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EP1682840B1 - Echangeur de chaleur, en particulier pour vehicules automobiles - Google Patents

Echangeur de chaleur, en particulier pour vehicules automobiles Download PDF

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Publication number
EP1682840B1
EP1682840B1 EP04765083A EP04765083A EP1682840B1 EP 1682840 B1 EP1682840 B1 EP 1682840B1 EP 04765083 A EP04765083 A EP 04765083A EP 04765083 A EP04765083 A EP 04765083A EP 1682840 B1 EP1682840 B1 EP 1682840B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger according
inlet
outlet
pipes
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
EP04765083A
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German (de)
English (en)
Other versions
EP1682840A1 (fr
Inventor
Walter Demuth
Michael Kohl
Martin Kotsch
Michael Kranich
Karl-Heinz Staffa
Christoph Walter
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1682840A1 publication Critical patent/EP1682840A1/fr
Application granted granted Critical
Publication of EP1682840B1 publication Critical patent/EP1682840B1/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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • 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
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the invention relates to a heat exchanger, in particular for motor vehicles, having a heat exchanger block which can be flowed through by a first medium on the primary side and can be flowed around on the secondary side by a second medium.
  • the local heat exchanger consists inter alia of flat tubes with flow channels, z. B. extruded multi-chamber pipes, which are flowed through by a first medium, preferably a refrigerant, in particular CO2.
  • the flat tubes are arranged parallel to each other and have flat tube ends, which are held in so-called end pieces, consisting of a bottom plate, a baffle plate and a cover plate. The end pieces each form a distribution or deflection unit for the refrigerant.
  • a particularly pressure-resistant heat exchanger is provided, which is particularly suitable for use in a powered with CO2 refrigerant circuit for a motor vehicle air conditioning, on the one hand as an evaporator and on the other hand as a gas cooler, wherein the secondary side loading takes place in each case by ambient air.
  • a heat exchanger in particular for a motor vehicle, is provided with a heat exchanger block, which on the primary side of a first medium and throughflowable on the secondary side of a second medium umströmbare pipes with flow channels and pipe ends, at least one Has tube ends receiving end piece with at least one base plate, distribution or baffle plate and cover plate and at least one connected to one or one end piece inlet and / or outlet chamber, wherein the first medium from the inlet chamber through the flow channels to the outlet chamber is conductive, and with a housing jacket enclosing the tubes with an inlet and an outlet for the second medium, wherein between the tubes corrugated sheets are arranged with longitudinal channels and the corrugated sheets are parallelogram-shaped and approximately triangular or trapezoidal inflow and outflow leave areas between the pipes.
  • a heat exchanger block consisting of tubes and at least one end piece, surrounded by a housing shell, through which a second medium is conductive.
  • the heat exchanger according to the invention can be used in this heat pump cycle both as a CO2 evaporator, which absorbs heat from the coolant, as well as a CO2 gas cooler, the heat to the coolant.
  • the housing shell which can be produced as a sheet metal part, allows many variations with regard to the flow guidance of the Coolant, so that a DC, countercurrent, crossflow and DC / counter crossflow is possible.
  • the most diverse requirements for the heat exchanger according to the invention can be taken into account.
  • the inlet and the outlet for the second medium may be arranged on the same side, on opposite sides and at opposite ends of the housing shell, wherein the housing jacket is flowed through in particular in the longitudinal direction. This results in the possibility of the direct current and the countercurrent of the first and the second medium.
  • distribution and collection chambers are formed in the housing shell in the region of inlet and outlet, so that the second medium is distributed uniformly over the individual gaps between the tubes or collected at the outlet.
  • turbulence inserts or corrugated ribs are arranged between the tubes, which form longitudinal channels and thus a guide in the longitudinal direction of the tubes for the second medium.
  • these turbulence inserts stretch only between the inlet and the outlet of the second medium, so that in the region of inlet and outlet in each case an inflow and an outflow are left, in which a cross-flow of the second medium, d. H. can be transverse to the longitudinal direction of the tubes.
  • the tubes from the second medium can also be overflowed in the transverse direction, namely one or more flooded.
  • This can be done by arranging lateral headers and partitions in conjunction with deflection boxes in the housing shell.
  • the turbulence inserts or the ribbing between the tubes is then designed so that transverse channels for guiding the second medium result. This ensures that both media, such as a refrigerant and a coolant can be performed in cross-DC or cross-countercurrent. This results in a more intense heat exchange.
