EP2260253B1 - Integrierte klimatisierunsganordnung mit einem inneren wärmetauscher - Google Patents

Integrierte klimatisierunsganordnung mit einem inneren wärmetauscher Download PDF

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Publication number
EP2260253B1
EP2260253B1 EP09721889.5A EP09721889A EP2260253B1 EP 2260253 B1 EP2260253 B1 EP 2260253B1 EP 09721889 A EP09721889 A EP 09721889A EP 2260253 B1 EP2260253 B1 EP 2260253B1
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Prior art keywords
fluid
tube
exchanger
integrated assembly
main
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EP09721889.5A
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English (en)
French (fr)
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EP2260253A1 (de
Inventor
Aurélie Bellenfant
Jimmy Lemee
Lionel Renault
Frédéric Bernard
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Valeo Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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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
    • 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
    • F28D7/0033—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 the conduits for one medium or the conduits for both media being bent
    • 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
    • F28D7/04—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 spirally coiled
    • 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
    • F28F9/0243—Header boxes having a 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

Definitions

  • the present invention relates to an integrated assembly for an air conditioning circuit operating with a refrigerant, and an air conditioning circuit comprising such an integrated assembly.
  • the invention finds a particularly advantageous application in the field of air conditioning circuits operating with a supercritical refrigerant fluid, such as carbon dioxide (CO2).
  • a supercritical refrigerant fluid such as carbon dioxide (CO2).
  • Air conditioning circuits of this type generally include a compressor, a gas cooler, an internal heat exchanger, a pressure reducer, an evaporator and an accumulator.
  • the refrigerant fluid carried at high pressure by the compressor is sent to the gas cooler to be cooled.
  • the high-pressure fluid from the cooler then flows into a first branch of the internal exchanger, and is then expanded by the expander.
  • the low pressure fluid then passes through the evaporator, then the accumulator before circulating in a second branch of the internal exchanger.
  • the refrigerant then returns to the compressor to undergo a new cycle.
  • the hot fluid at high pressure flowing in the first branch exchanges heat with the cold fluid at low pressure flowing in the second branch.
  • the accumulator disposed at the outlet of the evaporator is designed to store the excess liquid present in the cold fluid at low pressure leaving the evaporator.
  • This accumulator is generally in the form of a reservoir adapted to separate the liquid portion of the refrigerant fluid from the gas portion.
  • the accumulator sends the gaseous portion of the refrigerant fluid at low temperature to the compressor after passing through the internal exchanger.
  • the internal exchanger which, associated with a horizontal accumulator, constitutes the integrated assembly described in the French patent application no. 2,752,921 .
  • the internal exchanger has a general spiral shape. A spacing is provided between the windings of the internal exchanger to allow the circulation of the cold fluid, while the hot fluid circulates inside the spirally wound tube in parallel channels arranged perpendicularly to the axis of the tube.
  • a heat exchanger for air conditioning circuit comprising a tube defining a path for the circulation of a fluid, called high pressure, and a second fluid, called low pressure, the tube being wound around an axis so as to define successive windings.
  • the successive windings of the tube are closely clamped together so as to delimit so-called secondary channels, sealed for the circulation of the second fluid, these secondary channels being located between projecting areas of the tube.
  • the tube also has channels, said main, arranged in the projecting areas, to be traversed by the first fluid.
  • This known heat exchanger comprises an inner core of substantially cylindrical shape placed in the center of the tube and consisting of several nested elements which ensure, at the same time, the winding of the tube, the evacuation of the first fluid at the exit of the main channels and the second fluid supply to the inlet of the secondary channels.
  • an object of the invention is to provide an integrated assembly for an air conditioning circuit comprising a heat exchanger, which would in particular simplify the architecture of the aforementioned known exchanger at the outlet of the first fluid and the input of the second fluid.
  • US2002 / 0083733A disclosed an accumulator with internal heat exchanger for use in an air conditioning or refrigeration system having a compressor, a condenser, an expansion device and an evaporator.
