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WO2005038375A1 - 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
WO2005038375A1
WO2005038375A1 PCT/EP2004/010158 EP2004010158W WO2005038375A1 WO 2005038375 A1 WO2005038375 A1 WO 2005038375A1 EP 2004010158 W EP2004010158 W EP 2004010158W WO 2005038375 A1 WO2005038375 A1 WO 2005038375A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
exchanger according
inlet
outlet
medium
Prior art date
Application number
PCT/EP2004/010158
Other languages
German (de)
English (en)
Inventor
Walter Demuth
Michael Kohl
Martin Kotsch
Michael Kranich
Karl-Heinz Staffa
Christoph Walter
Original Assignee
Behr Gmbh & 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 & Co. Kg filed Critical Behr Gmbh & Co. Kg
Priority to DE502004009282T priority Critical patent/DE502004009282D1/de
Priority to EP04765083A priority patent/EP1682840B1/fr
Priority to US10/575,890 priority patent/US20070056720A1/en
Priority to JP2006534610A priority patent/JP2007508519A/ja
Publication of WO2005038375A1 publication Critical patent/WO2005038375A1/fr

Links

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, with a heat exchanger block through which a first medium can flow and on the secondary side around which a second medium can flow.
  • the heat exchanger there consists, among other things, of flat tubes with flow channels, eg. B. extruded multi-chamber tubes, which are flowed through by a first medium, preferably a refrigerant, in particular CO2.
  • the flat tubes are arranged parallel to one another and have flat tube ends which are held in so-called end pieces, consisting of a base plate, a deflection plate and a cover plate. The end pieces each form a distribution or deflection unit for the refrigerant.
  • the refrigerant is supplied via a manifold, which is connected to an end piece - analogously, the refrigerant is discharged via another manifold, which is either attached to the same end piece or to the opposite end piece.
  • This design creates a particularly pressure-resistant heat exchanger, which can be used in particular in a CO2-operated refrigerant circuit for a motor vehicle air conditioning system, on the one hand as an evaporator and on the other hand as a gas cooler, the secondary side being acted upon by ambient air.
  • a heat exchanger block consisting of tubes and at least one end piece, is surrounded by a housing jacket through which a second medium can be conducted.
  • a heat exchanger block consisting of tubes and at least one end piece, is surrounded by a housing jacket through which a second medium can be conducted.
  • the heat exchanger according to the invention in particular in a heat pump process with the refrigerant CO2 , Consumption-optimized engines do not provide enough heating energy, so that these vehicles require additional heating, so-called auxiliary heating.
  • the coolant for the cooling circuit of the engine is used as a heat source.
  • the heat exchanger according to the invention can be used in this heat pump circuit both as a CO2 evaporator, which absorbs heat from the coolant, and as a CO2 gas cooler, which emits heat to the coolant.
  • the housing jacket which can be manufactured as a sheet metal part, allows many possible variations with regard to the flow of the coolant, so that direct current, counter current, cross current and direct / counter cross current are possible. The most varied requirements for the heat exchangers according to the invention can thus be taken into account.
  • the inlet and the outlet for the second medium can be arranged on the same side, on opposite sides and at opposite ends of the housing shell, with the housing shell flowing through in particular in the longitudinal direction. This results in the possibility of direct current and countercurrent of the first and second medium.
  • distribution and collection chambers are formed in the housing jacket in the area of the inlet and outlet, so that the second medium is distributed evenly over the individual gaps between the pipes or is collected at the outlet.
  • so-called turbulence inserts or corrugated fins 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 only extend between the inlet and the outlet of the second medium, so that an inflow and an outflow region are left in the region of the inlet and outlet, in which a transverse flow of the second medium, i. H. can take place transversely to the longitudinal direction of the tubes.
