EP1305561B1 - Dispositif de transfert de chaleur - Google Patents

Dispositif de transfert de chaleur Download PDF

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Publication number
EP1305561B1
EP1305561B1 EP01951364A EP01951364A EP1305561B1 EP 1305561 B1 EP1305561 B1 EP 1305561B1 EP 01951364 A EP01951364 A EP 01951364A EP 01951364 A EP01951364 A EP 01951364A EP 1305561 B1 EP1305561 B1 EP 1305561B1
Authority
EP
European Patent Office
Prior art keywords
fluid
heat transfer
supporting element
abovementioned
plates
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
EP01951364A
Other languages
German (de)
English (en)
Other versions
EP1305561A1 (fr
Inventor
Stephan Leuthner
Petra Beil
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1305561A1 publication Critical patent/EP1305561A1/fr
Application granted granted Critical
Publication of EP1305561B1 publication Critical patent/EP1305561B1/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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
    • 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
    • F28F2225/00—Reinforcing means
    • F28F2225/08—Reinforcing means for header boxes
    • 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 device for heat transfer from a first fluid to a second fluid separated from the first fluid with at least two layers, in particular plates, comprising a stack-shaped or shell-like structure according to the preamble of claim 1.
  • heat exchangers are provided with a flowed through by a high-pressure side refrigerant first channel and a low-pressure-side refrigerant, separated from the first channel second channel in a CO 2 vehicle air conditioning.
  • a so-called internal or internal heat exchanger is provided.
  • the internal heat exchanger is flowed through by the refrigerant (CO 2 ) in a countercurrent or DC principle.
  • the fluids flow through the heat exchanger once on the way from the gas cooler to the evaporator and the second time between evaporator and compressor.
  • the main task of the internal heat exchanger is to additionally cool the refrigerant before expansion.
  • the heat is from the high pressure side of the gas cooler to the Low pressure side after the evaporator (before entering the compressor) delivered.
  • the partially still liquid refrigerant evaporates completely before it reaches the compressor.
  • Possible applications are for corresponding heat exchangers in vehicle air conditioners, heat pumps, portable air conditioners low power, dehumidifiers, dryers, fuel cell systems and similar applications.
  • heat exchangers which are made comparatively compact for mass and volume reduction.
  • micro-heat exchangers are provided. These consist in particular of structured plates which are stacked one above the other and either soldered together, screwed or connected accordingly. In this case, correspondingly provided channels of the heat exchanger are also sealed at the same time. The fluids that make thermal contact with each other in the heat exchanger are passed through the channels between the plates.
  • the fluids are passed through inlet openings or outlet openings in the individual layers, so that in different layers alternately flows a heat-absorbing and a heat-emitting fluid.
  • the distribution or merging of the fluids to or from the individual channels takes place here in the entry or exit area. In these areas, the respective fluid flow splits or collects.
  • the large pressurized area in the region of the free cross-section causes large material stresses to occur, resulting in material deformations, eg. B. flow, or may come to failure of the component.
  • the invention has the object to provide a device for heat transfer, which realizes a comparatively large heat-transmitting surface with a small volume and thereby ensures trouble-free operation even at a large different pressure level of the two fluids.
  • a device is characterized in that the inlet and / or outlet region comprises at least one support element which, like the channels, is formed by means of an applied or abrasive manufacturing process on the relevant, preferably plate-shaped layers of the device.
  • the resultant free cross-section and in particular the bending moment occurring in the entry or exit area is thereby substantially reduced, with particularly small geometric dimensions being able to be realized by the machining or removal manufacturing process.
  • an etching method can preferably be used. This ensures that the pressurized surface, in particular on the side operated with a comparatively low pressure, is supported and thus an adverse deformation of the plate is prevented.
  • each plate inventive support element corresponding pressure forces from plate to plate forward to possibly a comparatively massive cover plate absorbs the compressive forces, so that deformation of the plates or a failure of the entire component is effectively prevented.
  • numerous support elements are provided both in the entry and in the exit area, so that both the resulting free cross sections and the bending stresses occurring are further reduced.
  • this advantageously has comparatively many support elements on the side facing the heat transfer region. However, comparatively few supporting elements are provided on the side of the entry region facing the inlet opening. The corresponding is advantageously transferred to the exit area.
