EP1892491A2 - Unité, comportant un refroidisseur de gaz et un échangeur thermique interne, et échangeur thermique - Google Patents

Unité, comportant un refroidisseur de gaz et un échangeur thermique interne, et échangeur thermique Download PDF

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Publication number
EP1892491A2
EP1892491A2 EP07013144A EP07013144A EP1892491A2 EP 1892491 A2 EP1892491 A2 EP 1892491A2 EP 07013144 A EP07013144 A EP 07013144A EP 07013144 A EP07013144 A EP 07013144A EP 1892491 A2 EP1892491 A2 EP 1892491A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
unit according
tube
section
tubes
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Withdrawn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
EP07013144A
Other languages
German (de)
English (en)
Other versions
EP1892491A3 (fr
Inventor
Kurt Molt
Uwe FÖRSTER
Thomas Himmer
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 EP1892491A2 publication Critical patent/EP1892491A2/fr
Publication of EP1892491A3 publication Critical patent/EP1892491A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0461—Combination of different types of heat exchanger, e.g. radiator combined with tube-and-shell heat exchanger; Arrangement of conduits for heat exchange between at least two media and for heat exchange between at least one medium and the large body of fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded
    • 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

Definitions

  • the invention relates to a unit comprising a gas cooler or condenser and an internal heat exchanger, as used for air conditioning systems, in particular for motor vehicles, according to the preamble of claim 1, and a heat exchanger, in particular an internal heat exchanger, according to the preamble of claim 17 ,
  • the use of internal heat exchangers for heat transfer between high and low pressure side of air conditioning systems is known, wherein the heat exchanger is usually in a refrigerant circuit, eg. With R744 as a refrigerant, arranged and operated in countercurrent operation.
  • the heat exchanger is usually arranged on the high pressure side between a gas cooler and an expansion element and low pressure side between an accumulator and a compressor.
  • Such an internal heat exchanger serves to increase the COP value of the air conditioner.
  • the EP 1 046 524 B1 discloses a generic unit.
  • a high-pressure gas cooler is provided for a coolant circuit of a motor vehicle air conditioner, wherein CO 2 (R744) serves as a refrigerant.
  • This gas cooler has an integrated internal heat exchanger, ie the gas cooler and the internal heat exchanger form a single unit that is soldered.
  • the gas cooler here has a plurality of heat exchanger tubes, as well as the inner heat exchanger, and the inner heat exchanger is disposed above or below the gas cooler heat exchanger tubes.
  • the heat exchanger tubes both in the case of the gas cooler heat exchanger tubes and in the case of the heat exchanger tubes of the inner heat exchanger, they are flat tubes with a plurality of chambers arranged side by side, the profiles of all the heat exchanger tubes corresponding to one another and the heat exchanger tubes being different only for their length and exit areas differ.
  • the flat tubes of the inner heat exchanger are arranged close to each other and alternately with respect to the refrigerant flowing through, so that a flat tube connected to the high pressure side is disposed directly adjacent to a flat tube connected to the low pressure side, and so on.
  • the flat tubes are arranged in a known manner at a distance from one another and with the interposition of corrugated ribs. The entire arrangement gas cooler and inner heat exchanger is soldered together in a single block.
  • an air conditioner in particular a motor vehicle air conditioning system
  • the inner heat exchanger helical webs which separate the outer channels from each other, as well as the provision of turbulence elements on the webs disclosed.
  • From the EP 1 202 016 A2 is a one-piece heat exchanger tube with a multi-chamber profile known, according to which a plurality of outer channels are provided around a central channel.
  • the outer channels are divided by intermediate walls which extend in the radial direction.
  • wave-like projections are provided, which extend slightly into the central channel. These projections serve to reduce the cross-sectional area and thus increase the flow velocity.
  • the projections may also be helical, wherein constant, changing or changing slopes may be provided.
  • the inner channel is used in this heat exchanger tube as the high pressure side, the outer channels as the low pressure side.
