EP2118608B1 - Heat exchanger and built-in assembly including such exchanger - Google Patents

Heat exchanger and built-in assembly including such exchanger Download PDF

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Publication number
EP2118608B1
EP2118608B1 EP08717605A EP08717605A EP2118608B1 EP 2118608 B1 EP2118608 B1 EP 2118608B1 EP 08717605 A EP08717605 A EP 08717605A EP 08717605 A EP08717605 A EP 08717605A EP 2118608 B1 EP2118608 B1 EP 2118608B1
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EP
European Patent Office
Prior art keywords
fluid
tube
heat exchanger
main
exchanger according
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EP08717605A
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German (de)
French (fr)
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EP2118608A1 (en
Inventor
Jimmy Lemee
Stéphane MEUNIER
François VILLALONGA
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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
    • F28D7/04—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
    • 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
    • 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
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/04—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being formed by spirally-wound plates or laminae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the invention relates to a heat exchanger, in particular to an internal exchanger for an air conditioning circuit operating with a supercritical refrigerant fluid, such as carbon dioxide (CO 2 ).
  • a supercritical refrigerant fluid such as carbon dioxide (CO 2 ).
  • CO 2 carbon dioxide
  • the invention also relates to an integrated assembly for such a circuit.
  • An exchanger according to the preamble of claim 1 is known from the document FR 2 329 9 62 .
  • the supercritical refrigerant fluid remains substantially in the gaseous state and under a very high pressure.
  • Such a circuit generally comprises a compressor, a gas cooler, an internal exchanger, a pressure reducer, an evaporator and an accumulator.
  • the compressor passes the refrigerant at high pressure before sending it to the gas cooler where it is cooled.
  • the fluid then passes into a first part of the internal exchanger and is then expanded by the expander.
  • the expanded low pressure fluid then passes through the evaporator, then passes through the accumulator before passing into a second part of the internal exchanger.
  • the fluid then returns to the compressor.
  • the hot high pressure fluid of the first part of the heat exchanger exchanges heat with the cold fluid at low pressure of the second part.
  • the accumulator is provided at the outlet of the evaporator to store the excess liquid leaving the evaporator.
  • the accumulator is generally in the form of a reservoir adapted to separate the liquid part of the fluid refrigerant of the gaseous part.
  • the accumulator sends the gaseous portion of the refrigerant fluid at low temperature to the compressor after passing through the internal exchanger.
  • Such an air conditioning circuit requires a large number of components and connections, which complicates its manufacture, increases its cost and its size. Furthermore, it is subject to risks of leakage, especially in view of the high pressure of the refrigerant fluid in the gaseous state.
  • patents US 6,523,365 and US 2000-0 752 419 disclose an integrated assembly comprising an accumulator and an internal exchanger arranged coaxially.
  • the internal heat exchanger has a general spiral shape and is composed of two coiled tubes, one for the circulation of the hot fluid and the other for the circulation of the cold fluid.
  • the integrated assembly comprises an outer cylinder and an inner cylinder arranged inside the outer cylinder, and an accumulator.
  • the inner cylinder is in the form of a coiled flat tube provided with micro channels for the circulation of high pressure fluid.
  • This solution has the disadvantage of generating a large longitudinal footprint.
  • the invention improves the situation by providing a heat exchanger for an air conditioning circuit, comprising at least one tube defining a path for the circulation of a first fluid and a second fluid, the tube being wound around an axis. so as to define successive windings.
  • the invention also relates to the use of a heat exchanger, as defined above, as an internal exchanger, wherein the first fluid is a high pressure fluid and the second fluid is a low pressure fluid.
  • the invention further provides an integrated assembly for an air conditioning circuit operating with a refrigerant fluid.
  • the air conditioning circuit comprises an internal heat exchanger having one of the preceding characteristics and a housing in which is housed the internal heat exchanger, the housing delimiting a bottom.
  • the housing comprises an auxiliary tubing arranged outside the windings of the tube, the auxiliary tubing being adapted to receive the second fluid and to convey it to the bottom of the casing so as to send only the part vaporized from the second fluid into the secondary inlet tubing.
  • the invention also proposes an air conditioning circuit operating with a refrigerant fluid, comprising a compressor, a condenser, an expander, and an evaporator.
  • the circuit comprises the integrated assembly defined above.
  • the main inlet pipe is connected to the condenser, and the auxiliary pipe is connected to the compressor, while the main outlet pipe is connected to the lower part of an accumulator and receives the vaporized part of the fluid.
  • FIG 1 shows an air conditioning circuit 10 operating with a refrigerant fluid, in particular a supercritical refrigerant fluid, for example carbon dioxide (CO 2 ).
  • a refrigerant fluid in particular a supercritical refrigerant fluid, for example carbon dioxide (CO 2 ).
  • CO 2 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.
  • An air conditioning circuit operating in a supercritical refrigerant cycle essentially comprises a compressor 14, a gas cooler 11 associated with a fan 16, an internal heat exchanger 9, a pressure reducer 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 where it undergoes a gas phase cooling under high pressure.
  • the fluid is not condensed during cooling, unlike air conditioning circuits that use fluorinated compounds as a coolant.
  • the fluid cooled by the gas cooler 11 then passes into a first portion 90 of the internal exchanger, 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 then passes through the evaporator 13.
  • the evaporator 13 passes the fluid in the gaseous state, at constant pressure.
  • the exchange in the evaporator makes it possible to produce a flow of conditioned air that is sent to the passenger compartment of the vehicle.
  • the refrigerant flowing out of the evaporator 13 is not fully vaporized.
  • the accumulator is provided at the outlet of the evaporator for storing the excess of liquid leaving the evaporator.
  • 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 part of the refrigerant fluid at low temperature into a second part 92 of the internal exchanger 9, called the "cold" part, for a heat exchange with the "hot" part 90.
  • the internal exchanger 9 comprises a flat tube 5 wound in a spiral around an axis (XX) so as to define successive windings, and so that its general shape is substantially cylindrical. Thus, one end of the tube is outside the spiral while the other part is inside the spiral.
  • the successive windings of the tube are closely clamped together so as to define so-called "secondary" channels 54 sealed for the circulation of the fluid at low pressure.
  • the secondary channels 54 are situated between protruding zones or protuberances 53 of the tube 5.
  • the tube 5 has so-called "main" channels 52 at the projecting areas, to be traversed by the fluid at high pressure.
  • the tube 5 has salient main channels 52 for the circulation of the high-pressure fluid which circulates in the part 90 of the internal exchanger.
  • the main channels extend over the entire length of the tube and therefore between the outer end of the spiral and the inner end of the spiral.
  • the successive windings of the tube 50 are closely clamped together so as to delimit between certain at least adjacent main channels 52 sealed secondary channels 54 for the circulation of low pressure fluid (part 92 of the internal exchanger).
  • the secondary channels 54 are represented on the figure 4 .
  • the flat tube 5 is made in the form of a metal section monobloc having a particular section illustrated on the figure 3 .
  • the profile of the tube comprises on one of its faces ribs formed by the main channels 52 and grooves between the main channels 51.
  • the other side of the tube is substantially flat.
  • the ribs formed by the main channels 52 extend along the tubes and have a circular section.
  • the figure 4 is a sectional view showing two successive windings 50 n and 50 n + 1 .
  • the successive windings 50 n and 50 n + 1 are tightly clamped against each other, so that a secondary channel 54 for the circulation of the low pressure fluid is delimited by a groove 51 between two adjacent ribs 52. a given winding 50 n and the flat face of the next winding 50 n + 1 .
  • FIG 5 represents a view of a part of the internal exchanger, according to the state of the art.
  • the tube is still made in the form of a metal profile.
  • the profile of the tube shown in more detail on the figure 6 , has on both sides protruding ribs 520 formed by the main channels 52, and grooves 51 between these ribs.
  • the tube 5 furthermore has a symmetry along an axis (AA) perpendicular to the axis of the main channels 52.
  • each secondary channel 54 for the second fluid is delimited by a groove 51 between two adjacent ribs 52 of a given winding 50 n and the facing groove 51 n + 1 between two adjacent ribs 52 n +1 of the next winding 50 n + 1 .
  • Successive windings of the tube are again closely clamped against each other so as to ensure the sealing of the secondary channels 54.
  • the ribs facing 520 n and 520 n + 1 are in abutment against each other.
  • the internal exchanger 9 can be brazed or glued. During the soldering or gluing process, the windings 50 are fixed together.
  • the internal heat exchanger 9 of the invention thus has an alternation of hot main channels 52 and cold secondary channels 54 in the axis (XX) of the exchanger, which makes it possible to reduce the diametral size of the internal heat exchanger .