  • the second medium can also flow over the tubes in the transverse direction, in one or more passages.
  • This can be done by arranging side collection boxes and partition walls in connection with deflection boxes in the housing jacket.
  • the turbulence inserts or the fins between the tubes are then designed in such a way that transverse channels for guiding the second medium result.
  • This ensures that both media, " for example a refrigerant and a coolant, can be carried out in cross-cocurrent or cross-countercurrent. This results in a more intensive heat exchange.
  • the first medium can also be passed through the pipes both in single-flow and double-flow mode, the inlet and outlet chambers for the first medium being arranged either at one end piece or at different end pieces.
  • the heat exchanger according to the invention can thus be used to implement a wide variety of forms and combinations of cocurrent, countercurrent and crossflow between the first and second medium, 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. Embodiments of the invention are shown in the drawing and are described in more detail below. Show it
  • FIG. 1 shows a coolant / coolant heat exchanger with a housing jacket
  • FIG. 1a shows the heat exchanger according to FIG. 1 without a housing jacket
  • FIG. 1b shows the heat exchanger according to FIG. 1a in an exploded view
  • FIG. 1c shows a schematic illustration of the refrigerant circuit
  • FIG. 2 2a shows the heat exchanger according to FIG. 2, but without deflecting the refrigerant (single-flow)
  • FIG. 3 shows a heat exchanger with ribbing cut at right angles and double-flow refrigerant flow
  • FIG. 3a shows the heat exchanger according to FIG 3, but with a single-flow refrigerant flow
  • FIG. 4 shows a heat exchanger with double-flow coolant flow in the longitudinal direction
  • FIG. 5 shows a cross section through a heat exchanger with a view of the end faces of the flat tubes
  • FIG. 8 shows a further embodiment of a heat exchanger with a transversely guided and double-deflected coolant flow.
  • Fig. 1 shows a refrigerant / coolant heat exchanger 1, ie a heat exchanger, the primary side of a refrigerant, for. B. C02 (R744) and the secondary side is flowed through by a coolant, which simultaneously serves to cool an internal combustion engine, not shown, of a motor vehicle.
  • the cooling circuit of the internal combustion engine and the refrigerant circuit of a vehicle air conditioning system are thus in heat exchange with one another via this heat exchanger.
  • the refrigerant circuit when operated in the heat pump process, can be used as a heat source for heating the passenger compartment.
  • the Coolant in the evaporator is extracted from heat, "pumped" to a higher temperature level and returned to the coolant as heat input in the gas cooler.
  • 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 takes place under increased pressure compared to the conventional refrigerant process with R134a: for example, compression takes place up to approx. 120 bar, which therefore occur in the gas cooler, so the heat exchanger must be dimensioned and designed to be particularly pressure-resistant with regard to the refrigerant flow.
  • the heat exchanger 1 has a housing jacket 2, which is approximately box-shaped and has four long sides 2a-2d, of which the long sides 2a and 2b are visible in the drawing.
  • the housing jacket 2 is closed on the end side 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 fastened to this end piece 3.
  • a coolant inlet nozzle 6 are arranged (only partially visible) u ⁇ d ⁇ e. ⁇ "Kühlmittetaustrittsstutzen ⁇ . 7
  • the heat exchanger 1 on the one hand on to an unillustrated refrigerant, in particular CO2 cycle and on the other hand connected a cooling circuit, not shown, of an internal combustion engine of a motor vehicle.
  • FIG. 1 a shows the heat exchanger 1 according to FIG. 1 without the housing jacket 2, the same reference numbers being used for the same parts.
  • the end piece 3, to which the refrigerant manifolds 4, 5 are attached, is opposite an end piece 8, which is connected to the end piece 3 by a plurality of flat pipes 9.
  • a corrugated sheet 10 with longitudinal channels 10a running in the longitudinal direction of the flat tubes 9 is arranged on the uppermost flat tube 9.1.