  • EP 1 046 524 B1 it is an object of the invention to provide an improved unit comprising a gas cooler and an internal heat exchanger. Further an improved heat exchanger is to be made available, which is particularly suitable as an internal heat exchanger.
  • pipe in particular in connection with the inner heat exchanger - is to be interpreted very broadly below and refers not only to round cross-sections, but in particular also oval, rounded rectangular or any other cross-sections.
  • the pipe can also be two tubes arranged inside one another which have no direct connections (pipe-in-pipe arrangement).
  • positioning elements for the inner tube may be provided in the outer tube, such as provided on the outer and / or inner tube, radially inwardly or outwardly projecting ribs to optionally ensure a coaxial arrangement.
  • an integrally formed coaxial tube can be provided.
  • the arrangement of the inner tube or of the inner region in the outer tube can be coaxial, but does not have to be so that, in particular, off-center arrangements are also possible.
  • a plurality of inner tubes may be provided.
  • the inner tube or tubes may also be brazed or otherwise connected to the outer tube in the contact regions.
  • the division of the flow cross-section into individual open-ended chambers is possible, i.
  • the inner tube may be formed by one or more multi-chamber flat tubes, whereby the heat transfer area increases greatly.
  • a unit comprising a first heat exchanger, in particular a gas cooler, which the Heat transfer from a refrigerant to air or another medium flowing through the first heat exchanger medium, and at least one second, in particular inner heat exchanger, which are formed as a structural unit, wherein the second, inner heat exchanger laterally offset and slightly spaced and / or thermally insulated in one Plain arranged with the first heat exchanger and connected via at least one connecting line directly to the first heat exchanger to form the structural unit, in particular soldered, is.
  • the laterally offset arrangement allows due to the preferably provided gap between the two heat exchangers, in which optionally still an insulating material may be arranged, an improved decoupling with respect to the heat, which in the case of EP 1 046 524 B1 disclosed high-pressure gas cooler with integrated internal heat exchanger is not possible. Nevertheless, due to the structural unit - according to the EP 1 046 524 B1 - Soldering of the entire unit, ie the first heat exchanger and the second, in particular internal heat exchanger, possible in a single operation, however, the assembly can be quite simplified, since two separately prepositioned blocks and a somewhat flexible connection thereof instead of a single blocks are provided with significantly more components.
  • another heat exchanger in particular a fluid-fluid heat exchanger, preferably undergoes a phase transition in at least one, particularly preferably both fluids in at least a portion of the corresponding fluid flow.
  • the relative positions of the two heat exchangers to one another are preferably no longer changeable after soldering has taken place - if appropriate apart from slight corrections via the connection line, which interconnect the two heat exchangers preferably directly connects, in particular with regard to the bending of the same.
  • the choice of the inner heat exchanger is substantially independent of the shape of the first heat exchanger, so that the air conditioner can also be optimized with regard to the shape of the second, in particular inner heat exchanger.
  • the second, in particular inner heat exchanger is particularly preferably arranged parallel to a collector of the first heat exchanger and laterally offset thereto in a plane with the heat exchanger.
  • the second, in particular inner heat exchanger is arranged perpendicular to the collector, above or below the first heat exchanger and in a plane with the first heat exchanger, however, the first-mentioned embodiment is preferred.
  • the first heat exchanger is preferably a plate-type heat exchanger, ie the collector or collectors consist of a plurality of plate-like sheets soldered together, in particular a connecting plate, a distributor plate and a bottom plate.
  • the connecting plate On the connecting plate, the connecting lines are attached, via which refrigerant is fed to the heat exchanger and discharged.
  • the distributor plate has, for example, H-shaped and L-shaped openings, via which the refrigerant is distributed to the individual tubes.
  • the bottom plate is used to connect the individual tubes, which are preferably flat tubes, which are soldered directly into slot-like openings in the floor panel.
  • corrugated ribs or other structures which increase the heat transfer surface are preferably arranged between the tubes, in particular the flat tubes, wherein they are preferably soldered firmly to the tubes.
