DE10349150A1 - Heat exchanger, in particular for motor vehicles - Google Patents

Heat exchanger, in particular for motor vehicles

Info

Publication number
DE10349150A1
DE10349150A1 DE2003149150 DE10349150A DE10349150A1 DE 10349150 A1 DE10349150 A1 DE 10349150A1 DE 2003149150 DE2003149150 DE 2003149150 DE 10349150 A DE10349150 A DE 10349150A DE 10349150 A1 DE10349150 A1 DE 10349150A1
Authority
DE
Germany
Prior art keywords
heat exchanger
characterized
exchanger according
preceding
inlet
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.)
Withdrawn
Application number
DE2003149150
Other languages
German (de)
Inventor
Walter Dipl.-Ing. Demuth (Fh)
Michael Kohl
Martin Dipl.-Ing. Kotsch
Michael Dipl.-Ing. Kranich
Karl-Heinz Dipl.-Ing. Staffa
Christoph Dipl.-Ing. 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
Priority to DE2003149150 priority Critical patent/DE10349150A1/en
Publication of DE10349150A1 publication Critical patent/DE10349150A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02Header boxes; End plates
    • F28F9/026Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278Header 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16Heat-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
    • F28D7/1684Heat-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
    • F28D7/1692Heat-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025Elements 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2309/00Gas cycle refrigeration machines
    • F25B2309/06Compression machines, plant or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061Compression machines, plant or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B39/00Evaporators; Condensers
    • F25B39/02Evaporators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B9/00Compression machines, plant, or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002Compression machines, plant, or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008Compression machines, plant, or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Abstract

The invention relates to a heat exchanger (1), in particular for a motor vehicle having a heat exchanger block which can be flowed through on the primary side by a first medium and can be flowed around on the secondary side by a second medium, and with a housing jacket having an inlet and an outlet for a second medium.

