EP1717530A2 - Echangeur de chaleur, en particulier évaporateur arrière pour véhicule automobile - Google Patents

Echangeur de chaleur, en particulier évaporateur arrière pour véhicule automobile Download PDF

Info

Publication number
EP1717530A2
EP1717530A2 EP06005937A EP06005937A EP1717530A2 EP 1717530 A2 EP1717530 A2 EP 1717530A2 EP 06005937 A EP06005937 A EP 06005937A EP 06005937 A EP06005937 A EP 06005937A EP 1717530 A2 EP1717530 A2 EP 1717530A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
opening
exchanger according
injection
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.)
Granted
Application number
EP06005937A
Other languages
German (de)
English (en)
Other versions
EP1717530B1 (fr
EP1717530A3 (fr
Inventor
Gottfried Dipl.-Ing. Dürr
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
Publication of EP1717530A2 publication Critical patent/EP1717530A2/fr
Publication of EP1717530A3 publication Critical patent/EP1717530A3/fr
Application granted granted Critical
Publication of EP1717530B1 publication Critical patent/EP1717530B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F25B39/028—Evaporators having distributing means
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • 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

Definitions

  • the invention relates to a heat exchanger, in particular a rear evaporator for a motor vehicle, according to the preamble of claim 1 or 2.
  • a heat exchanger which has tubes which can be flowed through by a first medium along a plurality of hydraulically parallel flow paths constructed from sections (flat tubes) and by a second medium.
  • the heat exchanger has an inlet and an outlet section, wherein in each case a plurality of spaced-apart refrigerant inlet and outlet openings is provided in the inlet or outlet section.
  • a heat exchanger in particular a rear evaporator for a motor vehicle
  • refrigerant which can be flowed through by refrigerant, and which is constructed such that the refrigerant flowing into the heat exchanger refrigerant flow through a distributor to at least two from each other separated strands is distributed, such that there is no mutual mixing of each flowing therein refrigerant partial flow.
  • a combination of the refrigerant partial streams, in particular in the output region of the heat exchanger should not be excluded.
  • a heat exchanger in particular a rear evaporator for a motor vehicle, comprising pipes and a collecting box comprising a distributor plate, a baffle and a bottom plate in which the tubes terminate with at least one of their ends and that of refrigerant can be flowed through, wherein the collecting box has exactly one opening in the distributor plate, passes through which refrigerant into the collecting box and directly after which the refrigerant flow is distributed to at least two strands.
  • the refrigerant distribution is preferably uniformly to exactly two strands.
  • the uniform distribution of refrigerant due to the one opening in the distributor plate provided with an injection manifold opening in the deflector plate arranged thereafter allows even distribution of the refrigerant, especially when the refrigerant is in a two-phase demixed state, in others Evaporate to a strong inconsistent temperature profile leads. Due to the uniform distribution of refrigerant so the comfort of the rear vehicle occupants is significantly increased, the measures for this are very inexpensive.
  • R744 carbon dioxide
  • the injection distributor opening adjoining the opening in the distributor plate is preferably H-shaped. This form allows in a particularly simple and cost-effective manner a uniform distribution of the refrigerant on the two strands.
  • the baffle preferably has not only an H-shaped injection manifold opening but also a plurality of H-shaped openings for deflecting the flow of refrigerant from one pipe to the adjacent pipe. Due to the H-shaped configuration, the refrigerant is mixed with each deflection in the collecting box, so that the temperature profile on the flat tubes itself is very even.
  • the baffle preferably also has an H-shaped refrigerant outlet opening, which is arranged after the corresponding opening in the distributor plate and through which the refrigerant is sucked out of the collecting box.
  • the symmetrical design of the outlet opening supports a uniform temperature profile.
  • the H-shaped opening is designed to guide and optimize the flow with rounded corners.
  • the H-shaped opening is preferably formed rounded at its leg ends, wherein the width of the leg slightly widened.
  • the leg itself preferably ends straight.
  • the H-shaped opening preferably has a leg width which corresponds approximately to the width of the transverse connection between the two legs.
  • this embodiment enables a good mixing of the refrigerant in the region of the deflection and, on the other hand, it enables a sufficiently resilient design and solubility of the deflection plate.
  • the heat exchanger is preferably designed in two rows, wherein it is preferably also built very small.