  • the whole Heat exchanger is - preferably soldered together with the second heat exchanger - in a single operation.
  • the tubes of the first heat exchanger are - preferably in contrast to the tubes of the second internal heat exchanger - formed by flat tubes, more preferably by flat tubes with multiple flow channels.
  • a plurality of flat tubes may be arranged in the depth of the heat exchanger, but preferably a relatively broad flat tube with a plurality of flow channels is provided, which is viewed in the width direction flows through two different refrigerant streams, particularly preferably in the opposite flow direction.
  • the connecting line ie the direct connection of the two heat exchangers, is preferably designed to be short in comparison to the length of the second, in particular inner, heat exchanger, so that, inter alia, weight can be saved.
  • the second, parallel to a collector of the first heat exchanger and laterally offset in a plane arranged with the first heat exchanger, the second, in particular inner heat exchanger is shorter than the collector formed, in particular preferably so short that it fits between the terminals of the first heat exchanger and is protected to some extent by them. Furthermore, such a design allows a very compact, space-saving design. The space requirement for connecting lines can be minimized.
  • the second, in particular inner heat exchanger on a depth which is at most as large as the overall depth of the first heat exchanger, but with sufficient space in the depth in the height of the second, in particular inner heat exchanger also deeper second, in particular internal heat exchanger possible.
  • the second, inner heat exchanger is directly and firmly connected to the first heat exchanger via at least one connecting line.
  • This is preferably the outflow side of the first heat exchanger to the high-pressure side supply line of the refrigerant in the inner heat exchanger.
  • the connecting line is preferably designed to be short compared to the length of the second, in particular inner heat exchanger.
  • the connecting line is formed by a curved piece, in particular preferably by a 90 ° bend piece. This allows a short distance to the second, in particular internal heat exchanger and the same can be arranged parallel to the collector, from which the refrigerant flows out.
  • the second, in particular internal, heat exchanger is preferably arranged directly adjacent to the first heat exchanger, but is preferably not directly attached to it, i.e., not directly adjacent to the first heat exchanger. between the two heat exchangers, a heat-decoupling gap is provided.
  • advantages in terms of installation and optimum utilization of the installation space compared to a second, in particular internal, heat exchanger that is integrated into the first heat exchanger can result.
  • the entire arrangement is more flexible and adaptable without labor-intensive, fluidic recalculations to other conditions, for example.
  • connection piece with a bottom is preferably provided, which part is the flow cross-section is concealed and designed to be open for another part of the flow cross-section.
  • connection piece and bottom can also be formed in one piece.
  • the inflow and outflow preferably takes place substantially coaxially, for which the connecting piece is designed accordingly.
  • the inflow of the refrigerant into the "outer tube” takes place - depending on the design of the connection piece either axially or radially, but it can also be introduced and discharged via a connection formed separately from the connector in the radial direction.
  • At least one turbulence generator for example corrugated fins or turbulence sheets, is arranged in a flow cross section, which is preferably the larger flow cross section of the "outer tube".
  • a single continuous flow cross-section is provided for the first-pressure refrigerant and a plurality of smaller, non-connected and longitudinally-flowable chambers for the refrigerant under another pressure.
  • the lower-pressure refrigerant flows in the outer region, it is not divided into individual chambers.
  • it is also a divided into individual chambers embodiment of both flow areas, i. of the area in which the refrigerant coming from the high-pressure side and the area where the refrigerant coming from the low-pressure side flows.
  • the second, in particular inner heat exchanger preferably has an outer tube and a plurality of arranged in the same, possibly also in one piece with the same connected pipes with a multi-chamber profile, which may, for example, to flat tubes.
  • flow paths for the refrigerant flowing in the outer tube are formed between the individual multi-chamber profile tubes or multi-chamber profile-like regions.
  • These flow paths of the outer tube have a smallest flow cross section, which is preferably at least as large as the smallest flow cross section of the chambers of the inner tube or of the corresponding inner regions.
  • the heat exchanger is preferably flowed through in countercurrent operation, which improves the efficiency of heat transfer.
