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EP1903293A2 - Gas-Wasser-Wärmetauscher, insbesondere für eine Klimaanlage eines Kraftfahrzeugs, bei der eine Kühlflüssigkeit zum Einsatz kommt, die im superkritischen Zustand eingesetzt wird, wie CO2 - Google Patents

Gas-Wasser-Wärmetauscher, insbesondere für eine Klimaanlage eines Kraftfahrzeugs, bei der eine Kühlflüssigkeit zum Einsatz kommt, die im superkritischen Zustand eingesetzt wird, wie CO2 Download PDF

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Publication number
EP1903293A2
EP1903293A2 EP07116262A EP07116262A EP1903293A2 EP 1903293 A2 EP1903293 A2 EP 1903293A2 EP 07116262 A EP07116262 A EP 07116262A EP 07116262 A EP07116262 A EP 07116262A EP 1903293 A2 EP1903293 A2 EP 1903293A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
fluid
exchanger
heat
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Withdrawn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
EP07116262A
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English (en)
French (fr)
Other versions
EP1903293A3 (de
Inventor
Carlos Martins
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.)
Valeo Systemes Thermiques SAS
Original Assignee
Valeo Systemes Thermiques SAS
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 Valeo Systemes Thermiques SAS filed Critical Valeo Systemes Thermiques SAS
Publication of EP1903293A2 publication Critical patent/EP1903293A2/de
Publication of EP1903293A3 publication Critical patent/EP1903293A3/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05358—Assemblies of conduits connected side by side or with individual headers, e.g. section type radiators
    • 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
    • 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
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F28D7/0083—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 a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium
    • F28D7/0091—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 a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium the supplementary medium flowing in series through the units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • 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 heat exchangers of the liquid / gas type, especially for air conditioning equipment of a motor vehicle.
  • It relates more particularly (but without limitation) heat exchangers for air conditioning circuits using a refrigerant such as carbon dioxide (CO 2 ) operating in the supercritical state, that is to say where the fluid remains mostly in the gaseous state in the air conditioning circuit.
  • a refrigerant such as carbon dioxide (CO 2 ) operating in the supercritical state, that is to say where the fluid remains mostly in the gaseous state in the air conditioning circuit.
  • Such a circuit essentially comprises a compressor, a gas cooler, an internal heat exchanger, a pressure reducer, an evaporator and an accumulator.
  • the gas cooler which replaces the condenser of conventional air conditioning circuits, is arranged to cool the gaseous refrigerant fluid by heat exchange with either the ambient air (air / gas type heat exchanger) or with the engine coolant. (heat exchanger type lidquide / gas).
  • the invention relates more specifically to the heat exchangers of the liquid / gas type, also called “water / gas exchanger” or Water / Gas Cooler (“WGC”), equipping such circuits.
  • liquid / gas type also called “water / gas exchanger” or Water / Gas Cooler (“WGC”)
  • the cooling of the gas is generally operated on several stages, each with a specific liquid / gas heat exchanger.
  • FR-A-2,875,743 (Valeo Thermal Systems) thus describes an air conditioning circuit where a gaseous refrigerant such as CO 2 is cooled by a succession of three exchangers operating respectively at high temperature (80 to 100 ° C, typically 90 ° C), low temperature (50 ° C). at 70 ° C, typically 60 ° C) and at very low temperatures (30 to 60 ° C, typically 50 ° C).
  • These three heat exchangers are supplied with heat transfer liquid by different fluid circulation loops, with specific temperatures and flow rates at each stage of the gas cooler.
  • the air conditioning circuits using CO 2 as a refrigerant fluid are more complex to achieve, particularly in terms of mechanical resistance, given the fluid pressures that can reach values, up to 450 bar, much higher than the pressures usually encountered in conventional air conditioning systems using phase change fluids such as fluorinated compounds.
  • phase change fluids such as fluorinated compounds.
  • the problem that the invention aims to solve is that of reducing the size of the liquid / gas heat exchanger, to make it possible to facilitate the installation of the gas cooler under the hood of the vehicle in a maximum of possible architectures. to be encountered, in particular to bring the gas cooler closer to the compressor or the evaporator, and to reduce the lengths of gas pipes.