Description

  • The Invention relates to a heat exchanger, especially for Motor vehicles, with a primary side permeable by a first medium and secondary side by a second medium umströmbaren Heat exchanger block.
  • Such a heat exchanger is in the DE 102 60 030 A1 described. 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. The supply of the refrigerant via a manifold, which is connected to an end piece - analogously, the discharge of the refrigerant via another collecting tube, which is attached either to the same end piece or to the opposite end piece. By this construction, 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.
  • the across from It is an object of the present invention, the application possibilities such a heat exchanger to expand.
  • The solution of this object is achieved by the features of claim 1. According to the invention, 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. This results, for example, using the in the DE 102 60 030 A1 , the content of which is hereby expressly part of the disclosure, described heat exchanger block and a relatively easy to produce housing casing further applications for the heat exchanger according to the invention, especially in a heat pump process with the refrigerant CO2. Consumption-optimized engines supply too little 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 cycle both as a CO2 evaporator, which absorbs heat from the coolant, as well as a CO2 gas cooler, which gives off heat to the coolant. The housing shell, which can be produced as a sheet metal part, allows many variations with regard to the flow of the coolant, so that a DC, countercurrent, cross flow and DC / countercurrent flow is possible. Thus, the most diverse requirements for the heat exchanger according to the invention can be taken into account.
  • Further Embodiments of the invention are specified in the subclaims.
  • To Advantageous embodiments of the invention, the inlet and the outlet for the second Medium on the same side, on opposite sides and on opposite ends of the housing shell be arranged, wherein the housing shell is flowed through in particular in the longitudinal direction. This results in the possibility of DC and the countercurrent of the first and second medium.
  • To An advantageous development of the invention are in the field formed by inlet and outlet distribution and collection chambers in the housing shell, so that the second medium evenly over the single column distributed between the tubes or at the exit is collected.
  • To Another embodiment of the invention are between the tubes so-called turbulence inserts or corrugated fins arranged, the longitudinal channels and thus a guide longitudinal the pipes for form the second medium. Advantageously, these extend Turbulence inserts only between the inlet and the outlet of the second medium, so that in the area of inlet and outlet in each case an inflow and a Leave outflow area are in which a cross flow of the second medium, d. H. take place transversely to the longitudinal direction of the tubes can.
  • To a further advantageous embodiment of the invention are the Pipes from the second medium can also be overflowed in the transverse direction, namely one or more flooded. This can be done by arranging side collecting boxes and dividing walls in Connection with deflection boxes in the housing jacket respectively. The turbulence inserts or the ribbing between the Tubes is then designed so that cross channels to guide the second medium. This ensures that both media, for example, a refrigerant and a coolant, can be performed in cross-DC or cross-countercurrent. This gives a more intense heat exchange.
  • In a further advantageous embodiment of the invention, the first medium can be guided both single-flow and double-flow through the pipes who , wherein the inlet and outlet chambers for the first medium are arranged either at an end piece or at different end pieces. Thus, with 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.
  • embodiments The invention are illustrated in the drawings and will be described in more detail below. Show it
  • 1 a refrigerant / coolant heat exchanger with housing shell,
  • 1a the heat exchanger according to 1 without casing,
  • 1b the heat exchanger according to 1a in an exploded view,
  • 1c a schematic representation of the refrigerant connection,
  • 2 a heat exchanger with obliquely cut ribbing and deflection of the refrigerant (double-flow),
  • 2a the heat exchanger according to 2 , but without diverting the refrigerant (single-flow),
  • 3 a heat exchanger with a right-angled ribbing and a double-flow refrigerant flow,
  • 3a the heat exchanger according to 3 , but with one-flow refrigerant flow,
  • 4 a heat exchanger with double-flow coolant flow in the longitudinal direction,
  • 5 a cross section through a heat exchanger with a view of the end faces of the flat tubes,
  • 6 a longitudinal section through a flat tube with end pieces;
  • 7 a further embodiment of a heat exchanger with transversely guided coolant guide,
  • 8th a further embodiment of a heat exchanger with transversely guided and doubly diverted coolant flow.