  • the first medium can be performed both single-flow and double-flow through the tubes, wherein the inlet and outlet chambers are arranged for the first medium either at an end piece or at different end pieces.
  • the heat exchanger according to the invention the most diverse forms and combinations of DC, counter and cross-flow between the first and second medium can be realized, depending on the requirements of the heat exchanger, for example in a refrigerant circuit and in a coolant circuit of an internal combustion engine of a motor vehicle.
  • Fig. 1 shows a refrigerant / coolant heat exchanger 1, ie a heat exchanger, the primary side of a refrigerant, for. B. CO2 (R744) and the secondary side is flowed through by a coolant, which also serves the cooling of an internal combustion engine, not shown, of a motor vehicle.
  • a coolant which also serves the cooling of an internal combustion engine, not shown, of a motor vehicle.
  • the refrigerant circuit when operated in the heat pumping process, can be used as a heat source for heating the passenger compartment. This is the Coolant in the evaporator Heat extracted, pumped to a higher temperature level and returned to the gas cooler as a heat input to the coolant.
  • this heat exchanger 1 can be used both as an evaporator and as a gas cooler in the CO2 heat pump process.
  • the CO2 process is known to take place at elevated pressure compared to the conventional refrigerant process with R134a: for example, a compression takes place up to about 120 bar, which thus occur in the gas cooler. Therefore, the heat exchanger with respect to the refrigerant guide must be dimensioned and formed particularly pressure resistant.
  • the heat exchanger 1 has a housing jacket 2, which is approximately box-shaped and has four longitudinal sides 2a-2d, of which the longitudinal side 2a and 2b are visible in the drawing.
  • the housing shell 2 is closed at the end by end pieces, of which only the end piece 3 is visible in the drawing.
  • a refrigerant inlet pipe 4 and a refrigerant outlet pipe 5 are fixed.
  • a coolant inlet nozzle 6 (only partially visible) and a coolant outlet nozzle 7 are arranged.
  • the heat exchanger 1 is connected, on the one hand, to a refrigerant, in particular a CO2 cycle (not shown) and, on the other hand, to a cooling circuit (not shown) of an internal combustion engine of a motor vehicle.
  • Fig. 1a shows the heat exchanger 1 according to Fig. 1 without housing shell 2, wherein the same reference numerals are used for the same parts.
  • the end piece 3, to which the refrigerant collecting pipes 4, 5 are fastened, is opposite an end piece 8, which is connected by a plurality of flat tubes 9 with the end piece 3.
  • On the uppermost flat tube 9.1 a corrugated sheet 10 is arranged with extending in the longitudinal direction of the flat tubes 9 longitudinal channels 10a.
  • the profile of the corrugated sheet can - as shown in the drawing - be trapezoidal, but other shapes, such. B. sinusoidal or triangular profile.
  • the corrugated sheet 10 extends not over the entire length of the flat tubes 9 from the left end piece 3 to the right end piece 8, but has an oblique leading edge 10b, 10c on the front side.
  • Corrugated sheets 10 are - which is not visible in this illustration - each arranged between adjacent flat tubes 9, so that there is a longitudinal guidance of the coolant in these areas.
  • the corrugated sheets can also be provided with slots and / or offsets, so that an exchange between the longitudinal guide channels for the coolant and thus a more homogeneous distribution and / or turbulence of the coolant and ultimately an increased heat transfer is possible.
  • sheets with transverse coolant channels can be used to increase the surface area and thus to increase the efficiency of the heat exchanger.
  • Fig. 1b shows the heat exchanger block 11 in an exploded view. Again, the same reference numbers are used for the same parts again. It should be noted that some possibilities of refrigerant flow guidance in the DE 102 60 030 A1 are described, both in the illustrated here and in further embodiments and modifications.
  • the block 11 consists of a plurality of mutually parallel flat tubes 9 with flat tube ends 9a, 9b, which are each secured in a bottom plate 12, 13 and sealed.
  • each distribution or deflection plates 14, 15 are arranged, which are covered by a respective end plate 16, 17.
  • In the front cover plate 16 are refrigerant inlet openings 16a and refrigerant outlet openings 16b, in a row with the refrigerant inlet pipe 4 and the refrigerant outlet pipe 5, respectively.
  • the bottom plate 12, baffle 14 and cover 16 thus form the end piece 3, while the end piece 8 of the bottom plate 13, the baffle plate 15 and the cover 17 composed.
  • the structure of the end pieces 3, 8 may also be modified, for. B. floor and baffle plate or deflecting and cover plate can each be integrated into a plate. The same applies to the refrigerant guide, ie by a modified form of the distributor or deflecting plates 14, 15.
  • Fig. 1c shows a schematic representation of the refrigerant connection, ie the flow of the refrigerant according to Fig. 1b ,