  • the internal exchanger of the invention further ensures a sealed separation between the secondary channels 54 so that the risk of accumulation of liquid at the bottom of the internal exchanger is limited. Furthermore, the secondary channels 54 for the circulation of low pressure fluid have no direct contact with the two rows of neighboring main channels 52 where the high pressure fluid flows. Consequently, the risks of interference between the secondary channels 54 and the main channels 52 are extremely low.
  • figure 8 represents a partial perspective view of the upper part of the internal exchanger according to the state of the art.
  • the high pressure fluid and the low pressure fluid flow in opposite directions in their respective channels 52 and 54. More specifically, in the embodiments shown in the drawings, the high pressure fluid flows in the main channels 52 of the the outside of the spiral inward, while the low pressure fluid flows in the secondary channels 54 from the inside of the spiral outwardly.
  • the internal exchanger 9 comprises a main inlet pipe 6 connected to a high-pressure fluid inlet, a main pipe of outlet 32 connected to an outlet for the high pressure fluid, a secondary inlet pipe 30 connected to a low pressure fluid inlet, and a secondary outlet pipe 7 connected to an outlet for the low pressure fluid.
  • the main inlet pipe 6 and the secondary outlet pipe 7 are arranged at the outer end of the pipe 5, while the main outlet pipe 32 and the secondary inlet pipe 30 are arranged at the level of the pipe. inner end of the tube 5.
  • the main inlet pipe 6 receives the fluid from the gas cooler 11 (arrow F1) and the main outlet pipe 32 delivers the fluid to the regulator 12 (arrow F3).
  • the secondary inlet tubing 30 receives the low pressure fluid from the accumulator 17 (arrow F4) while the secondary outlet tubing 7 delivers the low pressure fluid to the compressor 14 (arrow F2).
  • the main inlet tubing 6 is represented on the figure 10 . It has a generally cylindrical shape with an axis parallel to the axis (XX).
  • the main tubing 6 further comprises an elongated opening 60 of shape conjugate to the profile of the tube 5 so as to receive the outer end of the tube 5.
  • the main inlet tubing 6 has a similar shape as represented on the figure 11 , with the exception of the elongate opening 60.
  • the high-pressure fluid thus arrives in the main inlet pipe from the gas cooler 11 and is then transmitted to the main channels 54 through the opening 60.
  • the main outlet pipe 32 for the high-pressure fluid has a general shape similar to that of the main pipe 6 and also has an elongate opening 320 of conjugate shape of the profile of the tube 5 so as to receive the inner end of the tube.
  • the main pipes 6 and 32 both have a closed bottom, while their fluid connections are provided at the top of the pipes.
  • the high-pressure fluid thus passes from the main channels 52 to the main inlet manifold, through the opening 320, then is conveyed outwards towards the expander 12.
  • the secondary inlet tubing 30 partially shown on the Figures 8 and 9 receives fluid at low pressure from bottom to top (arrow F4). It does not have a closed bottom. Apertures 34 elongate along the axis XX are provided on the part of the wall of the pipe 30 which is turned towards the outside of the internal exchanger so as to send the fluid into the secondary channels 54. Thus the fluid at low pressure arrives from the bottom of the tubing 30 before going up along it. The fluid then passes through the openings 34, as shown by the arrows indicated in the tubing 30, to spread in the secondary channels 54, at the beginning of the heat exchange.
  • the secondary inlet tubing 30 may comprise a plurality of channels 300 elongate along the axis (XX), to promote a better distribution in the secondary channels 54.
  • these channels are three in number. non-limiting example.
  • the inlet channels 300 generate a good distribution of the refrigerant on the vertical plane.
  • the openings 34 are arranged on the secondary inlet pipe 30 so as to optimize the distribution of the low-pressure fluid received in all the secondary channels 54.
  • the openings 34 are elongate and arranged to occupy substantially the entire length of the tube.
  • three openings 34 are provided for the fluid communication with each of the three channels 300 of the secondary inlet pipe 30.
  • the three openings are furthermore slightly offset so as to come into communication with each one. 300 channels of the secondary inlet tubing 30.
  • the secondary outlet tubing 7 extends along an axis parallel to the axis (XX) and has a closed bottom. Its fluidic connection is provided on its upper part. Moreover one or more openings 37 elongated along the axis (XX) are provided on the part of its wall facing the center of the internal exchanger to receive the fluid exiting the secondary channels. 54. An embodiment of the openings 37 is shown in FIG. figure 21 .
  • the low-pressure fluid thus passes secondary channels 54 inside the secondary outlet pipe 7, at the end of the heat exchange, then goes back up the along the tubing before being sent to the compressor 14.
  • the main inlet pipe 6 and the secondary outlet pipe 7 may be secured to a connecting plate 76 (see also FIG. figure 21 ).
  • the plate 76 has a curved section and a shape adapted to be housed between the penultimate outer winding of the tube and the last winding of the tube.
  • the secondary tubing 7 is arranged along the wall of the connecting plate under the last winding of the tube while the main inlet tubing 6 is arranged at an edge of the connecting plate, outside the windings.
  • the section of the secondary tubing 7 has a small radial width section to promote its insertion under the last winding of the tube.
  • the heat exchanger also comprises an inner core of substantially cylindrical shape around which the tube 5 is wound. This core 3 makes it possible to stiffen the internal exchanger.
  • the core may be in three nested parts 360, 38 and 32, the last part being the main outlet pipe while the secondary inlet pipe 30 is an integral part of the 360 part.
  • the assembly of the parts 360 and 38 delimits a recess adapted to house the main outlet pipe 32 for the outlet of the high-pressure fluid 32.
  • the core 3 is monobloc and of cylindrical general shape.
  • the main outlet pipe 32 and the secondary inlet pipe 30 form an integral part of the core 3.
  • a tubing 40 is also an integral part of the core 3 to define a passage for the realization of the spiral.
  • the core may consist of two coaxial portions 31 and 33.
  • the portion 33 constitutes an internal rigid structure having recesses in the form of grooves on its periphery while the portion 31 consists of a metal sheet surrounding the rigid structure 31 to define the main outlet tubing 32 and the secondary inlet tubing 30.
  • the tube 5 according to the invention is produced as a profiled monobloc piece and can be obtained by extrusion.
  • the tube 5 is made of aluminum alloy, but other materials are possible.
  • the invention makes it possible to obtain a reduced diametral bulk for the internal exchanger, thanks to the alternation of hot main channels 52 and cold secondary channels 54.
  • the sealed separation between, on the one hand, the secondary channels 54, and on the other hand, between the secondary channels 54 and the neighboring main channels 52 makes it possible to limit the risks of accumulation of liquid at the bottom of the exchanger and the risks of thermal interference.
  • the structure of the internal exchanger according to the invention further ensures good thermal insulation between the main channels 52 and the secondary channels 54, without it is necessary to interpose insulation sheets.
  • the invention therefore reduces the number of components in the exchanger, which simplifies the manufacturing process of the exchanger and reduces its costs.
  • the profile of the tube or tubes is defined in such a way that the channels formed by winding thereof do not comprise convex shapes in order to avoid any filling of the form previously mentioned with oil and therefore to increase the surface area. exchange.
  • the invention also relates to the use of a heat exchanger, as defined above, as an internal exchanger, in which the first fluid is a high-pressure fluid and the second fluid is a low-pressure fluid. .
  • the invention further provides an integrated assembly comprising an accumulator and the internal exchanger 9 described above.
  • the figure 1 schematically shows an air conditioning circuit incorporating such an integrated assembly 100.
  • the integrated assembly comprises an outer casing 115 in which the internal exchanger 9 and an accumulator 17 are arranged.
  • the casing 115 is delimited by a bottom and is closed by a cover, not shown, in order to form a sealed internal chamber.
  • the lid and the housing can be fixed together by soldering.
  • the lid and the housing may be formed of any suitable material.
  • the integrated assembly also comprises an auxiliary pipe 4 designed to receive the low-pressure fluid from the evaporator and convey it towards the bottom of the housing, as shown in FIGS. Figures 8 and 9 .
  • the auxiliary tubing 4 has a general shape cylindrical and is arranged outside the windings of the tube as shown in FIG. figure 9 .
  • the fluid that arrives in the tubing 4 is received in the bottom of the casing 115, so that the liquid portion of the low-pressure refrigerant remains at the bottom of the casing, while only the vaporized portion of the fluid passes into the secondary tubing of the casing. entry 30 whose bottom is open.
  • the low pressure fluid is then sent into the secondary channels 54 through the openings 34.
  • the main external tubing 6 receives the high pressure fluid that is sent into the main channels 52 to flow in the opposite direction to that of the low pressure fluid. pressure in the secondary channels 54.
  • the fluids exchange heat before exiting through their respective outlet pipes 32 and 7.
  • the number of main channels 52 may vary depending on the heat exchange to be performed.
  • the various components of the integrated assembly 100 are advantageously made of an aluminum alloy and are then brazed by means of solder plating.
  • the assembly can be brazed at one time by passing through a brazing furnace. The assembly being thus realized, it is then sufficient to connect it to the branches of the circuit as indicated above.
  • Such an integrated assembly reduces the overall size of the air conditioning circuit while providing satisfactory cooling performance.
  • the invention applies in particular to air conditioning circuits of motor vehicles.

