EP1400772B1 - Plate heat exchanger - Google Patents

Plate heat exchanger 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
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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)
French (fr)
Other versions
EP1400772A3 (en
EP1400772A2 (en
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
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Filing date
Publication date
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Publication of EP1400772A2 publication Critical patent/EP1400772A2/en
Publication of EP1400772A3 publication Critical patent/EP1400772A3/en
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Publication of EP1400772B1 publication Critical patent/EP1400772B1/en
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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.

Abstract

The heat exchanger consists of uprights (1), base plate (2), cover plate (3) and heat-transfer plates (4) in which is at least one preferably circular passage (5) for two media. The heat transfer plates are stacked in or one each other so that the passages form collector or distributor ducts (6-9) from which lead outlets or inlets to flow ducts (10,11). between heat transfer plates. A main body (12) extends through the distributor or collector duct, and is joined at one end (13) to the base plate and, at the other end(14)to the cover plate.

Description

Die Erfindung betrifft einen Plattenwärmeübertrager mit den Merkmalen des Oberbegriffs aus dem Anspruch 1. Die im Oberbegriff angegebenen Merkmale charakterisieren Plattenwärmeübertrager, die mittlerweile in vielen Quellen auch als "gehäuselose" Plattenwärmeübertrager bezeichnet werden.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.

Solche Plattenwärmeübertrager gehören seit geraumer Zeit zum Stand der Technik. Ein geeignetes, jedoch nicht dem Oberbegriff entsprechendes Beispiel kann der DE - OS 30 21 246 entnommen werden. Der bekannte Plattenwärmeübertrager besteht aus einem auflösbaren Stapel von Platten, zwischen denen Dichtungen angeordnet sind. Er ist wahrscheinlich zum Einsatz im Bereich der Nahrungsgüterwirtschaft vorgesehen. Der im Verteilerkanal und im Sammelkanal angeordnete Körper dient der besseren Aufteilung des einströmenden Mediums auf die Strömungskanäle, damit möglichst sämtliche Strömungskanäle an der Wärmeübertragung beteiligt werden. Dies ist besonders dann von Bedeutung, wenn der Plattenwärmeübertrager aus einer großen Anzahl von Wärmeübertragerplatten aufgebaut ist, die zu einer großen Anzahl erwähnter Strömungskanäle führt, wobei längst nicht alle Strömungskanäle ausreichend durchströmt werden.Such plate heat exchangers have been part of the state of the art for quite some time. A suitable, but not the preamble corresponding example can be found in DE - OS 30 21 246. 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.

Der bekannte Plattenwärmeübertrager ist für Medien, die unter besonders hohen Drücken stehen nicht anwendbar.The well-known plate heat exchanger is not applicable to media that are under particularly high pressures.

Zusätzlicher Stand der Technik wurde in der DE 30 20 557 A1, in DE 32 15 961 A1 sowie bspw. in FR 2 634 276 A1 beschrieben, auf den hiermit hingewiesen wird. Dieser Stand der Technik scheint weiter entfernt zu liegen, da er keine Plattenwärmeübertrager mit Wärmeübertragerplatten betrifft, die mindestens vier Durchbrüche aufweisen, welche genauso viele Sammel - oder Verteilerkanäle bilden. Somit betrifft dieser Stand der Technik keine "gehäuselosen" Plattenwärmeübertrager.Additional prior art has been described in DE 30 20 557 A1, DE 32 15 961 A1 and, for example, in FR 2 634 276 A1, to which reference is hereby made. This prior art seems to be further away because it does not relate to plate heat exchangers having heat exchanger plates having at least four apertures which form as many manifolds or manifolds. Thus, this prior art does not relate to "caseless" plate heat exchangers.

Der mit den Merkmalen des Oberbegriffs ausgestattete Plattenwärmetauscher ist aus der US 5 307 869 bekannt. Dort muss der sich durch den Verteiler - und durch den Sammelkanal erstreckende Körper nach dem Löten eingesetzt und mechanisch befestigt werden.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.

Die Aufgabe der Erfindung besteht darin, einen Plattenwärmeübertrager vorzuschlagen, der für unter hohem Druck stehende Medien, beispielsweise zum Wärmeaustausch zwischen dem Kältemittel in Klimaanlagen und einer Kühlflüssigkeit, einsetzbar ist.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.

Diese Aufgabe wird bei dem im Oberbegriff des Anspruchs 1 beschriebenen Plattenwärmeübertrager durch die im Kennzeichen aufgeführten Merkmale erfindungsgemäß gelöst.This object is achieved in the plate heat exchanger described in the preamble of claim 1 by the features listed in the characterizing feature according to the invention.