  • 1 shows a refrigerant / coolant heat exchanger 1 , ie a heat exchanger, the primary side of a refrigerant, eg. 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. Thus, the cooling circuit of the internal combustion engine and the refrigerant circuit of a vehicle air conditioning system are in heat exchange with each other via this heat exchanger. The refrigerant circuit, when operated in the heat pumping process, can be used as a heat source for heating the passenger compartment. Heat is removed from the coolant in the evaporator, "pumped" to a higher temperature level and returned to the coolant in the gas cooler as a heat input. In this respect, this heat exchanger 1 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 shell 2 on, which is approximately box-shaped and four longitudinal sides 2a - 2d has, of which the long side 2a and 2 B are visible in the drawing. The housing jacket 2 is closed at the end by end pieces, of which in the drawing, only the tail 3 is visible. At this tail 3 are a refrigerant inlet pipe 4 and a refrigerant outlet pipe 5 attached. On opposite sides of the housing shell 2 are a coolant inlet nozzle 6 (only partially visible) and a coolant outlet 7 arranged. As already mentioned, the heat exchanger 1 on the one hand connected to a not shown refrigerant, in particular CO2 cycle and on the other hand to a cooling circuit, not shown, of an internal combustion engine of a motor vehicle.
  • 1a shows the heat exchanger 1 according to 1 without housing jacket 2 , wherein like reference numerals are used for the same parts. The tail 3 at which the refrigerant collecting pipes 4 . 5 are attached, lies an end piece 8th opposite, which through a variety of flat tubes 9 with the tail 3 connected is. On the top flat tube 9.1 is a corrugated iron 10 with in the longitudinal direction of the flat tubes 9 extending longitudinal channels 10a arranged. The profile of the corrugated sheet can - as shown in the drawing - formed trapezoidal be, but also other forms, eg. B. sinusoidal or triangular profile. The corrugated iron 10 does not extend over the entire length of the flat tubes 9 from the left tail 3 to the right end piece 8th , but each has an oblique leading edge on the front side 10b . 10c on. corrugated sheets 10 are - which is not visible in this illustration - each between adjacent flat tubes 9 arranged so that there is a longitudinal guidance of the coolant 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. Also, sheets with transverse coolant channels can be used to increase the surface area and thus to increase the efficiency of the heat exchanger.
  • In the due to the oblique bleed 10b . 10c remaining areas a cross flow of the coolant is possible. The refrigerant flow - which will be explained in more detail below - takes place from the inlet pipe 4 over the tail 3 , which acts as a distribution unit, on the flat tubes 9 to the second end piece 8th , which acts as a deflection unit, back through the flat tubes 9 to the outlet pipe 5 , This refrigerant unit is as a heat exchanger block 11 or briefly as a block 11 designated.
  • 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 DE 102 60 030 A1 is thus fully included in the disclosure of this application.
  • The block 11 consists of several parallel flat tubes 9 with flat tube ends 9a . 9b , each in a base plate 12 . 13 attached and sealed. Over the floor plates 12 . 13 are each distribution or deflection plates 14 . 15 arranged by a respective end plate 16 . 17 be covered. In the front cover plate 16 are refrigerant inlet openings 16a and refrigerant outlets 16b in a row with the refrigerant inlet pipe 4 and the refrigerant outlet pipe 5 arranged. The bottom plate 12 , Baffle plate 14 and cover plate 16 thus form the tail 3 while the tail 8th from the bottom plate 13 , the diverter plate 15 and the cover plate 17 composed. As stated in the earlier application, the construction of the end pieces 3 . 8th 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 distributor or baffle plates 14 . 15 ,
  • 1c shows a schematic representation of the refrigerant connection, ie the flow of the refrigerant according to 1b , For details, reference is made to the earlier application, which - as stated above - has been made in full to the subject of this application. That via the refrigerant inlet pipe 4 entering, over the inlet openings 16a , distributed refrigerant enters the flat tubes 9 ie their right strand 18 , is in the deflection unit or the tail 8th by means of the baffle plate 15 in the direction of the arrow 19 deflected and then passes in the adjacent flat tube in the right strand 20 back to the bottom plate 12 where it is in the direction of the arrow 21 by means of the baffle plate 14 on the left strand 22 to be led. Thus, the refrigerant returns to the tail 8th where it is in the direction of the arrow 23 by means of the baffle plate 15 is deflected up to the strand 24 to flow back again. Over the baffle plate 14 , the refrigerant outlet 16b and the refrigerant outlet pipe 5 the refrigerant leaves the block 11 , The refrigerant outlet 16b are larger than the refrigerant inlet openings 16a because of this block 11 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.
