EP1734324A2 - Echangeur de chaleur interne réglable - Google Patents

Echangeur de chaleur interne réglable Download PDF

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Publication number
EP1734324A2
EP1734324A2 EP20060012225 EP06012225A EP1734324A2 EP 1734324 A2 EP1734324 A2 EP 1734324A2 EP 20060012225 EP20060012225 EP 20060012225 EP 06012225 A EP06012225 A EP 06012225A EP 1734324 A2 EP1734324 A2 EP 1734324A2
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EP
European Patent Office
Prior art keywords
heat exchanger
heat
tubes
exchanger according
media
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Withdrawn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
EP20060012225
Other languages
German (de)
English (en)
Inventor
Ralf Dr.-Ing. Manski
Bernd Schäfer
Thomas Strauss
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 EP1734324A2 publication Critical patent/EP1734324A2/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • 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
    • F28D7/0008—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 for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—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 for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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

Definitions

  • the invention relates to a heat exchanger for heat transfer between at least two heat-storing media. Furthermore, the invention relates to a heat exchanger assembly using such a heat exchanger and the use of the proposed heat exchanger or the proposed heat exchanger assembly.
  • Heat exchangers are used in a wide variety of applications for a very wide range of applications.
  • heat exchangers are used both in industrial processes, in motor vehicle construction, in air conditioning technology, in chemical processes and in power generation.
  • the size of the heat exchangers used in the process, as well as the heat-storing media used, cooled or heated, is correspondingly versatile.
  • heat energy is transferred from a first heat-storing medium to a second heat-storing medium.
  • the first medium releases heat
  • the second medium absorbs heat.
  • gaseous and liquid materials are considered as medium, although a mixture of liquid and gaseous substances may also be present.
  • at least one of the two media for example, solid state in the form of a suspension with it.
  • one or both of the media used in the course of Heat transfer changes its state of aggregation, that is, for example, a liquid (partially) evaporated or a gas (partially) condensed.
  • the inventors have made it their task to propose a heat exchanger, in which the heat output from the or the heat supply can be reduced in the corresponding heat-storing medium without the throughput of the heat storage medium through the heat exchanger or the heat exchanger assembly must be reduced -
  • the proposed heat exchanger or the proposed heat exchanger assembly should be particularly simple, inexpensive and space-saving, a low Have weight and as durable as possible, resistant and maintenance-insensitive or easy to be with the maintenance.
  • the inventors have set themselves the task of proposing a particularly advantageous use for such heat exchangers or such heat exchanger arrangements.
  • a heat exchanger for the heat transfer between at least two heat-storing media in such a way that it has a variable heat transfer interface, by means of which the degree of heat transfer between at least two of the media passed through the heat exchanger can be varied.
  • the heat transfer interface can also be constructed such that in her - in the presence of, for example, three or more media - the degree of heat transfer between each two of these media preferably can be changed individually and selectively.
  • a shift of a quotient of two heat transfer lines is to be considered.
  • the heat exchanger it is possible thanks to the proposed design of the heat exchanger that, for example, in the case of two heat-storing media, between which there is a heat transfer, one of the media or both media with unchanged mass flow rate can flow through the heat exchanger, and it is still possible that Heat transfer between the two Change media depending on the respective operating state of the plant having the heat exchanger.
  • the coolant radiator could thus be subjected to the usual coolant flow rate, it being still possible, for example during the warm-up phase of the engine, to reduce the heat removal from the coolant.
  • the heating time of the engine can be reduced, although it can be dispensed with a separate short-circuited refrigerant circuit, which requires corresponding branch points and components, in particular a thermostatic valve.
  • a separate short-circuited refrigerant circuit which requires corresponding branch points and components, in particular a thermostatic valve.
  • Such a structure may prove to be less expensive, more space-saving, more durable and less susceptible to interference.
  • variable heat transfer interface has a variable material introduction device. It would thus be possible for a heat-insulating material to be introduced or removed between two heat exchanger tubes penetrated by the respective heat-storing media, or else a heat-conducting material would be introduced or removed. A combination of these two possibilities is conceivable.