Es ist vorgesehen, dass mehrere Öffnungen um das Ende des Körpers herum ausgebildet sind, die eine hydraulische Verbindung zum Strömungsweg und weiter durch die zugeordneten Strömungskanälen zur Verfügung stellen, wobei der Querschnitt der Öffnungen etwa dem Querschnitt des Strömungswegs entspricht.It is envisaged that 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.

Da der Plattenwärmeübertrager eine insbesondere aus mit Lot beschichtetem Aluminiumblech aufgebaute Lötkonstruktion ist und der Körper sich im wesentlichen durch den gesamten Verteiler - bzw. Sammelkanal hindurch erstreckt, wobei er an einem Ende direkt oder indirekt mit der Grundplatte und am anderen Ende direkt oder indirekt mit der Deckplatte metallisch verbunden ist, erhält der Plattenwärmeübertrager eine ausgesprochen gute Druckstabilität, und er ist deshalb besonders zum Wärmeaustausch zwischen dem Kältemittel, bspw. CO2, einer Klimaanlage und der Kühlflüssigkeit des Motors eines Kraftfahrzeuges geeignet. Insbesondere das Kältemittel steht bekanntlich unter einem sehr hohen Druck von bis zu etwa 150 bar Arbeitsdruck, wobei der Plattenwärmeübertrager einem maximalen Druck von etwa 450 bar widerstehen soll, ohne seine Funktion zu verlieren.Since 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. In particular, 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.

Die Druckstabilität wird insbesondere durch die Anordnung des Körpers im Verteiler - und im Sammelkanal für das CO2 und durch die direkte oder indirekte Verbindung des Körpers mit der Grundplatte und mit der Deckplatte erreicht.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.

Die an sich bestens bekannte Ausbildung des Plattenwärmeübertragers aus mit einem Lotwerkstoff beschichtetem Aluminiumblech oder beispielsweise aus Edelstahlblech in einer kompakten Lötkonstruktion alleine, hat sich als nicht ausreichend herausgestellt, um die geforderte Druckstabilität zu gewährleisten.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.

Es wurde erkannt, dass die noch wirkungsvollere Einbindung der Deck - und der Grundplatte in den Festigkeitsverbund des Plattenwärmetauschers eine einfache und zuverlässige Problemlösung darstellt. Der Erfinder hat damit die Verwendung von Wärmeübertragerplatten mit größerer Blechdicke und all den anderen daraus folgenden Nachteilen vermieden.It has been recognized that even more effective integration of the deck and base plate into the strength of the plate heat exchanger is a simple and reliable solution to the problem. The inventor has thus avoided the use of heat exchanger plates with greater sheet thickness and all the other resulting disadvantages.

Die Grundplatte und die Deckplatte sind im allgemeinen mit wesentlich größerer Blechdicke ausgebildet als die Wärmeübertragerplatten und deshalb geeignet, Kräfte aufzunehmen und noch besser als bisher für Stabilität zu sorgen. Der Körper, der vorzugsweise ein geschlossenes Rundstab ist, trägt außerdem dazu bei, dass sich das Kältemittel ausgezeichnet auf alle Strömungskanäle verteilt, wodurch eine sehr gute Wärmeaustauschrate insbesondere dann erreicht wird, wenn eine große Anzahl von aus Wärmeübertragungsplatten gebildeten Strömungskanälen vorgesehen ist.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.

Der Strömungsweg des CO2 im Verteiler - und im Sammelkanal stellt sich vorzugsweise als ringförmiger Kanal dar, und er ist von der Wand des Körpers und vom Rand der Durchbrüche in den Wärmeübertragerplatten begrenzt. Der ringförmige Strömungsweg geht durch den gesamten Stapel hindurch und verteilt somit das CO2 auf diejenigen Strömungskanäle, die dem Verteilerkanal und dem Sammelkanal zugeordnet sind. Es muss aber betont werden, dass der Strömungsweg durchaus nicht über den gesamten Stapel mit gleicher Abmessung und ringförmig ausgebildet sein muss. Mit anderen Worten, der den Strömungsweg bestimmende Querschnitt des Körpers muss nicht über den gesamten Stapel gleichmäßig ausgebildet sein.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.