  • the injection manifold opening - seen in the flow direction of the heat exchanger through the air flowing - preferably arranged in the last row of tubes. Accordingly, the outlet opening is opposite on the other side, i. in the - viewed in the flow direction of the heat exchanger through the air flowing - arranged first row of tubes.
  • the heat exchanger is, in order to obtain a uniform temperature profile as possible, preferably mirror images to the central transverse axis and / or point symmetrical to the central axis formed, wherein - in the case of an unsuitable number of tubes - the corresponding inlet and outlet openings can also be arranged offset by one row.
  • asymmetrical air inflow it may also be advantageous to provide a different path length of the two strands through which the refrigerant flows through the heat exchanger. The same applies in other cases, for example, if due to the evaporator width or due to the installation conditions no symmetrical division is possible.
  • the injection tube and / or the suction tube are preferably soldered to the heat exchanger, resulting in a complete solution with as few soldering / connecting points.
  • the soldering - including the collecting box - can be done in one step, so that the manufacturing costs can be minimized.
  • connection points for the injection and suction pipe are preferably connected to the same center with respect to the width of the heat exchanger.
  • at least one, in particular both tubes run parallel to the direction of air flow.
  • a heat exchanger arrangement in particular for a rear evaporator of a motor vehicle, has at least one heat exchanger, preferably at least one heat exchanger, as described above, through which refrigerant of a refrigerant circuit can flow, and lines via which refrigerant can be supplied to and discharged from the heat exchanger the heat exchanger in a through a closed wall, which hereinafter not necessarily perpendicular walls, but also horizontally extending areas are understood, arranged separate from the environment interior, the other refrigerant circuit - apart from extending in the heat exchanger part - outside of the interior is designed to extend , And the connection points of the lines to the heat exchanger by means of at least one fixed to the heat exchanger flange, which is arranged in an opening in the wall, au Are arranged outside of the interior.
  • connection points or lines which are formed in conventional interior air conditioning in the vehicle interior or at least partially extending in the interior.
  • the sealing of the opening is preferably carried out by an inserted between the heat exchanger and the wall sealing element, which may be formed, for example, by a foam element, which can also compensate for certain unevenness and dimensional variations, without affecting its function.
  • the wall in which the opening is formed for the flange it handles preferably around the vehicle floor, so that the heat exchanger is supplied from below.
  • the opening for the flange is preferably arranged adjacent to a condensate drain for the condensate collecting in the heat exchanger.
  • Kafteschniklauf CO 2 is preferably provided as a refrigerant, but also any other refrigerant can be used.
  • the flange and / or the heat exchanger have at least one nub, which is mounted in a recess or opening of the heat exchanger or flange, in particular is pressed. This allows a simple prefixing, so that simplifies the further assembly of the heat exchanger.
  • the flange is firmly soldered to the heat exchanger.
  • the soldering of the flange with the corresponding surface of the heat exchanger is preferably carried out in one operation with the actual Solder the heat exchanger, so that only one soldering process is required, which energy and time and thus manufacturing costs can be saved.
  • the flange is preferably arranged on the heat exchanger base at a collection or distribution box.
  • the collection or distribution box as well as the flange preferably flat surfaces, which are brought into abutment against each other and firmly connected, so that a secure and tight connection of the flange and heat exchanger can be ensured.
  • a heat exchanger 1 in this case a rear evaporator of a motor vehicle, which is connected via an injection pipe 2 and a suction pipe 3 with an expansion element 4, according to the present embodiment, a collecting box 5 and a plurality of double-row arranged, U-shaped flat tubes 6.
  • the collecting box 5 has a distributor plate 7, each with an opening 8 with slightly outwardly projecting to the outside Edge 9 for the injection and suction of the refrigerant by means of the injection tube 2 and the suction tube 3, a deflector 10 soldered to the distributor plate 7 and a soldered to the baffle plate 10 bottom plate 11 with a plurality of slot-shaped openings 12, in which the ends the flat tubes 6 are inserted.
  • the injection tube 2 is closed at its end with a closure cap 13.
  • the refrigerant outlet from the injection tube 2 into the heat exchanger 1 is provided in the form of exactly one bore 14, which is arranged in the joining seam of the tube and has a bore diameter which is smaller than the inner diameter of the injection tube 2 (see Fig .. 8).
  • the bore 14 is arranged in alignment with the corresponding opening 10 in the distributor plate 7.