  • the heat exchanger comprises a tube having at least one high temperature channel and a low temperature channel extending through the interior of the tube.
  • the heat exchanger comprises a single spirally wound coaxial tube having an outer tube and an inner tube positioned inside the outer tube.
  • JP2002107069A discloses a refrigerant heat transfer tube and a water channel in thermal contact with each other to exchange heat between the refrigerant and the water.
  • the refrigerant heat transfer tube includes a plurality of microchannel flow paths.
  • the internal exchanger has a general spiral shape.
  • a spacing is provided between the windings of the internal exchanger to allow the circulation of the cold fluid, while the hot fluid circulates inside the spirally wound tube in parallel channels arranged perpendicularly to the axis of the tube.
  • a heat exchanger for air conditioning circuit comprising a tube defining a path for the circulation of a fluid, called high pressure, and a second fluid, called low pressure, the tube being wound around an axis so as to define successive windings.
  • the successive windings of the tube are closely clamped together so as to delimit so-called secondary channels, sealed for the circulation of the second fluid, these secondary channels being located between projecting areas of the tube.
  • the tube also has channels, said main, arranged in the projecting areas, to be traversed by the first fluid.
  • This known heat exchanger comprises an inner core of substantially cylindrical shape placed in the center of the tube and consisting of several nested elements which ensure, at the same time, the winding of the tube, the evacuation of the first fluid at the exit of the main channels and the second fluid supply to the inlet of the secondary channels.
  • an object of the invention is to provide an integrated assembly for an air conditioning circuit comprising a heat exchanger, which would in particular simplify the architecture of the aforementioned known exchanger at the outlet of the first fluid and the input of the second fluid.
  • the integrated assembly includes a heat exchanger comprising a first tube defining a path for the circulation of a first fluid, called high pressure fluid, said first tube being wound in a spiral about an axis, called the axis of the exchanger, remarkable in that said heat exchanger further comprises two second tubes defining a path for the circulation of a second fluid, called low pressure fluid, said second tubes being contiguous to a respective face of the first tube and spirally wound with said first tube about said axis.
  • first and the second fluids circulate in independent tubes, it is possible to separate the outlet of the first tube and the inlet of the second tube and thus to provide independent means. discharging the first fluid and supplying the second fluid, instead of using a single complex piece simultaneously providing these two functions.
  • the first fluid is a high pressure fluid and the second fluid is a low pressure fluid.
  • Said first and second fluids are constituted by the same refrigerant fluid, in particular a supercritical fluid.
  • Said first tube comprises a plurality of parallel main channels each defining a flow path of the first fluid spiral around the axis of the exchanger.
  • said main channels have a substantially circular section for a better resistance to the pressure of the first tube in which the first high pressure fluid flows.
  • Said second tubes comprise a plurality of parallel secondary channels each delimiting a circulation path of the second fluid spiral around the axis of the exchanger.
  • said secondary channels have a substantially rectangular section for a better heat exchange surface between the second low pressure fluid flowing in the second tube and the first high pressure fluid flowing in the first tube.
  • the heat exchanger comprises two second tubes respectively contiguous to one face of the first tube.
  • This embodiment makes it possible in fact to obtain, by increasing the passage sections offered to the second fluid, a reduction in the pressure drop in the second branch of the exchanger, the one in which the second low-level fluid circulates. pressure.
  • Said integrated assembly comprises a housing in which is housed the internal heat exchanger between a cover and a bottom, said bottom being provided with an inlet of the second fluid inside the windings constituted by said first and second tubes.
  • Said housing comprises inside a secondary inlet pipe of said fluid, parallel to the axis of the exchanger and one end of which communicates with said outlet orifice through said bottom, and a secondary outlet pipe of the fluid, parallel to the axis of the exchanger and having an outlet opening.
  • Said integrated assembly comprises an accumulator connected to the bottom of said integrated assembly, into which said secondary inlet pipe opens so as to communicate with said outlet orifice.
  • the main pipes and the secondary pipes are arranged to produce a circulation of the first fluid in the first co-current tube with the circulation of the second fluid in the second tube.
  • the main pipes and the secondary pipes are arranged to make a circulation of the first fluid in the first tube against the current with the circulation of the second fluid in the second tube.