  • the material introduced or to be removed can be a solid or else a suitable medium, in particular a suitable fluid, which can be introduced, for example, into a tube arranged between two heat transfer tubes interspersed by the respective heat-storing media filled with the appropriate medium or can be emptied of this.
  • the Heat transfer rate can be varied by a corresponding degree of filling.
  • a variable heat transfer coefficient can be realized for example by a corresponding pressurization.
  • the variable heat transfer rate can be realized by a correspondingly wide insertion or removal of the appropriate material.
  • variable heat transfer interface has at least one adjustable fluid supply device.
  • the variation of the degree of heat transfer between the respective heat-storing media can be achieved by a heat externally passed to the heat exchanger tubes fluid (for example, a gas, in particular ambient air) a first heat-storing medium, which transfers heat to a second heat-storing medium, heat energy, so that this heat energy is no longer available for transmission from the first to the second heat-storing medium.
  • a variation of the heat transfer between the first and second heat-storing medium can be achieved.
  • adjustable fluid supply device is at least partially designed as a flap blind and / or as a roller blind.
  • Such components are known per se and are widely used for other tasks. They are relatively inexpensive to obtain and usually have a state of development, which allows a low-cost, low-maintenance use.
  • a suitable tube configuration, in particular for the heat exchanger tubes, results if the heat exchanger has at least one coaxially formed pipe section.
  • two heat-storing media can be guided in particularly intimate thermal contact with each other, while still leaving the possibility to bring a third medium in good thermal contact with at least one of the two heat-storing media.
  • a preferred design in practice results when the heat exchanger is designed as a flat tube heat exchanger with stacked stacked, parallel to each other running flat tubes. With such an embodiment, a very good maximum degree of heat transfer between the heat-storing media can be realized at relatively low cost of materials and space requirements. Of course, it is also possible with flat tubes to realize a coaxial structure.
  • At least one pipe section of the heat exchanger has a plurality of flow channels for at least one of the media passed through the heat exchanger.
  • pressures in the range of 100, 120, 130, 133, 135, 140, 150, 180 or 200 bar are quite easily controlled with quite reasonable material costs and using conventional, relatively inexpensive materials.
  • the heat exchanger in such a way that at least one tube is formed in one piece, at least one tube is formed in several pieces or a combination thereof is present.
  • a good compromise of ease of manufacture, particularly good strength and durability, pressure tightness, manufacturing cost, material workability, etc. can be found.
  • a conceivable design results if at least a portion of the heat exchanger tubes is arranged directly above one another, at least in regions.
  • a particularly compact construction and a particularly high maximum heat transfer capacity can be realized.
  • At least a portion of the heat exchanger tubes is arranged at least partially spaced from each other. Such a distance can for example be used for introducing heat-insulating or heat-transferring materials or be used for tubular cavities that can be filled with heat-insulating or heat-transfer fluids.
  • variable in particular, if the variable cherrykragungstrestelle having an adjustable gas supply means, it is also useful if corrugated ribs are arranged between at least part of the heat exchanger tubes. By such corrugated fins, the interface surface to the fluid flowing through (for example, cooling air) can be increased.
  • first heat transfer medium - second heat transfer medium - first heat transfer medium - cavity - second heat transfer medium - corrugated rib - first heat transfer medium - etc. is chosen from the beginning.
  • heat exchanger tubes By a three-dimensional arrangement of heat exchanger tubes in particular space advantages can result.
  • heat exchanger tubes not only laid in a plane, but it is realized by superimposing two such levels a three-dimensional construction, resulting in a commonly referred to as a "double row" heat exchanger.
  • the proposed heat exchanger is at least partially made of aluminum and / or an aluminum alloy.
  • a particularly cost-effective production can in particular also arise if at least parts, such as in particular heat exchanger tubes and / or manifolds of the heat exchanger are manufactured by means of an extrusion process.
  • heat exchanger tubes provided with so-called "microchannels" can be manufactured in a particularly simple and cost-effective manner.
  • the heat exchanger is designed as an internal heat exchanger for a refrigerant circuit. It has been found that a heat exchanger with the proposed design is particularly advantageous for this application. This is especially true when using carbon dioxide as the refrigerant for the refrigerant circuit.
  • a heat exchanger arrangement in which at least one heat exchanger with the above-described construction, possibly including their variation options, and one or more other heat exchanger has.