  • As already mentioned and in the older one Registration executed, are other refrigerant interconnect variants possible.
  • 2 shows a refrigerant / coolant heat exchanger 25 in longitudinal section, the heat exchanger 1 in 1 corresponds; therefore, like reference numerals are used for like parts. The housing jacket 2 encloses the entire block 11 , consisting of flat tubes 9 and tails 3 . 8th , wherein the housing shell 2 in the area of the end pieces 3 . 8th has a paragraph, to each of which a widened area 26 . 27 connects that the tails 3 . 8th circumferentially includes and sealed against this, z. B. by soldering. On opposite sides 2a . 2c of the housing jacket 2 are the coolant inlet nozzle 6 and the coolant outlet 7 arranged, each via a distribution chamber 28 or a collection chamber 29 in the housing shell 2 pass. As a result, a distribution of the coolant over the entire width is ensured. The sectional view shows the flat tubes 9 from its longitudinal or broad side and thus also the corrugated iron 10 with longitudinal channels 10a , The corrugated iron 10 has - as already mentioned - oblique gate edges 10b . 10c on, so that inflow and outflow areas 30 . 31 arise, in which a cross flow of the coolant from the inlet nozzle 6 and in the direction of the outlet nozzle 7 is possible. Such inflow areas 30 and Auströmbereiche 31 are each between adjacent flat tubes 9 , Immediately behind the inflow area 30 the coolant is deflected approximately at right angles and flows through the heat exchanger 25 in the longitudinal direction, which is indicated by the arrow P. The refrigerant flows through the heat exchanger 25 as before for 1b and 1c described. Refrigerant and coolant are thus essentially (apart from the deflections) guided in cocurrent and countercurrent.
  • 2a shows a variant 32 the heat exchanger 25 out 2 The refrigerant guide is changed insofar as the refrigerant inlet pipe 4 ' at the tail 3 ' and the refrigerant outlet pipe 5 ' at the tail 8th' are located. This means that the refrigerant is substantially single-flow, ie in one direction through the heat exchanger 32 is guided while the coolant is guided according to the arrow P in the opposite direction. However, 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.
  • 3 shows a further embodiment of a heat exchanger 33 in which a rectangular cut corrugated metal sheet 34 with longitudinal channels 34a is provided. The coolant inlet nozzle 6 and the coolant outlet 7 are on the same page 2a arranged the housing shell. Between tail 8th and corrugated iron 34 results in the area of the inlet nozzle 6 an approximately rectangular inflow area 35 and in the area of the outlet nozzle 7 a corresponding outflow area 36 , Here, too, a cross flow of the coolant is possible while the heat exchanger 33 otherwise flows through in the longitudinal direction according to the arrow P. 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 2 ie refrigerant inlet tube 4 and refrigerant outlet pipe 5 are at the same tail 3 arranged.
  • 3a shows a variant 37 of the heat exchanger 33 to 3 , Different from the heat exchanger 33 is only the refrigerant guide, the in 2a corresponds, ie the refrigerant inlet pipe 4 ' is at the tail 3 ' and the refrigerant outlet pipe 5 ' is at the tail 8th' attached. This essentially results in a counterflow between the refrigerant and the coolant, which flows in the longitudinal direction according to the arrow P.
  • 4 shows a further embodiment of a heat exchanger 38 , wherein the refrigerant guide analogous to the embodiments in 2 and 3 takes place, ie it becomes a block 11 according to 1b used. The coolant inlet nozzle 6 and the coolant outlet 7 lie directly opposite each other at the same height, ie they are both in the area of the end piece 3 arranged. Between inlet nozzle 6 and outlet nozzle 7 is in the middle a partition 39 arranged, which has an inflow area 40 on the side of the inlet 6 and a discharge area 41 on the side of the outlet nozzle 7 demarcates. The partition 39 is in each case arranged between adjacent flat tubes. A corrugated iron 42 with longitudinal channels 42a closes to the partition 39 and extends to a deflection area 43 , The corrugated iron 42 has - as stated above - an approximately trapezoidal profile, which is in each case soldered to the adjacent flat tubes. This results in discrete longitudinal channels 42a formed, ie a transverse flow between the longitudinal channels 42a can not. The coolant thus flows out of the inflow region 40 first in the upper half of the heat exchanger 38 , following the arrow P1, into the deflection area 43 , where it is deflected according to the arrow P2 by 180 degrees, ie in the opposite direction. It then flows in the lower half of the heat exchanger 38 , following the arrow P3, back into the outflow area 41 and leaves there via the outlet nozzle 7 the heat exchanger 38 ,
  • The coolant thus sets - in comparison to the previous embodiments - the double way in the heat exchanger 38 back, so that an intense heat exchange with the refrigerant takes place. Likewise, a four- or (even) multi-flow through the heat exchanger for the refrigerant is possible.