Von einer direkten Verbindung zwischen den Enden des Körpers und der Grund- bzw. der Deckplatte kann dann gesprochen werden, wenn die Enden unmittelbar in oder an den Durchbrüchen der Grund - bzw. der Deckplatte angelötet sind. Indirekt ist die Verbindung dann, wenn ein Zwischenglied, beispielsweise ein Flansch oder dergleichen Einzelteil, vorhanden ist. Es ist absolut klar, dass mit der Grundplatte ein direkte Verbindung vorhanden sein kann, während mit der Deckplatte eine indirekte Verbindung ausgewählt wurde, oder umgekehrt. Jedenfalls soll die Wirkung des Körpers als Anker zwischen der Deckplatte und der Grundplatte vorhanden sein, damit er dem Innendruck entgegenwirken kann.From a direct connection between the ends of the body and the base or the cover plate can then be spoken, when the ends are soldered directly in or at the openings of the base and the cover plate. Indirectly, the connection is when an intermediate member, such as a flange or the like item is present. It is absolutely clear that there may be a direct connection to the base plate while an indirect connection has been selected with the cover plate, or vice versa. In any case, the effect of the body should be present as an anchor between the cover plate and the base plate so that it can counteract the internal pressure.

Wegen weiterer Merkmale der Erfindung wird auf die abhängigen Ansprüche und auf die folgende Beschreibung eines Ausführungsbeispiels anhand der Zeichnungen verwiesen.For further features of the invention, reference is made to the dependent claims and to the following description of an embodiment with reference to the drawings.

Die beiliegenden Figuren zeigen den Plattenwärmeübertrager erstens in perspektivischer und teilweise auseinandergezogener Darstellung und zweitens in einem durch die Anschlussstutzen geführten Schnitt durch den Plattenwärmeübertrager.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.

Der Plattenwärmeübertrager dient dem Wärmeaustausch zwischen dem Kältemittel CO2 und der Kühlflüssigkeit eines Kraftfahrzeugmotors und wird in bekannter und nicht gezeigter Weise in die Klimaanlage integriert.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.

