EP1640676B1 - Dispositif combiné d'échangeur de chaleur interne et d'accumulateur pour un circuit de climatisation - Google Patents

Dispositif combiné d'échangeur de chaleur interne et d'accumulateur pour un circuit de climatisation Download PDF

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Publication number
EP1640676B1
EP1640676B1 EP05017463A EP05017463A EP1640676B1 EP 1640676 B1 EP1640676 B1 EP 1640676B1 EP 05017463 A EP05017463 A EP 05017463A EP 05017463 A EP05017463 A EP 05017463A EP 1640676 B1 EP1640676 B1 EP 1640676B1
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EP
European Patent Office
Prior art keywords
container
refrigerating fluid
cylindrical wall
passage
low temperature
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.)
Not-in-force
Application number
EP05017463A
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German (de)
English (en)
French (fr)
Other versions
EP1640676A1 (fr
Inventor
Stefan Karl
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 EP1640676A1 publication Critical patent/EP1640676A1/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
    • F28D7/02—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 helically coiled
    • F28D7/026—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 helically coiled the conduits of only one medium being helically coiled and formed by bent members, e.g. plates, the coils having a cylindrical configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/105—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being corrugated elements extending around the tubular 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
    • F28F7/00—Elements not covered by group F28F1/00, F28F3/00 or F28F5/00
    • F28F7/02—Blocks traversed by passages for heat-exchange media
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/051—Compression system with heat exchange between particular parts of the system between the accumulator and another part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the invention relates to the field of air conditioning circuits, in particular for motor vehicles.
  • the refrigerant fluid usually a fluorinated compound
  • the refrigerant fluid is present in two different phases, namely a gas phase and a liquid phase.
  • the gaseous cooling fluid set in motion by a compressor is condensed in the liquid state in a condenser and then expanded in a pressure reducer. From there, he gains an evaporator where he turns into a gaseous state to win the compressor, and so on.
  • Air conditioning circuits have therefore been proposed which use such natural fluids, present in the supercritical state, which operate at much higher pressures than in the case of conventional air-conditioning circuits.
  • the refrigerant gas is sent by the compressor to a gas cooler and then in a first part of an internal heat exchanger before gaining an expander and an evaporator.
  • the coolant gains an accumulator then crosses a second part of the internal heat exchanger before returning to the compressor inlet.
  • the high-pressure refrigerant at high temperature exchanges heat with the same refrigerant at low pressure and low temperature.
  • this known device has a number of disadvantages.
  • the volume occupied by the internal heat exchanger in the accumulator is relatively high.
  • the diameter of the accumulator is determined by the minimum radius of curvature of the coaxially disposed heat exchanger.
  • the inner wall of the heat exchanger is at low temperature, which causes a large heat exchange with the surrounding environment resulting in a loss of efficiency of the system.
  • the relatively thick wall of the accumulator has no other function than to contain the coolant.
  • the thickness of the wall of the accumulator must be relatively large to withstand relatively high burst pressure levels.
  • the accumulator wall is in direct contact with the surrounding environment and placed in a high airflow zone, which increases the heat exchange with the surrounding environment and results in a loss of efficiency.
  • the connections for the coolant are placed at the four corners of the heat exchange module, which leads to complex connections.
  • the invention aims to provide a combined device for internal heat exchanger and accumulator for an air conditioning circuit traversed by a refrigerant, which overcomes the aforementioned drawbacks.
  • the invention proposes for this purpose a combined device of the type defined in the introduction, which comprises an outer cylindrical wall in which are formed a plurality of channels for the circulation of the high-pressure refrigerant at high temperature, a lower flange clean closing a lower end of the cylindrical wall, an upper flange adapted to close an upper end of the cylindrical wall, coolant access ports provided in the lower and upper flanges, a container disposed in the space defined by the cylindrical wall and the lower and upper flanges, a low-pressure, low-temperature refrigerant supply communicating with the container, and a passage for the circulation of the low-pressure, low-temperature refrigerant fluid provided between the cylindrical wall and the container and fed from the container.
  • connections for the refrigerant, for connection to the evaporator and the compressor are grouped respectively in the upper flange and in the lower flange, which simplifies the structure.
  • container here means an element which essentially delimits a phase separation zone for the cooling fluid, that is to say for separating the gaseous and liquid phases of this fluid. It is furthermore advantageous that this container also delimits a coolant storage zone in the liquid phase, thus forming a liquid reservoir.