  • the profile of the corrugated sheet can - as shown in the drawing - be trapezoidal, but other shapes, z. B. have a sine 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 each has an oblique cut edge 10b, 10c on the end face. Corrugated sheets 10 are arranged between adjacent flat tubes 9, which is not visible in this illustration, so that the coolant is guided longitudinally in these areas. Likewise, 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 also be used to increase the surface area and thus to increase the efficiency of the heat exchanger.
  • a cross-flow of the coolant is possible in the areas that remain free due to the oblique gates 10b, 10c.
  • the refrigerant flow - which will be explained in more detail below - takes place from the inlet pipe 4 via the end piece 3, which acts as a distribution unit, to the flat pipes 9 to the second end piece 8, which acts as a deflection unit, back through the flat pipes 9 to the outlet pipe 5
  • Refrigerant unit is referred to as a heat exchanger block 11, or block 11 for short.
  • the block 11 consists of several flat tubes 9 arranged parallel to one another with flat tube ends 9a, 9b, which are each fastened and sealed in a base plate 12, 13. Above the base plates 12, 13 are each. Distribution or deflection plates 14, 15 are arranged, which are each covered by an end plate 16, 17. In the front cover plate 16 there are refrigerant inlet openings 16a and refrigerant outlet openings 16b, arranged in a row with the refrigerant inlet pipe 4 and the refrigerant outlet pipe 5.
  • the base plate 12, deflection plate 14 and cover plate 16 thus form the end piece 3, while the end piece 8 is composed of the base plate 13, the deflection plate 15 and the cover plate 17.
  • the structure of the end pieces 3, 8 can also be modified, e.g. B. bottom and deflection plate or deflection and cover plate can be integrated into one plate. The same applies to the refrigerant guidance, ie through a modified form of the distributor or deflection plates 14, 15.
  • FIG. 1c shows a schematic representation of the refrigerant circuit, i. H. the flow of the refrigerant according to Fig. 1 b.
  • the refrigerant entering via the refrigerant inlet pipe 4 and distributed via the inlet openings 16a reaches the flat tubes 9, ie. H. whose right strand 18 is deflected in the deflection unit or the end piece 8 by means of the deflection plate 15 in the direction of arrow 19 and then passes in the adjacent flat tube in its right strand 20 back to the base plate 12, where it is in the direction of arrow 21 by means of the deflection plate 14 is led to the left strand 22.
  • the middle of the cold thus arrives again at the end piece 8, where it is deflected upward in the direction of arrow 23 by means of the deflection plate 15 in order to flow back again in the strand 24.
  • the refrigerant leaves the block 11 via the deflection plate 14, the refrigerant outlet opening 16b and the refrigerant outlet pipe 5.
  • the refrigerant outlet opening 16b is larger than the refrigerant inlet openings 16a because this block 11 is designed as an evaporator (with increasing specific volume); a gas cooler would have a different configuration, for example with the same inlet and outlet openings.
  • the refrigerant circuit described above therefore applies to two flat tubes lying next to each other.
  • Fig. 2 shows a refrigerant / coolant heat exchanger 25 in longitudinal section, which corresponds to the heat exchanger 1 in Fig. 1; therefore the same reference numerals are used for the same parts.
  • the housing jacket 2 encloses the entire block 11, consisting of flat tubes 9 and end pieces 3, 8, the housing jacket 2 having a shoulder in the region of the end pieces 3, 8, to each of which a widened region 26, 27 adjoins the End pieces 3, 8 includes the circumference and is sealed against this, for. B. by soldering.
  • the coolant inlet connector 6 and the coolant outlet connector 7 are arranged on opposite sides 2a, 2c of the housing jacket 2, each of which merges into the housing jacket 2 via a distribution chamber 28 and a collecting chamber 29. This ensures that the coolant is distributed over the entire width.
  • the sectional view shows the flat tubes 9 from their long and wide sides and thus also the corrugated sheet 10 with longitudinal channels 10 a.