Er besteht im gezeigten Ausführungsbeispiel komplett aus mit Lot beschichteten Aluminiumblechen von grundsätzlich rechteckiger Gestalt, wobei auch die Gestalt zweckentsprechend ausgewählt werden kann. Aus den Aluminiumblechen wurden wannenförmige Wärmeübertragerplatten 4 hergestellt, die einen einfach abgekanteten Rand 24 aufweisen und die mit jeweils vier Durchbrüchen 5 versehen sind. Die gleiche Gestalt wurde auch für die Deckplatte 3 und für die Grundplatte 2 vorgesehen. Die Grundplatte 2 ist in diesem Ausführungsbeispiel ohne Durchbrüche 5 ausgebildet, da die Zu - und Abführung des CO2 und der Kühlflüssigkeit an der Deckplatte 3 vorgesehen ist. Die Wärmeübertragerplatten 4 werden zu einem Stapel zusammengefügt. Zwischen den Wärmeübertragerplatten 4, bzw. zwischen deren beabstandeten Wärmeaustauschflächen wurden in den Strömungskanälen 10 in bekannter Art und Weise von der Kühlflüssigkeit durchströmbare Lamellen 32 eingefügt, die für einen effizienten Wärmeaustausch sorgen. Die Lamellen 32 tragen außerdem zu einer größeren Druckfestigkeit bei, denn sie sind mit den Wärmetauschflächen verlötet. In der Fig. 2 wurden die Lamellen 32 lediglich angedeutet. Die Grund - und die Deckplatte 2, 3 vervollständigen den Plattenwärmeübertrager. Im Ausführungsbeispiel zeigt der Rand 24 der Platten 2, 3, 4 nach unten. Die vier Durchbrüche 5 der aufeinander gestapelten Wärmeübertragerplatten 4 bilden vier vertikal durch den Stapel hindurchgehende Sammel - und Verteilerkanäle 6, 7, 8, 9. Die Bezugszeichen 6, 7, 8, 9 wurden an den Strömungspfeilen angebracht, die gleichzeitig zeigen sollen, dass bei 6 die Kühlflüssigkeit in den Verteilerkanal 6 des Plattenwärmetauschers über den Anschlussstutzen 1.2 einströmt und die über den Sammelkanal 7 und den Anschlussstutzen 1.2, nach Durchströmung der Strömungskanäle 10, denselben wieder verläßt. Analog strömt bei 9 das Kältemittel in den Plattenwärmeübertrager ein, welches nach Durchströmung der Strömungskanäle 11 den Plattenwärmeübertrager bei 8 wieder verläßt. Der Wärmeaustausch erfolgt somit im Gleichstrom, wobei jedoch in einem nicht gezeigten Ausführungsbeispiel Gegenstrom vorgesehen ist. Die Anschlussstutzen 1.1 für das Kältemittel sind spezielle Hochdruckfittinge. Im Verteilerkanal 9 und im Sammelkanal 8 für das Kältemittel befindet sich jeweils ein Körper 12. Der Körper 12 erstreckt sich durch den gesamten Verteilerkanal 9 bzw. durch den Sammelkanal 8 hindurch. Er ist von im Querschnitt allgemein runder Gestalt, deren Durchmesser kleiner sein muss als der Durchmesser der Durchbrüche 5, die den Verteilerkanal 9 und den Sammelkanal 8 bilden. Am zusammengefügten Plattenwärmeübertrager bildet sich deshalb zwischen dem Rand 15 der Durchbrüche 5 und dem Körper 12 ein im Ausführungsbeispiel ringförmiger Strömungsweg 16 innerhalb des Verteiler - und des Sammelkanals 8, 9 aus, der vom Kältemittel durchströmt wird. Jeder zweite Strömungskanal 11 ist hydraulisch mit dem Verteiler - und mit dem Sammelkanal 8, 9 verbunden. Da sich im gezeigten Ausführungsbeispiel die durch die Wärmeübertragerplatten 4 gebildeten Strömungskanäle 10 und 11 abwechseln, sind die ersten Strömungskanäle 10 hydraulisch mit dem Verteiler - und mit dem Sammelkanal 6, 7 verbunden. Die hydraulische Verbindung der Verteiler - und der Sammelkanäle 6, 7, 8, 9 mit den zugeordneten Strömungskanäle 10 bzw. 11 ist nicht detailliert gezeigt worden, weil solche Ausbildungen zum Stand der Technik gehören. Es ist aber aus der Fig. 2 erkennbar, dass um die Durchbrüche 5 herum durch Umformung hergestellte Durchzüge 15 angeordnet sind, die die hydraulische Verbindung vom Verteilerkanal 8 und dem Sammelkanal 9 in den Strömungskanal 10 hinein blockieren. Dieser und alle übernächsten Strömungskanäle 10 sind nur vom Verteilerkanal 6 und Sammelkanal 7 (für Kühlflüssigkeit) aus hydraulisch zugänglich, was jedoch nicht zeichnerisch dargestellt wurde. Dort fehlen dementsprechend die erwähnten Durchzüge 15. Anstelle der Durchzüge 15 könnten auch Ringe eingelegt werden.In the exemplary embodiment shown, it consists entirely of solder-coated aluminum sheets of basically rectangular shape, whereby the shape can also be selected appropriately. 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 durchströmbare 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. In Fig. 2, the fins 32 were merely indicated. The base and cover plates 2 , 3 complete the plate heat exchanger. In the exemplary embodiment, 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 . Similarly, at 9 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. In the distribution channel 9 and the collecting channel 8 for the refrigerant is in each case 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 . At the assembled plate heat exchanger therefore forms between the edge 15 of the apertures 5 and the body 12 in the embodiment an annular flow path 16 within the manifold - and the collecting channel 8, 9 , which is flowed through by the refrigerant. 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. 2 that 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.

Das im Bild untere Ende 13 des Körpers 12 ist metallisch direkt mit der Grundplatte 2 verbunden und das im Bild obere Ende 14 ist metallisch direkt mit der Deckplatte 3 verbunden, wodurch dem Plattenwärmeübertrager eine sehr gute Druckfestigkeit verliehen wurde. Die Grundplatte 2 und die Deckplatte 3 besitzen ausreichende Stabilität. Es bietet sich an, für die Anordnung der Körper 12 den Verteiler - und den Sammelkanal 8, 9 für das Kältemittel auszuwählen, da dasselbe unter einem wesentlich höheren Druck steht als die Kühlflüssigkeit. Eine Bedingung ist das jedoch nicht, denn auch durch die Anordnung der Körper 12 in dem anderen Verteiler - und dem Sammelkanal 6, 7 wird eine höhere Druckfestigkeit des Plattenwärmeübertragers erreicht.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.

Gleichfalls könnte in jedem Verteiler - und Sammelkanal 6, 7, 8, 9 ein solcher Körper 12 angeordnet sein, um extrem hohen Drücken widerstehen zu können.Likewise, in each manifold and collecting channel 6 , 7 , 8 , 9 such a body 12 could be arranged to withstand extremely high pressures.