  • the heat exchanger according to the invention compared to the prior art at the same pressure differences between the two fluids have much thinner plates, which can preferably lead to a given mass to be transferred heat and in particular to a significant mass and volume reduction of the entire heat exchanger.
  • the support elements increase the heat-transmitting surface, so that the heat transfer of the heat exchanger according to the invention is additionally improved.
  • the volume of a heat exchanger according to the invention can be additionally reduced in an advantageous manner for a given heat output to be transferred.
  • the length of the support element is designed as a multiple of its width. This ensures that the support element, for example, with a comparable flow resistance has a much greater support effect and heat-transferring surface.
  • the heat exchanger can hereby advantageously be subjected to a greater pressure difference between the two fluid streams without any disadvantageous material deformation or failure of the heat exchanger.
  • the support element is designed as a fluid guide element.
  • the fluid is uniformly distributed to the channels of the heat transfer area or streamlined from the channels and forwarded to a corresponding collection channel. This can be implemented a more uniform distribution of the channel structure of the heat transfer area, which in turn leads to improved heat transfer of the heat exchanger.
  • two adjacent support elements are arranged at an angle of less than 20 °, preferably between 10 ° and 15 ° to each other.
  • the opening angle of the fluid flow is often over 50 °.
  • a comparatively small opening angle between two adjacent support elements according to the invention prevents, for example, a detachment of the fluid flow in the entry or exit area, so that disadvantageous energy losses can be minimized and at the same time uneven loading of the channel structure of the heat transfer area can be prevented.
  • Reynolds number which is dependent for example on the opening angle, the fluid pressure and the arrangement or design of the support elements or the channels of the heat transfer area.
  • the side wall of the support element is rectilinear and / or curved.
  • the configuration of a support element as a polygon is also conceivable.
  • the support elements are material technically and geometrically designed such that they achieve the greatest possible support effect and a very good flow distribution with a comparatively low flow pressure loss.
  • elongate support members may advantageously have widened portions for improving the support effect and the flow guidance.
  • At least one support element is formed as an extension of a partition between two channels of the heat transfer area.
  • a Support member formed as an extension of the channel partition wall it is preferably provided a curved transition from the support member to the channel partition.
  • a curved transition can lead to an advantageous fluid flow, so that disadvantageous pressure losses can be minimized.
  • the support element may have a curved side wall, but also the channel partition wall may have a curvilinear side wall having at least in the edge region, so that a more favorable fluid flow can be generated.
  • this is a transition with a slight fold, which has a relatively small kink, feasible.
  • the various layers of the stack-shaped or cup-shaped device are formed as flat or curved plates or as cylindrical, stackable due to different diameter components, so that an advantageous production of the heat exchanger according to the invention can be realized.
  • the heat exchanger final cover plates are provided.
  • the design and arrangement of the support elements is adapted to the channels of the heat transfer area.
  • the channels and the support elements are produced on or in the layers by means of a removing or applying manufacturing process, so that the support elements and the channels are relatively small to produce.
  • corresponding recesses of the plates are produced by a photolithographic patterning process with a subsequent etching process, so that optionally all process steps both for the production of the channels of the heat transfer region as well as for the production of the support elements in the entry or exit area in each case a work step can be realized.
  • the heat exchanger is formed by plates stacked on top of one another and soldered together, in which at least partially the corresponding recesses, for example for the formation of the channels or support elements, are provided.
  • at least one soldering layer can be provided between the plates for a soldering process.
  • the soldering process is advantageously carried out in a vacuum or in an inert gas atmosphere.
  • the plates are stacked with at least one intermediate solder layer in the later arrangement of the component on each other and in particular in the cold state, even before the soldering process, pressed.
  • FIG. 1 shows a heat exchanger according to the prior art.
  • the heat exchanger comprises individual plates 1, 2, 3 for heat transfer, which are soldered or welded together, between two cover plates 8, 9 are packed and with small channels 11, 12, 13 and flow openings 4, 5, 6, 7 are provided.