  • Also here we can the corrugated sheets 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 elevated one Heat transfer possible is. Also here are sheets with transverse coolant channels for Magnification of the surface and thus to an increase the efficiency of the heat exchanger used.
  • 5 shows a cross section through a heat exchanger 44 , which is the heat exchanger in 2 matches, with the tail 3 is omitted. You can therefore see directly on the front sides of the flat tubes 9 , which are extruded multi-chamber tubes with circular flow channels 45 are formed. Between adjacent flat tubes 9 is each a corrugated iron 10 arranged with trapezoidal profile and with the flat tubes 9 soldered. There through are discrete longitudinal channels 10a formed for the coolant. 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.
  • In the event that no deflection of the coolant - as in 4 shown - is provided, but only a single-flow, are no discrete longitudinal channels 10a necessary, rather, a cross-connection between the individual longitudinal channels may be desired. This can be realized by so-called turbulence plates, not shown, in which the trapezoidal profile is offset in each case according to certain longitudinal sections, so that there are new leading edges and thus increased turbulence. The housing jacket 2 is here as a U-shaped frame with a heel and a widening 26 formed, in which the end piece, not shown, is used. The heat exchanger block 11 (see. 1a . 1b ) can thus easily into the housing 2 used and closed by a lid, not shown. The at the Einstrittsstutzen 6 subsequent 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 on. This results in a distribution of the coolant between all flat tubes 9 possible and also collecting the coolant in the collection chamber 29 on the exit side.
  • 6 shows a longitudinal section through a flat tube 9 , which with its flat tube end 9a in the tail 3 and its flat tube end 9b in the tail 8th is included. The two tails 3 . 8th are like in 1b illustrated, formed. This design for the flat tubes 9 with the tails 3 . 8th Single plates are particularly suitable for high pressures as they occur in the CO2 refrigerant process.
  • 7 shows a further embodiment of a heat exchanger 46 with a changed coolant guide. A refrigerant block 47 is in principle similar in structure to the block 11 according to 1b ie it has a first end piece 48 with refrigerant inlet pipe 49 and refrigerant outlet pipe 50 as well as a second tail 51 on, in which the deflection of the refrigerant takes place. The tail 48 has a laterally extended bottom plate 52 on, at which a coolant inlet channel 53 is attached. Also the tail 51 has an extended bottom plate 54 on, on which a coolant outlet channel 55 is attached. A housing shell 56 encloses the block 47 and each forms a wedge-shaped coolant inlet chamber 57 and a coolant exit chamber 58 , The coolant passes through the inlet channel 53 into the entrance chamber 57 and from there between the column of the flat tubes of the block 47 , flows through it in the transverse direction according to the arrows P4, enters the outlet chamber 58 and from there into the coolant outlet channel 55 , This construction is a simple cross-flow of the block 47 possible. To increase the heat transfer can - which is not shown here - in turn 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.
  • 8th 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 it is in 6 is illustrated. A refrigerant block 60 is through two partitions 61 . 62 divided into three flow areas I, II, III. The areas I, II are through a deflection chamber 63 and the areas II, III through a further deflection chamber 64 connected on the opposite side. The coolant enters via an inlet connection 65 - Also shown only schematically - in the area I of the block 60 A, is in the deflection chamber 63 deflected, then flows through the area II in the deflection chamber 64 , is redirected there again and finally enters the area III, which it via an outlet nozzle 66 leaves. Inlet and outlet nozzles 55 . 66 as well as deflection chambers 63 . 64 are part of a housing shell, not shown, which the block 60 surrounds. By this flow guidance, according to the arrows P5, P6, P7, the coolant is three times across the block 60 guided; This results in a crossflow between the refrigerant and the coolant. Of course, also - which is not shown here - only a simple deflection with a partition and a deflection box and a three and multiple deflection of the coolant possible.
  • The Embodiments described above for refrigerant / coolant heat exchangers are preferred soldered, especially for the flowed through by CO2 Block applies. The housing jacket against it could - because of the significant lower pressure of the coolant - also through alternative bonding techniques, z. B. by gluing or rubber seals with the block or its tails get connected. Here comes for the housing shell also other materials, such as plastic, in question.
  • The invention has been explained using the example of a refrigerant / coolant heat exchanger, but also includes other heat exchangers. Beispielswei se is a heat exchanger according to the invention of oil and / or air can flow through, which exchange heat with each other or with other media.