  • this may result in a type of heat exchanger module, in which the heat exchanger module has a heat exchanger of the construction proposed in advance and in which other parts are designed as further, other tasks, heat exchangers.
  • Such a design as a multifunctional module may prove to be advantageous, in particular with regard to space requirements, but also with regard to assembly.
  • the further heat exchangers of the heat exchanger arrangement may be, for example, gas coolers, condensers, coolant coolers, oil coolers, intercoolers, exhaust gas coolers and / or evaporators.
  • Such heat exchangers are usually present in a large part of the currently produced motor vehicles.
  • At least one collecting tube for the heat exchanger and at least one collecting tube for a further heat exchanger is designed as a continuous collecting tube, in particular as a fluidically continuous collecting tube.
  • a mechanically continuous, but possibly fluidly separated manifold may prove to be beneficial, for example, in terms of stability and manufacturing cost of the heat exchanger assembly.
  • the fluidic separation can be realized for example by a soldered or welded disc.
  • the manifold can also be carried out fluidically throughout, which is particularly advantageous if the corresponding medium anyway must flow through different heat exchanger in sequence, as is the case for example in a gas cooler with a downstream internal heat exchanger (IWT).
  • IWT internal heat exchanger
  • heat exchanger tubes of at least two different heat exchangers it is possible for heat exchanger tubes of at least two different heat exchangers to be arranged at least partially spaced from each other. As a result, a particularly good thermodynamic separation of the corresponding heat exchanger regions of the heat exchanger arrangement can be realized.
  • heat exchanger tubes of at least two different heat exchangers may be formed directly adjacent to one another at least in regions in the heat exchanger arrangement. This may possibly bring a simplification in the production of the heat exchanger assembly with it.
  • an inherently undesirable heat transfer occurs by the associated with the mechanical contact thermal coupling, but this can for example a Have magnitude in which the resulting effects in relation to other benefits are only of minor importance.
  • thermal insulation means in particular between the heat exchanger tubes of different heat exchangers, are provided.
  • Thermal insulation means in this sense can be not only insulating materials, but also, for example, suitable thermal insulation recesses, so that thermal decoupling is realized, for example, by a corresponding removal of material (which, for example, can also be provided in the corrugated fins) ,
  • FIG. 1 shows a block diagram of a refrigerant circuit 10 which in the present case uses R744 or carbon dioxide as the refrigerant.
  • the refrigerant circuit 10 comprises in a conventional manner a compressor 4, a gas cooler 3 (since a carbon dioxide refrigeration cycle is usually operated supercritically, is spoken by a gas cooler 3 instead of a condenser), the high-pressure part 8 of an internal heat exchanger (IWT) 2, an expansion device 6, an evaporator 5, a Kätteschakkumulator 1 and the low-pressure part 9 of the inner heat exchanger 2, which are flowed through during operation of the air conditioner in this order from the refrigerant.
  • the gas boiler 3 and the inner heat exchanger 2 are part of a heat exchanger assembly 7 described in more detail below, which additionally has further, not shown in Figure 1 for illustrative reasons, heat exchanger.
  • the inner heat exchanger 2 is, according to the invention, designed as a heat exchanger with a variable heat transfer rate.
  • refrigerant circuits which use carbon dioxide as a refrigerant can under certain operating conditions, eg. B. in the case of a high pressure ratio between the high pressure side 8 and low pressure side 9 shortly after switching on the air conditioning or at very high ambient temperatures, occur that the refrigerant due to the compression in the compressor 4 at the output side of the compressor 4 has a very high temperature above a maximum permissible refrigerant temperature (hot gas temperature).
  • hot gas temperature a maximum permissible refrigerant temperature
  • the compressor power 4 is reduced so that the hot gas temperature does not exceed the maximum allowable value.
  • this method ensures compliance with the temperature limits, this is done at the expense of the refrigeration capacity of the air conditioner.
  • such a reduction of the cooling capacity is undesirable, in particular at high outside temperatures or shortly after switching on the air conditioning system, because a comfortable interior temperature in the vehicle can not or can be achieved only much later.
  • the inventors have now recognized that it is also possible to reduce the inlet temperature of the refrigerant at the inlet to the compressor 4, which also results in a reduction of the hot gas temperature of the refrigerant after the compressor 4.
  • the simplest way initially would be to dispense with the installation of an internal heat exchanger 2.
  • this would result in a deterioration of the cooling capacity and a deterioration of the efficiency of the refrigerant circuit result.