  • incoming CO 2 high pressure (arrow FE2) flows through the flow opening 4 of the heat transfer plate 1 through the middle heat transfer plate 2, through the channels 12 in the direction of arrow down and flows from there through the flow opening 6 of the heat transfer plate first and through the outlet opening 16 of the cover plate 8 (arrow FA2).
  • CO 2 of low pressure (arrow FE 1) flows into an inlet opening 15 of the cover plate 8, through the channels 11 of the Heat transfer plate 1 from bottom to top, further through the flow opening 5 of the heat transfer plate 2 to the heat transfer plate 3 and there also through the small channels from bottom to top and through the corresponding flow openings 7 of the heat transfer plates 3, 2, 1 and then through the outlet opening 17 of the Cover plate 8 off (arrow FA1).
  • the illustrated heat exchanger is flowed through by the high-pressure side refrigerant (black arrows) in a first direction and in countercurrent to the low-pressure side refrigerant (hatched arrows).
  • the heat exchanger shown in Figure 1 due to a more advantageous representation, only three heat transfer plates 1, 2, 3, on. This consists of individual, defined by the heat transfer plates 1, 2, 3 layers in countercurrent to the CO 2 , which is on one side at high pressure (up to approximately 150 bar) at high temperature and on the other hand at low pressure ( flows up to approximately 60 bar) and low temperature.
  • the heat transfer coefficient on the low pressure side is generally much smaller than that on the high pressure side.
  • An inventive heat exchanger can be advantageously made of copper and copper alloy, stainless steel, aluminum and other materials.
  • An inventive heat exchanger can be used advantageously as an inner heat exchanger of a CO 2 air conditioning system in vehicles, in particular motor vehicles.
  • the first (high pressure) flow channel marked by black arrows in a first flow path from a gas cooler to an evaporator and the second (low pressure) flow channel marked by hatched arrows in the figure lie in a second flow path from the evaporator to one Compressor of the vehicle air conditioner.
  • FIG. 2 schematically shows a free cross-section 24 which arises, for example, as a result of overlapping the inlet region E1 of the fluid I with the outlet region A2 of the fluid II according to the prior art.
  • the free cross-section 24 has a comparatively large pressure-loaded surface and thus has to absorb comparatively large material stresses, which can lead to deformations, in particular of the plates 2, 3 and to the failure of the heat exchanger.
  • FIG. 3 shows a section of the two plates 2, 3 corresponding to the section of FIG. 2.
  • the entry or exit region of the plates 2, 3 according to the invention has support elements 18 according to the invention.
  • the support elements 18 according to FIG. 3 are designed as rectilinear support elements 18.
  • an opening angle ⁇ which is formed from two adjacent support elements 18, is substantially smaller than an opening angle ⁇ without support elements 18 according to the prior art according to the invention.
  • the flow of the fluids distributed more evenly on the channels of the heat transfer area and the opening angle is reduced, for example, from about 50 ° to about 10 ° to 15 °.
  • the prevention of detachment and thus the reduction of energy losses depends essentially on the prevailing Reynolds number. This in turn depends, among other things, on the opening angle and also on the set pressures of the fluids.
  • FIG. 3 illustrates that the reduced free cross-section 23, compared to the free cross-section 24 of FIG. 2, represents a substantial reduction in the pressure-applied Represent surface and thus significantly reduces the bending stresses occurring. As a result, deformation of the plates 1, 2, 3 or a failure of the heat exchanger is largely prevented.
  • supporting elements 18 are shown in FIG. 4, which have local reinforcements 20 for reinforcing the supporting effect according to the invention.
  • support elements 18 are shown having a curved side wall.
  • This inventive design of the support elements 18 leads in particular to an advantageous flow guidance and distribution of the fluids to the channels 11, 12, 13.
  • the curved support elements 18 shown in Figure 5 have a polygonal transition 21.
  • a not-shown curved transition 21 can lead to a further improvement of the flow guidance in this case.
  • a curved end region of the channel partition walls 19 may also be advantageous.
  • the support elements 18 according to the invention distributed the load occurring much better, so that they have an additional supporting function. According to the state of the art, among other things, the occurring load had to be taken over predominantly by the edge regions of the plates 1, 2, 3, so that material can advantageously be saved with the aid of the support elements 18 according to the invention, for example in the edge regions.
  • the plates 1, 2, 3 are alternately flowed through by a heat-absorbing and a heat-emitting fluid in a countercurrent or co-current principle.
  • a heat-absorbing and a heat-emitting fluid in a countercurrent or co-current principle.
  • two adjacent plates 1, 2 are flowed through by the same fluid and only the subsequent plate 3 and also several adjacent plates are flowed through by the other fluid.