Claims (28)

  1. Heat exchanger, in particular for a motor vehicle, with a heat exchanger block ( 11 ), which can be flowed through on the primary side by a first medium and on the secondary side by a second medium umströmbare tubes ( 9 ) with flow channels ( 45 ) and pipe ends ( 9a . 9b ), at least one of the pipe ends ( 9a . 9b ) receiving end piece ( 3 . 8th ) each with at least one base plate ( 12 . 13 ), Baffle ( 14 . 15 ) and cover plate ( 16 . 17 ) and at least one with one or one end piece ( 3 . 8th ) connected inlet and / or outlet chamber ( 4 . 5 ), wherein the first medium from the inlet chamber ( 4 ) through the flow channels ( 45 ) to the outlet chamber ( 5 ) is conductive, and with a the pipes ( 9 ) enclosing Ge housing jacket ( 2 ) with an inlet ( 6 ) and an outlet ( 7 ) for the second medium.
  2. Heat exchanger according to claim 1, characterized in that the tubes are extruded in particular Flat tubes are formed.
  3. Heat exchanger according to one of the preceding claims, characterized that the tubes each have a plurality of flow channels.
  4. Heat exchanger according to one of the preceding claims, characterized that the heat exchanger block at least two tails having.
  5. Heat exchanger according to one of the preceding claims, characterized that the housing shell between two end pieces is arranged.
  6. Heat exchanger according to one of the preceding claims, characterized in that at least two plates of an end piece are formed in one piece.
  7. Heat exchanger according to one of the preceding claims, characterized in that the housing jacket ( 2 ) is designed as a one-piece or multi-part sheet metal jacket.
  8. Heat exchanger according to one of the preceding claims, characterized in that the housing jacket ( 2 ) with the at least one end piece ( 3 . 8th ) is materially connected, in particular soldered.
  9. Heat exchanger according to one of the preceding claims, characterized in that the housing jacket ( 2 ) has a substantially rectangular cross section with four sides ( 2a . 2 B . 2c . 2d ) having.
  10. Heat exchanger according to one of the preceding claims, characterized in that the inlet ( 6 ) and the outlet ( 7 ) on opposite sides ( 2a . 2c ) of the housing shell ( 2 ) are arranged.
  11. Heat exchanger according to one of the preceding claims, characterized in that the inlet ( 6 ) and the outlet ( 7 ) on the same page ( 2a ) of the housing shell ( 2 ) are arranged.
  12. Heat exchanger according to one of the preceding claims, characterized in that the inlet ( 6 ) and the outlet ( 7 ) at opposite ends of the housing shell ( 2 ) are arranged.
  13. Heat exchanger according to one of the preceding claims, characterized in that in the region of inlet and outlet ( 6 . 7 ) Distribution and collection chambers ( 28 . 29 ) in the housing shell ( 2 ) are formed.
  14. Heat exchanger according to one of the preceding claims, characterized in that between the tubes ( 9 ) Corrugated sheets ( 10 ) with longitudinal channels ( 10a ) are arranged.
  15. Heat exchanger according to claim 14, characterized in that the corrugated sheets ( 10 ) have a longitudinal extent which corresponds to the distance between inlet ( 6 ) and outlet ( 7 ) corresponds.
  16. Heat exchanger according to one of the preceding claims, characterized in that the corrugated sheets ( 34 ) are rectangular in shape and have an approximately rectangular inflow and outflow area ( 35 . 36 ) between the pipes ( 9 ).
  17. Heat exchanger according to one of the preceding claims, characterized in that the corrugated sheets ( 10 ) are formed parallelogrammför mig and about triangular or trapezoidal inflow and outflow areas ( 30 . 31 ) between the pipes ( 9 ).
  18. Heat exchanger according to one of the preceding claims, characterized in that the inlet ( 6 ) and the outlet ( 7 ) are arranged opposite one another and that between inlet ( 6 ) and outlet ( 7 ) a partition wall ( 39 ) for forming an inflow region ( 40 ) and an outflow area ( 41 ) and at the inlet and outlet ( 6 . 7 ) facing away from the housing shell a deflection ( 43 ) is left and that the housing jacket on the secondary side at least two bends in the longitudinal direction (P1, P3) can be flowed through.
  19. Heat exchanger according to one of the preceding claims, characterized in that the second medium substantially transversely to the longitudinal direction of the tubes through the block ( 47 ) is guided.
  20. Heat exchanger according to claim 19, characterized in that the second medium at least once deflected in the longitudinal direction and the heat exchanger block ( 60 ) can be flowed through at least twice.
  21. Heat exchanger according to one of the preceding claims, characterized in that the housing jacket ( 56 ) with the tubes or the block ( 47 ) an inlet chamber ( 57 ) and an exit chamber ( 58 ) forms for the second medium, which extend in the longitudinal direction of the tubes.
  22. Heat exchanger according to claim 21, characterized in that at the end pieces ( 48 . 51 ) Entry and exit channels ( 53 . 54 ) are arranged for the second medium, with the inlet and outlet chambers ( 57 . 58 ) communicate.
  23. Heat exchanger according to one of the preceding claims, characterized in that in the housing shell at least one deflection box ( 63 . 64 ) and between the tubes at least one transverse partition ( 61 . 62 ) are arranged.
  24. Heat exchanger according to one of the preceding claims, characterized that arranged between the tubes corrugated ribs or turbulence inserts are the cross channels for the form second medium.
  25. Heat exchanger according to one of the preceding claims, characterized in that the heat exchanger block ( 11 ) is flooded on the primary side in one flow.
  26. Heat exchanger according to one of the preceding claims, characterized in that the heat exchanger block ( 11 . 47 ) on the primary side can flow through two or more flooded.
  27. Heat exchanger according to one of the preceding claims, characterized that the first medium is a particular biphasic or supercritical operable refrigerant is.
  28. Heat exchanger according to one of the preceding claims, characterized that the second medium is liquid and in particular a liquid coolant is.
DE2003149150 2003-10-17 2003-10-17 Heat exchanger, in particular for motor vehicles Withdrawn DE10349150A1 (en)