  • the invention relates to an air conditioning circuit operating with a refrigerant, comprising a compressor, a gas cooler, a pressure reducer and an evaporator, remarkable in that said air conditioning circuit comprises an integrated element according to the invention, the main tubing. inlet pipe being connected to the gas cooler and the main outlet pipe being connected to the expansion valve, while the secondary inlet pipe is connected to the evaporator and the secondary outlet pipe is connected to the compressor.
  • an air conditioning circuit 10 operating with a refrigerant fluid, in particular a supercritical refrigerant fluid, for example carbon dioxide (CO2).
  • a refrigerant fluid in particular a supercritical refrigerant fluid, for example carbon dioxide (CO2).
  • CO2 carbon dioxide
  • the air conditioning circuit 10 can be installed in a motor vehicle to cool the air of the passenger compartment, according to the needs of the passengers.
  • Such an air conditioning circuit operating according to a supercritical refrigerant cycle essentially comprises a compressor 14, a gas cooler 11 associated with a fan 16, an internal heat exchanger 9, an expander 12, an evaporator 13, and an accumulator 17. .
  • the compressor 14 compresses the refrigerant fluid to a discharge pressure, called high pressure.
  • the fluid then passes through the gas cooler 11 where it undergoes a gas phase cooling under high pressure. During this cooling, the fluid is not condensed unlike air conditioning circuits that use fluorinated compounds as refrigerant.
  • the fluid thus cooled by the gas cooler 11 then flows into a first branch 90 of the internal heat exchanger 9, called "hot" branch, to be further cooled.
  • the fluid then passes into the regulator 12 which lowers its pressure, bringing it at least partly in the liquid state.
  • the fluid passing through the evaporator 13 then passes to the gaseous state under constant pressure.
  • the heat exchange in the evaporator 13 makes it possible to produce a flow of conditioned air which is sent towards the passenger compartment of the vehicle.
  • the accumulator 17 is provided at the outlet of the evaporator 13 to store the excess of liquid still contained in the fluid.
  • the conventional accumulators are in the form of a reservoir adapted to separate the liquid portion of the refrigerant fluid from the gaseous portion.
  • the accumulator 17 then sends the gaseous portion of the refrigerant fluid at low temperature into a second branch 92 of the internal heat exchanger 9, called the "cold" branch, for a heat exchange with the high temperature refrigerant circulating in the "hot" branch 90.
  • the figure 2 shows such an integrated assembly 100 comprising, in the same housing 130, a battery 17 surmounted by an internal heat exchanger 9.
  • the internal exchanger 9 of the figure 2 is essentially organized around a heat exchange device 140 between the high pressure fluid and the low pressure fluid.
  • this device 140 comprises a first tube 110 which defines a path for the circulation of the high-pressure fluid, this first tube 110 being wound in a spiral about an axis A which will be referred to in the following axis of the exchanger.
  • the heat exchange device 140 further comprises two second tubes 120a, 120b each defining a path for the circulation of the second fluid at low pressure. These second tubes are contiguous to a respective face of the first tube 110 and spirally wound simultaneously with said first tube about the axis A of the internal exchanger 9. At each winding, the inner wall of the second inner tube 120a can come into contact with the outer wall of the second outer tube 120b.
  • the coolant is identical in the first tube 110 and in the second tube 120a, 120b with the exception of its pressure level. Indeed, this fluid is subjected to a pressure (called high pressure) in the first tube 110 greater than the pressure (so-called low pressure) of the fluid in the second tube 120a, 120b.
  • the first high pressure tube 110 is "sandwiched" between the two second tubes 120a, 120b low pressure so as to promote an exchange between the high pressure fluid and the low pressure fluid.
  • the tubes 110, 120a, 120b can be extruded and joined together by brazing or gluing.
  • the circulation of the high-pressure fluid in the first tube 110 is provided by a plurality of parallel main channels each delimiting a flow path of the high-pressure fluid spirally around the axis A of the exchanger. These main channels are contained in successive planes perpendicular to the axis A. Although they are not shown in the figures, it will be found in the French patent application no. 2,752,921 a description of a structure of such main channels.
  • said main channels have a substantially circular section, in order to offer a better resistance to pressure.
  • This same channel structure can also be implemented to produce in each second tube 120a, 120b of the secondary channels each delimiting a flow path of the low-pressure fluid in a spiral around the axis A of the exchanger, these main channels. being contained in successive planes perpendicular to the axis A.