  • the channels formed in the outer cylindrical wall are preferably parallel.
  • the lower and upper flanges are closure members for sealing the outer cylindrical wall at its lower and upper ends.
  • the lower and upper flanges are advantageously provided respectively with a lower groove arranged to receive the lower end of the outer cylindrical wall and an upper groove. arranged to receive an upper end of the outer cylindrical wall.
  • the container comprises an inner cylindrical wall spaced internally from the outer cylindrical wall to define an annular space, forming a passage for the circulation of the refrigerant fluid at low pressure and at low temperature, which communicates in part upper with the container and in the lower part with a low-pressure refrigerant discharge passage at low temperature, which passes through the lower flange.
  • the annular space may constitute a passage without obstacles, or direct passage, for the circulation of refrigerant fluid at low pressure and low temperature.
  • said annular space can accommodate a heat exchange means to form a helical channel between the outer cylindrical wall and the inner cylindrical wall.
  • This heat exchange means may be, for example, a helical member or a helical capillary tube which extends into the container.
  • the inner cylindrical wall is advantageously connected to a domed bottom which rests against the lower flange.
  • the outer cylindrical wall is advantageously formed of an extruded profile in which the channels are formed for the circulation of the refrigerant fluid at high pressure and at high temperature.
  • the device comprises an extruded profile comprising external channels which constitute the channels for the circulation of the refrigerant fluid at high pressure and high temperature and internal channels that constitute the circulation passage of the refrigerant fluid at low pressure and low temperature.
  • the refrigerant supply at low pressure and at low temperature, communicating with the container, advantageously comprises means for forming a vortex in the refrigerant fluid at low pressure and low temperature entering the container to separate the gas phase and the phase liquid refrigerant.
  • the means for forming this vortex can be constituted for example by a helical tube housed in the container, or by cyclone means.
  • the device of the invention advantageously comprises a return member to ensure the transfer of a lubricating oil conveyed by the refrigerant from the bottom of the container to the passage ensuring the circulation of the coolant at low pressure and low temperature.
  • the lower flange comprises an internal passage forming an inlet adapted to be connected to the outlet of a compressor and an outlet outlet adapted to be connected to the inlet of a gas cooler.
  • the cooling fluid is advantageously carbon dioxide.
  • the invention in another aspect, relates to a gas cooler for an air conditioning circuit traversed by a refrigerant fluid in the gas phase, this cooler being equipped with a combined device of internal heat exchanger and accumulator as defined above.
  • the gas cooler preferably comprises a manifold having an inlet adapted to be connected to the outlet a compressor, through a passage in the lower flange, and a clean outlet to be connected to an inlet of the lower flange.
  • FIG. 1 shows a combined device of internal heat exchanger and accumulator, designated as a whole by the reference 10.
  • the device 10 is part of an air conditioning circuit traversed by a fluid gaseous refrigerant, operating in the supercritical state, for example carbon dioxide (CO 2 ).
  • the circuit comprises a compressor 12, a gas cooler 14, an expander 16 and an evaporator 18.
  • the device 10 comprises an outer cylindrical wall 20, in the example of circular section, in which are formed a multiplicity of channels 22, in the example of the parallel channels, for the circulation of the refrigerant fluid at high pressure and at high temperature. from the gas cooler 14.
  • the wall 20 is bounded by an inner surface 20a and an outer surface 20b, both cylindrical.
  • the wall 20 is mounted between a lower flange 24 and an upper flange 26.
  • the lower flange 24 is provided with a lower groove 28, here of circular shape, arranged to receive the lower end of the cylindrical wall 20.
  • the upper flange 26 is provided with an upper groove 30, here of circular shape, arranged to receive the end upper part of the outer cylindrical wall 20.
  • a container 32 is disposed in the space (cylindrical volume) defined by the outer cylindrical wall 20 and the flanges 24 and 26.
  • the container 32 delimits at the same time a separation zone of the gaseous and liquid phases of the cooling fluid and a zone of storage of the coolant in the liquid phase, thereby forming a liquid reservoir for the accumulation of coolant
  • This container comprises a cylindrical wall 34 disposed coaxially and at a distance from the outer wall 20 and a convex bottom 36, which rests against an upper face 38 of the lower flange 24.
  • the latter is also bounded externally by a lower face 40.
  • the wall 34 may be described as an "inner wall” of the device insofar as it is internally spaced from the outer wall 20.
  • the wall 34 is bounded by an inner surface 34a and an outer surface 34b.
  • the domed bottom 36 and the lower flange 24 define an annular channel for the discharge of the refrigerant, as will be seen later.
  • the upper flange 26 is limited by a lower face 42 and an upper face 44.
  • the two flanges are advantageously made in the form of machined blocks.