  • the corrugated sheet 10 has oblique cut edges 10b, 10c, so that inflow and outflow regions 30, 31 result in which a cross-flow of the coolant from the inlet connection 6 and in the direction of the outlet connection 7 is possible.
  • Such inflow regions 30 and outflow regions 31 are each located between adjacent flat tubes 9.
  • the coolant is deflected approximately at a right angle and flows through the heat exchanger 25 in the “ longitudinal direction; which is indicated by the arrow P. 1b and 1c previously described, refrigerants and coolants are therefore 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 guidance has been changed in that the refrigerant inlet pipe 4 'is at the end piece 3' and the refrigerant outlet pipe 5 'at the end piece 8'.
  • the refrigerant is guided through the heat exchanger 32 essentially in one direction, ie in one direction, while the coolant is guided in the opposite direction according to the arrow P.
  • the refrigerant can also be led through three, five or (odd) multiple flows through the heat transfer. This essentially results in a counterflow between the refrigerant and the coolant.
  • FIG. 1 shows a variant 32 of the heat exchanger 25 from FIG. 2: the refrigerant guidance has been changed in that the refrigerant inlet pipe 4 'is at the end piece 3' and the refrigerant outlet pipe 5 'at the end piece 8'.
  • the refrigerant is guided through the heat exchanger 32 essentially in one direction, ie in one
  • FIG. 3 shows a further exemplary embodiment of a heat exchanger 33, in which a corrugated sheet 34 cut at right angles with longitudinal channels 34a is provided.
  • the coolant inlet connector 6 and the coolant outlet connector 7 are arranged on the same side 2a of the housing jacket. Between the end piece 8 and the corrugated sheet 34 there is an approximately rectangular inflow area 35 in the area of the inlet connection 6 and a corresponding outflow area 36 in the area of the outlet connection 7.
  • a cross-flow of the coolant is also possible here, while the heat exchanger 33 is otherwise corresponding in the longitudinal direction the arrow P is flowed through.
  • the areas 35 and 36 can also be provided with corrugated sheets or other turbulence generators.
  • the refrigerant flow guide corresponds to that 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 according to FIG. 3.
  • the only difference from the heat exchanger 33 is the refrigerant guide which corresponds to that in FIG. 2a, ie the refrigerant inlet pipe 4 'is at the end piece 3' and the refrigerant outlet pipe 5 'is at End piece 8 'fastened.
  • This essentially results in a countercurrent between the refrigerant " ; •" and " refrigerant third " , "” which flows in the longitudinal direction according to the arrow P.
  • FIG. 4 shows a further exemplary embodiment of a heat exchanger 38, in which the refrigerant is guided analogously to the exemplary embodiments in FIGS. 2 and 3, ie a block 11 according to FIG. 1b is used.
  • the coolant inlet connector 6 and the coolant outlet connector 7 are directly opposite one another, ie they are both arranged in the region of the end piece 3.
  • a partition 39 is arranged in the center between the inlet nozzle 6 and the outlet nozzle 7 and delimits an inflow region 40 on the inlet nozzle 6 side and an outflow region 41 on the outlet nozzle 7 side.
  • the partition 39 is arranged between adjacent flat tubes.
  • a corrugated sheet 42 with longitudinal channels 42a adjoins the partition 39 and extends as far as a deflection area 43.
  • the corrugated sheet 42 has an approximately trapezoidal profile, each with the adjacent flat tubes is soldered. As a result, discrete longitudinal channels 42a are formed, ie a cross flow between the longitudinal channels 42a is not possible.
  • the coolant thus flows from the inflow region 40 first 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 and there leaves the heat exchanger 38 via the outlet connection 7.
  • the coolant thus - compared to the previous exemplary embodiments - covers the double path in the heat exchanger 38, so that an intensive heat exchange takes place with the refrigerant.
  • a four or (even number) multi-flow flow through the heat exchanger for the refrigerant is also possible.
  • the corrugated sheets can 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 increased heat transfer is possible.
  • Sheets with transverse cooling center channels can also be used here to increase the surface area and thus to increase the efficiency of the heat exchanger.