  • Another object of the invention is to make it possible to fix the exchanger on the engine or on the compressor, a configuration which has the particular advantage of allowing the use of rigid pipes in the most heat-stressed zone between the compressor. and gas cooler.
  • Another object of the invention is to allow the integration in the same functional block not only of the liquid / gas heat exchanger ("WGC”) cooling the gas output of the compressor, but also the exchanger internal gas / gas heat of the cooling circuit.
  • This internal heat exchanger also called “IHX” (In ternal Heat eXchanger ) is in fact arranged in the circulation loop of the refrigerant gas just downstream of the cooler WGC (hot circuit) and upstream of the compressor (Cold circuit), so that it would be advantageous to be able to mechanically and functionally combine the gas cooler WGC and the internal heat exchanger IHX so as to eliminate the lengths of connections between exchangers and minimize the length of connection to the compressor.
  • Yet another object of the invention is to allow the realization of a liquid / gas type heat exchanger which is, in practice, as compact and provides the same performance as an air / gas heat exchanger.
  • the liquid / gas exchangers proposed so far were indeed, at equal performance, generally more bulky than an air / gas exchanger, which made them prefer despite their disadvantages, in particular the need for long lengths of high gas tubes.
  • pressure to connect to the rest of the circuit the air / gas exchanger mounted on the front of the vehicle to allow satisfactory cooling). In the case of rigid tubes, these connections are expensive and difficult to decouple from the engine; in the case of flexible connections, these are very thermally and mechanically stressed.
  • a liquid / gas type exchanger does not need to be mounted on the front panel and can therefore be fixed close to the motor or compressor, with rigid pipes in the most thermally and mechanically stressed areas. .
  • the invention proposes a heat exchanger between a first fluid and a second fluid of the known type described in FIG. FR-A-2,852,383 above, that is to say comprising an interior space and a bundle of tubes provided in said interior space, in which the first fluid circulates and is cooled by the second fluid, and wherein the second fluid is introduced into the heat exchanger through an inlet pipe and discharged through an outlet pipe and occupies the interior space of the heat exchanger (will be understood as “space inside the exchanger "the space between, on the one hand, the tubes used to convey the first fluid and, on the other hand, the outer walls or the envelope of the heat exchanger).
  • a heat exchanger considered as such, which does not intrinsically include the collector or boxes conventionally serving as an inlet and outlet chamber for one of the fluids .
  • the heat exchanger defines at least two passes for the second fluid ("pass" means the path of a fluid in one direction).
  • the fluid circulates within the heat exchanger (which extends generally in a plane) in two directions and following two distinct paths, these two directions of circulation being usually - but not necessarily - opposite the one to another.
  • the fluid flows in the plane defined by the exchanger with two directions of circulation and three paths.
  • the number of passes is related to the number of changes in fluid flow direction.
  • a two-pass fluid has a change of direction while a three-pass fluid has two changes in direction of flow.
  • the heat exchanger can further define at least two passes also for the first fluid.
  • the first fluid is a gas and the second fluid is a liquid
  • WGC liquid / gas heat exchanger
  • the interior space comprises at least two housings, each of the housings enclosing a plurality of tubes and delimiting a pass for the first fluid
  • housing means an outer casing for the heat exchanger.
  • the walls of this envelope may be formed in part by one or collector box walls (s) attached (s) to the heat exchanger).
  • the two casings may have a common wall, in particular parallel to the tube bundle, which comprises at least one orifice for placing the internal space of the two casings in communication.
  • the heat exchanger may comprise collecting boxes, disposed at the ends of the bundle, capable of assembling and placing the tubes of the bundle in communication at their ends, these collecting boxes being adapted to be further connected to a circulation circuit of the first fluid.
  • a heat exchange module comprising at least two adjacent heat exchangers as defined above according to the first aspect of the invention, with a first heat exchanger and a second heat exchanger.
  • One of the heat exchangers is connected to an inlet pipe and the other heat exchanger is connected to an outlet pipe, these two pipes being adapted to be placed in communication with a circuit of the second fluid.
