EP2199709B1 - Dispositif combiné comprenant un échangeur de chaleur interne et un accumulateur - Google Patents

Dispositif combiné comprenant un échangeur de chaleur interne et un accumulateur Download PDF

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Publication number
EP2199709B1
EP2199709B1 EP09179140.0A EP09179140A EP2199709B1 EP 2199709 B1 EP2199709 B1 EP 2199709B1 EP 09179140 A EP09179140 A EP 09179140A EP 2199709 B1 EP2199709 B1 EP 2199709B1
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EP
European Patent Office
Prior art keywords
heat exchanger
combined device
flat tube
central axis
pipe
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Application number
EP09179140.0A
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German (de)
English (en)
French (fr)
Other versions
EP2199709A3 (fr
EP2199709A2 (fr
Inventor
Jimmy Lemee
Christophe Denoual
Alain Pourmarin
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
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Valeo Systemes Thermiques SAS
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Publication of EP2199709A3 publication Critical patent/EP2199709A3/fr
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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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F28D7/0008—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
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels

Definitions

  • the present invention is in the field of air conditioning loops cooperating with a ventilation system, heating and / or air conditioning of a motor vehicle. It relates to a combined device comprising a heat exchanger and a accumulator participating in such a loop. It also relates to an air conditioning loop comprising such a combined device.
  • a motor vehicle is commonly equipped with a ventilation, heating and / or air conditioning system to regulate the aerothermal parameters of the air contained inside the passenger compartment of the vehicle.
  • a ventilation, heating and / or air conditioning system to regulate the aerothermal parameters of the air contained inside the passenger compartment of the vehicle.
  • Such an installation cooperates with an air conditioning loop to cool a stream of air prior to the delivery of the latter inside the passenger compartment.
  • Said loop comprises a plurality of elements or components inside which circulates successively, that is to say in series, a cooling fluid, such as a supercritical fluid, carbon dioxide known under the reference R744.
  • These elements comprise at least one compressor, a gas cooler, a heat exchanger, more particularly called internal heat exchanger, an expansion member, an evaporator and an accumulator.
  • the refrigerant flows from the compressor to the gas cooler, then through a "high pressure” branch of the internal heat exchanger, then to the expansion member, then through the evaporator, and then to the accumulator, and finally through a branch "low pressure" of the internal heat exchanger, to return to the compressor.
  • the compressor is intended to receive the refrigerant fluid in the gaseous state and to compress it to carry it at high pressure.
  • the gas cooler is able to cool the compressed refrigerant at a relatively constant pressure, giving up heat to its environment.
  • the expansion member is able to lower the pressure of the refrigerant leaving the gas cooler by bringing it at least partly in the liquid state.
  • the evaporator is itself able to bring the refrigerant fluid arriving in the liquid state coming from the expansion element, at a relatively constant pressure, into the gaseous state, by taking heat from a flow of air which crosses the evaporator. The vaporized refrigerant is then sucked by the compressor.
  • the air conditioning loop includes a "high pressure" line that starts at the outlet of the compressor and ends at the inlet of the expansion member, according to a direction of circulation of the refrigerant fluid inside the air conditioning loop, the cooler of gas and the branch "high pressure" of the heat exchanger being interposed between these two points.
  • the air conditioning loop also comprises a "low pressure" line which starts at the outlet of the expansion device and ends at the inlet of the compressor, according to the direction of circulation of the refrigerant inside the air conditioning loop, the evaporator, the accumulator and the branch "low pressure" of the heat exchanger being interposed between these two points.
  • the accumulator provides a separation function between a gaseous phase and a liquid phase of the refrigerant.
  • the accumulator comprises a separation zone dedicated to this function.
  • the accumulator also provides a storage function for a circulating coolant charge depending on the conditions of use of the air conditioning loop.