Abstract

The invention relates to a heat exchanger (1) for an air conditioning circuit, that comprises at least one tube (5) defining a path for the circulation of a first fluid and a second fluid, the tube being wound about an axis in order to define successive windings, said windings being tightly arranged against each other in order to define so-called sealed secondary channels (54) for the circulation of the second fluid, said secondary channels (54) being located between protruding areas of said tube (5), and said tube (5) including so-called main channels (52) at the protruding areas, in which the first fluid flows. The invention can particularly be used in air-conditioning for automotive vehicles.

Description

L'invention se rapporte à un échangeur de chaleur, notamment à un échangeur interne pour un circuit de climatisation fonctionnant avec un fluide réfrigérant supercritique, comme le dioxyde de carbone (CO2). L'invention concerne également un ensemble intégré destiné à un tel circuit. Un échangeur selon le préambule de la revendication 1 est connu du document FR 2 329 9 62 .The invention relates to a heat exchanger, in particular to an internal exchanger for an air conditioning circuit operating with a supercritical refrigerant fluid, such as carbon dioxide (CO 2 ). The invention also relates to an integrated assembly for such a circuit. An exchanger according to the preamble of claim 1 is known from the document FR 2 329 9 62 .

Dans les circuits de climatisation connus de ce type, le fluide réfrigérant supercritique reste essentiellement à l'état gazeux et sous une pression très élevée.In known air conditioning circuits of this type, the supercritical refrigerant fluid remains substantially in the gaseous state and under a very high pressure.

Un tel circuit comprend généralement un compresseur, un refroidisseur de gaz, un échangeur interne, un détendeur, un évaporateur et un accumulateur. Le compresseur fait passer le fluide réfrigérant à haute pression avant de l'envoyer au refroidisseur de gaz où il est refroidi. Le fluide passe ensuite dans une première partie de l'échangeur interne, puis est détendu par le détendeur. Le fluide à basse pression détendu passe ensuite à travers l'évaporateur, puis traverse l'accumulateur avant de passer dans une deuxième partie de l'échangeur interne. Le fluide retourne ensuite vers le compresseur.Such a circuit generally comprises a compressor, a gas cooler, an internal exchanger, a pressure reducer, an evaporator and an accumulator. The compressor passes the refrigerant at high pressure before sending it to the gas cooler where it is cooled. The fluid then passes into a first part of the internal exchanger and is then expanded by the expander. The expanded low pressure fluid then passes through the evaporator, then passes through the accumulator before passing into a second part of the internal exchanger. The fluid then returns to the compressor.