  • the two heat exchangers have a common wall extending parallel to the tube bundle and having at least one orifice for communicating the internal space of the first heat exchanger with the internal space of the second heat exchanger.
  • the fluid inlet and outlet pipes are disposed at the same respective end of the first heat exchanger and the second heat exchanger, the port (s) being placed in communication with each other. disposed in the region of the opposite end of the first heat exchanger and the second heat exchanger.
  • each heat exchanger comprises a casing with two side walls facing each other between which the tube bundle extends transversely, and in that the transverse dimension separating these walls is substantially the same as that of the bundle of tubes. tubes, except for enlarged side regions in the vicinity tubing and (s) the port (s) of communication.
  • the side walls and the bundle of tubes can then be brazed together in particular in the region where the transverse dimension separating these walls is substantially the same as that of the bundle of tubes.
  • the manifolds are formed of a superposition of plates alternately forming fluid passage and spacer for the selective distribution of the first fluid in the various tubes of the bundle, and the wall common to both exchangers comprises in the longitudinal direction.
  • said at least two adjacent heat exchanger modules are two main heat exchangers forming a first heat exchanger stage, and at least two adjoining auxiliary heat exchangers are provided forming a second heat exchanger stage, distinct from the first stage exchanger and mounted adjacent to it.
  • the collector boxes of the first and second exchanger stages are interconnected successively in series so as to allow the circulation of the first fluid successively in the first and the second exchanger stage.
  • the device of the invention further includes an internal heat exchanger stage.
  • This comprises a stack of elongate multi-channel tubes, these tubes being joined and stacked alternately in two sets of nested tubes, with a first series of tubes connected to the outlet of the heat exchanger (s) so as to be traveled by the first high pressure fluid delivered by this (these) heat exchanger (s), and a second series of tubes adapted to be connected to a low pressure branch of the first fluid circuit so as to be traversed by the first fluid cold circulating in this branch.
  • the internal exchanger stage may advantageously be configured adjacent to the assembly formed by the first and second heat exchange stages.
  • This internal exchanger stage can comprise in particular collecting boxes arranged at the opposite ends of the stack of tubes, able to join and connect at their ends the respective tubes of the two series of tubes and to selectively distribute the first fluid, these boxes. collectors further comprising means for connecting to the circuit of the first fluid.
  • manifolds are preferably arranged in alignment with the manifolds of the first and second heat exchanger heat exchangers.
  • They can also be connected in series with the collector boxes of the heat exchangers of the first and second heat exchanger stages so as to allow the supply of the internal exchanger stage by the hot fluid at high pressure delivered directly by the first and second stages heat exchangers.
  • an air conditioning equipment for a motor vehicle comprising a heat exchanger, or a heat exchange module, as defined above.
  • Figure 1 is a diagram showing the various elements of a motor vehicle air conditioning system using a refrigerant operating in the supercritical state such as CO 2 .
  • Figure 2 is a perspective view of a double liquid / gas heat exchanger according to the invention.
  • FIG. 3 is a front view of the exchanger of FIG. 2, illustrating in particular the flow directions of the gas and liquid circuits.
  • FIG. 4 is an exploded perspective view of the exchanger of FIG. 2.
  • Figure 5 is a side view in section, along V-V of Figure 3, at the passages of communication of the water circuits of the various modules.
  • Figure 6 is a perspective view of a double liquid / gas heat exchanger of the type illustrated in Figure 2, further associated with an internal heat exchanger disposed in the same functional unit.
  • FIG. 7 is an exploded perspective view of the internal heat exchanger of the assembly of FIG. 6.
  • Figure 8 is a plan view, in section, of the heat exchanger at the high pressure hot circuit.
  • Figure 9 is a plan view, in section, of the heat exchanger at the low pressure cold circuit.
  • FIG. 1 illustrates a motor vehicle air conditioning circuit using a refrigerant fluid operating in the supercritical state, such as CO 2 , where the temperature of the coolant is lowered by heat exchange with the engine coolant.
  • a refrigerant fluid operating in the supercritical state such as CO 2
  • the circuit comprises a compressor 10, for example an externally controlled compressor controlled by a control electronics 12.