  • FIG. 5 shows a cross section through a heat exchanger 44, which corresponds to the heat exchanger in FIG. 2, the end piece 3 being omitted.
  • the flat tubes 9 which are designed as extruded multi-chamber tubes with circular flow channels 45.
  • a corrugated sheet 10 with a trapezoidal profile is arranged and soldered to the flat tubes 9.
  • discrete longitudinal channels 10a for the coolant are formed.
  • These sheets can also be provided with slots and / or offsets in order to enable an exchange between the longitudinal channels for the coolant and thus a more homogeneous distribution and / or turbulence of the coolant.
  • there is no deflection of the coolant as shown in FIG.
  • the housing jacket 2 is designed here as a U-shaped frame with a shoulder and a widening 26, into which the end piece, not shown, is inserted.
  • the heat exchanger block 11 (cf. FIGS. 1 a, 1 b) can thus simply be inserted into the housing 2 and closed by a cover (not shown).
  • the distributor chamber 28 adjoining the inlet connection 6 extends over the entire height of the housing wall 2c; analogously, the collecting chamber 29 on the side of the outlet connection 7 has approximately the height of the side wall 2a. This makes it possible to distribute the coolant between all flat tubes 9 and also to collect the coolant in the collecting chamber 29 on the outlet side.
  • FIG. 6 shows a longitudinal section through a flat tube 9, which is received 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 formed as shown in Fig. 1 b.
  • This design for the flat tubes 9 with the end pieces 3, 8 made of individual plates is particularly suitable for high pressures, such as occur in the CO2 refrigerant process.
  • FIG. 7 shows a further exemplary embodiment of a heat exchanger 46 with a modified coolant guide.
  • a refrigerant block 47 is constructed similarly to the block 11 according to FIG. 1b, ie it has a first end piece 48 with a refrigerant inlet pipe 49 and a refrigerant outlet pipe 50, and a second end piece 51 in which the refrigerant is deflected.
  • the end piece 48 has a laterally elongated base plate 52 to which a coolant inlet channel 53 is attached.
  • the end piece 51 has an elongated base plate 54, to which an uhimitteiausi ⁇ tts- channel 55 is attached.
  • a housing jacket 56 surrounds the block 47 and in each case forms a wedge-shaped coolant inlet chamber 57 and a coolant outlet chamber 58.
  • the coolant enters the inlet chamber 57 through the inlet channel 53 and from there passes between the gaps of the flat tubes of the block 47 and flows through them Transverse direction according to the arrows P4, enters the outlet chamber 58 and from there into the coolant outlet channel 55.
  • This design enables a simple transverse flow through the block 47.
  • corrugated sheets or turbulence inserts can be arranged - which is not shown here - between the individual flat tubes, which guide the coolant in the direction of arrow P4 and generate turbulence.
  • FIG. 8 shows a further exemplary embodiment of a heat exchanger 59 with a coolant flow, which is also guided transversely, but which is only shown schematically. This is illustrated by means of a longitudinal section through a flat tube 9, as shown in FIG. 6.
  • a refrigerant block 60 is divided into three flow areas I, II, III by two partition walls 61, 62.
  • the areas I, II are connected to one another by a deflection chamber 63 and the areas II, III by a further deflection chamber 64 on the opposite side.
  • the coolant enters the area I of the block 60 via an inlet connection 65 - also shown only schematically -, is deflected in the deflection chamber 63, then flows through the area II into the deflection chamber 64, is redirected there and finally reaches the area III, which it leaves via an outlet connection 66.
  • Inlet and outlet ports 55, 66 and deflection chambers 63, 64 are part of a housing jacket, not shown, which surrounds the block 60.
  • the coolant is guided three times across block 60 by this flow guide, in accordance with arrows P5, P6, P7; there is thus a cross flow between the refrigerant and the coolant.
  • a heat exchanger according to the invention can be flowed through by oil and / or air, which exchange heat with one another 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)