Dans l'échangeur interne, le fluide chaud à haute pression de la première partie de l'échangeur de chaleur échange de la chaleur avec le fluide froid à basse pression de la deuxième partie.In the internal heat exchanger, the hot high pressure fluid of the first part of the heat exchanger exchanges heat with the cold fluid at low pressure of the second part.

L'accumulateur est prévu en sortie de l'évaporateur pour stocker l'excédent de liquide qui sort de l'évaporateur. L'accumulateur se présente généralement sous la forme d'un réservoir adapté pour séparer la partie liquide du fluide réfrigérant de la partie gazeuse. L'accumulateur envoie la partie gazeuse du fluide réfrigérant à basse température vers le compresseur après avoir traversé l'échangeur interne.The accumulator is provided at the outlet of the evaporator to store the excess liquid leaving the evaporator. The accumulator is generally in the form of a reservoir adapted to separate the liquid part of the fluid refrigerant of the gaseous part. The accumulator sends the gaseous portion of the refrigerant fluid at low temperature to the compressor after passing through the internal exchanger.

Parmi les échangeurs internes classiquement utilisés, la solution la plus courante consiste à utiliser deux tubes plats brasés l'un à l'autre avec à leurs extrémités des collecteurs distincts pour les entrées et les sorties de fluide. Cette solution présente l'inconvénient de nécessiter l'ajout de matériaux de soudage sur les tubes et génère un encombrement important.Among the internal exchangers conventionally used, the most common solution consists in using two flat tubes brazed to one another with at their ends separate collectors for the fluid inlets and outlets. This solution has the disadvantage of requiring the addition of welding materials on the tubes and generates a large footprint.

D'autres échangeurs internes connus, comme par exemple JP 2003-121086 et JP2003-202197 , utilisent un tube profilé extrudé dans lequel sont ménagées deux rangées de canaux, l'une pour la circulation du fluide chaud, à haute pression, et l'autre pour la circulation du fluide froid, à basse pression. Les collecteurs sont raccordés aux tubes au moyen de fentes aménagées sur un côté du tube. Cette solution génère un encombrement qui reste très important.Other known internal exchangers, for example JP 2003-121086 and JP2003-202197 , use an extruded profile tube in which are formed two rows of channels, one for the circulation of hot fluid at high pressure, and the other for the circulation of cold fluid at low pressure. The manifolds are connected to the tubes by means of slots on one side of the tube. This solution generates a congestion that remains very important.

Un tel circuit de climatisation nécessite un grand nombre de composants et de connexions, ce qui complique sa fabrication, augmente son coût et son encombrement. Par ailleurs, il est sujet à des risques de fuites, compte tenu en particulier de la pression élevée du fluide réfrigérant à l'état gazeux.Such an air conditioning circuit requires a large number of components and connections, which complicates its manufacture, increases its cost and its size. Furthermore, it is subject to risks of leakage, especially in view of the high pressure of the refrigerant fluid in the gaseous state.

Pour minimiser le nombre de composants et leur connexion, ainsi que l'encombrement général du circuit de climatisation, d'autres solutions ont proposé l'intégration ou la combinaison de certains des composants du circuit.To minimize the number of components and their connection, as well as the overall size of the air conditioning circuit, other solutions have proposed the integration or combination of some of the components of the circuit.

Ainsi, les brevets US 6 523 365 et US 2000-0 752 419 divulguent un ensemble intégré comprenant un accumulateur et un échangeur interne disposés de manière coaxiale. L'échangeur de chaleur interne a une forme générale de spirale et est composé de deux tubes enroulés, l'un pour la circulation du fluide chaud et l'autre pour la circulation du fluide froid.Thus, patents US 6,523,365 and US 2000-0 752 419 disclose an integrated assembly comprising an accumulator and an internal exchanger arranged coaxially. The internal heat exchanger has a general spiral shape and is composed of two coiled tubes, one for the circulation of the hot fluid and the other for the circulation of the cold fluid.

On connaît également d'après FR 2 752 921 un ensemble intégré comportant un accumulateur horizontal et un échangeur interne ayant une forme générale de spirale. Un écartement est prévu entre les enroulements de l'échangeur interne pour permettre la circulation du fluide froid, tandis que le fluide chaud circule à l'intérieur du tube enroulé en spirale.It is also known from FR 2 752 921 an integrated assembly comprising a horizontal accumulator and an internal exchanger having a generally spiral shape. A gap 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.

Les solutions précédentes nécessitent de prévoir un espace entre chaque enroulement pour créer le canal du fluide à basse pression. Elles génèrent par conséquent un encombrement diamétral important.The previous solutions require providing a space between each winding to create the low pressure fluid channel. They therefore generate a large diametral bulk.

Dans le brevet US 2005/0103046 , un ensemble intégré qui remédie aux problèmes de l'encombrement diamétral est proposé. L'ensemble intégré comporte un cylindre externe et un cylindre interne aménagé à l'intérieur du cylindre externe, ainsi qu'un accumulateur. Le cylindre interne se présente sous la forme d'un tube plat enroulé muni de micro canaux pour la circulation de fluide à haute pression.In the patent US 2005/0103046 , an integrated set that addresses the problems of the diametral clutter is proposed. The integrated assembly comprises an outer cylinder and an inner cylinder arranged inside the outer cylinder, and an accumulator. The inner cylinder is in the form of a coiled flat tube provided with micro channels for the circulation of high pressure fluid.

Cette solution présente l'inconvénient de générer un encombrement longitudinal important.This solution has the disadvantage of generating a large longitudinal footprint.

L'invention vient améliorer la situation en proposant un échangeur de chaleur pour circuit de climatisation, comprenant au moins un tube délimitant un parcours pour la circulation d'un premier fluide et d'un deuxième fluide, le tube étant enroulé autour d'un axe de manière à définir des enroulements successifs.The invention improves the situation by providing a heat exchanger for an air conditioning circuit, comprising at least one tube defining a path for the circulation of a first fluid and a second fluid, the tube being wound around an axis. so as to define successive windings.