  • said secondary channels have a substantially rectangular section, so as, on the one hand, to offer a larger heat exchange surface with the first tube 110 and, on the other hand, to reduce the pressure drop the along the path followed by the fluid at low pressure by maximizing the useful cross section of the fluid through the second tubes 120a, 120b.
  • the main channels of the first tube 110 extend between a main inlet pipe 111 adapted to receive the high pressure fluid from the gas cooler 11 of the air conditioning circuit, and a main outlet pipe 112 capable of delivering the fluid at high pressure outside the exchanger, in particular to the regulator 12 of the air conditioning circuit.
  • These main pipes 111, 112 have a substantially cylindrical shape with an axis parallel to the axis A of the exchanger and respectively have an opening 113, 114, shown in FIGS. Figures 3 and 4 , capable of receiving one of the ends of the first tube 110.
  • the main pipes 111, 112 are not in contact with the inner or outer faces of the second tubes 120a, 120b.
  • the main pipes 111, 112 are brazed or glued to the ends of the first tube 110.
  • the main pipes 111, 112 are closed at one of their ends by plugs 115, 116, the latter are made by means of shutter insert or directly integrated in the tubing 111 or 112 for example by a folding and a brazing of the end.
  • the heat exchange device 140 provided with the main pipes 111, 112 is housed inside the housing 130 between a cover 150 and a bottom 160. In this space are also housed the secondary pipes 121, 122 for controlling the circulation of the fluid at low pressure in the internal exchanger 9.
  • a secondary tubing 121 of low-pressure fluid inlet parallel to the axis A of the exchanger, for receiving the low-pressure fluid from the evaporator 13 of the air conditioning circuit, and to pass it into the accumulator 17 through the bottom 160 of the exchanger.
  • the low-pressure fluid freed from its liquid phase leaves the accumulator 17 via a low-pressure fluid inlet orifice 161a, 161b in the heat exchange device 140, inside the windings constituted by the first tube 110 and the second tubes 120a, 120b.
  • the low pressure fluid After circulating in the two second tubes 120a, 120b and exchanging heat therewith with the high pressure fluid flowing in the first tube 110, the low pressure fluid opens secondary channels into the housing 130 where it is collected by a secondary outlet pipe 122 provided with an opening 123. The low pressure fluid is then driven through the secondary outlet pipe 122 outside the exchanger towards the compressor 14 of the air conditioning circuit.
  • the bottom 160 comprises two plates 160a, 160b.
  • the plate 160a said upper bottom plate, has holes 163a, 164a on which are brazed respectively the secondary tubing 122 of the low pressure fluid outlet and the main pipe 111 inlet of the high pressure fluid.
  • Another hole referenced 162a is formed in the upper bottom plate 160a through which the secondary tubing 121 enters the fluid at low pressure.
  • two variants are possible: one in which the secondary tubing 121 is brazed to the plate 160a at the hole and another or the secondary tubing 121 is not mechanically connected to the plate 160a.
  • Another hole 161a situated substantially in the center of the windings of the tubes participates in the inlet orifice of the fluid at low pressure in the heat exchange device 140.
  • the plate 160b called bottom bottom plate, has a hole 162b for the passage of the secondary tubing 121 of low pressure fluid inlet, a hole 164b for the housing of the plug 115 of the main pipe 111 of the fluid inlet at high pressure and a hole 161b constituting with the hole 161a of the upper plate 160a bottom the fluid orifice at low pressure.
  • the secondary tubing 122 of low pressure fluid outlet simply bears against the bottom plate 160b.
  • the cover 150 of the exchanger consists of two plates referenced 150a, 150b.
  • the plate 150a called the lower lid plate, has four holes 151a, 152a, 153a, 154a on which the main outlet pipe 112 for the high-pressure fluid, the secondary pipe 121 for the inlet of the low-pressure fluid, are respectively brazed. the secondary tubing 122 of low pressure fluid outlet, and the main pipe 111 of high pressure fluid inlet.
  • the plate 150b makes it possible to bind the inlets / outlets of the high and low pressure fluids of the internal exchanger 9 to the corresponding user-side inlets / outlets which are located on a plug 170 which can be fixed on studs. 151b, 152b of the top cover plate 150b by means of screws passing through holes 171, 172 of the plug 170.
  • the connection between the plug 170 and the top plate 150b is performed by soldering at the studs 151b and 152b .
  • the accumulator delimits the housing 130 of the integrated assembly, this housing having the shape of a tank where the lower part delimits a fluid receiving chamber subjected to low pressure, this lower part extending to the right of the internal heat exchanger to end with an overlap zone with the cap 170, the latter entering the accumulator. It is therefore understood that the integrated assembly according to the invention is completely integrated with the accumulator.