  • the suction pipe 3 is formed corresponding to the injection pipe 2 and arranged with respect to the distributor plate 7, but the bore 14 at the end of the suction pipe 3 has a bore diameter corresponding to the inner diameter of the suction pipe 3 (see Fig. 13).
  • the injection tube 2 as well as the suction tube 3 are presently connected directly to the distributor plate 7, for which the respective slightly outwardly projecting edge 9 of the openings 8 in the distributor plate 7 projects into the corresponding bore 14 in the respective tube.
  • the height of the edge corresponds approximately to the pipe wall thickness.
  • the tubes can also be introduced into the distributor plate with their ends or can be provided a multi-part embodiment, in which case the firmly connected to the distributor plate or possibly also integrally formed part in terms of its function as a part of the injection tube or Suction tube is called.
  • baffle 10 will be explained in more detail.
  • the function of the baffle 10 is primarily the deflection of the effluent from a flat tube 6 refrigerant to the adjacent flat tube 6, wherein the refrigerant is to be mixed in addition, so that a uniform temperature profile is possible.
  • an H-shaped configuration is particularly advantageous.
  • an elongated hole 16 is provided, which extends in length over both rows of H-shaped openings 15 and conducts the refrigerant from one row to the other row (see FIG. 16).
  • the H-shaped configuration of an injection distributor opening 15a, which is arranged opposite to the refrigerant outlet of the distributor plate 7, corresponds in the present case exactly to that of the other openings 15, whereby exactly this embodiment is particularly advantageous with regard to a uniform distribution of the refrigerant to the two strands.
  • the discharge opening 15b of the deflection plate 10, which is opposite the refrigerant outlet of the distributor plate 7, is likewise designed accordingly.
  • the H-shape of the apertures 15, 15a and 15b has rounded edges in all regions, the ends of the legs being provided with outwardly projecting fillets so that the leg width is somewhat increased at the ends (see Fig. 17).
  • the cross connection has the same Width as the thighs up.
  • the leg width corresponds approximately to the width of the opening of the flat tubes 6, the leg length is formed accordingly.
  • the present rear evaporator has, as is common practice, compared to conventional evaporators, as used for front-side motor vehicle air conditioners, reduced dimensions. While conventional front evaporator dimensions are in the range of 180 mm to 310 mm for the width, 180 mm to 260 mm for the height, and 40 mm to 50 mm for the depth, the present evaporator has a width of 130 mm and a height of 130 mm at a depth of 40 mm. However, all values in the range of 100 mm to 160 mm, in particular 110 mm to 150 mm, especially 120 mm to 140 mm for height and / or width of the rear evaporator are particularly favorable.
  • Figures 21 and 22 show a variant of a double row rear evaporator having twelve tubes in width.
  • the Käfteschzu- and removal takes place in parallel in the longitudinal direction of the collecting tank in the middle thereof (see Fig. 22).
  • the refrigerant flow is evenly distributed in both directions after the injection due to the symmetrical configuration (mirror image embodiment with respect to the central transverse axis of the heat exchanger) of the injection manifold opening 15a, so that there is a relatively uniform temperature profile.
  • Figures 23, 24 and 25 show another arrangement of the injection and suction pipe, namely in Fig. 23 is a parallel arrangement in which the flow direction in the two tubes is the same, in Fig. 24 a lateral arrangement, in which both tubes are relatively short before the connection to the rear evaporator have a kink (45 ° bend), and in Fig. 25 is a lateral arrangement in which a tube is straight and the other tube provided with a kink.
  • the basic structure of the collecting tank however, including the injection manifold opening 15a is identical to that shown in FIG.
  • Figures 26 and 27 show a second variant of a double-row rear evaporator having twelve tubes in width.
  • the refrigerant supply and discharge takes place diagonally offset, in each case at the laterally outermost H-shaped opening.
  • the refrigerant flow is in turn distributed evenly on both strands, wherein the strand downstream in the air flow direction, the corresponding series of flat tubes flows through and the other part flow is deflected after flowing through the corresponding side most rear flat tube in the depth direction of the rear evaporator and then flows through the front row until it reaches the last H-shaped opening passes to the suction pipe.
  • the injection and the suction pipe can be arranged to extend parallel in the direction of the longitudinal extent of the collecting tank, as shown in FIG. 26.
  • FIGS. 28 to 30 Particularly advantageous in this case is the embodiment according to FIG. 30, according to which the refrigerant supply and removal is provided at different corners of the heat exchanger, and in which one of the two tubes, in this case the suction pipe, is arranged parallel to and adjacent to the collection box of the heat exchanger ,