Selon l'invention, il est prévu un échangeur selon la revendication 1. Des caractéristiques optionnelles de l'échangeur de chaleur selon l'invention, complémentaires ou de substitution, sont énoncées ci-après:

  • Les extrémités des canaux principaux sont reçues entre une tubulure principale d'entrée propre à recevoir le premier fluide, et une tubulure principale de sortie propre à délivrer le premier fluide à l'extérieur de l'échangeur, tandis que les extrémités des canaux secondaires sont en communication fluidique avec une tubulure secondaire d'entrée propre à recevoir le deuxième fluide et une tubulure secondaire de sortie propre à délivrer le deuxième fluide à l'extérieur de l'échangeur.
  • Chaque tubulure principale a une forme sensiblement cylindrique autour d'un axe parallèle à l'axe de l'échangeur et présente une ouverture adaptée pour recevoir l'une des extrémités du tube.
  • Chaque tubulure secondaire présente des ouvertures allongées sur une partie de sa paroi pour une communication fluidique avec les canaux secondaires.
  • L'échangeur comporte une plaque de liaison ayant une section courbée de forme adaptée pour venir se loger entre l'avant dernier enroulement externe du tube et le dernier enroulement externe du tube, tandis que la tubulure principale d'entrée et la tubulure secondaire de sortie sont solidaires de la plaque de liaison.
  • L'échangeur comporte un noyau interne de forme sensiblement cylindrique.
  • Le noyau est monobloc.
  • Le noyau est constitué de plusieurs parties imbriquées qui assurent l'alimentation et la distribution du circuit primaire et du circuit secondaire ainsi que l'enroulement du ou des tubes.
  • Le noyau est constitué de deux parties coaxiales, la première partie comportant une structure rigide munie de gorges sur son pourtour et la deuxième partie comportant une feuille métallique enroulée autour de la première partie de manière à définir la tubulure principale de sortie et la tubulure secondaire d'entrée.
  • Les tubulures secondaires d'entrée et de sortie comprennent une ou plusieurs ouvertures allongées dans l'axe de l'échangeur de manière à être en communication fluidique avec les canaux secondaires.
  • Les ouvertures sont décalées radialement et dans l'axe de l'échangeur les unes par rapport aux autres.
  • La tubulure secondaire d'entrée comporte une ou plusieurs ouvertures et elle est divisée en un ou plusieurs canaux d'entrée de sorte que chaque canal d'entrée communique avec l'une au moins des ouvertures.
  • Le tube est formé en tant que pièce profilée en un ou plusieurs éléments.
  • Le tube est obtenu par extrusion.
  • Les canaux principaux du tube présentent une section sensiblement circulaire.
According to the invention, there is provided an exchanger according to claim 1. Optional features of the heat exchanger according to the invention, complementary or substitution, are set out below:
  • The ends of the main channels are received between a main inlet pipe adapted to receive the first fluid, and a main outlet pipe adapted to deliver the first fluid to the outside of the exchanger, while the ends of the secondary channels are in fluid communication with a secondary inlet tubing adapted to receive the second fluid and a secondary outlet pipe clean to deliver the second fluid outside the exchanger.
  • Each main tubing has a substantially cylindrical shape about an axis parallel to the axis of the exchanger and has an opening adapted to receive one of the ends of the tube.
  • Each secondary tubing has elongated apertures on a portion of its wall for fluid communication with the secondary channels.
  • The exchanger comprises a connecting plate having a curved section of shape adapted to be housed between the penultimate outer winding of the tube and the last outer winding of the tube, while the main inlet pipe and the secondary outlet pipe are integral with the connecting plate.
  • The exchanger comprises an inner core of substantially cylindrical shape.
  • The nucleus is monobloc.
  • The core consists of several nested parts that provide power and distribution of the primary circuit and the secondary circuit and the winding of the tube or tubes.
  • The core is made up of two coaxial parts, the first part having a rigid structure provided with grooves on its periphery and the second part comprising a metal sheet wound around the first part so as to define the main outlet pipe and the secondary tubing. 'Entrance.
  • The inlet and outlet secondary pipes comprise one or more elongate openings in the axis of the exchanger so as to be in fluid communication with the secondary channels.
  • The openings are offset radially and in the axis of the exchanger relative to each other.
  • The secondary inlet manifold has one or more openings and is divided into one or more inlet channels such that each inlet channel communicates with at least one of the openings.
  • The tube is formed as a profiled piece in one or more elements.
  • The tube is obtained by extrusion.
  • The main channels of the tube have a substantially circular section.

L'invention concerne aussi l'utilisation d'un échangeur de chaleur, tel que défini précédemment, en tant qu'échangeur interne, dans laquelle le premier fluide est un fluide à haute pression et le deuxième fluide est un fluide à basse pression.The invention also relates to the use of a heat exchanger, as defined above, as an internal exchanger, wherein the first fluid is a high pressure fluid and the second fluid is a low pressure fluid.

L'invention propose en outre un ensemble intégré pour un circuit de climatisation fonctionnant avec un fluide réfrigérant. Le circuit de climatisation comporte un échangeur interne ayant l'une des caractéristiques précédentes et un boîtier dans lequel est logé l'échangeur interne, le boîtier délimitant un fond. Le boîtier comporte une tubulure auxiliaire agencée à l'extérieur des enroulements du tube, la tubulure auxiliaire étant propre à recevoir le deuxième fluide et à l'acheminer vers le fond du boîtier de manière à envoyer seulement la partie vaporisée du deuxième fluide dans la tubulure secondaire d'entrée.The invention further provides an integrated assembly for an air conditioning circuit operating with a refrigerant fluid. The air conditioning circuit comprises an internal heat exchanger having one of the preceding characteristics and a housing in which is housed the internal heat exchanger, the housing delimiting a bottom. The housing comprises an auxiliary tubing arranged outside the windings of the tube, the auxiliary tubing being adapted to receive the second fluid and to convey it to the bottom of the casing so as to send only the part vaporized from the second fluid into the secondary inlet tubing.

L'invention propose également un circuit de climatisation fonctionnant avec un fluide réfrigérant, comprenant un compresseur, un condenseur, un détendeur, et un évaporateur. Le circuit comporte l'ensemble intégré défini ci-dessus. La tubulure principale d'entrée est reliée au condenseur, et la tubulure auxiliaire est reliée au compresseur, tandis que la tubulure principale de sortie est reliée à la partie basse d'un accumulateur et reçoit la partie vaporisée du fluide.The invention also proposes an air conditioning circuit operating with a refrigerant fluid, comprising a compressor, a condenser, an expander, and an evaporator. The circuit comprises the integrated assembly defined above. The main inlet pipe is connected to the condenser, and the auxiliary pipe is connected to the compressor, while the main outlet pipe is connected to the lower part of an accumulator and receives the vaporized part of the fluid.