  • the free flow cross section of the high pressure side is preferably smaller than the free flow cross section of the low pressure side.
  • the free flow cross sections differ such that the free flow cross section of the high pressure side is preferably at most half as large and preferably at least a quarter as large, more preferably about one third +/- 10% is as large as the free flow cross section of the low pressure side.
  • the second, in particular inner, heat exchanger and / or the first heat exchanger preferably consists at least partially of aluminum or an aluminum alloy.
  • the essential parts of the second, in particular inner, heat exchanger ie the parts which form the heat transfer surfaces or at least essential regions thereof, are preferably produced by extrusion, both as an integrally formed profile and as a component composed of two or more profiles.
  • other types of profiles are possible, in particular bent and pressed or welded sheet metal profiles. Of course, this is also conceivable in the case of the first heat exchanger.
  • the second, inner heat exchanger can be formed both in one piece, particularly preferably as an extruded tube with a plurality of flow channels, as well as in several parts, in particular as a tube-in-tube arrangement.
  • the second, in particular inner, heat exchanger preferably has a circular cross section, but any other suitable cross section, for example also an oval or flat tube-like cross section, may be used.
  • the second heat exchanger - which can be used both alone and in the unit according to the invention as an internal heat exchanger - has at least one tubular flow channel, formed by an outer tube, for a first medium, and at least one in the at least one flow channel in the direction of Flow channel arranged line, formed by an inner tube, for a second medium, wherein the line is at least partially formed independently of the wall of the flow channel.
  • the inner tube has a plurality of inner channels through which the second medium flows.
  • the media may preferably be refrigerants of a single refrigerant circuit with different temperatures.
  • a plurality of flat-tube-like, inner tubes or flat tube-like regions of the inner tube, each having a plurality of inner channels are provided, which are arranged in the outer tube.
  • the outer tube and the one or more inner tubes are firmly connected to each other at exactly one point.
  • the connection can by means of Soldering or similar respectively.
  • the tubes are configured in one piece, ie the connection is made via a connecting region in the region of the inner wall of the outer tube.
  • turbulence generators for example.
  • corrugated fins provided to increase the efficiency of the heat exchanger.
  • An inventive unit of heat exchanger and inner heat exchanger can be used in particular for heat exchangers, preferably for motor vehicle air conditioning systems, particularly preferably for high-pressure air conditioning systems of motor vehicles, but other applications are possible.
  • the internal heat exchanger described can also be used alone, i. especially not in the previously described, rigid orientation to another heat exchanger.
  • a as a gas cooler for the same flowing through refrigerant CO 2 (R744) serving heat exchanger 1 of a motor vehicle air conditioner, of which only a small part is shown in Fig. 1, has a known construction with side collectors 2, extending between the same heat exchanger tubes, in the present case formed by flat tubes 3, and arranged between the flat tubes 3 corrugated fins 4, wherein in the present case, the individual parts were soldered together in one operation.
  • an inner heat exchanger 5 is further arranged, which is flowed through by the refrigerant and serves to increase the COP value of the air conditioner.
  • the inner heat exchanger 5 is arranged with its high pressure side H in the flow direction of the refrigerant behind the gas cooler and before an expansion element and with its low pressure side N behind a collector and in front of the compressor, wherein high and low pressure side of the inner heat exchanger 5 are flowed through in countercurrent operation.
  • the inner heat exchanger 5 is present, as shown in the section shown in Fig. 4a, formed by a round tube 6 and three arranged in the round tube 6, parallel, multi-chamber flat tubes 7, wherein two of the three flat tubes 7 have a cross section corresponding to each other and the third, arranged between the two flat tubes flat tube has a slightly wider cross section with a chamber more.
  • the maximum outer diameter of the inner heat exchanger 5, which substantially corresponds to the outer diameter of the round tube 6, in this case has the same dimension as the overall depth of the gas cooler.
  • the length of the inner heat exchanger is, as shown in FIG. 1, sufficiently smaller than the height of the gas cooler to have sufficient space for the connections of the heat exchanger.