  • FIGS. 31 and 32 show a second variant of a double-row rear evaporator with twelve tubes in width, in which the injection distributor opening lies between those of the two variants described above.
  • the connection is designed according to the variant described above.
  • Other connection possibilities correspond to those of FIGS. 28 to 30.
  • FIGS. 33 and 34 show a variant of a double-row rear evaporator with ten tubes in the width, in FIG. 35 a connection variant for connection of Fig. 33, but also other arrangement of the injection and suction pipes is possible, in particular as shown in Figures 23-25.
  • a further apart inlet and outlet of the refrigerant is possible, that is offset with respect to the illustration of Fig. 34 by a respective H-shaped opening 15 to the right or to the left.
  • FIGS. 36 and 37 also show two variants of the refrigerant supply and discharge for a double-row rear evaporator with eight tubes each in width.
  • the arrangement of the injection and suction pipes may be formed according to the previous variants.
  • Figures 38 and 39 show a variant of a rear evaporator with different path length of the two strands.
  • a different path length of the two strands may be useful in an unequal distribution of air flow through the rear evaporator to optimize the temperature profile.
  • the injection distributor opening 15a is preferably arranged in the second (or the rearmost) row when viewed in the air flow direction, but the outlet opening 15b is arranged in the first row. This enables optimization of the cooling capacity.
  • the heat exchanger according to the embodiment described above is at operating pressures of 90 bar here, but at least 50 bar, designed (test pressure in this case 160 bar), so that in particular R744, ie CO 2 , can be used as a refrigerant.
  • FIG. 40 shows a particularly advantageous variant of the arrangement of the connections for a rear evaporator, the injection and suction pipe being apart from an end region of the injection pipe in which one of the two tubes at the end is slightly bent to allow connection at the same height - are arranged parallel to each other.
  • the tubes are substantially parallel to the direction of air flow, wherein the connection points are arranged centrally on the rear evaporator.
  • This embodiment is particularly advantageous with regard to the temperature distribution over the rear evaporator.
  • Fig. 41 shows a variant which substantially corresponds to the embodiment of Fig. 40, but the flow direction of the refrigerant is reversed, so that injection and suction pipe are reversed.
  • the dimensions of injection and suction pipe are not shown to scale in the figures.
  • connection points are arranged centrally with respect to the rear evaporator, but in the present case only the injection tube is aligned parallel to the air flow direction.
  • the suction pipe runs perpendicular to this and is bent only laterally of the rear evaporator.
  • a in a non-illustrated refrigerant circuit arranged heat exchanger 1, in this case a rear evaporator of a motor vehicle, via a flange 102 and one connected to this flange 102 injection pipe and suction pipe (not shown) with a remote in the Front region arranged expansion element (not shown), comprises a collection box formed of sheet metal plates 5 and a plurality of double row arranged U-shaped flat tubes 6, between which corrugated fin packages are arranged, as in Fig. 45 indicated in some areas.
  • the collecting box 5 has a distributor plate 7, each with an opening 8, which are continued in the flange 102 in the form of two passages 103a and 103b, for the injection (8a) and suction (8b) of the refrigerant by means of the injection or the suction tube a soldered to the distributor plate 7 baffle 10 and a soldered to the baffle plate 10 bottom plate 11 with a plurality of slot-shaped openings 12 into which the ends of the U-shaped flat tubes 6 are inserted and soldered to the same.
  • the injection tube is fixedly connected at its end to a corresponding opening in the flange 102 by means of a fastening device, not shown in the drawing, formed in a manner known in principle, with a pin and a screw screwed into the flange 102.
  • the suction pipe is formed according to the injection pipe and secured to the flange 102 by a second fastening device, wherein, however, the diameter of the suction pipe, in particular the inner diameter due to the larger volume flow, which must be removed, is greater than that of the injection pipe.
  • the flange 102 is substantially cuboid.
  • the passage 103a in the flange 102 for the supply of the refrigerant to the heat exchanger 1 is continued from a bore in an obliquely extending on the underside of the flange 102 channel (see Fig. 50), which is closed by the distributor plate 7 and in the region of the opening 8a ends.
  • the channel course is due to the configuration of the Käfteschzu Installation conditionally.
  • the refrigerant is discharged via the trained as a hole with different diameter changes bushing 103b.