  • the refrigerant returns to the end piece 8, where it is deflected in the direction of arrow 23 by means of the baffle plate 15 upwards to flow back into the strand 24 again.
  • the baffle plate 15 Via the baffle 14, the refrigerant outlet opening 16b and the refrigerant outlet pipe 5, the refrigerant leaves the block 11.
  • the refrigerant outlet opening 16b are larger than the refrigerant inlet openings 16a, because this block 11 is designed as an evaporator (with increasing specific volume); a gas cooler would result in a different configuration, for example with equal inlet and outlet openings.
  • the refrigerant connection described above thus applies in each case to two flat tubes lying next to each other.
  • Fig. 2 shows a refrigerant / coolant heat exchanger 25 in longitudinal section
  • the heat exchanger 1 in Fig. 1 corresponds; therefore, like reference numerals are used for like parts.
  • the housing shell 2 encloses the entire block 11, consisting of flat tubes 9 and end pieces 3, 8, wherein the housing shell 2 in the region of the end pieces 3, 8 has a shoulder, to each of which a widened region 26, 27 connects, the end pieces. 3 , 8 peripherally includes and sealed against this, z. B. by soldering.
  • the coolant inlet connection 6 and the coolant outlet connection 7 are arranged, which in each case pass over a distribution chamber 28 or a collection chamber 29 into the housing jacket 2.
  • the sectional view shows the flat tubes 9 of their longitudinal or broad side and thus also the corrugated sheet 10 with longitudinal channels 10a.
  • the corrugated sheet 10 has - as already mentioned - oblique gate edges 10b, 10c, so that inlet and Ausström Suitee 30, 31 result, in which a cross-flow of the coolant from the inlet nozzle 6 and in the direction of the outlet nozzle 7 is possible.
  • the coolant is deflected approximately at right angles and flows through the heat exchanger 25 in the longitudinal direction, which is marked by the arrow P. Die Einström Societye 30 und Auström Schemee 31 , The refrigerant flows through the heat exchanger 25, as previously for Fig.1b and 1c described. Refrigerant and coolant are thus essentially (apart from the deflections) guided in cocurrent and countercurrent.
  • Fig. 2a shows a variant 32 of the heat exchanger 25 from Fig. 2
  • the refrigerant guide is changed in that the refrigerant inlet pipe 4 'is located at the end piece 3' and the refrigerant outlet pipe 5 'is located at the end piece 8'.
  • the refrigerant is essentially single-flow, ie guided in one direction through the heat exchanger 32, while the coolant is guided in the opposite direction according to the arrow P.
  • the refrigerant can also be three, five or (odd) multiple flooded by the heat transfer. This essentially results in a counterflow between the refrigerant and the coolant.
  • Fig. 3 shows a further embodiment of a heat exchanger 33, in which a rectangular cut corrugated sheet 34 is provided with longitudinal channels 34a.
  • the coolant inlet nozzle 6 and the coolant outlet nozzle 7 are arranged on the same side 2a of the housing shell.
  • an approximately right-angled inflow region 35 results in the region of the inlet stub 6 and a corresponding outflow region 36 in the region of the outlet stub 7.
  • the areas 35 and 36 may also be provided with corrugated sheets or other turbulence generators.
  • the refrigerant flow guide is the same as in Fig. 2 ie refrigerant inlet pipe 4 and refrigerant outlet pipe 5 are arranged on the same end piece 3.
  • Fig. 3a shows a variant 37 of the heat exchanger 33 after Fig. 3 , Unlike the heat exchanger 33 is only the refrigerant guide, the in Fig. 2a corresponds, ie, the refrigerant inlet pipe 4 'is on the end piece 3' and the refrigerant outlet pipe 5 'is attached to the end piece 8'. This essentially results in a counterflow between the refrigerant and the coolant, which flows in the longitudinal direction according to the arrow P.
  • Fig. 4 shows a further embodiment of a heat exchanger 38, wherein the refrigerant guide analogous to the embodiments in Fig. 2 and 3 takes place, ie it is a block 11 according to Fig. 1b used.
  • the coolant inlet connection 6 and the coolant outlet connection 7 are located directly opposite one another at the same height, ie they are both arranged in the region of the end piece 3.
  • a partition wall 39 is centrally arranged, which delimits an inflow region 40 on the side of the inlet nozzle 6 and an outflow region 41 on the side of the outlet nozzle 7.
  • the partition wall 39 is arranged in each case between adjacent flat tubes.
  • a corrugated sheet 42 with longitudinal channels 42a connects to the partition 39 and extends to a deflection 43.
  • the corrugated sheet 42 has - as stated above - an approximately trapezoidal profile, which in each case with the adjacent flat tubes is soldered. As a result, discrete longitudinal channels 42a are formed, ie a transverse flow between the longitudinal channels 42a is not possible.
  • the coolant thus flows from the inflow region 40 initially in the upper half of the heat exchanger 38, following the arrow P1, into the deflection region 43, where it is deflected by 180 degrees, ie in the opposite direction, according to the arrow P2. It then flows in the lower half of the heat exchanger 38, following the arrow P3, back into the outflow region 41, where it leaves the heat exchanger 38 via the outlet connection 7.