  • the cylindrical wall 34 of the container 32 has an open end 46 which is at a small distance d from the lower face 42 of the upper flange. In this way, the interior of the container 32 can communicate with a passage 48 of annular shape between the outer wall 20 and the container, this passage being intended for the circulation of refrigerant fluid at low pressure and at low temperature.
  • the above-mentioned passage 48 coincides with the annular space delimited between the cylindrical wall 34 of the container, which constitutes an inner wall, and the outer cylindrical wall 20.
  • This annular space allows here a passage without obstacles, or direct passage, for the circulation of the coolant at low pressure and at low temperature.
  • the annular space thus formed communicates in the lower part with a discharge passage 50 for the refrigerant fluid at low pressure and at low temperature, which passes through the lower flange 24, between its faces 38 and 40, and which thus constitutes an orifice of 52.
  • the passage 50 opens in the upper part in the aforementioned annular channel, formed between the curved bottom 36 and the upper face 38 of the lower flange 24.
  • the upper flange 26 has a feed passage 54 for the refrigerant fluid at low pressure and low temperature.
  • This passage 54 is made in the form of a bore passing through the flange 26 and opening on its faces 42 and 44.
  • the passage 54 forms an inlet orifice 56 for the refrigerant fluid at low pressure and at low temperature coming from the evaporator 18.
  • This helical tube 60 constitutes means for forming a vortex in the refrigerant fluid low pressure and low temperature entering the container. This makes it possible to separate the gaseous and liquid phases of the refrigerant fluid.
  • the liquid phase thus separated accumulates in the container 32, the level of the liquid being identified by the reference N in FIG. while the gaseous phase gains the passage 48 to leave the device 10 by the evacuation passage 50.
  • the coolant conveys an oil that is necessary to ensure the lubrication of the compressor 12.
  • This lubricating oil is discharged from the container 32 by a return member 64, here made in the form of a capillary tube, the lower end 66 reaches the bottom of the container, while the upper end 68, in the form of a stick, opens in the upper part of the passage 48.
  • the upper flange 26 further comprises an outlet orifice 70 communicating with the upper groove 30 and adapted to be connected to the inlet of the expander 16.
  • the lower flange 24 comprises an orifice 72 opening into the lower groove 28 and adapted to be connected to the outlet of the gas cooler 14. Furthermore, the lower flange 24 comprises an internal passage 74 made by two bores at right angles which communicate between they and which open on the lower face 40 of the flange 24 and on a side face 76 of the flange to form an inlet port 78 to be connected to the output of the compressor 12 and an outlet port 80 to be connected at the inlet of the gas cooler 14.
  • the orifices 72 and 80 of the flange 24 are located close to each other, opening on the lateral face 76, to facilitate connection or soldering of the flange to the cooler of gas 14.
  • the circuit thus equipped with the device 10 operates in the following manner.
  • the gaseous cooling fluid coming from the compressor 12 passes through the internal passage 74 of the flange 24 to reach the gas cooler 14.
  • the coolant reaches the lower groove 28 and then flows vertically, from bottom to top, in the channels 22 of the wall 20 as shown by the arrows.
  • the refrigerant wins the throat upper 30 then passes successively through the expander and the evaporator 18 to gain the inlet orifice 56.
  • the refrigerant then enters the container 32 via the helical tube 60. Due to the vortex movement thus produced, the liquid and gaseous phases refrigerant are separated.
  • the gaseous refrigerant then gains the passage 48 to access the evacuation passage 50 and reach the inlet of the compressor 12.
  • the lubricating oil is discharged from the bottom of the container by the capillary tube 64 and is then conveyed in the refrigerant to allow lubrication of the compressor.
  • the thermal performance is increased because the heat exchange between the accumulator (i.e. the container 32) and the ambient is reduced. This also results in a reduction of possible leaks due to the reduced number of connections.
  • the outer cylindrical wall 20 is advantageously made in the form of an extruded profile, preferably made of metallic material, in which the parallel channels 22 are formed.
  • the container 32 is made in the form of a separate component, in this case a container with a convex bottom, which is received inside this wall 20.
  • other embodiments are possible.
  • FIG 2 is a detailed view of an upper part of a device 10 according to Figure 1.
  • the elements common with those of Figure 1 are designated by the same references.
  • a bore 82 is seen in the form of a blind hole which opens onto the upper face 44 of the upper flange 26. This bore is intended for fixing a counter flange (not shown) via of a screw or the like.
  • FIG. 3 which is an end view of the upper flange 26, the bore 82 and the orifices 56 and 76 are also visible.
  • FIG 4 is a detailed view of the lower part of the combined device of Figure 2.
  • the elements common with those of Figure 1 are designated by the same reference numerals.
  • the lower flange 24 also comprises a bore 84 formed in the form of a blind hole which opens on the lower face 40 of the flange 24. This bore is intended to allow the attachment of a counter flange (not shown) by the intermediate of a screw or the like.