  • the accumulator comprises a refrigerant storage zone in the liquid state that said accumulator collects from the evaporator.
  • the accumulator consists of an enclosure housing the separation zone and the accumulation zone, the enclosure comprising a bottom wall which delimits the accumulation zone in the lower part of the enclosure.
  • the heat exchanger is called internal heat exchanger or internal heat exchanger in that it is configured so that the refrigerant circulating inside the branch "high pressure” can yield heat to the circulating refrigerant inside the "low pressure” branch. It is therefore understood that the exchange is between the same fluid circulating at different locations of the air conditioning loop, without exchanging with air for example.
  • the document JP 10019421 proposes to associate the internal heat exchanger and the accumulator in a combined device.
  • the latter comprises said enclosure which is provided with an opening.
  • the chamber houses the internal heat exchanger which overhangs the refrigerant storage zone in the liquid state, the heat exchanger being interposed between the separation zone and the accumulation zone, in the use position. of the combined device on the air conditioning loop.
  • the high pressure refrigerant fluid from the gas cooler enters the interior of the combi device through a "high pressure” inlet through the enclosure to circulate within the heat exchanger internal and finally be discharged out of the combined device via a "high pressure” outlet also provided through the enclosure.
  • the refrigerant fluid at low pressure from the evaporator enters the interior of the combined device through a "low pressure" input still formed through the enclosure.
  • the refrigerant fluid at low pressure and in the liquid state tends to accumulate by gravity above the lower wall of the enclosure while the refrigerant fluid at low pressure and in the gaseous state tends to concentrate in an upper zone of the enclosure.
  • the latter houses a bent duct arranged in a U, a first end of which is disposed in the upper part of the enclosure to admit the refrigerant fluid at low pressure and in the gaseous state into the duct, and convey it to a second end of the conduit in communication with the internal heat exchanger. Inside the latter, the high-pressure refrigerant yields heat to the refrigerant at low pressure.
  • the refrigerant fluid at low pressure and in the gaseous state is discharged out of the internal heat exchanger and out of the combined device through a "low pressure" outlet also formed through a wall of the enclosure.
  • the object of the present invention is therefore to solve the disadvantages described above mainly by cleverly arranging the heat exchanger in the chamber of the accumulator. To do this, the heat exchanger is offset relative to the enclosure so as to minimize the outer dimensions of the combined device. This arrangement makes it possible to create a lateral evacuation chamber at the exchanger without having to either increase the diameter of the enclosure or to lengthen the enclosure to create an evacuation chamber under the heat exchanger.
  • the subject of the invention is therefore a combined device comprising an enclosure housing at least one heat exchanger and an accumulation zone, said enclosure extends along a primary central axis and said heat exchanger extends along a secondary central axis, characterized in that the primary central axis is offset with respect to the secondary central axis.
  • the offset between the primary central axis and the secondary central axis is between one and twenty-five millimeters.
  • the enclosure and the heat exchanger are of cylindrical shape.
  • the heat exchanger comprises at least a first flat tube wound on itself around the secondary central axis.
  • the first flat tube comprises a plurality of channels.
  • the heat exchanger comprises an intake chamber which extends in the center of the first flat tube wound on itself.
  • the combined device comprises an evacuation chamber located at least partially around the heat exchanger, this evacuation chamber being delimited by an outer wall of the heat exchanger and by an inner wall of the enclosure.
  • the heat exchanger comprises a first circulation path delimited by the multiplicity of channels of the first flat tube, this first circulation path being in communication via a first end of the flat tube with the admission chamber and in communication with the evacuation chamber via a second end of the first flat tube.
  • the first circulation path is delimited by a second flat tube wound with the first flat tube.
  • the heat exchanger comprises a second circulation path delimited by a plurality of channels of a third flat tube wound with the first flat tube.