  • a simple bore, as for the refrigerant removal (feedthrough 103b) may also be provided for the passage 103a.
  • baffle 10 and its function in the collection box 5 will be explained in more detail.
  • the function of the baffle 10 is primarily the deflection of the effluent from a flat tube 6 refrigerant to the adjacent flat tube 6, wherein the refrigerant is to be mixed in addition, so that a uniform temperature profile is possible. This takes place here within the rows with the aid of the double row arranged H-shaped openings 15 in the baffle 10, wherein the refrigerant through a leg of the H-shaped opening 15 on, through the connecting web and over the second leg of the H-shaped opening 15 flows out again into the adjacent U-shaped flat tube 6.
  • At both longitudinal ends of the baffle 10 each have a slot-like opening 16 is provided, which extends in length over both rows of H-shaped openings 15 and directs the refrigerant from one row to the other row.
  • openings 15, in particular that of the openings 15, which serve only the deflection of a flat tube 6 to the adjacent flat tube 6 and possibly also the discharge of the last two flowed through flat tubes 6 in the suction pipe, possible.
  • an H-shaped configuration is particularly advantageous.
  • the H-shaped configuration of an injection Verteiterö Anlagen 15 a, which is arranged opposite to the refrigerant outlet of the distributor plate 7, in the present case corresponds exactly to that of the other openings 15, where exactly this embodiment is particularly advantageous with regard to a uniform distribution of the refrigerant to the two strands.
  • the discharge opening 15b of the deflection plate 10, which is opposite the refrigerant outlet of the distributor plate 7, is likewise designed accordingly.
  • the H-shape of the openings 15, 15a and 15b has rounded edges in all areas, with the centrally arranged ends of the legs being provided with outwardly projecting rounded portions, so that the leg width is somewhat enlarged at the ends (see FIG ).
  • the cross-connection has twice the width as the legs.
  • the leg width corresponds approximately to the width of the opening of the flat tubes 6, the leg length is formed accordingly.
  • the present rear evaporator has, as is common practice, compared to conventional evaporators, as used for front-side motor vehicle air conditioners, reduced dimensions. While conventional front evaporator dimensions range from 180 mm to 310 mm for the width, 180 mm to 260 mm for the height and 40 mm to 50 mm for the depth, the present heat exchanger has a width of 130 mm and a height of 130 mm at a depth of 40 mm. However, all values in the range of 100 mm to 160 mm, in particular 110 mm to 150 mm, especially 120 mm to 140 mm for height and / or width of the rear evaporator are particularly favorable.
  • the collecting box 5 is arranged at the bottom, so that the flange 102 is positioned below the heat exchanger 1 and the supply and discharge takes place from below or towards the bottom.
  • the heat exchanger 1 is placed directly on the vehicle floor 20, which in the region of the flange 102 has an opening 121 through which the flange 102 projects.
  • the opening 121 is arranged by means of a between the distributor plate 7 and the edge of the vehicle floor 120 Sealing element 122 sealed airtight.
  • a rib structure is formed for stiffening.
  • a condensate drain 123 is provided, through which the condensate collecting in the heat exchanger 1 can be dissipated down.
  • the condensate drain 123 is formed to well below the flange 102 extending, i. to below the connection level of the injection and suction pipe.
  • the flange 102 is secured to the distributor plate 7 by means of a nub 103c (see Fig. 50) projecting over the underside of the flange 102 and into a mounting aperture 8c provided in the distributor plate 7 (see Figs ) is pressed in, prefixed and, after the baffle plate 10 and the bottom plate 11 caulked with the distributor plate 7 and then the flat tubes 6 are mounted together with corrugated fins packages soldered in the context of soldering the entire heat exchanger 1 in a single soldering.
  • the connection of the pipes and the filling of the refrigerant circuit with refrigerant takes place only during the assembly in the vehicle.
  • nubs and mounting holes may be provided, more preferably three, the nubs in principle also on the distributor plate 7 and the mounting holes on the flange 102 may be arranged or a mixed configuration, ie Nubs on both the flange and on the distributor plate, is possible.
  • the heat exchanger according to the embodiment described above is at operating pressures of 90 bar here, but at least 50 Bar, designed (test pressure in this case 160 bar), so that in particular R744, ie CO 2 , can be used as a refrigerant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP06005937.5A 2005-04-29 2006-03-23 Echangeur de chaleur, en particulier évaporateur arrière pour véhicule automobile Not-in-force EP1717530B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005020499A DE102005020499A1 (de) 2005-04-29 2005-04-29 Verdampfer, insbesondere Heckverdampfer für ein Kraftfahrzeug
DE102006004673 2006-01-31