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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)

Claims (10)

  1. Integrierte Einheit für einen mit einem Kühlfluid arbeitenden Klimatisierungskreislauf, wobei die integrierte Einheit (100) ein Gehäuse (130) aufweist, in dem ein innerer Wärmetauscher (9) untergebracht ist, der ein erstes Rohr (110) enthält, das einen Weg für die Strömung eines Fluids begrenzt, wobei das erste Rohr spiralförmig um eine Achse des Tauschers genannte Achse (A) gewickelt ist, wobei der Wärmetauscher (9) zwei zweite Rohre (120a, 120b) enthält, die einen Weg für die Strömung des Fluids begrenzen, wobei die zweiten Rohre (120a, 120b) an eine jeweilige Seite des ersten Rohrs (110) angefügt und mit dem ersten Rohr (110) spiralförmig um die Achse (A) gewickelt sind, wobei der innere Wärmetauscher (9) zwischen einem Deckel (150) und einem Boden (160) untergebracht ist, wobei der Boden mit einer Eingangsöffnung (161a, 161b) des Fluids ins Innere der von den ersten (110) und zweiten Rohren (120a, 120b) gebildeten Wicklungen versehen ist, wobei das erste Rohr (110) eine Vielzahl von parallelen Hauptkanälen aufweist, die je einen Strömungsweg des Fluids spiralförmig um die Achse (A) des Tauschers herum begrenzen, wobei die zweiten Rohre (120a, 120b) eine Vielzahl von parallelen Nebenkanälen aufweisen, die je einen Strömungsweg des Fluids spiralförmig um die Achse (A) des Tauschers herum begrenzen, wobei das Fluid im ersten Rohr (110) und in den zweiten Rohren (120a, 120b) gleich und im ersten Rohr (110) einem Druck ausgesetzt ist, der höher ist als der Druck des Fluids in den zweiten Rohren (120a, 120b), wobei der innere Wärmetauscher (9) einen Haupteingangsstutzen (111), der das Fluid aufnehmen kann, und einen Hauptausgangsstutzen (112) enthält, der das Fluid nach außerhalb des Tauschers liefern kann, wobei die Hauptkanäle sich zwischen dem Haupteingangsstutzen (111) und dem Hauptausgangsstutzen (112) erstrecken, wobei mindestens einer der Hauptstutzen (111, 112) eine im Wesentlichen zylindrische Form mit einer Achse parallel zur Achse (A) des Tauschers hat und eine Öffnung (113, 114) aufweist, die ein Ende des ersten Rohrs (110) aufnehmen kann, wobei das Gehäuse innen einen Nebeneingangsstutzen (121) des Fluids parallel zur Achse (A) des Tauschers und von dem ein Ende mit der Ausgangsöffnung (161a, 161b) durch den Boden (160) hindurch in Verbindung steht, und einen Nebenausgangsstutzen (122) des Fluids parallel zur Achse (A) des Tauschers und eine Ausgangsöffnung (123) aufweisend aufweist, wobei die integrierte Einheit (100) einen Akkumulator (17) enthält, der an den Boden (160) der integrierten Einheit (9) angeschlossen ist, in den der Nebeneingangsstutzen (121) mündet, um mit der Ausgangsöffnung (161a, 161b) in Verbindung zu treten, wobei das Gehäuse (130) sich in der Verlängerung des inneren Wärmetauschers (9) nach dem Boden (160) erstreckt und eine Aufnahmekammer des Fluids auf niederem Druck aufweist.
  2. Integrierte Einheit für einen Klimatisierungskreislauf nach Anspruch 1, wobei die Hauptkanäle einen im Wesentlichen kreisförmigen Querschnitt aufweisen.
  3. Integrierte Einheit für einen Klimatisierungskreislauf nach einem der Ansprüche 1 bis 2, wobei die Nebenkanäle einen im Wesentlichen rechtwinkligen Querschnitt aufweisen.
  4. Integrierte Einheit für einen Klimatisierungskreislauf nach einem der Ansprüche 1 bis 3, wobei die ersten (110) und zweiten Rohre (120a, 120b) extrudiert werden.
  5. Integrierte Einheit für einen Klimatisierungskreislauf nach einem der Ansprüche 1 bis 4, wobei die ersten (110) und zweiten Rohre (120a, 120b) durch Löten oder Kleben angefügt werden.
  6. Integrierte Einheit nach einem der vorhergehenden Ansprüche, wobei die Hauptstutzen (111, 112) und die Nebenstutzen (121, 122) eingerichtet sind, um eine Strömung des Fluids im ersten Rohr (110) im Gleichstrom mit der Strömung des Fluids im zweiten Rohr (120a, 120b) herzustellen.
  7. Integrierte Einheit nach Anspruch 6, wobei die Hauptstutzen (111, 112) und die Nebenstutzen (121, 122) eingerichtet sind, um eine Strömung des Fluids im ersten Rohr (110) im Gegenstrom zur Strömung des Fluids im zweiten Rohr (120a, 120b) herzustellen.
  8. Integrierte Einheit nach Anspruch 7, wobei das Hochdruckfluid und das Niederdruckfluid aus dem gleichen Kühlfluid bestehen.
  9. Integrierte Einheit nach Anspruch 8, wobei das Kühlfluid ein überkritisches Fluid ist.
  10. Klimatisierungskreislauf, der mit einem Kühlfluid arbeitet, der einen Kompressor (14), einen Gaskühler (11), ein Expansionsventil (12) und einen Verdampfer (13) enthält, dadurch gekennzeichnet, dass der Klimatisierungskreislauf (10) ein integriertes Element (100) nach einem der Ansprüche 1 bis 8 aufweist, wobei der Haupteingangsstutzen (111) mit dem Gaskühler (11) und der Hauptausgangsstutzen (112) mit dem Expansionsventil (12) verbunden ist, während ein Nebeneingangsstutzen (121) mit dem Verdampfer (13) und der Nebenausgangsstutzen (122) mit dem Kompressor (14) verbunden ist.
EP09721889.5A 2008-03-20 2009-03-17 Integrierte klimatisierunsganordnung mit einem inneren wärmetauscher Active EP2260253B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0801546A FR2928997B1 (fr) 2008-03-20 2008-03-20 Echangeur de chaleur et ensemble integre de climatisation comprenant un tel echangeur.
PCT/EP2009/001932 WO2009115284A1 (fr) 2008-03-20 2009-03-17 Echangeur de chaleur et ensemble integre de climatisation comprenant un tel echangeur