  • the second circulation path is, on the one hand, in communication with a first pipe placed on the periphery of the heat exchanger and, on the other hand, in communication with a second pipe of which the axis is aligned with the secondary central axis.
  • first flat tube and the second flat tube, the third flat tube, the first pipe and the second pipe form a unitary unit.
  • the enclosure is closed by an upper partition and a lower partition and the accumulation zone comprises a bottom wall disposed at the boundary between the heat exchanger and said accumulation zone.
  • the device according to the invention comprises a first conduit which passes through the upper partition and opens into a separation zone located in the chamber and above the accumulation zone.
  • the combined device comprises a second conduit which passes through the lower partition and opens into the evacuation chamber.
  • the invention also relates to an air conditioning loop in which is incorporated a combined device incorporating at least one of the features described above.
  • a first advantage of the invention lies in the fact that it is possible to keep a component of small external dimensions without increasing the internal pressure losses, in particular on the first flow path. This makes it easier to integrate the component according to the invention into an engine compartment where space is increasingly reduced.
  • the figure 1 illustrates a combined device 1 according to the invention comprising an enclosure 2 closed by an upper partition 3, otherwise called upper cover, and a lower partition 4, or lower cover.
  • the enclosure 2 extends along a primary central axis A in a longitudinal direction.
  • the chamber 2 has a section of cylindrical shape but it can also be parallelepipedal shape (square, rectangular, ).
  • the length of the chamber 2 measured in the direction of the primary central axis A is greater than the outside diameter measured perpendicular to the primary central axis A.
  • the combined device 1 also comprises a "high pressure" inlet 5 through which a refrigerant fluid 16 from a gas cooler is admitted inside the combined device 1.
  • This "high pressure” inlet 5 is materialized by a first pipe 12 of tubular shape which passes through the lower partition 4 to connect to a heat exchanger 9.
  • the combined device 1 further comprises a "high pressure” outlet 6 through which the high pressure refrigerant is discharged from the device combined 1 towards the relaxing organ.
  • This "high pressure” outlet 6 takes the form of a second tubular pipe 13, which starts at the heat exchanger 9 to pass through the internal volume of the chamber 2 and open through the upper wall 3.
  • the combined device 1 also comprises a "low pressure" inlet 7 through which the refrigerant fluid from the evaporator is admitted inside the combined device 1.
  • the "low pressure” inlet 7 takes the form of a “low pressure” inlet 7.
  • first pipe 14 which passes through the upper wall 3.
  • the combined device 1 finally has a “low pressure” outlet 8 through which the fluid Low pressure refrigerant is discharged from the combined device 1 to the compressor.
  • This "low pressure” outlet 8 here also takes the form of a second pipe 15 of tubular shape which passes through the lower partition 4.
  • the combined device 1 comprises the enclosure 2, sealed from the outside, which houses the heat exchanger 9, a separation zone 10 between the gas phase 16a and the liquid phase 16b of the refrigerant leaving the the evaporator and an accumulation zone 11 of the refrigerant fluid in the liquid state from the evaporator, or more particularly from the separation zone 10.
  • Said separation zone 10 preferably has a cyclonic structure in the sense that the first pipe 14 is offset relative to the primary central axis A of the enclosure 2 of the combined device 1 to allow a tangential admission of the refrigerant fluid from the The tangential inlet is put into practice by means of a lumen 17 made through the cylindrical wall of the first pipe 14. These provisions are intended to promote the separation between them.
  • One end of the first pipe 14 located inside the internal volume of the chamber 2 is closed by a plate 18. The latter extends perpendicular to the primary central axis A of the chamber 2. A weak game is maintained between the periphery of this plate 18 and the inner wall 19 of the chamber 2 so as to allow the descent by gravity of the liquid phase 16b of the refrigerant 16 to the accumulation zone 11.
  • the accumulation zone 11 is delimited by a bottom wall 20 against which the coolant in the liquid state from the evaporator accumulates by gravity.
  • the "low pressure" inlet 7 being, in the position of use of the combined device 1 on the air-conditioning loop and / or in the operating position of the combined device 1 alone, placed above the lower wall 20, the fluid refrigerant 16 in the liquid state falls naturally by gravity from the entry "low pressure" 7 to the bottom wall 20 to finally rest against it.