  • connections of the inner heat exchanger 5 are in the present case designed such that in each case a connection 8 is provided in the axial direction and a connection 9 in the radial direction at each end thereof, the refrigerant being supplied to the chambers of the three flat tubes 7 via the connection 8 in the axial direction or is discharged from the same, and via the terminal 9 in the radial direction, the refrigerant is supplied to the free interior of the round tube 6 and discharged from the same.
  • the gas cooler, ie, the first heat exchanger 1, and the inner heat exchanger 5 the rigidly present to each other via one of the connecting lines 10, namely the connection line 10 shown in Fig. 1 below, which is soldered directly from the collector 2, form a structural Unit.
  • the inner heat exchanger can also be arranged parallel to the flat tubes of the gas cooler, in particular below or above the gas cooler.
  • the inner heat exchanger can also be arranged at another suitable location in the low and / or high pressure side of the refrigerant circuit.
  • connection line 10 may also be a fixed connection pipe fixed to the connector 11, to which the actual connection line, for example, by means of a mechanical fastening device or by means of a forming process can be fastened.
  • connection piece can, for example, also be provided with a mechanical fastening device, so that the connection line does not have to be soldered to the connection piece or connected in a non-detachable manner in other ways. This is particularly useful on one side of the inner heat exchanger, which is not soldered to the gas cooler with the involvement of the corresponding connection line.
  • a distributor chamber 12 is formed centrally in the connecting piece 11, which has a slightly larger inner diameter than the inner diameter of the connecting line 10, however has a smaller inner diameter than the outer diameter of the type of line 10.
  • the connector 11 On the opposite side, which is referred to below as the heat exchanger side, the connector 11 has a much larger inner diameter than the connection line side and as in the distribution chamber 12, wherein the transition again in the form of a step, the present significantly larger than the wall thickness of the round tube. 6 is done.
  • the round tube 6 At the step formed by the step is the round tube 6, whose outer diameter corresponds to the inner diameter of the connecting piece 11 in this area, at.
  • the end of the round tube 6 is provided with a bottom 13, which in the present case has three openings 14 whose cross-section corresponds to the outer dimensions of the flat tubes 7 arranged in the round tube 6.
  • the connection piece-side ends of the round tube 6, the bottom 13 and the flat tubes 7 are presently arranged in a plane.
  • the flat tubes 7 have such a dimension that all three flat tubes 7 with at least a small portion of their ends in contact with the connector 11, but as far as possible, none of the chambers in the interior of the flat tubes 7 is covered by the connector 11, so that the Flow cross-section of all chambers of the flat tubes 7 as completely as possible available.
  • the low-pressure-side connection 9 takes place, as shown in Fig. 2 - or FIG. 5, which does not differ from the present embodiment in terms of the design of the round tube and in particular the low-pressure side connection - in the radial direction of the round tube 6, for which a bore 14 and a tube 15 introduced therein and soldered to the round tube 6 is provided.
  • the internal cross-sectional area of the tube 15 substantially corresponds to the free flow area in the round tube 6, i. the inner cross-sectional area minus the area of the flat tubes 7 arranged therein.
  • the operating pressure on the low pressure side is according to the present embodiment about 130 bar, the corresponding bursting pressure 264 bar, and the operating pressure on the high pressure side is about 160 bar, the corresponding Bursting pressure 352 bar.
  • the stated pressure values relate in particular to the use of CO 2 as refrigerant.
  • an improved, defined flow of the high-pressure refrigerant can be realized via the corresponding connection piece 11; in particular, as shown in FIG. 2, a relatively deflection-free flow of the high-pressure refrigerant in the direction of the longitudinal axis of the flat tubes 7 is provided , whereby the pressure loss can be reduced and thereby the cooling capacity can be improved.
  • the flow of the low-pressure refrigerant takes place in the radial direction with respect to the longitudinal axis of the round tube. 6
  • the round tube, as well as the flat tubes 7 in the interior of the round tube 6, in the present case are extruded tubes made of aluminum.
