages 15 and rings could be inserted.
  • the bottom in the picture 13 of the body 12 is metallically connected directly to the base plate 2 and the upper end in the picture 14 is metallically connected directly to the cover plate 3 , whereby the plate heat exchanger was given a very good compressive strength.
  • the base plate 2 and the cover plate 3 have sufficient stability. It is advisable to choose for the arrangement of the body 12 the manifold - and the collecting channel 8 , 9 for the refrigerant, since it is under a much higher pressure than the cooling liquid. However, this is not a condition, because even by the arrangement of the body 12 in the other manifold - and the collecting channel 6 , 7 , a higher compressive strength of the plate heat exchanger is achieved.
  • each manifold and collecting channel 6 , 7 , 8 , 9 such a body 12 could be arranged to withstand extremely high pressures.
  • the connecting pieces 1.1 are located on the manifold - and the collecting channel 8 and 9 , which are intended for the refrigerant. Because of the extremely high pressure prevailing there, a very special design is required, which will be described in more detail below.
  • the connecting flanges 20 have been formed from the cover plate 3 by forming.
  • the flange plates 23 on the base plate 2 also, wherein the flange plate 23 has a reducer 31 , in which the lower end 13 of the body 12 is soldered.
  • the body 12 has at the upper end 14 a taper 30 , which can be inserted into the flange 20 integrally formed on the reducer 21 to be metallically connected there.
  • To the reducer 21 around several openings 22 have been introduced, which are distributed around the circumference. Of these, five openings 22 in FIG. 1 can be seen.
  • the connecting piece 1.1 was soldered onto the connecting flange 20 and on the cover plate 3 , wherein its Border 25 extends around the openings 22 and around the reducer 21 around.
  • the connecting piece 1.1 has inside about sawtooth-like cut-outs 26, through which the CO 2 can flow from the line, not shown, where it will continue to flow through the openings 22 into the distribution channel 9 into it.
  • a ring-like flow path 26 is formed from the access to the flow channels 11 is ensured.
  • the cooled CO 2 can leave the plate heat exchanger on the other connection 1.1 again, even if that is not recognizable from the illustration, since the sectional plane is not identical in two connecting pieces 1.1 .
  • Such a design is particularly advantageous because it ensures that the accesses from the flow path 16 into the flow channels 11 (and out) are constructive or manufacturing easier to produce.
  • the cross-sectional area of the body 12 is matched to the cross-sectional area of the manifold 9 and the collection channel 8 so that the cross-sectional area of the remaining flow path 16 approximately corresponds to the cross-sectional area of the openings 22 and the cut-outs 26 to provide favorable flow conditions.
  • the annular flow path 26 has been marked di and da , which is intended to mean the inner diameter and the outer diameter of the cross-sectional area of the flow path 26 .
  • FIG. 2 it can also be seen that two different types of heat exchanger plates 4 are used in this embodiment.
  • One type is in the sheet thickness approximately equal to that of the base plate 2 and the cover plate 3 , while the other type is much thinner. This is also due to the fact that the pressures are extremely high.

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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)
  • Separation By Low-Temperature Treatments (AREA)
  • Fuel Cell (AREA)

Claims (9)