  • the bottom wall 20 is sealed against the inner wall 19 of the enclosure 2.
  • the accumulation zone 11 is crossed by the second pipe 13 but is also crossed by an intermediate pipe 21, a first end 21a opens into the separation zone 10, a few millimeters above a plane defined by the plate 18.
  • This arrangement makes it possible to ensure that the liquid phase 16b of the cooling fluid does not enter the intermediate pipe 21 so as to let in only the gas phase 16a of the refrigerating fluid 16.
  • the intermediate pipe 21 passes through the bottom wall 20 and has a second end 21b which is in communication with the heat exchanger 9.
  • the intermediate pipe 21 is of a larger diameter than the second pipe 6 and is mounted coaxially with respect to the latter.
  • both the axis of the intermediate duct 21 and the axis of the second duct 6 are offset with respect to the primary central axis A of the enclosure 2.
  • the intermediate pipe 21 is always of a larger diameter than the second pipe 6.
  • the central axis of the intermediate pipe 21 is coincidental or coaxial with the primary central axis A. It is therefore clear that the intermediate pipe is in the center of the cylinder formed by the enclosure 2. In this configuration, however, the heat exchanger 9 is always shifted as required by the invention.
  • the second pipe 6 is shifted in the intermediate pipe 21, in other words the central axis of the second pipe 6 is not coaxial or coincides with the central axis of the intermediate pipe 21, the latter being confused with the primary central axis A.
  • the bottom wall 20 is preferably perpendicular to the primary central axis A of the chamber 2 of the combined device 1.
  • the separation zone 10 is contiguous to said upper partition 3, being positioned directly below the latter.
  • the accumulation zone 11 is placed between the separation zone 10 and the bottom wall 20, the plate 18 being interposed between the separation zone 10 and the accumulation zone 11.
  • the lower wall 20, which delimits the accumulation zone 11 in the lower part, is disposed above the heat exchanger 9. It will be noted that the accumulation zone 11 is disposed above the heat exchanger 9. along the axis of Earth's gravity.
  • the section of the chamber 2 and the section of the heat exchanger 9 are both cylindrical, which offers perfect form cooperation.
  • the accumulation zone 11 overhanging or placed above the heat exchanger 9 is higher than the heat exchanger 9, along the primary central axis A of the enclosure 2.
  • the heat exchanger 9 consists of a first flat tube 22 wound on itself, preferably around a secondary central axis B of the heat exchanger, this secondary central axis B being distinct, that is to say non-coaxial, of the primary central axis A of the chamber 2 of the combined device 1. It will be noted that this offset d, formed by the distance between the primary central axis A of the secondary central axis B , allows to release an area of the lower partition 4 in which it is then easier to unclog the second pipe 15 without increasing the external dimensions of the chamber 2, and therefore the combined device as a whole. Note that the primary central axis A and the secondary central axis B are parallel.
  • the first flat tube 22 houses a multiplicity of channels 23, otherwise called micro-channels, for the passage of refrigerant fluid at low pressure.
  • This multiplicity of channels 23 materializes a first flow path of the refrigerant fluid at low pressure.
  • This first circulation path is in communication on one side with an intake chamber 24 and on the other with an evacuation chamber 25.
  • the admission chamber 24 is delimited by the end 21b of the intermediate pipe 21 by the first turn of first flat tube 22 wound on itself and by the lower partition 4.
  • the evacuation chamber 25 is delimited by a peripheral winding of the winding of the first flat tube 22 and / or a third flat tube 27 (which will be described below in more detail), thus defining the wall external of the heat exchanger 9, by the bottom wall 20, by the lower partition 4 and finally by the inner wall 19 of the chamber 2 to the right of the heat exchanger 9.
  • the consequence of the shift d between the primary central axis A and the secondary central axis is the ovoid shape that takes the section of the evacuation chamber.
  • the first circulation path comprises a second flat tube 26 provided with a plurality of channels 23.
  • This second flat tube 26 is wound with the first flat tube 22 and together forms the first flow path of the refrigerant fluid 16 at "low pressure" .
  • the heat exchanger 9 further comprises a third flat tube 27 whose multiple channels 23 defines a second circulation path, the latter being borrowed by the refrigerant fluid "high pressure".