D'autres caractéristiques et avantages de l'invention apparaîtront à l'examen de la description détaillée ci-après et des dessins annexés sur lesquels :

  • la figure 1 est un schéma d'un circuit de climatisation selon l'invention,
  • la figure 2 est une vue en perspective montrant une partie de l'échangeur interne selon l'invention,
  • la figure 3 est un schéma en coupe du tube de l'échangeur interne selon l'invention,
  • la figure 4 est un schéma en coupe de l'échangeur interne montrant deux enroulements successifs selon l'invention,
  • la figure 5 est une vue en perspective d'une partie de l'échangeur interne selon l'état de la technique,
  • la figure 6 est un schéma en coupe du tube de l'échangeur interne selon l'état de la technique
  • la figure 7 est un schéma en coupe de l'échangeur interne montrant deux enroulements successifs selon l'état de la technique,
  • la figure 8 est une vue en perspective partielle de l'échangeur interne selon l'invention,
  • la figure 9 est une vue de haut de l'échangeur de la figure 8,
  • la figure 10 est une vue en perspective d'une tubulure d'entrée pour le fluide à haute pression selon l'état de la technique,
  • la figure 11 représente une tubulure d'entrée pour le fluide à haute pression, selon le deuxième mode de réalisation de l'invention,
  • la figure 12 est une vue de dessus d'un échangeur interne, comprenant un noyau en trois parties,
  • les figures 13 à 15 représentent les éléments du noyau de l'échangeur interne de la figure 12,
  • la figure 16 est une vue de dessus d'un échangeur interne, comprenant un noyau monobloc,
  • la figure 17 représente le noyau de l'échangeur interne de la figure 16,
  • la figure 18 est une vue en perspective d'un échangeur de chaleur interne utilisant un noyau en deux parties coaxiales,
  • les figures 19 et 20 représentent les éléments du noyau de l'échangeur interne de la figure 18, et
  • la figure 21 est une vue partielle en perspective montrant une réalisation possible des ouvertures de la tubulure secondaire de sortie.
Other characteristics and advantages of the invention will appear on examining the detailed description below and the attached drawings in which:
  • the figure 1 is a diagram of an air conditioning circuit according to the invention,
  • the figure 2 is a perspective view showing part of the internal exchanger according to the invention,
  • the figure 3 is a sectional diagram of the tube of the internal exchanger according to the invention,
  • the figure 4 is a sectional diagram of the internal exchanger showing two successive windings according to the invention,
  • the figure 5 is a perspective view of part of the internal exchanger according to the state of the art,
  • the figure 6 is a sectional diagram of the tube of the internal exchanger according to the state of the art
  • the figure 7 is a sectional diagram of the internal exchanger showing two successive windings according to the state of the art,
  • the figure 8 is a partial perspective view of the internal heat exchanger according to the invention,
  • the figure 9 is a view from the top of the exchanger of the figure 8 ,
  • the figure 10 is a perspective view of an inlet pipe for the high-pressure fluid according to the state of the art,
  • the figure 11 represents an inlet pipe for the high-pressure fluid, according to the second embodiment of the invention,
  • the figure 12 is a top view of an internal exchanger, comprising a three-part core,
  • the Figures 13 to 15 represent the core elements of the internal exchanger of the figure 12 ,
  • the figure 16 is a top view of an internal exchanger, comprising a monoblock core,
  • the figure 17 represents the core of the internal exchanger of the figure 16 ,
  • the figure 18 is a perspective view of an internal heat exchanger using a coaxial two-part core,
  • the Figures 19 and 20 represent the core elements of the internal exchanger of the figure 18 , and
  • the figure 21 is a partial perspective view showing a possible embodiment of the openings of the secondary outlet tubing.

Il est tout d'abord fait référence à la figure 1 qui montre un circuit de climatisation 10 fonctionnant avec un fluide réfrigérant, en particulier un fluide réfrigérant supercritique, par exemple du dioxyde de carbone (CO2).First of all, it refers to the figure 1 which shows an air conditioning circuit 10 operating with a refrigerant fluid, in particular a supercritical refrigerant fluid, for example carbon dioxide (CO 2 ).

Le circuit de climatisation 10 peut être installé dans un véhicule automobile pour refroidir l'air de l'habitacle, en fonction des besoins des passagers.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.

Un circuit de climatisation fonctionnant selon un cycle réfrigérant supercritique comprend pour l'essentiel un compresseur 14, un refroidisseur de gaz 11 associé à un ventilateur 16, un échangeur de chaleur interne 9, un détendeur 12, un évaporateur 13, et un accumulateur 17. Le compresseur 14 comprime le fluide réfrigérant jusqu'à une pression de décharge, dite haute pression. Le fluide traverse ensuite le refroidisseur de gaz où il subit un refroidissement en phase gazeuse sous haute pression. Dans le refroidisseur de gaz 11, le fluide n'est pas condensé pendant le refroidissement, contrairement aux circuits de climatisation qui utilisent des composés fluorés comme fluide réfrigérant.An air conditioning circuit operating in a supercritical refrigerant cycle essentially comprises a compressor 14, a gas cooler 11 associated with a fan 16, an internal heat exchanger 9, a pressure reducer 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 where it undergoes a gas phase cooling under high pressure. In the gas cooler 11, the fluid is not condensed during cooling, unlike air conditioning circuits that use fluorinated compounds as a coolant.

Le fluide refroidi par le refroidisseur de gaz 11 passe ensuite dans une première partie 90 de l'échangeur interne, dite branche "chaude", pour être encore refroidie. Le fluide passe ensuite dans le détendeur 12 qui abaisse sa pression, en l'amenant au moins en partie à l'état liquide.The fluid cooled by the gas cooler 11 then passes into a first portion 90 of the internal exchanger, 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.

Le fluide traverse alors l'évaporateur 13. L'évaporateur 13 fait passer le fluide à l'état gazeux, à pression constante. L'échange dans l'évaporateur permet de produire un flux d'air climatisé qui est envoyé vers l'habitacle du véhicule.The fluid then passes through the evaporator 13. The evaporator 13 passes the fluid in the gaseous state, at constant pressure. The exchange in the evaporator makes it possible to produce a flow of conditioned air that is sent to the passenger compartment of the vehicle.

Généralement, le fluide réfrigérant qui sort de l'évaporateur 13 n'est pas entièrement vaporisé. L'accumulateur est prévu en sortie de l'évaporateur pour stocker cet excédent de liquide qui sort de l'évaporateur. Les accumulateurs classiques se présentent sous la forme d'un réservoir adapté pour séparer la partie liquide du fluide réfrigérant de la partie gazeuse. L'accumulateur 17 envoie ensuite la partie gazeuse du fluide réfrigérant à basse température dans une deuxième partie 92 de l'échangeur interne 9, dite partie "froide", pour un échange de chaleur avec la partie "chaude" 90.Generally, the refrigerant flowing out of the evaporator 13 is not fully vaporized. The accumulator is provided at the outlet of the evaporator for storing the excess of liquid leaving the evaporator. 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 part of the refrigerant fluid at low temperature into a second part 92 of the internal exchanger 9, called the "cold" part, for a heat exchange with the "hot" part 90.

On se réfère maintenant à la figure 2 qui représente une vue d'une partie de l'échangeur interne selon l'invention. L'échangeur interne 9 comporte un tube plat 5 enroulé en spirale autour d'un axe (XX) de manière à définir des enroulements successifs, et de sorte que sa forme générale est sensiblement cylindrique. Ainsi, l'une des extrémités du tube se situe à l'extérieur de la spirale tandis que l'autre partie se situe à l'intérieur de la spirale.We now refer to the figure 2 which represents a view of a part of the internal exchanger according to the invention. The internal exchanger 9 comprises a flat tube 5 wound in a spiral around an axis (XX) so as to define successive windings, and so that its general shape is substantially cylindrical. Thus, one end of the tube is outside the spiral while the other part is inside the spiral.