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EP2260253A1 EP2260253A1 (de) 2010-12-15
EP2260253B1 true EP2260253B1 (de) 2019-07-31

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US (1) US9920999B2 (de)
EP (1) EP2260253B1 (de)
JP (1) JP5555220B2 (de)
CN (1) CN102037305B (de)
FR (1) FR2928997B1 (de)
WO (1) WO2009115284A1 (de)

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CN103712380B (zh) * 2014-01-06 2015-11-04 天津商业大学 能够实现三股流体换热的回热器及制冷系统
CN106610241A (zh) * 2015-10-26 2017-05-03 北京肯思得能源科技有限公司 管壳式换热器及其管壳式换热器组
EP3374717B1 (de) * 2015-11-09 2020-01-01 Franke Technology and Trademark Ltd Wärmetauscher
FR3062714A1 (fr) * 2017-02-06 2018-08-10 Valeo Systemes Thermiques Circuit de gestion thermique et echangeur thermique associe
CN111721147B (zh) * 2019-03-22 2022-02-25 中国石油化工股份有限公司 换热单元及换热反应器
DE102022212036A1 (de) 2022-11-14 2024-05-16 Robert Bosch Gesellschaft mit beschränkter Haftung Verteilermodul für einen Kältemittelkreislauf
US20240310094A1 (en) * 2023-03-13 2024-09-19 Hanon Systems Serviceable accumulator with integrated plate fin heat exchanger

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000346584A (ja) * 1999-06-02 2000-12-15 Denso Corp 熱交換器
JP2002107069A (ja) * 2000-09-28 2002-04-10 Sanyo Electric Co Ltd 熱交換器及びそれを用いたヒートポンプ給湯機