  • Compressed refrigerant gas G then passes through a gas cooler 14 comprising one or more successive exchangers, namely three exchangers WGC1, WGC2 and WGC3 mounted in series in the example shown.
  • the refrigerant gas G passes through an internal exchanger IHX referenced 16, then is expanded in a pressure reducer 18, for example an expansion valve controlled also by the control electronics 12.
  • the gas thus relaxed is led to an exchanger 20 performing the same function as the evaporator of a conventional refrigerant phase change air conditioning circuit, then to an accumulator 22 and the internal exchanger 16, before being recycled to the compressor 10.
  • the gas cooler 14 comprises for example, as illustrated in FIG. 1, a series of three exchangers WGC1, WGC2 and WGC3 operating respectively at high temperature, low temperature and very low temperature.
  • the first exchanger WGC1 is a water / gas exchanger using as a cold source the engine coolant, which here constitutes the heat transfer liquid L flowing in the water side exchanger. This liquid is usually water with antifreeze (brine) or liquid similar.
  • the low temperature heat exchanger WGC2 also uses the engine coolant L as a cold source via a loop distinct from the loop feeding the exchanger WGC1.
  • the very low temperature heat exchanger WGC3 can also use as cooling source the coolant of the engine L, via a loop distinct from the loop feeding the exchanger WGC1, or operate by contact with ambient air taken from outside the engine. vehicle.
  • the third stage WGC3 of the cooler can be omitted, the coolant then simply being cooled by two exchangers both traversed by the engine coolant.
  • the high temperature is usually of the order of 80 to 100 ° C (typically 90 ° C), the low temperature of the order of about 50 to 70 ° C (typically 60 ° C), and the very low temperature of the order of 30 to 60 ° C (typically 50 ° C) in the case of a water / gas exchanger using the engine coolant, or a temperature depending on the ambient air in the case of an air exchanger / gas (the "temperature” being understood as the temperature of the coolant circulating in the water / gas heat exchanger).
  • the invention relates more particularly to the mechanical production of low temperature exchangers WGC2 and / or very low temperature WGC3.
  • exchanger block of the invention can also be integrated into an assembly comprising other members of the circuit of the air conditioning equipment.
  • the reference 24 generally denotes a unitary unit grouping together the two exchangers WGC2 and WGC3 operating respectively at low and very low temperatures.
  • This unit block 24 comprises a gas inlet 26 receiving the refrigerant gas G after it has been cooled by the very high temperature exchanger WGC1., And a gas outlet 28 delivering the gas cooled by the exchangers WGC2 and WGC3 to the internal exchanger 16 for expansion and recycling to the compressor.
  • the low temperature heat exchanger WGC2 consists of two superposed cooler modules 30, 40, of similar external dimensions.
  • the upper module 30 is provided with a pipe 32 for the outlet of the heat-transfer liquid L, and the lower module 40 for a pipe 42 for the admission of the coolant L.
  • the very low temperature heat exchanger WGC3 consists of two superposed cooler modules 30 ', 40', of external dimensions similar to each other and similar to those of the modules 30 and 40.
  • the upper module 30 ' is provided with a tube 32 the heat transfer liquid L, and the lower module 40 'of a tube 42' for admission of the coolant L.
  • each of the modules comprises a bundle of flat elongated multichannel tubes traversed by the refrigerant gas.
  • the upper module 30 of the exchanger WGC2 thus includes a beam referenced 34, and the lower module 40, a beam referenced 44.
  • the modules 30 'and 40' of the exchanger WGC2 have an identical structure.
  • the tubes of the bundles 34, 44 are of the multichannel type, pierced internally by a multiplicity of parallel channels traversed by the refrigerant gas under pressure.
  • the different multichannel tubes of the bundle extend parallel to each other in the longitudinal direction (that is to say the direction of the largest dimension of the modules 30, 40) and are spaced apart so as to allow the circulation of the heat transfer liquid between the tubes, and therefore on each of the faces of the flat tubes internally traversed by the gas to be cooled.
  • manifold boxes 36, 38 (likewise 46, 48 for the bundle 44 of the module 40).