Priority Applications (1)

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DE2003149150 DE10349150A1 (en) 2003-10-17 2003-10-17 Heat exchanger, in particular for motor vehicles

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Application Number Priority Date Filing Date Title
DE2003149150 DE10349150A1 (en) 2003-10-17 2003-10-17 Heat exchanger, in particular for motor vehicles
EP20040765083 EP1682840B1 (en) 2003-10-17 2004-09-10 Heat exchanger in particular for motor vehicles
JP2006534610A JP2007508519A (en) 2003-10-17 2004-09-10 Heat transfer body for automobile
DE200450009282 DE502004009282D1 (en) 2003-10-17 2004-09-10 Heat transmitter, especially for motor vehicles
KR1020067007400A KR20060113897A (en) 2003-10-17 2004-09-10 Heat exchanger, in particular for motor vehicles
US10/575,890 US20070056720A1 (en) 2003-10-17 2004-09-10 Heat exchanger in particular for motor vehicles
AT04765083T AT427468T (en) 2003-10-17 2004-09-10 Warm transmitter, especially for motor vehicles
PCT/EP2004/010158 WO2005038375A1 (en) 2003-10-17 2004-09-10 Heat exchanger in particular for motor vehicles

Publications (1)

Publication Number Publication Date
DE10349150A1 true DE10349150A1 (en) 2005-05-19

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DE2003149150 Withdrawn DE10349150A1 (en) 2003-10-17 2003-10-17 Heat exchanger, in particular for motor vehicles
DE200450009282 Active DE502004009282D1 (en) 2003-10-17 2004-09-10 Heat transmitter, especially for motor vehicles

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DE200450009282 Active DE502004009282D1 (en) 2003-10-17 2004-09-10 Heat transmitter, especially for motor vehicles

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US (1) US20070056720A1 (en)
EP (1) EP1682840B1 (en)
JP (1) JP2007508519A (en)
KR (1) KR20060113897A (en)
AT (1) AT427468T (en)
DE (2) DE10349150A1 (en)
WO (1) WO2005038375A1 (en)