  • This third flat tube 27 is on one side in communication with the first pipe 12 placed at the periphery of the heat exchanger and the other, in communication with the second pipe 13 whose axis is aligned or coincident with the secondary central axis B of the heat exchanger 9.
  • the first pipe 12 is then sealingly connected (for example soldered, soldered, etc.) to the end of the third flat tube 27 and the multiplicity of channels 23 communicates fluidly with the interior of the first pipe 12.
  • the other end of the third flat tube 27 which communicates with the second pipe 13.
  • the heat exchanger 9 does not comprise a second flat tube 26, it then consists of a first flat tube 22 and a third flat tube 27 wound together to form respectively the first circulation path and the second road.
  • the third flat tube 27 is then inserted, or sandwiched, between the first and the second flat tube.
  • the three flat tubes (first, third and second) are wound around the secondary central axis B of the heat exchanger 9 so that the respective turns formed by said tubes are nested one in the other.
  • An intermediate subassembly consists of the first flat tube 22 and the second flat tube 26, the third flat tube 27, the first pipe 12 and the second pipe 13 so as to form a unitary assembly.
  • This set is constituted as soon as the elements mentioned above are connected indemontrably without destroying the unitary unit. It is advantageously a solid and waterproof connection (provided for example by soldering, welding, etc ...) which allows to connect all these elements together.
  • the figure 2 illustrates the invention in a sectional view perpendicular to the primary central axis A of the enclosure 2.
  • the intersection between the broken line CC and the broken line FF illustrates the primary central axis A of the enclosure 2, plus particularly, the central axis of the volume defined by the inner wall 19.
  • the thickness of the chamber 2 has been voluntarily shown in part so as not to overload the figure 2 .
  • the intersection between the broken line EE and the broken line FF illustrates the secondary central axis B of the heat exchanger 9.
  • the offset d is the distance that separates the primary central axis A of the chamber 2 and the secondary central axis B of the heat exchanger 9, this offset being a minimum value of one millimeter below which the space saving laterally to the heat exchanger 9 becomes marginal.
  • the maximum value of the offset d is twenty-five millimeters because it is the maximum value to maintain a satisfactory compromise between the outer diameter of the heat exchanger and the outside diameter of the enclosure 2.
  • the invention releases a lateral space to the heat exchanger 9, this space then constituting the evacuation chamber 25. It can be seen that the second duct 15 can then be placed more easily without requiring an increase in the diameter. of the enclosure 2, this with heat exchanger diameter 9, enclosure diameter 2 and constant second pipe diameter 15.
  • the third flat tube 27 is connected at one end to the first pipe 12 located at the periphery of the heat exchanger 9, while the other end of the third flat tube 27 is connected to the second pipe 13 whose axis is coincides with the secondary central axis B of the heat exchanger 9.
  • the first flat tube 22 and the second flat tube 26 capture the refrigerant fluid in the gaseous state and at "low pressure" in the intake chamber via the end of the flat tubes.
  • the refrigerant fluid "low pressure” travels in the first and second flat tubes 22, 26 against the current circulation of the "high pressure” refrigerant which travels in the third flat tube 27.
  • the fluid "low pressure” out through the ends of the first and second flat tubes 22 and 26 to spread in the discharge chamber 25 and out of the combined device 1 via the second pipe 15.
  • the combined device 1 is capable of being fluidly connected to the air conditioning loop via the upper and lower partitions 4.
  • the connections between the combined device 1 and on the one hand the compressor and on the other hand the gas cooler are made via conduits connected to the lower partition 4 while the connections between the combined device 1 and on the one hand the evaporator and other the detent member is formed by means of conduits connected to the upper partition 3.
  • Such arrangements facilitate the integration of the combined device 1 on the air conditioning loop and therefore its integration into the engine compartment of the motor vehicle.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP09179140.0A 2008-12-22 2009-12-14 Dispositif combiné comprenant un échangeur de chaleur interne et un accumulateur Active EP2199709B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0807422A FR2940418B1 (fr) 2008-12-22 2008-12-22 Dispositif combine comprenant un echangeur de chaleur interne et un accumulateur