  • the inventors propose an internal heat exchanger 2 in which the degree of exchange between the low-pressure side refrigerant 9 (refrigerant) flowing from the accumulator 1 to the compressor 4 and high-pressure side refrigerant 8 (refrigerant flowing from the gas cooler 3 to the expansion valve 6) are varied can.
  • the degree of exchange is chosen to be large, so that the coming of the gas cooler 3 refrigerant can be pre-cooled in the inner heat exchanger 2 and only then flows to the expansion element 6, where it is further cooled during the expansion and thereby liquefied.
  • FIG 2 the schematic structure of the heat exchanger assembly 7 used in Figure 1 is outlined.
  • the heat exchanger arrangement is characterized by an air flow, which is indicated in Figure 2 by arrows A, with external cooling air applied. If, under certain driving conditions of the motor vehicle provided with the heat exchanger arrangement 7, an increased admission of external cooling air is required (eg at high outside temperatures in traffic jams or slow uphill driving with high towing loads), a fan 13 integrated in the heat exchanger arrangement 7 can be activated be to increase the air flow rate A through the heat exchanger module 7.
  • the heat exchanger module 7 has an inner heat exchanger 2, a gas cooler 3, a charge air cooler 11 and a coolant cooler 12.
  • Gas cooler 3 and inner heat exchanger 2 are arranged in a plane and are supplied in parallel with cooling air A. Behind the plane of inner heat exchanger 2 and gas cooler 3 are - in series and in this order - the intercooler 11, the intercooler 12 and the (suction) fan 13th
  • the air supply duct 17 for the inner heat exchanger 2 is a presently designed as a jalousie 16 adjustable air supply device.
  • a roller blind is possible, such as a roller blind.
  • the folding blind 16 (or another type of construction) can, moreover, also be arranged adjacent to the inner heat exchanger 2 or also with respect to the air flow A behind the inner heat exchanger 2.
  • FIG. 3 shows a first possible exemplary embodiment of an internal heat exchanger 2 with a variable degree of heat exchange between high-pressure side 8 and low-pressure side 9 refrigerant.
  • the inner heat exchanger 2 is shown as a flat tube heat exchanger with a plurality of flat tubes 20 arranged one above the other. Between the flat tubes 20 corrugated fins 25 are arranged, which increase the heat transfer to the possibly passing outside air A.
  • the flat tubes 20 are, as shown in FIGS. 4 and 5, designed as coaxial flat tubes 20.
  • the flat tubes are formed in an extrusion process with a plurality of microchannels 15.
  • the inner microchannels 15 lie in the high pressure side 8 part 28 of the refrigerant circuit 10. Accordingly, the outer microchannels 15 are in the low pressure side 9 part 29 of the refrigerant circuit.
  • the high-pressure-side part 28 of the flat tubes 20 is made longer in relation to the low-pressure-side part 29 of the flat tubes 20.
  • Figure 6 only one end side 30 of the flat tube 20 is shown;
  • the extended version 30 of the high-pressure-side part 28 of the flat tube 20 relates to both sides 30 of the flat tube 20.
  • the high-pressure-side 8 tube projections 30, which can be seen in FIGS. 4 and 6, can be formed, for example, in that the flat tube 20 is extruded in one piece and the corresponding side portion 30 of the flat tube is tapered by a chipping processing on the high pressure side inner part 28. It is also possible that the high-pressure side inner part 28 of the flat tube 20 and the low-pressure side outer part 29 of the flat tube 20 are each extruded separately and then plugged into each other (multi-piece structure). Depending on the requirement, both types of construction can be considered to be more favorable for the respective purpose.
  • the low-pressure-side outer part 29 of the flat tube 20 opens into a low-pressure-side collecting tube 21 of the inner heat exchanger 2 designed as a round tube.
  • the high-pressure-side 8 inner region 28 of the flat tube engages with its Side region 30, the low-pressure side manifold 21 completely and flows into the high-pressure side manifold 18, which is also designed here as a round tube.
  • one of the high-pressure side manifolds 18 fluidly communicates with a manifold of the gas cooler 3 in connection.
  • the collecting pipes 18 of the inner heat exchanger 2 are completely separated from the collecting pipes of the gas cooler 3, for example by introducing a separating disk.
  • connecting flanges 22, 23 are sketched, which serve as inlet 26 and outlet 27 for the low pressure level 9 located refrigerant.
  • the illustrated in Figure 3 internal heat exchanger 2 is designed as a so-called “single-entry" heat exchanger, that is, the supplied through the flange 22, located at low pressure level 9 refrigerant passes through the respective outer regions 29 of the flat tubes 20 in the same direction flow direction B and then the connection flange It is noted that the flow direction of the refrigerant B refers only to the low-pressure side 9 part 29. In contrast, the high-pressure side 8 refrigerant can flow in the same or opposite direction through the inner region 28 of the flat tubes 20.
  • FIG. 8 also outlines a low-pressure-side flow rate deviating from FIG. 3 in the form of a so-called "double-flow" heat exchanger.