  • the manifolds 36, 38 consist of an alternating stack of hollow plates allowing the circulation and distribution of the gas refrigerant, and spacers plates to define the interval between the successive tubes of the beam.
  • the refrigerant gas introduced through the inlet 26 is distributed by the manifold 36 so as to distribute the circulation of this gas, under high pressure, in the different channels of the different tubes. Beam 34.
  • the manifold 38 connects the different channels of the different tubes to direct the flow of gas to the manifold 48 of the lower module 40 located immediately below the manifold 38.
  • the gas flows then in the bundle of tubes 44 of the lower module 40 in the opposite direction from that in which it circulated in the bundle 34 of the upper module, and this up to the opposite end, to reach the header box 46.
  • the gas flow is then directed from the manifold 46 to the manifold 36 'of the upper module of the exchanger WGC3, where it will follow a circuit comparable to that it followed in the exchanger WGC2, it is ie via the manifold 36 ', the tube bundle of the upper module 30', the manifolds 38 'and 48', the bundle of tubes of the lower module 40 ', then the manifold 46' before reach the gas outlet 28.
  • the liquid is admitted through the inlet pipe 42 located at one end of the lower module 40 of the exchanger WGC2.
  • the liquid will flow to the other end of the same module, against the current of the gas flow direction (see in particular Figure 3), passing between the tubes of the beam.
  • Disruptive elements of the exchanger may be provided, in a manner known per se, to increase the turbulence of the liquid flow and thus promote heat exchange with the tubes of the beam with which this fluid is in contact.
  • the circulation of the coolant is similar in the modules 30 'and 40' of the very low temperature exchanger WGC3.
  • the gas flowing in the different bundles of successive tubes exchangers WGC2 and WGC3 will be able to be cooled, from one module to another, by the circulation of the coolant, always against the current with the gas.
  • the casing of the module 30 consists of a U-shaped element 50 comprising a bottom wall 52 extending parallel to the bundle of tubes 34, below and at a distance from it, with two lateral walls 54, 56. assembly is formed by a flat top member 58 forming a cover.
  • the bottom wall 52 also constitutes the upper wall of the casing of the lower module 40, acting as a cover for the latter.
  • the manifolds 36 and 38 are brazed to the walls 52, 54, 56 and 58 so as to seal the housing there.
  • the tubes of the bundle 34 are also soldered to the side walls 54, 56, at least on the central part of these walls, so as to mechanically stiffen the tube bundle and allow it to withstand the very high pressures of the refrigerant gas.
  • the bottom wall 52 of the casing 50 is provided with orifices 60 allowing the heat-transfer fluid to pass through this wall in order to put the inner volume of this upper module 30 in communication with the internal volume. of the lower module 40.
  • the side walls 54, 56 have enlarged regions 62 making it possible, as can be seen in the section of FIG. 5, to ensure the circulation of the coolant on the entire height of the bundle of tubes 34, so as to thereby supply by the coolant flow all the intervals between the different tubes of the bundle.
  • the tubes of the bundle are located at a distance from the lateral wall 54, 56 in this enlarged region 62, and are not not in contact with this wall while they are in contact and brazed with the wall in the region of the casing located beyond the enlarged regions 62.
  • enlarged regions 64 in the vicinity of the outlet pipe 32, so as to allow the communication between all the intervals between the different tubes of the bundle 34 with this outlet pipe 32
  • the bundle of tubes is located at a distance from the side wall 54, 56 in the widened regions 64, the solder connection between the tubes and the wall being established only beyond this widened region 64 (FIG. therefore in the part of the walls 54, 56 located between the enlarged regions 62, 64, with the exception of these regions).
  • the bottom wall 52 is devoid of a communication port such as 60, so as to prevent any communication at this point between the upper module 30 and the lower module 40, and to force and the liquid admitted by the inlet pipe 42 to travel the module 40 over its entire length, then via the orifices 60, the module 30 over its entire length to the outlet pipe 32.
  • the bottom wall 52 is provided, on the side of the manifolds 36 and 46, with an extension 66 coming between these two manifolds and prohibiting the communication between their respective conduits. 60, 70 gas circulation.