Publications (3)

Publication Number Publication Date
EP2199709A2 EP2199709A2 (fr) 2010-06-23
EP2199709A3 EP2199709A3 (fr) 2012-01-04
EP2199709B1 true EP2199709B1 (fr) 2016-11-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP09179140.0A Active EP2199709B1 (fr) 2008-12-22 2009-12-14 Dispositif combiné comprenant un échangeur de chaleur interne et un accumulateur

Country Status (6)

Country Link
US (1) US20100155012A1 (zh)
EP (1) EP2199709B1 (zh)
JP (1) JP5497419B2 (zh)
CN (1) CN101799232B (zh)
ES (1) ES2615510T3 (zh)
FR (1) FR2940418B1 (zh)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2928997B1 (fr) * 2008-03-20 2014-06-20 Valeo Systemes Thermiques Echangeur de chaleur et ensemble integre de climatisation comprenant un tel echangeur.
FR2940420B1 (fr) * 2008-12-22 2010-12-31 Valeo Systemes Thermiques Dispositif combine comprenant un echangeur de chaleur interne et un accumulateur constitutifs d'une bouche de climatisation
FR2940419B1 (fr) * 2008-12-22 2010-12-31 Valeo Systemes Thermiques Dispositif combine constitue d'un echangeur de chaleur interne et d'un accumulateur, et pourvu d'un composant interne multifonctions
GB201411563D0 (en) * 2014-06-30 2014-08-13 Eaton Ind Ip Gmbh & Co Kg Accumulator for an air conditioning system
US10429096B2 (en) * 2016-03-24 2019-10-01 Laird Technologies, Inc. Combined heater and accumulator assemblies
JP6889541B2 (ja) * 2016-11-08 2021-06-18 サンデンホールディングス株式会社 内部熱交換器一体型アキュムレータ及びこれを用いた冷凍サイクル
DE102021201509B4 (de) * 2021-02-17 2022-11-17 Hanon Systems Kombination eines Kältemittel-Akkumulators und eines internen Wärmeübertragers für Kältemittel

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2621903A (en) * 1949-07-02 1952-12-16 Irving H Cohler Heat exchange tubing
US2637983A (en) * 1950-08-22 1953-05-12 Kramer Trenton Co Refrigerating apparatus with hot gas defrosting means
US3264837A (en) * 1965-04-09 1966-08-09 Westinghouse Electric Corp Refrigeration system with accumulator means
JPS4611800Y1 (zh) * 1968-02-14 1971-04-23
US4537045A (en) * 1984-12-07 1985-08-27 Westinghouse Electric Corp. Combination refrigerant receiver, accumulator and heat exchanger
SU1291795A1 (ru) * 1985-10-10 1987-02-23 Специальное Конструкторско-Технологическое Бюро Компрессорного И Холодильного Машиностроения Ресивер конденсатора компрессионной холодильной машины
DE19635454B4 (de) * 1996-08-31 2010-06-17 Behr Gmbh & Co. Kg Sammler-Wärmeübertrager-Baueinheit und damit ausgerüstete Klimaanlage
JP2001174083A (ja) * 1999-12-16 2001-06-29 Zexel Valeo Climate Control Corp 熱交換器
JP2002195677A (ja) * 2000-10-20 2002-07-10 Denso Corp ヒートポンプサイクル
JP4492017B2 (ja) * 2000-11-09 2010-06-30 株式会社デンソー アキュムレータモジュール
US20030102112A1 (en) * 2001-12-03 2003-06-05 Smithey David W. Flattened tube heat exchanger made from micro-channel tubing
JP2004028460A (ja) * 2002-06-26 2004-01-29 Denso Corp 蒸気圧縮式冷凍機
DE10258618B3 (de) * 2002-12-16 2004-06-24 Daimlerchrysler Ag Klimaanlage, insbesondere für Kraftfahrzeuge
DE102004050409A1 (de) * 2004-10-15 2006-04-27 Valeo Klimasysteme Gmbh Akkumulator mit internem Wärmetauscher für eine Klimaanlage
DE102005058153B4 (de) * 2005-04-22 2007-12-06 Visteon Global Technologies Inc., Van Buren Wärmeübertrager mit Mehrkanalflachrohren
DE102005021787A1 (de) * 2005-05-11 2006-11-16 Modine Manufacturing Co., Racine Vorrichtung zur Behandlung des Kältemittels

Also Published As

Publication number Publication date
JP5497419B2 (ja) 2014-05-21
FR2940418A1 (fr) 2010-06-25
ES2615510T3 (es) 2017-06-07
CN101799232B (zh) 2014-08-20
FR2940418B1 (fr) 2012-12-07
EP2199709A3 (fr) 2012-01-04
JP2010169387A (ja) 2010-08-05
US20100155012A1 (en) 2010-06-24
CN101799232A (zh) 2010-08-11
EP2199709A2 (fr) 2010-06-23

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