  • the same are with the bottoms 13, the fittings 11 and the radial connections 9 forming tubes soldered, which is advantageously carried out in one operation.
  • the soldering of the parts can also - with a corresponding arrangement of the inner heat exchanger 5 on at least one refrigerant-carrying and directly connected to the guest pipe - done in a single operation with the soldering of the gas cooler.
  • the same can also be designed as a stamped and bent part, so that in particular the region extending in the direction of the adjoining tube can be made larger so that, if necessary, a short, short, soldered pipe section or the direct soldering of the connection line omitted and can be provided directly to the edge of the fitting a corresponding attachment for the pipe to be connected.
  • connection piece in the case of a formation of the connection piece as a stamped and bent part, the same can also with ribs or the like. be formed stiffening structures. Furthermore, the provision of extended regions, ribs or other guide structures also makes it possible to optimize the shape of the distributor space with regard to the inflow and outflow of the refrigerant into the chambers of the flat tubes or corresponding refrigerant-carrying structures.
  • the inlet and / or outlet direction of the refrigerant into and out of the connection piece does not necessarily have to be in the axial direction to the inner heat exchanger, although this direction is the most favorable with regard to the refrigerant flow. Rather, a radial flow direction, for example. Parallel to the flow direction of the radial port or an oblique flow direction is possible, which may be particularly advantageous in view of the required space for the connecting lines. Likewise, high and low pressure side can be arranged reversed compared to the first embodiment.
  • the floor described above may also be formed integrally with the connector. Although production is more difficult to manufacture, the number of individual parts and the number of points to be sealed in the course of manufacture are thereby reduced. Furthermore, the distributor space can be made more pressure- and flow-compatible. The one-piece design further allows a slight increase in the heat-transmitting length of the inner heat exchanger.
  • each of the widths of the outer flat tubes 7 and the central flat tubes 7 corresponds to each other, so that the flat tubes 7 relatively evenly in the interior of the round tube 6 are arranged distributed.
  • the configuration of the terminals corresponds to that of the first embodiment, i.
  • the flat tubes end in a bottom, which is accommodated in a connection piece.
  • the number of flat tubes can be increased, also in principle round tubes or tubes can be used with other cross-sections instead of the flat blanks.
  • Fig. 4c shows a third embodiment with a single, € -like design tube 7, which is arranged in the round tube 6 to form an annular gap with the same.
  • a plurality of longitudinally continuous, adjacently arranged chambers are formed whose function corresponds to that of the chambers of the multi-chambered flat tubes.
  • the same is formed by a plurality of centrally interconnected flat tubes of different widths.
  • the longitudinally continuous chambers are also provided in the connection area.
  • Fig. 4e shows the inner tube 7 according to the fifth embodiment, which in turn is arranged in a round tube (not shown).
  • This inner tube 7 has a meandering cross section with a plurality of longitudinally continuous chambers.
  • the sixth embodiment shown in Fig. 4f substantially corresponds to the embodiment of Fig. 4c, but the inner tube 7 and the round tube are connected to each other via a web, which forms a transitional area, i. integrally formed.
  • the production of this tube is done by means of extrusion in a single operation.
  • fork-like, flat tube-like regions 7 are formed integrally with the circular tube 6 with chambers extending in the longitudinal direction.
  • the outer flat tube-like regions 7 are, in order to obtain as uniformly wide flow cross sections as possible, curved slightly in the direction of one another in the region of their free ends, and the middle flat tube-like region 7 is shorter.
  • Fig. 4h shows the eighth embodiment, which substantially corresponds to the seventh embodiment, but the individual, inner flat tubes, which are connected to one side with the outer round tube, straight and have different widths to fill the interior of the round tube as evenly as possible ,
  • the ninth exemplary embodiment illustrated in FIG. 4i has wedge-shaped regions with chambers extending in the longitudinal direction, in addition to chambers arranged at an angle to one another, integrally connected to one side with the outer circular tube, inner flat tubes the channels between the wedges and flat tubes present have a constant width.