Die Anschlussstutzen 1.1 befinden sich an dem Verteiler - und dem Sammelkanal 8 und 9, die für das Kältemittel gedacht sind. Wegen des dort herrschenden extrem hohen Drucks ist eine ganz besondere Konstruktion erforderlich, die im Folgenden näher beschrieben werden soll.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.

Die Anschlussflansche 20 sind aus der Deckplatte 3 durch Umformung gebildet worden. Die Flanschplatten 23 an der Grundplatte 2 ebenfalls, wobei auch die Flanschplatte 23 ein Reduzierstück 31 aufweist, in dem das untere Ende 13 des Körpers 12 eingelötet ist. Der Körper 12 besitzt am oberen Ende 14 eine Verjüngung 30, die in das am Anschlussflansch 20 angeformte Reduzierstück 21 eingeführt werden kann, um dort metallisch verbunden zu werden. Um das Reduzierstück 21 herum sind mehrere Öffnungen 22 eingebracht worden, die um den Umfang verteilt sind. Davon sind fünf Öffnungen 22 in der Fig 1 erkennbar. Der Anschlussstutzen 1.1 wurde auf dem Anschlussflansch 20 und auf der Deckplatte 3 aufgelötet, wobei seine Umrandung 25 um die Öffnungen 22 und um das Reduzierstück 21 herum reicht. Der Anschlussstutzen 1.1 besitzt innen etwa sägezahnartige Ausschnitte 26, durch die das CO2 von der nicht gezeigten Leitung aus einströmen kann, wobei es weiter durch die Öffnungen 22 bis in den Verteilerkanal 9 hinein strömen wird. Im Verteilerkanal 9 ist ein ringartiger Strömungsweg 26 ausgebildet von dem aus der Zugang zu den Strömungskanälen 11 gewährleistet ist. (siehe gestrichelte Pfeile in Fig. 2, rechts) In analoger Weise kann das gekühlte CO2 den Plattenwärmeübertrager über den anderen Anschlussstutzen 1.1 wieder verlassen, auch wenn das aus der Darstellung nicht erkennbar ist, da die Schnittebene in beiden Anschlussstutzen 1.1 nicht identisch ist. Eine solche Ausbildung ist besonders vorteilhaft, da sie dafür sorgt, dass die Zugänge von dem Strömungsweg 16 in die Strömungskanäle 11 hinein (und heraus) konstruktiv bzw. fertigungstechnisch leichter herstellbar sind. Es ist zu bedenken, dass bei einem beispielsweise etwa 6 mm im Durchmesser messenden Verteilerkanal bzw. Sammelkanal die Ausbildung der Zugänge zu erheblichen Problemen führen würde. Durch das Vorsehen des Körpers 12 mit dem beschriebenen Strömungsweg 16 wurde es möglich, deutlich größere Freiheiten bei der Ausbildung der Zugänge anzubieten, und was weiter wesentlich ist, ohne dabei die gesamte Querschnittsfläche wesentlich zu vergrößern, denn dieselbe geht bekanntlich bei der Bestimmung der in dem Plattenwärmeübertrager wirkenden Druckkräfte in die Berechnung ein. Der Querschnittsfläche des Körpers 12 ist abgestimmt mit der Querschnittsfläche des Verteiler 9 - und des Sammelkanals 8, so dass die Querschnittsfläche des verbleibenden Strömungsweges 16 etwa mit der Querschnittsfläche der Öffnungen 22 und der Ausschnitte 26 korrespondiert, um günstige Strömungsbedingungen zu schaffen. Der ringartige Strömungsweg 26 wurde mit di und da markiert, womit der Innendurchmesser und der Außendurchmesser der Querschnittsfläche des Strömungswegs 26 gemeint sein soll.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. In the distribution channel 9 , a ring-like flow path 26 is formed from the access to the flow channels 11 is ensured. (see dashed arrows in Fig. 2, right) In an analogous manner, 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. It should be remembered that with a distribution channel or collection channel measuring, for example, about 6 mm in diameter, the formation of the access points would lead to considerable problems. By providing the body 12 with the described flow path 16 , it has been possible to offer significantly greater freedom in the formation of the access, and what is essential, without substantially increasing the entire cross-sectional area, because it is known in the determination of the in the Plate heat exchanger acting compressive forces in the calculation. 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 .