  • the 26 refrigerant entering via the connection flange 21 is directed through a partition wall 22 located in one of the two low-pressure-side header tubes 21 through the flat tube 20 which is at the bottom in FIG.
  • a further deflection in the right in Figure 8 located on the low pressure side manifold 21 it flows in the opposite direction through the two above in Figure 8 flat tubes 20 back to left in Figure 8 low-pressure manifold 21, where it finally exits at the connecting flange 23.
  • the flow direction in the high-pressure side 8 inner part 28 of the flat tubes 20 is independent of the respective flow direction in the low-pressure side 8 outer region 28 of the flat tubes 20th
  • FIGS. 9 to 11 show, by way of example, further possible combinations for a heat exchanger module 7 with an inner heat exchanger 2.
  • the inner heat exchanger 2 is formed in a lower region of the gas cooler 3.
  • the gas cooler 3 is constructed as shown in Figure 9 construction of the heat exchanger module 7 as a double-row flat tube gas cooler. In the lower area in FIG. 9, however, one of the two rows of flat tubes of the gas cooler 3 serves as the inner heat exchanger 2. This structure can be of advantage, in particular in the case of particularly cramped space conditions.
  • the inner heat exchanger 2 can in any way as part of the heat exchanger module 7 integrally formed (as indicated in Figure 10) or be formed separately from the heat exchanger module 7.
  • FIG. 11 shows a construction in which the inner heat exchanger 2 is formed integrally in the heat exchanger module 7 and is aligned with parts of the charge air cooler 11 and coolant cooler 12 in a plane with the gas cooler 3. However, the inner heat exchanger 2 is fluidly removed with the aid of an air partition wall 14 from the outside air flow A.
  • heat exchangers with a variable heat transfer rate in which the variation of the heat transfer rate takes place without exposure of the heat exchanger to outside air passing through it, are advantageous.
  • Conceivable embodiments of such heat exchangers are outlined in Figures 12 and 13.
  • first medium lines 31 are provided for a first heat-storing medium (eg medium to be cooled), which are formed as a flat tube 20 with a multiplicity of microchannels 15.
  • second medium lines 32 are provided, through which a second heat-storing medium (for example, medium to be heated) flows- first medium lines 31 and second medium lines 32 are stacked one on top of the other alternately. It is between first Medium lines 31 and second medium lines 32 each have a coupling tube 33 is arranged.
  • the coupling tube 33 has a cavity 35, which can be filled with an insulating or thermally conductive fluid, or can be emptied again.
  • the heat transfer between the first medium lines 31 and second medium lines 32 which are in each case thermally contacted via the coupling tube 33, varies in size, resulting in the desired variability of the heat transfer between first and second medium.
  • FIG. 13 shows a further embodiment of a heat exchanger with variable heat transfer coefficient.
  • triple stack 36 of first medium lines 31 and second medium lines 32 are formed.
  • a first version 36 a of the triplet stack 36 is a second medium line 32 in the middle and is (at their flat sides covered) of two first Mediumleiturigen 31.
  • the second version 36 b the triplet stack 36, the first medium line 31 in the middle arranged and their flat outer sides are covered by second medium lines 32.
  • the two versions 36 a, 36 b each alternate from each other, wherein in each case between two Dreierstapein 36 a coupling tube 33 of the type already described is provided.
  • the tubes illustrated in FIGS. 12 and 13 can be connected to one another by soldering, for example.
  • the cavities 35 of the coupling tubes 33 can be filled or emptied by filling openings not shown in FIGS. 12 and 13 for reasons of clarity.
  • the coupling tubes 33 it is also conceivable that corresponding recesses are provided in the example, control slide can be inserted.
  • heat exchangers 34 shown in Figures 12 and 13 are also suitable for other heat exchanger applications than for use as an internal heat exchanger in refrigerant circuits.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP20060012225 2005-06-17 2006-06-14 Echangeur de chaleur interne réglable Withdrawn EP1734324A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510028510 DE102005028510A1 (de) 2005-06-17 2005-06-17 Verstellbarer innerer Wärmeübertrager

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Cited By (3)

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Publication number Priority date Publication date Assignee Title
FR2906353A1 (fr) * 2006-09-21 2008-03-28 Valeo Systemes Thermiques Echangeur de chaleur interne pour circuit de fluide refrigerant
US10183269B2 (en) 2015-06-10 2019-01-22 Corning Incorporated Continuous flow reactor with tunable heat transfer capability
CN114777360A (zh) * 2022-04-01 2022-07-22 浙江理工大学 一种家用小型太阳能空气源复合热泵系统

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DE102020110299A1 (de) 2020-04-15 2021-10-21 Volkswagen Aktiengesellschaft Kombinationsbauteil für eine Klimatisierungsvorrichtung für ein Kraftfahrzeug

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CN114777360A (zh) * 2022-04-01 2022-07-22 浙江理工大学 一种家用小型太阳能空气源复合热泵系统

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