  • the bottom wall is provided with a similar extension 72 to be interposed between the manifolds 38 and 48.
  • This extension 72 is on the other hand provided with an orifice 74 ensuring the communication of the respective conduits 76, 78 of these two manifolds 38 and 48.
  • the conformation of these elements makes it possible to force the flow of the gas arriving through the inlet 26 into the manifold 36, so that it traverses the bundle of tubes 34, then the manifolds 38 and 48 through the orifice 74, then the bundle of tubes 44 of the lower module 40, to the manifold 46.
  • the configuration just described makes it possible to ensure a countercurrent flow of the water and gas flows, inside each of the modules 30 and 40 and a module at the same time.
  • the bottom wall 52 which on one side (that of the manifolds 38 and 48) is provided with liquid passages 60 and gas 74, and on the other side (that of the manifolds 36 and 46 and manifolds 32 and 42) is devoid of liquid and gas passages.
  • the extensions 66, 72 constitute a single additional layer of the sheet stack of the manifolds 36, 46, allowing easy assembly and soldering of the various elements.
  • a spacer may be provided between the two exchangers WGC2 and WGC3, more precisely between the lower module 40 of the exchanger WGC2 and the upper module 30 'of the exchanger WGC3, so as to mechanically separate these two organs from the gas cooler.
  • FIGS. 6 to 9 illustrate an embodiment variant in which the device of the invention incorporates in the same functional unit not only the gas cooler WGC (more precisely, the liquid / gas stages WGC2 and WGC3), but also the heat exchanger internal gas / gas IHX (referenced 16 in Figure 1).
  • This internal exchanger IHX is in fact mounted in the refrigerant gas circulation loop directly at the outlet of the gas cooler 14, downstream of the stage WGC3, and crosses the gas circuit delivered at the outlet of the evaporator 20. Its function is to cool the high-pressure gas leaving the gas cooler 14 by the low-pressure gas leaving the evaporator 20.
  • FIG. 6 represents a unitary assembly grouping together the two exchangers WGC2 and WGC3, each formed of two modules 30, 40 and 30 ', 40' configured as described with reference to FIGS. 2 to 5.
  • the unitary assembly also incorporates the heat exchanger. internal gas / gas heat IHX, generally designated 80.
  • This internal gas / gas exchanger IHX substantially has, in length and width, the same overall dimensions as the exchangers WGC2 and WGC3, so as to constitute a homogeneous block grouping in the vicinity of the compressor the maximum of elements contributing to the exchange thermal and gas cooling.
  • the length of the IHX internal heat exchanger is not related to that of the WGC gas cooler; the internal heat exchanger IHX may be longer or shorter, since the output connection of the gas cooler WGC3 is common to the inlet of the IHX internal exchanger.
  • FIGS 7 to 9 illustrate more precisely the structure of the IHX internal heat exchanger 80.
  • the flat elements 82 are intended to be traversed by the hot gas at high pressure delivered at the outlet of the exchanger WGC3. They each comprise a multichannel tube 86 of the same nature as the multichannel tubes described above tube bundles liquid / gas exchangers WGC2 and WGC3. The channels of each tube are communicated at their ends by a tip 88 or 90, respectively, forming a collector.
  • the flat elements 84 are intended to be traversed by the cold gas at low pressure from the evaporator and returning to the compressor.
  • the structure of these flat elements 84 (illustrated in Figure 9) and similar to that of the flat elements 82, with a multichannel tube 92 provided at each end of a tip 94 or 96, respectively, forming a collector.
  • the tubes 86, 92 tubes are stacked alternately to form two sets of nested tubes, where the hot gas under high pressure and the cold gas under low pressure circulate against the current in successive layers of the stack.
  • the adjacent tubes 86 and 92 of each series of tubes are in mutual contact, so as to allow heat exchange by conduction between the tubes.
  • the number of tubes 86, 92 whose stack makes up the IHX internal exchanger depends on the length and the hydraulic diameter of the low pressure circuit and the high pressure circuit, and will be adapted according to the circumstances.