  • the coolant thus deposits the double path in the heat exchanger 38, in comparison to the previous exemplary embodiments, so that an intensive heat exchange with the refrigerant takes place. Likewise, a four- or (even) multi-flow through the heat exchanger for the refrigerant is possible.
  • the corrugated sheets may be provided with slots and / or offsets, so that an exchange between the longitudinal guide channels for the coolant and thus a more homogeneous distribution and / or turbulence of the coolant and ultimately an increased heat transfer is possible.
  • plates with transverse Külstoffkanälen to increase the surface and thus to increase the efficiency of the heat exchanger can be used.
  • Fig. 5 shows a cross section through a heat exchanger 44, the heat exchanger in Fig. 2 corresponds, with the end piece 3 is omitted. It can therefore be seen directly on the end faces of the flat tubes 9, which are formed as extruded multi-chamber tubes with circular flow channels 45. Between adjacent flat tubes 9, a corrugated metal sheet 10 with a trapezoidal profile is in each case arranged and soldered to the flat tubes 9. As a result, discrete longitudinal channels 10a for the coolant are formed. These plates may also be provided with slots and / or offsets to allow an exchange between the longitudinal channels for the coolant and thus a more homogeneous distribution and / or turbulence of the coolant.
  • the housing shell 2 is formed here as a U-shaped frame with a shoulder and a widening 26, in which the end piece, not shown, is used.
  • the heat exchanger block 11 (see. Fig. 1a, 1b ) can thus be easily inserted into the housing 2 and closed by a lid, not shown.
  • the adjoining the Einsbergsstutzen 6 distribution chamber 28 extends over the entire height of the housing wall 2c, analogously, the collection chamber 29 on the side of the outlet nozzle 7 about the height of the side wall 2a.
  • a distribution of the coolant between all flat tubes 9 is possible and also a collection of the coolant in the collection chamber 29 on the outlet side.
  • Fig. 6 shows a longitudinal section through a flat tube 9, which is taken with its flat tube end 9a in the end piece 3 and its flat tube end 9b in the end piece 8.
  • the two end pieces 3, 8 are as in Fig. 1b illustrated, formed.
  • This design for the flat tubes 9 with the end pieces 3, 8 of individual plates is particularly suitable for high pressures, such as occur in the CO2 refrigerant process.
  • FIG. 7 shows a further embodiment of a heat exchanger 46 with a changed coolant guide.
  • a refrigerant block 47 is in principle similar in construction to the block 11 according to FIG Fig. 1b that is, it has a first end 48 with refrigerant inlet pipe 49 and refrigerant outlet pipe 50 and a second end 51, in which the deflection of the refrigerant takes place.
  • the end piece 48 has a laterally extended bottom plate 52, to which a coolant inlet channel 53 is attached.
  • the tail 51st has an extended bottom plate 54, to which a coolant outlet channel 55 is attached.
  • a housing jacket 56 surrounds the block 47 and each forms a wedge-shaped coolant inlet chamber 57 and a coolant outlet chamber 58.
  • the coolant enters through the inlet channel 53 into the inlet chamber 57 and from there between the column of the flat tubes of the block 47, flows through it in the transverse direction accordingly Arrows P4, enters the outlet chamber 58 and from there into the coolant outlet channel 55.
  • a simple cross-flow of the block 47 is possible.
  • corrugated sheets or turbulence inserts can be arranged between the individual flat tubes, which cause a guide of the coolant in the direction of arrow P4 and turbulence generation.
  • Fig. 8 shows a further embodiment of a heat exchanger 59 with a likewise transversely guided coolant flow, which, however, is shown only schematically. This is based on a longitudinal section through a flat tube 9, as in Fig. 6 is illustrated.
  • a refrigerant block 60 is divided by two dividing walls 61, 62 into three flow areas I, II, III. The areas I, II are interconnected by a deflection chamber 63 and the areas II, III by a further deflection chamber 64 on the opposite side.
  • the coolant enters the region I of the block 60 via an inlet connection 65, which is also shown only schematically, is deflected in the deflection chamber 63, then flows through the region II into the deflection chamber 64 where it is again deflected and finally reaches the region III, which it leaves via an outlet 66.
  • Inlet and outlet ports 55, 66 and deflection chambers 63, 64 are part of a housing shell, not shown, which surrounds the block 60.
  • the exemplary embodiments described above for refrigerant / coolant heat exchangers are preferably soldered, which applies in particular to the block through which CO2 flows.
  • the housing shell could - because of the significant lower pressure of the coolant - by alternative bonding techniques, eg. B. by gluing or rubber seals with the block or its end pieces are connected. In this case, other materials, such as plastic, come into question for the housing shell.
  • the invention has been explained using the example of a refrigerant / coolant heat exchanger, but also includes other heat exchangers.
  • an inventive heat exchanger of oil and / or air can flow through, which exchange heat with each other or with other media.