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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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Claims (9)

  1. Dispositif pour transmettre la chaleur d'un premier fluide à un deuxième fluide séparé du premier fluide, dont la structure en pile ou en coque comprend au moins deux couches (1, 2, 3), en particulier des plaques (1, 2, 3),
    chaque couche (1, 2, 3) comprenant une zone thermoconductrice comportant de nombreux canaux (11, 12, 13), une zone d'entrée placée en amont de la zone thermoconductrice en direction d'écoulement et une zone de sortie placée en aval de la zone thermoconductrice en direction d'écoulement,
    la zone d'entrée et/ou la zone de sortie comprenant au moins un élément d'appui (18),
    caractérisé en ce que
    les canaux (11, 12, 13) et/ou l'élément d'appui (18) sont formés d'après un procédé de fabrication qui dépose ou qui retire du matériau.
  2. Dispositif selon la revendication 1,
    caractérisé en ce que
    le procédé de retrait est un procédé de corrosion.
  3. Dispositif selon la revendication 1 ou 2,
    caractérisé en ce que
    la longueur de l'élément d'appui est un multiple de sa largeur.
  4. Dispositif selon l'une des revendications précédentes,
    caractérisé en ce que
    l'élément d'appui (18) est un élément directionnel de fluide (18).
  5. Dispositif selon l'une des revendications précédentes,
    caractérisé en ce que
    deux éléments d'appui (18) voisins forment l'un par rapport à l'autre un angle (α) inférieur à 20°.
  6. Dispositif selon l'une des revendications précédentes,
    caractérisé en ce que
    la paroi latérale de l'élément d'appui est rectiligne et/ou courbe.
  7. Dispositif selon l'une des revendications précédentes,
    caractérisé en ce que
    au moins un élément d'appui (18) est un prolongement d'une paroi de séparation (19) entre deux canaux.
  8. Dispositif selon l'une des revendications précédentes,
    caractérisé en ce que
    une transition (21) courbe est prévue de l'élément d'appui (18) vers la paroi de séparation (19).
  9. Dispositif selon l'une des revendications précédentes,
    caractérisé en ce que
    les couches (1, 2, 3) sont des plaques (1, 2, 3) planes ou bombées ou des éléments de construction (1, 2, 3) cylindriques qui peuvent être emboîtés les uns dans les autres par des diamètres différents.
EP01951364A 2000-07-21 2001-06-09 Dispositif de transfert de chaleur Expired - Lifetime EP1305561B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10035939 2000-07-21
DE10035939A DE10035939A1 (de) 2000-07-21 2000-07-21 Vorrichtung zur Wärmeübertragung
PCT/DE2001/002162 WO2002008680A1 (fr) 2000-07-21 2001-06-09 Dispositif de transfert de chaleur

Publications (2)

Publication Number Publication Date
EP1305561A1 EP1305561A1 (fr) 2003-05-02
EP1305561B1 true EP1305561B1 (fr) 2005-09-21

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP01951364A Expired - Lifetime EP1305561B1 (fr) 2000-07-21 2001-06-09 Dispositif de transfert de chaleur

Country Status (8)

Country Link
US (1) US7040387B2 (fr)
EP (1) EP1305561B1 (fr)
JP (1) JP2004504584A (fr)
KR (1) KR20020032602A (fr)
BR (1) BR0106982A (fr)
DE (2) DE10035939A1 (fr)
ES (1) ES2248358T3 (fr)
WO (1) WO2002008680A1 (fr)

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WO2002008680A1 (fr) 2002-01-31
US20030094271A1 (en) 2003-05-22
DE10035939A1 (de) 2002-02-07
US7040387B2 (en) 2006-05-09
BR0106982A (pt) 2002-05-14
JP2004504584A (ja) 2004-02-12
ES2248358T3 (es) 2006-03-16
EP1305561A1 (fr) 2003-05-02
KR20020032602A (ko) 2002-05-03
DE50107511D1 (de) 2005-10-27

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