  1. Echangeur de chaleur à plaques sous la forme d'une construction brasée, composé de raccords (1), d'une plaque de base (2), d'une plaque de recouvrement (3) et de plaques échangeuses de chaleur (4) avec au moins quatre orifices (5) de préférence circulaires pour deux fluides, les plaques échangeuses de chaleur (4) étant empilées les unes dans les autres ou les unes sur les autres entre la plaque de base (2) et la plaque de recouvrement (3) de 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 existant 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 la transmission de la chaleur, ainsi qu'avec un corps (12) disposé de manière sensiblement coaxiale dans un espace distributeur et dans l'espace collecteur correspondant (8, 9) et relié à une extrémité (13) avec la plaque de base (2) et, à l'autre extrémité (14), avec la plaque de recouvrement (3), et s'étendant sensiblement à travers tout le canal collecteur ou distributeur (6, 7), afin de s'opposer à la pression interne dans l'échangeur de chaleur à plaques, une voie d'écoulement (16) étant formée entre le corps (12) et le bord (15) du canal collecteur ou distributeur (8, 9) formé par les orifices (5), caractérisé en ce que plusieurs ouvertures (22) sont ménagées autour de l'extrémité (14 ou 13) du corps (12), fournissant une connexion hydraulique vers la voie d'écoulement (16) et ensuite à travers les canaux d'écoulement (11) correspondants, la section transversale des ouvertures (22) correspondant sensiblement à la section transversale de la voie d'écoulement (16).
  2. Echangeur de chaleur à plaques selon la revendication 1, caractérisé en ce que le corps (12) est de préférence une tige ronde, de sorte que la voie d'écoulement (16) a une forme annulaire (di, da) dans le canal distributeur et dans le canal collecteur (8, 9).
  3. Echangeur de chaleur à plaques selon l'une des revendications précédentes, caractérisé en ce que le corps (12) présente, à au moins l'une de ses extrémités (14), un rétrécissement (30), en ce que cette extrémité (14) est disposée sur le côté où se trouve le raccord (1.1) correspondant, en ce que le rétrécissement (30) débouche dans une bride de raccordement (20) munie d'une réduction (21) et est brasé dans celle-ci, et en ce que plusieurs ouvertures (22) sont ménagées autour de la réduction (21).
  4. Echangeur de chaleur à plaques selon les revendications 1 et 3, caractérisé en ce que le raccord (1.1) est de préférence brasé sur la bride de raccordement (20) enveloppant la réduction (21) et les ouvertures (22) avec son rebord (25).
  5. Echangeur de chaleur à plaques selon les revendications 3 et 4, caractérisé en ce que la bride de raccordement (20) est soit réalisée au moyen d'une déformation sur la plaque de recouvrement ou sur la plaque de base (2, 3), soit est réalisée comme une pièce individuelle.
  6. Echangeur de chaleur à plaques selon l'une des revendications précédentes, caractérisé en ce que l'autre extrémité (13) du corps (12) est brasée de manière fixe sur la plaque de base (2) au moyen d'une bride (23), cette bride (23) étant également réalisée par déformation de la plaque de base (2).
  7. Echangeur de chaleur à plaques selon l'une des revendications précédentes, caractérisé en ce que les plaques échangeuses de chaleur (4) ont une forme de cuvette avec un bord (24) périphérique réalisé par un pliage simple et possèdent, pour le reste, une surface d'échange de chaleur au moins pour l'essentiel plane, de sorte qu'elles peuvent être empilées les unes dans les autres de sorte que les bords (24) de plaques adjacentes puissent être reliés par brasage et qu'il se forme à chaque fois un canal d'écoulement (10, 11) entre les surfaces d'échange de chaleur, et des moyens (traversées 15 ou bagues) connus en soi étant prévus sur au moins deux orifices (5) dans les plaques échangeuses de chaleur (4) pour isoler hydrauliquement un canal d'écoulement (10) du canal distributeur et du canal collecteur (8, 9), qui sera par contre relié hydrauliquement avec l'autre canal distributeur et avec l'autre canal collecteur (6, 7) par le biais des orifices (5) non munis de traversées ou de bagues (15).
  8. Echangeur de chaleur à plaques selon l'une des revendications précédentes, caractérisé en ce qu'au moins quelques-unes des plaques échangeuses de chaleur (4) sont réalisées avec une épaisseur de matériau plus importante que celle des autres plaques échangeuses de chaleur (4), l'épaisseur de matériau des plaques échangeuses de chaleur (4) plus épaisses (4) correspondant sensiblement à l'épaisseur de matériau de la plaque de recouvrement (3) et de la plaque de base (2).
  9. Utilisation de l'échangeur de chaleur à plaques selon l'une des revendications précédentes, caractérisée en ce que les canaux distributeurs et collecteurs (8, 9) contenant le corps (12) et les canaux d'écoulement correspondants (11) sont prévus pour du CO2 en tant que fluide frigorigène d'installations de climatisation dans des véhicules automobiles, tandis que le liquide de refroidissement du moteur s'écoule dans les autres canaux distributeurs et collecteurs (6, 7) et dans les canaux d'écoulement correspondants (10).
EP03016863A 2002-09-19 2003-07-24 Echangeur de chaleur à plaques Expired - Lifetime EP1400772B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10243522 2002-09-19
DE10243522A DE10243522A1 (de) 2002-09-19 2002-09-19 Plattenwärmeübertrager

Publications (3)

Publication Number Publication Date
EP1400772A2 EP1400772A2 (fr) 2004-03-24
EP1400772A3 EP1400772A3 (fr) 2005-10-05
EP1400772B1 true EP1400772B1 (fr) 2007-05-16

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP03016863A Expired - Lifetime EP1400772B1 (fr) 2002-09-19 2003-07-24 Echangeur de chaleur à plaques

Country Status (4)

Country Link
US (1) US6918434B2 (fr)
EP (1) EP1400772B1 (fr)
AT (1) ATE362603T1 (fr)
DE (2) DE10243522A1 (fr)

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CN106556263B (zh) * 2015-09-28 2019-01-25 丹佛斯微通道换热器（嘉兴）有限公司 板式换热器
EP3179190A1 (fr) * 2015-12-11 2017-06-14 Alfa Laval Corporate AB Échangeur thermique à plaque
WO2017201252A1 (fr) * 2016-05-20 2017-11-23 Modine Manufacturing Company Échangeur de chaleur et système d'échange de chaleur
US10935288B2 (en) * 2017-08-28 2021-03-02 Hanon Systems Condenser
KR102440596B1 (ko) * 2017-11-28 2022-09-05 현대자동차 주식회사 차량용 열교환기
EP3521742B1 (fr) * 2018-02-01 2020-07-22 Hamilton Sundstrand Corporation Échangeur de chaleur
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015012029A1 (de) 2015-09-15 2017-03-16 Modine Manufacturing Company Plattenwärmetauscher

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EP1400772A3 (fr) 2005-10-05
US20040112579A1 (en) 2004-06-17
DE10243522A1 (de) 2004-04-01
US6918434B2 (en) 2005-07-19
ATE362603T1 (de) 2007-06-15
EP1400772A2 (fr) 2004-03-24
DE50307283D1 (de) 2007-06-28

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