Publications (3)

Publication Number Publication Date
EP1717530A2 true EP1717530A2 (fr) 2006-11-02
EP1717530A3 EP1717530A3 (fr) 2011-11-09
EP1717530B1 EP1717530B1 (fr) 2017-06-28

Family

ID=36755451

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06005937.5A Not-in-force EP1717530B1 (fr) 2005-04-29 2006-03-23 Echangeur de chaleur, en particulier évaporateur arrière pour véhicule automobile

Country Status (2)

Country Link
EP (1) EP1717530B1 (fr)
DE (1) DE102005020499A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150300758A1 (en) * 2014-02-19 2015-10-22 MAHLE Behr GmbH & Co. KG Heat exchanger
WO2022244091A1 (fr) * 2021-05-18 2022-11-24 東芝キヤリア株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006046671A1 (de) * 2006-09-29 2008-04-03 Behr Gmbh & Co. Kg Wärmetauscher in Plattenbauweise, insbesondere Verdampfer für eine Kraftfahrzeug-Klimaanlage
DE102014221168A1 (de) 2014-10-17 2016-04-21 Mahle International Gmbh Wärmeübertrager
DE102015210962A1 (de) 2015-06-15 2016-12-15 Mahle International Gmbh Wärmeübertrager

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10260107A1 (de) 2001-12-21 2003-10-02 Behr Gmbh & Co Wärmeübertrager, insbesondere für ein Kraftfahrzeug

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5241839A (en) * 1991-04-24 1993-09-07 Modine Manufacturing Company Evaporator for a refrigerant
DE10049256A1 (de) * 2000-10-05 2002-04-11 Behr Gmbh & Co Serpentinen-Wärmeübertrager
JP4098495B2 (ja) * 2001-06-22 2008-06-11 カルソニックカンセイ株式会社 車両用空気調和装置

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10260107A1 (de) 2001-12-21 2003-10-02 Behr Gmbh & Co Wärmeübertrager, insbesondere für ein Kraftfahrzeug

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150300758A1 (en) * 2014-02-19 2015-10-22 MAHLE Behr GmbH & Co. KG Heat exchanger
US10281223B2 (en) * 2014-02-19 2019-05-07 MAHLE Behr GmbH & Co. KG Heat exchanger
WO2022244091A1 (fr) * 2021-05-18 2022-11-24 東芝キヤリア株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération

Also Published As

Publication number Publication date
EP1717530B1 (fr) 2017-06-28
DE102005020499A1 (de) 2006-11-09
EP1717530A3 (fr) 2011-11-09