  • FIG. 5 is a horizontal sectional view of the device of FIG. 4. It shows in detail the structure of the cylindrical wall 20, which is in the form of an extruded profile and which defines the channels 22. It is also seen that the container 32 is made in the form of a separate component which is housed coaxially inside the wall 20.
  • FIG. 6 is a perspective view showing the coaxial arrangement of the outer wall 20 and the inner wall 34 of the container 32.
  • the device comprises an extruded profile 86 which comprises, on the one hand, external channels 22 which constitute the parallel channels for the circulation of the refrigerant fluid at high pressure and at high temperature, and internal channels 88 which constitute the circulation passage of the refrigerant fluid at low pressure and at low temperature.
  • the channels 20 and 22 are arranged in a circular configuration which surrounds another circular configuration formed by the channels 88. In this way, the high temperature and high temperature refrigerant circulates countercurrently with the low pressure refrigerant and at low temperature.
  • the refrigerant circulates in a single pass, both in the channels 22 and in the passage 48 or the channels 88.
  • the outer wall 20 is divided into two parts, a portion 20A for fluid flow in one direction and a portion 20B for fluid flow in another direction.
  • the passage 48 is divided into two parts, a portion 48A in correspondence of the portion 20A and a portion 48B in correspondence of the portion 20B.
  • the fluid can flow up and down in the portion 20A and up and down in the portion 20B, from bottom to top in the portion 48A and from top to bottom in the portion 48B. This assumes of course to arrange the grooves flanges to allow each time a return of the fluid.
  • FIG. 9 shows another alternative embodiment in which the annular space between the outer wall 20 and the wall 34 of the container 32 houses a heat exchange means 90, for example a flat wire wound helically around the wall 34, for forming a helical channel 91 between the walls 20 and 34.
  • a heat exchange means 90 for example a flat wire wound helically around the wall 34, for forming a helical channel 91 between the walls 20 and 34.
  • it may be a helically wound capillary tube which extends into the container to form the tube 64 mentioned above.
  • the objective is to reduce the passage section in the annular passage 48 to cause an increase in the flow rate of the refrigerant fluid at low pressure and low temperature. This increase in speed has a positive impact on the heat exchange coefficient between the wall 20 and the refrigerant.
  • FIG. 10 shows a gas cooler 14 equipped with a combined device 10 according to the invention.
  • the gas cooler 14 comprises a beam 92 mounted between two tubular collectors 94 and 96 capable of being arranged vertically.
  • the combined device 10 is substantially vertically and coaxially implanted along the manifold 94.
  • the lower flange 24 comprises, as in Figs. 1 and 4, an inlet port 72 and an outlet port 80.
  • the outlet port 80 is adapted to be connected to an inlet port 98 of the manifold 94 for connection of the manifold to the outlet of the compressor 12 through the passage 74 formed in the lower flange.
  • the collector 94 further comprises an outlet orifice 100 adapted to be connected to the inlet orifice 72 of the lower flange which opens into the lower groove 28.
  • FIG. 10 also shows the orifices 52 and 78 of the lower flange which allow the connection with the compressor 12 as well as the orifices 70 and 56 of the upper flange which allow the connection with
  • the cylindrical wall 34 of the container 32 has an outer surface 34b of very slightly corrugated shape to create corrugations which are pressed against the inner surface 20a of the wall 20 and thus form channels 102 for the circulation of refrigerant fluid at low pressure and at low temperature. These channels 102 together form the passage 48 mentioned above.
  • the container 32 is thus in thermal contact with the profile 20 and the exchange surface in contact with the refrigerant fluid at low pressure and at low temperature is considerably increased.
  • the inner surface 34a of the wall 34 is provided with an insulating coating 104 to reduce the heat transfer from the wall 20 to the coolant in liquid form which is contained in the container 32.
  • FIGS. 13 and 14 illustrate another variant in which a cylinder 106 with a corrugated surface is inserted between the inner surface 20a of the wall 20 and the outer surface 34b of the wall 34.
  • the corrugated cylinder 106 is brazed on the wall 20, the two being made for example of an aluminum-based material.
  • the container 32 is formed of a material that does not brace easily with aluminum, for example steel, to withstand the brazing temperature.
  • the container 32 is not provided with an inner liner 104.
  • the invention is not limited to the embodiments described above as examples and extends to other variants.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Power Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Compressor (AREA)
  • Central Air Conditioning (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP05017463A 2004-09-24 2005-08-11 Dispositif combiné d'échangeur de chaleur interne et d'accumulateur pour un circuit de climatisation Not-in-force EP1640676B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0410133A FR2875894B1 (fr) 2004-09-24 2004-09-24 Dispositif combine d'echangeur de chaleur interne et d'accumulateur pour un circuit de climatisation