Aus der Fig. 2 ist ferner zu sehen, dass zwei verschiedene Arten von Wärmeübertragerplatten 4 in diesem Ausführungsbeispiel verwendet werden. Die eine Art ist in der Blechdicke etwa mit derjenigen der Grundplatte 2 und der Deckplatte 3 zu vergleichen, während die andere Art wesentlich dünner ist. Dies ist ebenfalls der Tatsache geschuldet, dass die Drücke extrem hoch sind.From 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.

Claims (9)

  1. Plate heat exchanger in the form of a brazed structure, consisting of connecting pieces (1), base plate (2), top plate (3) and heat exchanger plates (4) with at least four preferably circular orifices (5) for two media, the heat exchanger plates (4) being stacked in such a way in or on one another between base plate (2) and top plate (3) that the orifices (5) form collector or distributor channels (6, 7, 8, 9) passing through the stack of heat exchanger plates (4), inlets or outlets from the collector or distributor channels (6, 7, 8, 9) to flow channels (10, 11) between the heat exchanger plates (4) being present, in which heat exchange takes place, and with a body (12) arranged approximately coaxially in a distributor space and in the associated collector space (8, 9), which body (12) is connected at one end (13) to the base plate (2) and at the other end (14) to the top plate (3) and extends substantially through the entire distributor or collector channel (6, 7), in order to counteract the internal pressure in the plate heat exchanger, a flow path (16) being formed between the body (12) and the rim (15), formed by the orifices (5), of the distributor or collector channel (8, 9), characterized in that a plurality of openings (22) are formed around the end (14 or 13) of the body (12), which provide a hydraulic connection to the flow path (16) and additionally through the associated flow channels (11), the cross-section of the openings (22) corresponding approximately to the cross-section of the flow path (16).
  2. Plate heat exchanger according to Claim 1, characterized in that the body (12) is preferably a round rod, such that the flow path (16) is formed in an annular manner (di, da) in the distributor channel and in the collector channel (8, 9).
  3. Plate heat exchanger according to one of the preceding claims, characterized in that the body (12) is tapered (30) at at least one end (14), in that this end (14) is arranged on the side where the associated connecting piece (1.1) is located, in that the taper (30) opens in a connecting flange (20) with a reducing fitting (21) and is brazed therein and in that the plurality of openings (22) are introduced around the reducing fitting (21).
  4. Plate heat exchanger according to Claims 1 and 3, characterized in that the connecting piece (1.1) is preferably brazed on the connecting flange (20), encompassing the reducing fitting (21) and the openings (22) with its edge (25).
  5. Plate heat exchanger according to Claims 3 and 4, characterized in that the connecting flange (20) is formed either by shaping of the top or base plate (2, 3), or is a separate part.
  6. Plate heat exchanger according to one of the preceding claims, characterized in that the other end (13) of the body (12) is brazed firmly to the base plate (2) by means of a flanged plate (23), the flanged plate (23) likewise being formed by shaping of the base plate (2).
  7. Plate heat exchanger according to one of the preceding claims, characterized in that the heat exchanger plates (4) are trough-shaped, wherein they have a circumferential, singly bent edge (24) and otherwise an at least predominantly planar heat exchange face, such that they may be stacked in one another in such a way that the edges (24) of adjacent plates may be connected by brazing and in each case a flow channel (10, 11) is formed between the heat exchange faces, and wherein per se known means (eyelets 15 or rings) are provided at at least two orifices (5) in the heat exchanger plates (4), in order to separate a flow channel (10) hydraulically from the one distributor channel and the one collector channel (8, 9), which is in turn connected hydraulically via the orifices (5) without eyelets or rings (15) to the other distributor channel and the other collector channel (6, 7).
  8. Plate heat exchanger according to one of the preceding claims, characterized in that at least some of the heat exchanger plates (4) have a greater material thickness than the other heat exchanger plates (4), the material thickness of the thicker heat exchanger plates (4) corresponding approximately to the material thickness at the top plate (3) and at the base plate (2).
  9. Use of the plate heat exchanger according to one of the preceding claims, characterized in that the distributor and collector channels (8, 9) containing the body (12) and the associated flow channels (11) are provided for CO2 as refrigerant in motor vehicle air-conditioning systems, while the engine coolant flows through the other distributor and collector channels (6, 7) and through associated flow channels (10).
EP03016863A 2002-09-19 2003-07-24 Plate heat exchanger Expired - Lifetime EP1400772B1 (en)

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DE10243522A DE10243522A1 (en) 2002-09-19 2002-09-19 Plate heat exchangers

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015012029A1 (en) 2015-09-15 2017-03-16 Modine Manufacturing Company Plate heat exchanger

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

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