  • the end collecting tips 88, 90 and 94, 96 are respectively configured so as to constitute, by stacking, end collecting boxes ensuring the selective distribution, for the two high-pressure and low-pressure circuits, of the refrigerant gas in the various tubes. stacking.
  • the cold gas at low pressure passes through an orifice 98 of the nozzle 88, without communication with the tube 86 which is part of the high pressure circuit, while on the opposite side, the high pressure fluid flowing in this tube 86 is collected by an enlarged opening 100 allowing communication with the rest of the high pressure circuit.
  • the nozzle 94 comprises an enlarged opening 102 allowing communication with the low pressure circuit, and in communication with the orifice 98.
  • the tip 96 comprises an isolated orifice 104 allowing the passage of the high pressure hot fluid without communication with the tube 92 traversed by the low pressure fluid.
  • elements 106, 108 make it possible to link to the rest of the circuit refrigerant gas side low pressure, that is to say from the evaporator 20 and to the compressor 10 ( Figure 1).
  • the high pressure refrigerant gas is directly admitted from the manifold 46 'of the module 40' of the exchanger WGC3 (FIG. 6), thanks to a suitable dimensioning of the end pieces forming the manifolds. of the internal heat exchanger IHX and the liquid / gas heat exchangers WGC2 and WGC3.
  • the stack of elements that form the manifolds is sufficient to ensure the direct communication of the output of the exchanger WGC3 with the inlet of the IHX exchanger, in the same way as was achieved the direct communication of the output of the exchanger WGC2 with the input of the exchanger WGC3.
  • the advantageous solution of the invention makes it possible to mechanically and functionally combine the WGC gas cooler and the IHX internal exchanger. This allows, in addition to the removal of flanges, screws, joints and hoses high pressure (thereby reducing the risk of leakage), minimize the lengths of the connections of these exchangers to the compressor.
  • An advantage which results therefrom is the reduction of the volume of refrigerant gas in the circuit, with correlatively a reduction in the size of the gas accumulator 22 which, according to the architecture of the circuit, can further contribute to a better distribution of the volumes of refrigerant gas in the loop.
  • Yet another advantage of the integration of the IHX internal heat exchanger with the WGC2 / WGC3 gas cooler is the improvement of the overall thermal performance of the circuit under difficult operating conditions, in particular by high ambient temperature.

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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)
EP07116262A 2006-09-21 2007-09-12 Gas-Wasser-Wärmetauscher, insbesondere für eine Klimaanlage eines Kraftfahrzeugs, bei der eine Kühlflüssigkeit zum Einsatz kommt, die im superkritischen Zustand eingesetzt wird, wie CO2 Withdrawn EP1903293A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0608280A FR2906357B1 (fr) 2006-09-21 2006-09-21 Echangeur de chaleur de type liquide/gaz,notamment pour un equipement de climatisation de vehicule automobile utilisant un fluide refrigerant operant a l'etat supercritique tel que co2

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EP1903293A2 true EP1903293A2 (de) 2008-03-26
EP1903293A3 EP1903293A3 (de) 2008-04-09

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010108992A1 (fr) * 2009-03-26 2010-09-30 Valeo Systemes Thermiques Echangeur de chaleur, en particulier condenseur de climatisation
FR2947045A1 (fr) * 2009-06-23 2010-12-24 Valeo Systemes Thermiques Bloc d'echangeur de chaleur, en particulier pour condenseur de climatisation