Abstract

L'invention concerne un échangeur de chaleur (1), en particulier pour un véhicule automobile, lequel échangeur est composé d'un bloc échangeur de chaleur, traversé, côté primaire, par un premier milieu et contourné, côté secondaire, par un second milieu, ainsi que d'une enveloppe pourvue d'une entrée et d'une sortie pour un second milieu.
PCT/EP2004/010158 2003-10-17 2004-09-10 Echangeur de chaleur, en particulier pour vehicules automobiles WO2005038375A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE502004009282T DE502004009282D1 (de) 2003-10-17 2004-09-10 Wärmeübertrager, insbesondere für kraftfahrzeuge
EP04765083A EP1682840B1 (fr) 2003-10-17 2004-09-10 Echangeur de chaleur, en particulier pour vehicules automobiles
US10/575,890 US20070056720A1 (en) 2003-10-17 2004-09-10 Heat exchanger in particular for motor vehicles
JP2006534610A JP2007508519A (ja) 2003-10-17 2004-09-10 自動車用の熱伝達体

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10349150A DE10349150A1 (de) 2003-10-17 2003-10-17 Wärmeübertrager, insbesondere für Kraftfahrzeuge
DE10349150.3 2003-10-17

Publications (1)

Publication Number Publication Date
WO2005038375A1 true WO2005038375A1 (fr) 2005-04-28

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Family Applications (1)

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

Country Status (7)

Country Link
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)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1724535A2 (fr) 2005-05-10 2006-11-22 Modine Manufacturing Company Echangeur de chaleur intermédiaire
WO2007048603A2 (fr) * 2005-10-26 2007-05-03 Behr Gmbh & Co. Kg Echangeur de chaleur et procede de fabrication d'un echangeur de chaleur
FR2906357A1 (fr) * 2006-09-21 2008-03-28 Valeo Systemes Thermiques Echangeur de chaleur de type liquide/gaz,notamment pour un equipement de climatisation de vehicule automobile utilisant un fluide refrigerant operant a l'etat supercritique tel que co2
EP2090851A1 (fr) * 2008-02-15 2009-08-19 Delphi Technologies, Inc. Échangeur de chaleur doté d'une chambre de mélange
WO2009013179A3 (fr) * 2007-07-23 2009-11-05 M.T.A. S.P.A. Echangeur de chaleur pourvu de minicanaux et/ou de microcanaux et son procédé de fabrication
CN101661914A (zh) * 2008-08-26 2010-03-03 株式会社丰田自动织机 液冷式冷却装置
WO2010108992A1 (fr) * 2009-03-26 2010-09-30 Valeo Systemes Thermiques Echangeur de chaleur, en particulier condenseur de climatisation
CN101956600A (zh) * 2010-09-29 2011-01-26 芜湖中宇散热器有限公司 一种用于改装车上的中冷器
EP2315244A1 (fr) * 2009-10-26 2011-04-27 Kabushiki Kaisha Toyota Jidoshokki Dispositif refroidissant de type refroidissement par liquide
FR3006432A1 (fr) * 2013-05-28 2014-12-05 Delphi Automotive Systems Lux Echangeur de chaleur
DE102014203038A1 (de) 2014-02-19 2015-08-20 MAHLE Behr GmbH & Co. KG Wärmeübertrager
EP4417925A1 (fr) * 2023-02-15 2024-08-21 Valeo Systemes Thermiques Echangeur de chaleur