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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)
  • Air-Conditioning For Vehicles (AREA)

Claims (26)

  1. Echangeur de chaleur, en particulier pour un véhicule automobile, comprenant un bloc d'échangeurs de chaleur (11) qui présente des tubes (9) traversés, côté primaire, par un premier milieu, et, côté secondaire, baignés par un deuxième milieu, lesdits tubes comportant des conduits d'écoulement (45) et des extrémités de tubes (9a, 9b), au moins une partie terminale (3, 8) logeant les extrémités de tubes (9a, 9b), ladite partie terminale comportant à chaque fois au moins une plaque de base (12, 13), une plaque de distribution ou de renvoi (14, 15) et une plaque de recouvrement (16, 17), ainsi qu'au moins une chambre d'entrée et / ou de sortie (4, 5) raccordée à une ou à chacune des parties terminales (3, 8), où le premier milieu peut être guidé à travers les conduits d'écoulement (45), passant de la chambre d'entrée (4) à la chambre de sortie (5), et comprenant une enveloppe de carter (2) entourant les tubes (9), ladite enveloppe de carter comportant une entrée (6) et une sortie (7) pour le deuxième milieu, où des tôles ondulées (10) comportant des conduits longitudinaux (10a) sont disposées entre les tubes (9), et les tôles ondulées (10) sont configurées en forme de parallélogramme et laissent, entre les tubes, des zones d'admission et d'évacuation (30, 31) ayant à peu près la forme d'un triangle ou d'un trapèze.
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les tubes sont configurés en particulier comme des tubes plats extrudés.
  3. Echangeur de chaleur selon l'une ou l'autre des revendications précédentes, caractérisé en ce que les tubes présentent à chaque fois plusieurs conduits d'écoulement.
  4. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le bloc d'échangeurs de chaleur présente au moins deux parties terminales.
  5. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'enveloppe du carter est disposée entre deux parties terminales.
  6. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins deux plaques d'une partie terminale sont configurées en formant une seule et même pièce.
  7. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'enveloppe de carter (2) est configurée comme une enveloppe en tôle réalisée en une ou en plusieurs parties.
  8. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'enveloppe de carter (2) est raccordée, par continuité de forme, en particulier brasée à la partie terminale (3, 8) au moins au nombre de un.
  9. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'enveloppe de carter (2) présente une section, pratiquement rectangulaire, comportant quatre côtés (2a, 2b, 2c, 2d).
  10. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'entrée (6) et la sortie (7) sont disposées sur des côtés opposés (2a, 2c) de l'enveloppe de carter (2).
  11. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'entrée (6) et la sortie (7) sont disposées sur le même côté (2a) de l'enveloppe de carter (2).
  12. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'entrée (6) et la sortie (7) sont disposées sur des extrémités opposées de l'enveloppe de carter (2).
  13. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que des chambres de répartition (28) et des chambres collectrices (29) sont formées dans l'enveloppe de carter (2), dans la zone de l'entrée (6) et de la sortie (7).
  14. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les tôles ondulées (10) présentent une dimension longitudinale qui correspond à la distance comprise entre l'entrée (6) et la sortie (7).
  15. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les tôles ondulées (34) sont configurées en forme de rectangle et laissent, entre les tubes (9), une zone d'admission et d'évacuation (35, 36) à peu près de forme rectangulaire.