  • three inner flat tubes 7 arranged parallel to one another and at a distance from each other are provided, which are connected in one piece with the outer round tube 6 on one side.
  • the side connected to the round tube alternates, so that, in contrast to the embodiment of FIG. 4h, no fork-shaped regions but a meandering region remains between the individual flat tubes.
  • the eleventh embodiment shown in FIG. 4k differs from the tenth embodiment shown in FIG. 4j only in that, instead of three flat tubes, four flat tubes 7 are integrally and mutually connected to the round tube 6.
  • an outer tube can be used with a different cross section, in particular preferably with an oval cross section.
  • the tubes in which the longitudinally continuous chambers are formed in the cross-section of the (outer) tube, i. a single tube provides the channels for high and low pressure side.
  • the outer tube can also with ribs or similar. be formed, as well as have changing wall thicknesses.
  • the longitudinal extent does not necessarily have to be straight; on the contrary, a curved, for example U-shaped, or a helical configuration of the tube, as well as a corresponding configuration of the inner tube or chambers, is possible.
  • Fig. 5 shows a part of an inner heat exchanger 5, which corresponds in cross section substantially to the inner heat exchanger of Fig. 4i, in which, however, in the channels around the flat tubes 7 baffles 15 are provided.
  • baffles 15 are each arranged only in a partial region of the cross section and each offset from one another, so that the refrigerant flowing in the channel is constantly deflected. This prevents the formation of a laminar flow and mixes the refrigerant flowing outside and in the middle of the flow channel with each other, so that a very uniform temperature profile is formed and the heat transfer of the counterflowing refrigerant flows is optimized.
  • FIG. 5 in the upper, left-hand region, the opening 14 for the connection 9 in the radial direction can be seen, through which the low-pressure-side refrigerant is introduced into the inner heat exchanger 5.
  • the refrigerant is conveyed through the first deflecting plate 15, in particular into the width of the inner heat exchanger 5, i. distributed to the rearmost channel, so that even this inflow area is flowed through evenly by refrigerant.
  • the design of the discharge area is designed accordingly, so that the entire length of the inner heat exchanger 5 is used optimally.
  • the baffles 15 are presently arranged at equidistant intervals from each other and soldered to the flat tubes 7 and the inner wall of the round tube 6.
  • the baffles can also be integrally connected to one another and loosely inserted into the inner heat exchanger.
  • FIG. 6 shows a further embodiment of the outer tube as a round tube 6.
  • four flat tubes 7 arranged parallel to one another are arranged, wherein corrugated ribs 16 are respectively arranged between the flat tubes 7 for enlarging the heat transfer surface.
  • the ribs 16 lie with a portion each on the outside of the flat tubes 7 and here take heat from the same (or possibly also give heat to the same from). This heat is conducted into the oblique connection areas, which are surrounded by the refrigerant, which absorbs the heat.
  • the corrugated fins 16 are used for turbulence generation, ie prevent the formation of a laminar flow and thus ensure equalization of the temperature profile over the entire flow cross-section.