Publications (2)

Publication Number Publication Date
EP1640676A1 EP1640676A1 (fr) 2006-03-29
EP1640676B1 true EP1640676B1 (fr) 2007-10-24

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EP05017463A Not-in-force EP1640676B1 (fr) 2004-09-24 2005-08-11 Dispositif combiné d'échangeur de chaleur interne et d'accumulateur pour un circuit de climatisation

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Country Link
EP (1) EP1640676B1 (es)
AT (1) ATE376656T1 (es)
DE (1) DE602005002995T2 (es)
ES (1) ES2296024T3 (es)
FR (1) FR2875894B1 (es)

Cited By (1)

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EP3757485A4 (en) * 2018-02-24 2021-10-27 Sanhua Holding Group Co., Ltd. GAS LIQUID SEPARATOR AND HEAT EXCHANGE SYSTEM

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DE102005021787A1 (de) * 2005-05-11 2006-11-16 Modine Manufacturing Co., Racine Vorrichtung zur Behandlung des Kältemittels
FR2890726B1 (fr) * 2005-09-13 2007-12-14 Valeo Systemes Thermiques Ensemble integre pour circuit de climatisation fonctionnant avec un fluide refrigerant supercritique
FR2930018B1 (fr) * 2008-04-15 2010-04-16 Valeo Systemes Thermiques Dispositif combine comprenant un echangeur de chaleur interne et un accumulateur.
WO2013114384A1 (en) * 2011-12-26 2013-08-08 Robert Bosch Engineering And Business Solutions Limited An accumulator for a refrigerant recovery and recharge device
EP2631566B1 (en) 2012-02-24 2018-11-21 Airbus Operations GmbH Accumulator arrangement with an integrated sub-cooler
DE102014207660A1 (de) * 2014-04-23 2015-10-29 Mahle International Gmbh Innerer Wärmeübertrager
CN106461337B (zh) 2014-06-30 2019-01-29 株式会社Ihi 冷凝器以及清洗装置
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US11573036B2 (en) 2018-02-24 2023-02-07 Sanhua Holding Group, Co., Ltd. Gas-liquid separator and heat exchange system

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DE602005002995D1 (de) 2007-12-06
DE602005002995T2 (de) 2008-08-21
EP1640676A1 (fr) 2006-03-29
FR2875894A1 (fr) 2006-03-31
ATE376656T1 (de) 2007-11-15
ES2296024T3 (es) 2008-04-16
FR2875894B1 (fr) 2006-12-15

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