  16. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'entrée (6) et la sortie (7) sont disposées à l'opposé l'une de l'autre et qu'une paroi de séparation (39) servant à la formation d'une zone d'admission (40) et d'une zone d'évacuation (41) est laissée entre l'entrée (6) et la sortie (7), une section de renvoi (43) étant laissée au niveau de l'extrémité de l'enveloppe de carter, placée à l'opposé de l'entrée (6) et de la sortie (7), et en ce que l'enveloppe de carter peut être traversée, côté secondaire, par au moins deux flux circulant dans la direction longitudinale (P1, P3).
  17. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le deuxième milieu est dirigé, à travers le bloc, pratiquement de façon transversale par rapport à la direction longitudinale des tubes.
  18. Echangeur de chaleur selon la revendication 17, caractérisé en ce que le deuxième milieu peut être dévié au moins une fois dans la direction longitudinale, le bloc d'échangeurs de chaleur (60) pouvant être traversé par au moins deux flux.
  19. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'enveloppe de carter (56) forme, avec les tubes ou avec le bloc (47), une chambre d'entrée (57) et une chambre de sortie (58) pour le deuxième milieu, chambres qui s'étendent dans la direction longitudinale des tubes.
  20. Echangeur de chaleur selon la revendication 19, caractérisé en ce que des conduits d'entrée et de sortie (53, 54) pour le deuxième milieu sont disposés sur les parties terminales (48, 51), conduits d'entrée et de sortie qui communiquent avec les chambres d'entrée ou de sortie (57, 58).
  21. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins une boîte de renvoi (63, 64) est disposée dans l'enveloppe de carter, et au moins une paroi de séparation (61, 62) s'étendant transversalement est disposée entre les tubes.
  22. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que, entre les tubes, sont disposées des ailettes ondulées ou des pièces intercalaires de turbulence qui forment des conduits transversaux pour le deuxième milieu.
  23. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le bloc d'échangeurs de chaleur (11) peut être traversé, côté primaire, par un seul flux.
  24. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le bloc d'échangeurs de chaleur (11, 47) peut être traversé, côté primaire, par deux flux ou plus.
  25. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier milieu est un fluide frigorigène pouvant fonctionner en particulier en deux phases ou bien de façon supercritique.
  26. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le deuxième milieu est liquide et, en particulier, un agent de refroidissement liquide.
EP04765083A 2003-10-17 2004-09-10 Echangeur de chaleur, en particulier pour vehicules automobiles Expired - Lifetime EP1682840B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10349150A DE10349150A1 (de) 2003-10-17 2003-10-17 Wärmeübertrager, insbesondere für Kraftfahrzeuge
PCT/EP2004/010158 WO2005038375A1 (fr) 2003-10-17 2004-09-10 Echangeur de chaleur, en particulier pour vehicules automobiles

Publications (2)

Publication Number Publication Date
EP1682840A1 EP1682840A1 (fr) 2006-07-26
EP1682840B1 true EP1682840B1 (fr) 2009-04-01

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EP04765083A Expired - Lifetime EP1682840B1 (fr) 2003-10-17 2004-09-10 Echangeur de chaleur, en particulier pour vehicules automobiles

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US (1) US20070056720A1 (fr)
EP (1) EP1682840B1 (fr)
JP (1) JP2007508519A (fr)
KR (1) KR20060113897A (fr)
AT (1) ATE427468T1 (fr)
DE (2) DE10349150A1 (fr)
WO (1) WO2005038375A1 (fr)

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CN113251831A (zh) * 2021-04-30 2021-08-13 三花控股集团有限公司 换热器及换热模块
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Also Published As

Publication number Publication date
WO2005038375A1 (fr) 2005-04-28
KR20060113897A (ko) 2006-11-03
DE10349150A1 (de) 2005-05-19
EP1682840A1 (fr) 2006-07-26
ATE427468T1 (de) 2009-04-15
DE502004009282D1 (de) 2009-05-14
US20070056720A1 (en) 2007-03-15
JP2007508519A (ja) 2007-04-05

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