Les enroulements successifs du tube sont étroitement serrés entre eux de manière à délimiter des canaux dits « secondaires » 54 étanches pour la circulation du fluide à basse pression. Les canaux secondaires 54 se situent entre des zones saillantes ou excroissances 53 du tube 5.The successive windings of the tube are closely clamped together so as to define so-called "secondary" channels 54 sealed for the circulation of the fluid at low pressure. The secondary channels 54 are situated between protruding zones or protuberances 53 of the tube 5.

En outre, le tube 5 présente des canaux dits « principaux » 52 au niveau des zones saillantes, destinés à être traversés par le fluide à haute pression.In addition, the tube 5 has so-called "main" channels 52 at the projecting areas, to be traversed by the fluid at high pressure.

Autrement dit, le tube 5 présente des canaux principaux saillants 52 pour la circulation du fluide à haute pression qui circule dans la partie 90 de l'échangeur interne. Comme le montre la figure 2, les canaux principaux s'étendent sur toute la longueur du tube et donc entre l'extrémité externe de la spirale et l'extrémité interne de la spirale. Par ailleurs, les enroulements successifs du tube 50 sont étroitement serrés entre eux de manière à délimiter entre certains au moins des canaux principaux adjacents 52 des canaux secondaires étanches 54 pour la circulation du fluide à basse pression (partie 92 de l'échangeur interne). Les canaux secondaires 54 sont représentés sur la figure 4.In other words, the tube 5 has salient main channels 52 for the circulation of the high-pressure fluid which circulates in the part 90 of the internal exchanger. As shown in figure 2 , the main channels extend over the entire length of the tube and therefore between the outer end of the spiral and the inner end of the spiral. Furthermore, the successive windings of the tube 50 are closely clamped together so as to delimit between certain at least adjacent main channels 52 sealed secondary channels 54 for the circulation of low pressure fluid (part 92 of the internal exchanger). The secondary channels 54 are represented on the figure 4 .

Dans l'invention, le tube plat 5 est réalisé sous la forme d'un profilé métallique monobloc présentant une section particulière illustrée sur la figure 3.In the invention, the flat tube 5 is made in the form of a metal section monobloc having a particular section illustrated on the figure 3 .

L'utilisation d'un tube profilé monobloc simplifie le procédé de fabrication de l'échangeur interne par rapport aux réalisations existantes basées sur l'utilisation de capillaires.The use of a single-piece profiled tube simplifies the manufacturing process of the internal exchanger compared to existing embodiments based on the use of capillaries.

Plus précisément, le profil du tube comporte sur l'une de ses faces des nervures formées par les canaux principaux 52 et des rainures entre les canaux principaux 51. L'autre face du tube est sensiblement plane. Les nervures constituées par les canaux principaux 52 s'étendent le long des tubes et présentent une section circulaire.More specifically, the profile of the tube comprises on one of its faces ribs formed by the main channels 52 and grooves between the main channels 51. The other side of the tube is substantially flat. The ribs formed by the main channels 52 extend along the tubes and have a circular section.

La figure 4 est une vue en coupe montrant deux enroulements successifs 50n et 50n+1. Les enroulements successifs 50n et 50n+1 sont serrés étroitement l'un contre l'autre, de sorte qu'un canal secondaire 54 pour la circulation du fluide à basse pression est délimité par une rainure 51 entre deux nervures adjacentes 52 d'un enroulement donné 50n et la face plane de l'enroulement suivant 50n+1.The figure 4 is a sectional view showing two successive windings 50 n and 50 n + 1 . The successive windings 50 n and 50 n + 1 are tightly clamped against each other, so that a secondary channel 54 for the circulation of the low pressure fluid is delimited by a groove 51 between two adjacent ribs 52. a given winding 50 n and the flat face of the next winding 50 n + 1 .

On se réfère maintenant à la figure 5 qui représente une vue d'une partie de l'échangeur interne, selon l'état de la technique.We now refer to the figure 5 which represents a view of a part of the internal exchanger, according to the state of the art.

Dans ce cas le tube est encore réalisé sous la forme d'un profilé métallique. Toutefois, le profil du tube, illustré plus en détail sur la figure 6, comporte sur ses deux faces des nervures saillantes 520 formées par les canaux principaux 52, et des rainures 51 entre ces nervures. Le tube 5 présente en outre une symétrie selon un axe (AA) perpendiculaire à l'axe des canaux principaux 52.In this case the tube is still made in the form of a metal profile. However, the profile of the tube, shown in more detail on the figure 6 , has on both sides protruding ribs 520 formed by the main channels 52, and grooves 51 between these ribs. The tube 5 furthermore has a symmetry along an axis (AA) perpendicular to the axis of the main channels 52.

Il est maintenant fait référence à la figure 7 qui montre deux enroulements successifs 50n et 50n+1 Comme on peut le voir sur cette figure, chaque canal secondaire 54 pour le deuxième fluide est délimité par une rainure 51 entre deux nervures adjacentes 52 d'un enroulement donné 50n et la rainure en regard 51n+1 entre deux nervures adjacentes 52n+1 de l'enroulement suivant 50n+1. Les enroulements successifs du tube sont là encore étroitement serrés les uns contre les autres de manière à garantir l'étanchéité des canaux secondaires 54. Sur la figure 7, les nervures en regard 520n et 520n+1 sont en appui l'une contre l'autre.Now reference is made to figure 7 which shows two successive windings 50 n and 50 n + 1 As can be seen in this figure, each secondary channel 54 for the second fluid is delimited by a groove 51 between two adjacent ribs 52 of a given winding 50 n and the facing groove 51 n + 1 between two adjacent ribs 52 n +1 of the next winding 50 n + 1 . Successive windings of the tube are again closely clamped against each other so as to ensure the sealing of the secondary channels 54. figure 7 , the ribs facing 520 n and 520 n + 1 are in abutment against each other.

L'échangeur interne 9 peut être brasé ou collé. Au cours du procédé de brasage ou de collage, les enroulements 50 sont fixés entre eux.The internal exchanger 9 can be brazed or glued. During the soldering or gluing process, the windings 50 are fixed together.

L'échangeur interne 9 de l'invention présente ainsi une alternance de canaux principaux chauds 52 et de canaux secondaires froids 54 dans l'axe (XX) de l'échangeur, ce qui permet de réduire l'encombrement diamétral de l'échangeur interne.The internal heat exchanger 9 of the invention thus has an alternation of hot main channels 52 and cold secondary channels 54 in the axis (XX) of the exchanger, which makes it possible to reduce the diametral size of the internal heat exchanger .