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DE102005012761A1 (en) * 2005-03-19 2006-09-21 Modine Manufacturing Co., Racine Intercooler for motor vehicle supercharger has flat tubes with manifolds, and cover and side sections brazed into place
DE102005013922A1 (en) * 2005-03-26 2006-09-28 Modine Manufacturing Co., Racine Heat exchanger e.g. intercooler, for motor vehicle, has frames provided at ends of stack of heat exchanging plates, where region of plates between holes is formed on side of flow path as heat exchanging region or as open channel section
DE102006005362A1 (en) * 2006-02-07 2007-08-09 Modine Manufacturing Co., Racine Exhaust gas heat exchanger in an exhaust gas recirculation arrangement
DE102006046671A1 (en) * 2006-09-29 2008-04-03 Behr Gmbh & Co. Kg Plate construction heat exchanger, especially evaporator for motor vehicle air conditioning, has at least one equal medium distribution arrangement close to deflection openings that causes uniform medium flow distribution on flat pipes
US8915292B2 (en) 2006-02-07 2014-12-23 Modine Manufacturing Company Exhaust gas heat exchanger and method of operating the same
DE202018101360U1 (en) * 2018-03-12 2019-06-13 Autokühler GmbH & Co. KG heat exchangers

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FR2906357B1 (en) * 2006-09-21 2013-01-18 Valeo Systemes Thermiques Liquid / gas type heat exchanger, in particular for a motor vehicle air conditioning equipment using a supercritical operating refrigerant fluid such as co2
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EP2090851A1 (en) * 2008-02-15 2009-08-19 Delphi Technologies, Inc. Heat exchanger with a mixing chamber
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JP5061065B2 (en) * 2008-08-26 2012-10-31 昭和電工株式会社 Liquid cooling system
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JP2011091301A (en) * 2009-10-26 2011-05-06 Showa Denko Kk Liquid cooling type cooling device
CN101956600A (en) * 2010-09-29 2011-01-26 芜湖中宇散热器有限公司 Intercooler on refit vehicle
DE102012208771A1 (en) * 2012-05-24 2013-11-28 Behr Gmbh & Co. Kg Heat exchanger for tempering a first fluid using a second fluid
FR3006432B1 (en) * 2013-05-28 2017-12-08 Delphi Automotive Systems Lux Heat exchanger
US20160215735A1 (en) * 2013-09-11 2016-07-28 International Engine Intellectual Property Company, Llc Thermal screen for an egr cooler
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DE102005012761A1 (en) * 2005-03-19 2006-09-21 Modine Manufacturing Co., Racine Intercooler for motor vehicle supercharger has flat tubes with manifolds, and cover and side sections brazed into place
DE102005013922A1 (en) * 2005-03-26 2006-09-28 Modine Manufacturing Co., Racine Heat exchanger e.g. intercooler, for motor vehicle, has frames provided at ends of stack of heat exchanging plates, where region of plates between holes is formed on side of flow path as heat exchanging region or as open channel section
DE102006005362A1 (en) * 2006-02-07 2007-08-09 Modine Manufacturing Co., Racine Exhaust gas heat exchanger in an exhaust gas recirculation arrangement
US8020610B2 (en) 2006-02-07 2011-09-20 Modine Manufacturing Company Exhaust gas heat exchanger and method of operating the same
US8915292B2 (en) 2006-02-07 2014-12-23 Modine Manufacturing Company Exhaust gas heat exchanger and method of operating the same
DE102006046671A1 (en) * 2006-09-29 2008-04-03 Behr Gmbh & Co. Kg Plate construction heat exchanger, especially evaporator for motor vehicle air conditioning, has at least one equal medium distribution arrangement close to deflection openings that causes uniform medium flow distribution on flat pipes
DE202018101360U1 (en) * 2018-03-12 2019-06-13 Autokühler GmbH & Co. KG heat exchangers

Also Published As

Publication number Publication date
US20070056720A1 (en) 2007-03-15
DE502004009282D1 (en) 2009-05-14
WO2005038375A1 (en) 2005-04-28
EP1682840A1 (en) 2006-07-26
AT427468T (en) 2009-04-15
JP2007508519A (en) 2007-04-05
EP1682840B1 (en) 2009-04-01
KR20060113897A (en) 2006-11-03

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