Similar Documents

Publication Publication Date Title
EP2026028B1 (fr) Échangeur de chaleur, en particulier pour véhicule automobile
EP1798506B1 (fr) Evaporateur
EP2232183B1 (fr) Échangeur de chaleur, en particulier radiateur pour des véhicules automobiles
DE10314782A1 (de) Wärmetauscher für den Wärmeaustausch zwischen einem inneren und einem äußeren Fluid und Verfahren zur Herstellung desselben
DE19719251A1 (de) Verteil-/Sammel-Kasten eines mindestens zweiflutigen Verdampfers einer Kraftfahrzeugklimaanlage
DE10349150A1 (de) Wärmeübertrager, insbesondere für Kraftfahrzeuge
EP1881288A1 (fr) Echangeur thermique avec bloc de connexion or raccordement
EP1717530A2 (fr) Echangeur de chaleur, en particulier évaporateur arrière pour véhicule automobile
DE102005059920B4 (de) Wärmetauscher, insbesondere Verdampfer
EP1725823A1 (fr) Dispositif pour echanger de la chaleur, et procede de production de ce dispositif
DE102005059917A1 (de) Verdampfer
DE102008025910A1 (de) Wärmeübertrager
WO2005100895A1 (fr) Echangeur de chaleur pour vehicules automobiles
EP1798507A2 (fr) Echangeur de chaleur, en particulier évaporateur
EP1934545B1 (fr) Corps chauffant, circuit de refrigerant, appareil de climatisation pour une installation de climatisation de vehicule automobile, et installation de climatisation pour un vehicule automobile
DE102008036614A1 (de) Wärmetauscher
EP1816424A1 (fr) Echangeur thermique pour un cycle frigorifique
EP1816426B1 (fr) Dispositif de transfert de chaleur, en particulier d'un évaporateur arrière dans un véhicule automobile
DE10250287C1 (de) Wärmetauscher, insbesondere für eine Heiz- und/oder Klimaeinrichtung eines Kraftfahzeuges
EP2049859A1 (fr) Climatisation pour véhicule à moteur, échangeur de chaleur, en particulier radiateur, pour une climatisation pour véhicule à moteur de ce type ainsi que procédé de fonctionnement d'un échangeur de chaleur d'une climatisation pour véhicule à moteur
EP1859217A1 (fr) Echangeur thermique, en particulier evaporateur d'une installation de climatisation pour vehicules
DE102006004983A1 (de) Wärmetauscher, insbesondere Verdampfer einer Kraftfahrzeug-Klimaanlage
EP1382926B1 (fr) Evaporateur pour système de climatisation de véhicules automobiles
DE102009021796A1 (de) Verschaltung zweier Heizkörper zu einem Hochleistungskörper
DE19959621A1 (de) Wärmetauscher für Fahrzeug-Klimaanlage und Verfahren zu seiner Herstellung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

RIC1 Information provided on ipc code assigned before grant

Ipc: F28F 9/02 20060101ALI20111005BHEP

Ipc: F28D 1/047 20060101ALI20111005BHEP

Ipc: F25B 39/02 20060101AFI20111005BHEP

Ipc: F28F 27/02 20060101ALI20111005BHEP

17P Request for examination filed

Effective date: 20120509

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

17Q First examination report despatched

Effective date: 20130624

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAHLE BEHR GMBH & CO. KG

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20170201

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

GRAL Information related to payment of fee for publishing/printing deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR3

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

GRAR Information related to intention to grant a patent recorded

Free format text: ORIGINAL CODE: EPIDOSNIGR71

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

INTC Intention to grant announced (deleted)
RIN1 Information on inventor provided before grant (corrected)

Inventor name: DUERR, GOTTFRIED DIPL.-ING.

Inventor name: KRANICH, MICHAEL DIPL.-ING.

Inventor name: WALTER, CHRISTOPH DIPL.-ING.

Inventor name: STAFFA, KARL-HEINZ DIPL.-ING.

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

INTG Intention to grant announced

Effective date: 20170519

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 905237

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170715

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502006015555

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170929

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20170628

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170928

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171028

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502006015555

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20180329

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20180323

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20180331

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180323

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180323

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180331

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180331

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180331

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180323

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 905237

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180323

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180323

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20060323

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170628

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20210323

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20210518

Year of fee payment: 16

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502006015555

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220331

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20221001