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DE102005013922A1 (de) * 2005-03-26 2006-09-28 Modine Manufacturing Co., Racine Wärmetauscher, insbesondere Ladeluftkühler
DE102006005362A1 (de) * 2006-02-07 2007-08-09 Modine Manufacturing Co., Racine Abgaswärmetauscher in einer Abgasrückführungsanordnung
US8915292B2 (en) 2006-02-07 2014-12-23 Modine Manufacturing Company Exhaust gas heat exchanger and method of operating the same
DE102006046671A1 (de) * 2006-09-29 2008-04-03 Behr Gmbh & Co. Kg Wärmetauscher in Plattenbauweise, insbesondere Verdampfer für eine Kraftfahrzeug-Klimaanlage
SE532837C2 (sv) * 2008-03-28 2010-04-20 Titanx Engine Cooling Holding Värmeväxlare, såsom en laddluftkylare
DE102012208771A1 (de) * 2012-05-24 2013-11-28 Behr Gmbh & Co. Kg Wärmetauscher zum Temperieren eines ersten Fluids unter Verwendung eines zweiten Fluids
WO2015038111A1 (fr) * 2013-09-11 2015-03-19 International Engine Intellectual Property Company, Llc Écran thermique pour un refroidisseur de recirculation de gaz d'échappement (egr)
JP2019074267A (ja) * 2017-10-17 2019-05-16 イビデン株式会社 熱交換器
DE202018101360U1 (de) * 2018-03-12 2019-06-13 Autokühler GmbH & Co. KG Wärmeaustauscher
WO2019223797A1 (fr) * 2018-05-25 2019-11-28 杭州三花研究院有限公司 Boîte collectrice de tuyau et échangeur de chaleur
DE102018215398A1 (de) * 2018-09-11 2020-03-12 Mahle International Gmbh Elektrische Heizeinrichtung
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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EP1724535A3 (fr) * 2005-05-10 2008-07-02 Modine Manufacturing Company Echangeur de chaleur intermédiaire
EP1724535A2 (fr) 2005-05-10 2006-11-22 Modine Manufacturing Company Echangeur de chaleur intermédiaire
US8967235B2 (en) 2005-10-26 2015-03-03 Behr Gmbh & Co. Kg Heat exchanger, method for the production of a heat exchanger
WO2007048603A2 (fr) * 2005-10-26 2007-05-03 Behr Gmbh & Co. Kg Echangeur de chaleur et procede de fabrication d'un echangeur de chaleur
WO2007048603A3 (fr) * 2005-10-26 2007-08-02 Behr Gmbh & Co Kg Echangeur de chaleur et procede de fabrication d'un echangeur de chaleur
JP2009513921A (ja) * 2005-10-26 2009-04-02 ベール ゲーエムベーハー ウント コー カーゲー 熱交換器、および熱交換器を製造するための方法
FR2906357A1 (fr) * 2006-09-21 2008-03-28 Valeo Systemes Thermiques Echangeur de chaleur de type liquide/gaz,notamment pour un equipement de climatisation de vehicule automobile utilisant un fluide refrigerant operant a l'etat supercritique tel que co2
EP1903293A3 (fr) * 2006-09-21 2008-04-09 Valeo Systèmes Thermiques Echangeur de chaleur de type liquide/gaz, notamment pour un équipement de climatisation de véhicule automobile utilisant un fluide réfrigérant opérant à l'état supercritique tel que CO2
WO2009013179A3 (fr) * 2007-07-23 2009-11-05 M.T.A. S.P.A. Echangeur de chaleur pourvu de minicanaux et/ou de microcanaux et son procédé de fabrication
EP2090851A1 (fr) * 2008-02-15 2009-08-19 Delphi Technologies, Inc. Échangeur de chaleur doté d'une chambre de mélange
WO2009101035A1 (fr) * 2008-02-15 2009-08-20 Delphi Technologies, Inc. Échangeur thermique équipé d’une chambre de mélange
CN101661914A (zh) * 2008-08-26 2010-03-03 株式会社丰田自动织机 液冷式冷却装置
EP2159839A3 (fr) * 2008-08-26 2010-09-08 Kabushiki Kaisha Toyota Jidoshokki Dispositif refroidissant de type refroidissement par liquide
US20100051234A1 (en) * 2008-08-26 2010-03-04 Kabushiki Kaisha Toyota Jidoshokki Liquid-cooled-type cooling device
US9159645B2 (en) 2008-08-26 2015-10-13 Kabushiki Kaisha Toyota Jidoshokki Liquid-cooled-type cooling device
WO2010108992A1 (fr) * 2009-03-26 2010-09-30 Valeo Systemes Thermiques Echangeur de chaleur, en particulier condenseur de climatisation
FR2943776A1 (fr) * 2009-03-26 2010-10-01 Valeo Systemes Thermiques Echangeur de chaleur, en particulier condensateur de climatisation
EP2315244A1 (fr) * 2009-10-26 2011-04-27 Kabushiki Kaisha Toyota Jidoshokki Dispositif refroidissant de type refroidissement par liquide
CN101956600A (zh) * 2010-09-29 2011-01-26 芜湖中宇散热器有限公司 一种用于改装车上的中冷器
FR3006432A1 (fr) * 2013-05-28 2014-12-05 Delphi Automotive Systems Lux Echangeur de chaleur
DE102014203038A1 (de) 2014-02-19 2015-08-20 MAHLE Behr GmbH & Co. KG Wärmeübertrager
EP4417925A1 (fr) * 2023-02-15 2024-08-21 Valeo Systemes Thermiques Echangeur de chaleur

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EP1682840A1 (fr) 2006-07-26
KR20060113897A (ko) 2006-11-03
DE502004009282D1 (de) 2009-05-14
ATE427468T1 (de) 2009-04-15
US20070056720A1 (en) 2007-03-15
JP2007508519A (ja) 2007-04-05
EP1682840B1 (fr) 2009-04-01
DE10349150A1 (de) 2005-05-19

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