EP2463611A1 (de) * 2010-12-10 2012-06-13 Valeo Systèmes Thermiques Wärmetauscher vom Typ Flüssigkeit/Gas, insbesondere für Klimaanlagengeräte in einem Kraffahrzeug
EP2463612A1 (de) * 2010-12-10 2012-06-13 Valeo Systemes Thermiques Antriebskopf eines Wärmetauschers zwischen einem ersten Fluid und einem zweiten Fluid, und Wärmetauscher, insbesondere für Fahrzeuge, der einen solchen Antriebskopf umfasst
WO2013001011A1 (fr) * 2011-06-30 2013-01-03 Valeo Systemes Thermiques Echangeur thermique notamment pour vehicule automobile
CN104197750A (zh) * 2014-09-23 2014-12-10 大连葆光节能空调设备厂 楔形管式换热器
FR3045802A1 (fr) * 2015-12-21 2017-06-23 Valeo Systemes Thermiques Echangeur thermique, notamment pour vehicule automobile
CN108154941A (zh) * 2016-12-05 2018-06-12 国家电投集团科学技术研究院有限公司 反应堆安全壳外置空冷器
JP2021032549A (ja) * 2019-08-29 2021-03-01 サンデン・アドバンストテクノロジー株式会社 熱交換器

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Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010108992A1 (fr) * 2009-03-26 2010-09-30 Valeo Systemes Thermiques Echangeur de chaleur, en particulier condenseur de climatisation
FR2943776A1 (fr) * 2009-03-26 2010-10-01 Valeo Systemes Thermiques Echangeur de chaleur, en particulier condensateur de climatisation
FR2947045A1 (fr) * 2009-06-23 2010-12-24 Valeo Systemes Thermiques Bloc d'echangeur de chaleur, en particulier pour condenseur de climatisation
WO2010149452A1 (fr) * 2009-06-23 2010-12-29 Valeo Systemes Thermiques Bloc d'échangeur de chaleur, en particulier pour condenseur de climatisation
EP2463611A1 (de) * 2010-12-10 2012-06-13 Valeo Systèmes Thermiques Wärmetauscher vom Typ Flüssigkeit/Gas, insbesondere für Klimaanlagengeräte in einem Kraffahrzeug
EP2463612A1 (de) * 2010-12-10 2012-06-13 Valeo Systemes Thermiques Antriebskopf eines Wärmetauschers zwischen einem ersten Fluid und einem zweiten Fluid, und Wärmetauscher, insbesondere für Fahrzeuge, der einen solchen Antriebskopf umfasst
FR2968752A1 (fr) * 2010-12-10 2012-06-15 Valeo Systemes Thermiques Echangeurs de chaleur de type liquide/gaz, notamment pour les equipements de climatisation de vehicule automobile
FR2968751A1 (fr) * 2010-12-10 2012-06-15 Valeo Systemes Thermiques Tete de lame d'echangeur de chaleur entre un premier fluide et un second fluide et echangeur de chaleur, notamment pour automobile, comprenant une telle tete de lame
CN103890524A (zh) * 2011-06-30 2014-06-25 法雷奥热系统公司 特别用于机动车辆的热交换器
FR2977306A1 (fr) * 2011-06-30 2013-01-04 Valeo Systemes Thermiques Echangeur thermique notamment pour vehicule automobile
WO2013001011A1 (fr) * 2011-06-30 2013-01-03 Valeo Systemes Thermiques Echangeur thermique notamment pour vehicule automobile
JP2014524005A (ja) * 2011-06-30 2014-09-18 ヴァレオ システム テルミク 特に自動車用の熱交換器
US9562466B2 (en) 2011-06-30 2017-02-07 Valeo Systemes Thermiques Heat exchanger for exchanging heat between a first fluid and a second fluid, both having U-circulation
CN103890524B (zh) * 2011-06-30 2018-02-16 法雷奥热系统公司 特别用于机动车辆的热交换器
CN104197750A (zh) * 2014-09-23 2014-12-10 大连葆光节能空调设备厂 楔形管式换热器
FR3045802A1 (fr) * 2015-12-21 2017-06-23 Valeo Systemes Thermiques Echangeur thermique, notamment pour vehicule automobile
WO2017109345A1 (fr) * 2015-12-21 2017-06-29 Valeo Systemes Thermiques Échangeur thermique, notamment pour véhicule automobile
CN108154941A (zh) * 2016-12-05 2018-06-12 国家电投集团科学技术研究院有限公司 反应堆安全壳外置空冷器
JP2021032549A (ja) * 2019-08-29 2021-03-01 サンデン・アドバンストテクノロジー株式会社 熱交換器
JP7332393B2 (ja) 2019-08-29 2023-08-23 サンデン株式会社 熱交換器

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EP1903293A3 (de) 2008-04-09
FR2906357A1 (fr) 2008-03-28
FR2906357B1 (fr) 2013-01-18

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