  • Such corrugated ribs can of course also be provided in connection with other types of flat tube geometries 7, in particular in conjunction with the above-mentioned embodiments of the flat tubes. 7
  • the described air conditioning system may also be used in an R134a refrigerant circuit or in a circuit with another suitable refrigerant.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP07013144A 2006-07-12 2007-07-05 Unité, comportant un refroidisseur de gaz et un échangeur thermique interne, et échangeur thermique Withdrawn EP1892491A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200610032570 DE102006032570A1 (de) 2006-07-12 2006-07-12 Einheit, aufweisend einen Gaskühler und einen inneren Wärmetauscher, und Wärmetauscher

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EP1892491A2 true EP1892491A2 (fr) 2008-02-27
EP1892491A3 EP1892491A3 (fr) 2009-02-18

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2402694A1 (fr) * 2010-06-30 2012-01-04 Valeo Systemes Thermiques Condenseur, notamment pour systeme de climatisation d'un vehicule automobile et echangeur de chaleur equipe d'un tel condenseur
DE102012017404A1 (de) * 2012-09-03 2014-03-27 GM Global Technology Operations, LLC (n.d. Ges. d. Staates Delaware) Interner Wärmetauscher für eine Kraftfahrzeug-Klimaanlage
CN110553533A (zh) * 2019-09-11 2019-12-10 上海蓝滨石化设备有限责任公司 一种铝制式空冷器多孔扁管与管板的连接结构

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007051123A1 (de) * 2007-10-24 2009-04-30 Behr Gmbh & Co. Kg Innerer Wärmerübertrager für einen Kältekreis
DE102009050888A1 (de) * 2009-10-27 2011-04-28 Behr Gmbh & Co. Kg Wärmeübertrager
KR101438608B1 (ko) * 2012-12-13 2014-09-05 현대자동차 주식회사 차량용 쿨링모듈
EP3742073B1 (fr) * 2019-05-21 2022-03-30 Carrier Corporation Appareil de réfrigération et utilisation associée

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19830757A1 (de) * 1998-07-09 2000-01-13 Behr Gmbh & Co Klimaanlage
DE10060114A1 (de) * 1999-12-09 2001-06-13 Valeo Climatisation Klimakreis, insbesondere für ein Kraftfahrzeug
FR2825456A1 (fr) * 2001-05-29 2002-12-06 Valeo Thermique Moteur Sa Echangeur de chaleur a boitier allonge, en particulier pour vehicule automobile
FR2840674A1 (fr) * 2002-06-11 2003-12-12 Denso Corp Dispositif d'echange de chaleur pour un cycle frigorifique a compression
JP2005221087A (ja) * 2004-02-03 2005-08-18 Matsushita Electric Ind Co Ltd 熱交換器
EP1724536A2 (fr) * 2005-05-11 2006-11-22 Modine Manufacturing Company Echangeur de chaleur avec partie accumulatrice
EP1734325A1 (fr) * 2004-03-17 2006-12-20 T.RAD Co,.Ltd Changeur de chaleur double tube et methode de production de celui-ci

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19830757A1 (de) * 1998-07-09 2000-01-13 Behr Gmbh & Co Klimaanlage
DE10060114A1 (de) * 1999-12-09 2001-06-13 Valeo Climatisation Klimakreis, insbesondere für ein Kraftfahrzeug
FR2825456A1 (fr) * 2001-05-29 2002-12-06 Valeo Thermique Moteur Sa Echangeur de chaleur a boitier allonge, en particulier pour vehicule automobile
FR2840674A1 (fr) * 2002-06-11 2003-12-12 Denso Corp Dispositif d'echange de chaleur pour un cycle frigorifique a compression
JP2005221087A (ja) * 2004-02-03 2005-08-18 Matsushita Electric Ind Co Ltd 熱交換器
EP1734325A1 (fr) * 2004-03-17 2006-12-20 T.RAD Co,.Ltd Changeur de chaleur double tube et methode de production de celui-ci
EP1724536A2 (fr) * 2005-05-11 2006-11-22 Modine Manufacturing Company Echangeur de chaleur avec partie accumulatrice

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2402694A1 (fr) * 2010-06-30 2012-01-04 Valeo Systemes Thermiques Condenseur, notamment pour systeme de climatisation d'un vehicule automobile et echangeur de chaleur equipe d'un tel condenseur
FR2962199A1 (fr) * 2010-06-30 2012-01-06 Valeo Systemes Thermiques Condenseur, notamment pour systeme de climatisation d'un vehicule automobile.
DE102012017404A1 (de) * 2012-09-03 2014-03-27 GM Global Technology Operations, LLC (n.d. Ges. d. Staates Delaware) Interner Wärmetauscher für eine Kraftfahrzeug-Klimaanlage
CN110553533A (zh) * 2019-09-11 2019-12-10 上海蓝滨石化设备有限责任公司 一种铝制式空冷器多孔扁管与管板的连接结构

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EP1892491A3 (fr) 2009-02-18

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