Family Cites Families (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2136153A (en) * 1934-04-14 1938-11-08 Rosenblads Patenter Ab Heat exchanger and method of making same
NL43858C (de) * 1936-02-01
JPS5188866A (de) * 1975-01-20 1976-08-03
US4100762A (en) * 1976-11-02 1978-07-18 Sundstrand Corporation Integrated controls assembly
US4655174A (en) * 1979-04-26 1987-04-07 Fillios Jean P R Hot liquid generator with condensation and installation incorporating this generator
DE8117144U1 (de) * 1981-03-31 1981-11-26 Feraton Anstalt, 9494 Schaan Waermetauscher
FI75664C (fi) * 1985-10-14 1990-01-30 Outokumpu Oy Dubbelspiralvaermeoeverfoerare.
US5242015A (en) * 1991-08-22 1993-09-07 Modine Manufacturing Co. Heat exchanger
JPH0791867A (ja) * 1993-09-20 1995-04-07 Matsushita Seiko Co Ltd 熱交換器
JP3397021B2 (ja) 1995-10-11 2003-04-14 株式会社デンソー 熱交換器
DE19635454B4 (de) 1996-08-31 2010-06-17 Behr Gmbh & Co. Kg Sammler-Wärmeübertrager-Baueinheit und damit ausgerüstete Klimaanlage
US20020092646A1 (en) * 2000-01-07 2002-07-18 Carsten Kuhn Spiral heat exchanger
CA2297598C (en) * 2000-01-28 2003-12-23 Ki-Sun Jason Ryu Accumulator for an air-conditioning system
PL338281A1 (en) * 2000-02-07 2001-08-13 Andrzej Sokulski Refrigeration unit
US6523365B2 (en) * 2000-12-29 2003-02-25 Visteon Global Technologies, Inc. Accumulator with internal heat exchanger
US6607027B2 (en) * 2001-04-05 2003-08-19 Modine Manufacturing Company Spiral fin/tube heat exchanger
JP3945208B2 (ja) * 2001-10-09 2007-07-18 株式会社デンソー 熱交換用チューブ及び熱交換器
US20030121648A1 (en) * 2001-12-28 2003-07-03 Visteon Global Technologies, Inc. Counter-flow heat exchanger with optimal secondary cross-flow
JP2004144343A (ja) * 2002-10-23 2004-05-20 Hitachi Home & Life Solutions Inc 熱交換器
US6681597B1 (en) * 2002-11-04 2004-01-27 Modine Manufacturing Company Integrated suction line heat exchanger and accumulator
CN2584436Y (zh) * 2002-12-13 2003-11-05 上海易初通用机器有限公司 车用空调系统带回热装置的气液分离器
JP3863854B2 (ja) * 2003-02-21 2006-12-27 三洋電機株式会社 分離型ヒートポンプ式給湯装置
JP4196774B2 (ja) * 2003-07-29 2008-12-17 株式会社デンソー 内部熱交換器
US20060196223A1 (en) * 2005-03-07 2006-09-07 Halla Climate Control Canada Inc. Accumulator with oil vanes/indentations
JP4948136B2 (ja) * 2005-11-30 2012-06-06 古河電気工業株式会社 放熱用伝熱管および放熱器
US8003265B2 (en) * 2006-05-11 2011-08-23 Ford Motor Company Gas conditioning device and method
US20090114380A1 (en) * 2006-05-23 2009-05-07 Carrier Corporation Spiral flat-tube heat exchanger
KR100784611B1 (ko) * 2006-08-18 2007-12-11 주식회사 두원공조 냉방장치의 내부열교환기 일체형 기액분리기
FR2913764B1 (fr) 2007-03-12 2009-12-11 Valeo Systemes Thermiques Echangeur de chaleur et ensemble integre incorporant un tel echangeur
EP1978317B1 (de) * 2007-04-06 2017-09-06 Samsung Electronics Co., Ltd. Kältekreislaufvorrichtung
JP5188866B2 (ja) * 2008-04-17 2013-04-24 日油技研工業株式会社 滅菌検知インジケータおよびその製造方法
FR2940418B1 (fr) * 2008-12-22 2012-12-07 Valeo Systemes Thermiques Dispositif combine comprenant un echangeur de chaleur interne et un accumulateur

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000346584A (ja) * 1999-06-02 2000-12-15 Denso Corp 熱交換器
JP2002107069A (ja) * 2000-09-28 2002-04-10 Sanyo Electric Co Ltd 熱交換器及びそれを用いたヒートポンプ給湯機

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CN102037305B (zh) 2015-03-18
JP5555220B2 (ja) 2014-07-23
US20110083468A1 (en) 2011-04-14
WO2009115284A1 (fr) 2009-09-24
FR2928997A1 (fr) 2009-09-25
EP2260253A1 (de) 2010-12-15
US9920999B2 (en) 2018-03-20
JP2011515644A (ja) 2011-05-19
FR2928997B1 (fr) 2014-06-20

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