L'échangeur interne de l'invention garantit de plus une séparation étanche entre les canaux secondaires 54 de sorte que les risques d'accumulation de liquide au fond de l'échangeur interne sont limités. Par ailleurs, les canaux secondaires 54 pour la circulation du fluide à basse pression n'ont aucun contact direct avec les deux rangées de canaux principaux 52 avoisinantes où circule le fluide à haute pression. Par conséquent, les risques d'interférence entre les canaux secondaires 54 et les canaux principaux 52 sont extrêmement faibles.The internal exchanger of the invention further ensures a sealed separation between the secondary channels 54 so that the risk of accumulation of liquid at the bottom of the internal exchanger is limited. Furthermore, the secondary channels 54 for the circulation of low pressure fluid have no direct contact with the two rows of neighboring main channels 52 where the high pressure fluid flows. Consequently, the risks of interference between the secondary channels 54 and the main channels 52 are extremely low.

Il est maintenant fait référence à la figure 8 qui représente une vue partielle en perspective de la partie haute de l'échangeur interne selon l'état de la technique.Now reference is made to figure 8 which represents a partial perspective view of the upper part of the internal exchanger according to the state of the art.

Comme montré par les flèches de la figure 9 qui est une vue de dessus de l'échangeur de la figure 8, le fluide à haute pression et le fluide à basse pression circulent dans des sens opposés dans leurs canaux respectifs 52 et 54. Plus précisément, dans les formes de réalisation représentées sur les dessins, le fluide à haute pression circule dans les canaux principaux 52 de l'extérieur de la spirale vers l'intérieur, tandis que le fluide à basse pression circule dans les canaux secondaires 54 de l'intérieur de la spirale vers l'extérieur.As shown by the arrows of the figure 9 which is a top view of the exchanger of the figure 8 the high pressure fluid and the low pressure fluid flow in opposite directions in their respective channels 52 and 54. More specifically, in the embodiments shown in the drawings, the high pressure fluid flows in the main channels 52 of the the outside of the spiral inward, while the low pressure fluid flows in the secondary channels 54 from the inside of the spiral outwardly.

Des connexions fluidiques sont prévus pour l'arrivée et la sortie des fluides dans l'échangeur interne 9. Ainsi, l'échangeur interne 9 comporte une tubulure principale d'entrée 6 reliée à une arrivée de fluide à haute pression, une tubulure principale de sortie 32 reliée à une sortie pour le fluide à haute pression, une tubulure secondaire d'entrée 30 reliée à une arrivée de fluide à basse pression, et une tubulure secondaire de sortie 7 reliée à une sortie pour le fluide à basse pression. La tubulure principale d'entrée 6 et la tubulure secondaire de sortie 7 sont agencées au niveau de l'extrémité externe du tube 5, tandis que la tubulure principale de sortie 32 et la tubulure secondaire d'entrée 30 sont agencées au niveau de l'extrémité interne du tube 5.Fluidic connections are provided for the arrival and the exit of the fluids in the internal exchanger 9. Thus, the internal exchanger 9 comprises a main inlet pipe 6 connected to a high-pressure fluid inlet, a main pipe of outlet 32 connected to an outlet for the high pressure fluid, a secondary inlet pipe 30 connected to a low pressure fluid inlet, and a secondary outlet pipe 7 connected to an outlet for the low pressure fluid. The main inlet pipe 6 and the secondary outlet pipe 7 are arranged at the outer end of the pipe 5, while the main outlet pipe 32 and the secondary inlet pipe 30 are arranged at the level of the pipe. inner end of the tube 5.

Lorsque l'échangeur 9 est utilisé comme échangeur interne d'une installation de climatisation à cycle supercritique, la tubulure principale d'entrée 6 reçoit le fluide en provenance du refroidisseur de gaz 11 (flèche F1) et la tubulure principale de sortie 32 délivre le fluide vers le détendeur 12 (flèche F3). La tubulure secondaire d'entrée 30 reçoit le fluide à basse pression en provenance de l'accumulateur 17 (flèche F4) tandis que la tubulure secondaire de sortie 7 délivre le fluide à basse pression vers le compresseur 14 (flèche F2).When the exchanger 9 is used as internal exchanger of a supercritical air conditioning system, the main inlet pipe 6 receives the fluid from the gas cooler 11 (arrow F1) and the main outlet pipe 32 delivers the fluid to the regulator 12 (arrow F3). The secondary inlet tubing 30 receives the low pressure fluid from the accumulator 17 (arrow F4) while the secondary outlet tubing 7 delivers the low pressure fluid to the compressor 14 (arrow F2).

La tubulure principale d'entrée 6 selon l'invention est représentée sur la figure 10. Elle présente une forme généralement cylindrique d'axe parallèle à l'axe (XX). La tubulure principale 6 comporte en outre une ouverture allongée 60 de forme conjuguée au profil du tube 5 de manière à recevoir l'extrémité externe du tube 5. Dans l'état de la technique, la tubulure principale d'entrée 6 a une forme analogue comme représentée sur la figure 11, à l'exception de l'ouverture allongée 60. Le fluide à haute pression arrive ainsi dans la tubulure principale d'entrée, en provenance du refroidisseur de gaz 11, puis est transmis aux canaux principaux 54, à travers l'ouverture 60.The main inlet tubing 6 according to the invention is represented on the figure 10 . It has a generally cylindrical shape with an axis parallel to the axis (XX). The main tubing 6 further comprises an elongated opening 60 of shape conjugate to the profile of the tube 5 so as to receive the outer end of the tube 5. In the state of the art, the main inlet tubing 6 has a similar shape as represented on the figure 11 , with the exception of the elongate opening 60. The high-pressure fluid thus arrives in the main inlet pipe from the gas cooler 11 and is then transmitted to the main channels 54 through the opening 60.

La tubulure principale de sortie 32 pour le fluide à haute pression présente une forme générale analogue à celle de la tubulure principale 6 et comporte également une ouverture allongée 320 de forme conjuguée du profil du tube 5 de manière à recevoir l'extrémité interne du tube. Les tubulures principales 6 et 32 comportent toutes deux un fond fermé, tandis que leurs raccords fluidiques sont prévus en haut des tubulures. Le fluide à haute pression passe ainsi des canaux principaux 52 à la tubulure principale d'entrée, à travers l'ouverture 320, puis est acheminé vers l'extérieur en direction du détendeur 12.The main outlet pipe 32 for the high-pressure fluid has a general shape similar to that of the main pipe 6 and also has an elongate opening 320 of conjugate shape of the profile of the tube 5 so as to receive the inner end of the tube. The main pipes 6 and 32 both have a closed bottom, while their fluid connections are provided at the top of the pipes. The high-pressure fluid thus passes from the main channels 52 to the main inlet manifold, through the opening 320, then is conveyed outwards towards the expander 12.

La tubulure secondaire d'entrée 30 représentée partiellement sur les figures 8 et 9 reçoit le fluide à basse pression de bas en haut (flèche F4). Elle ne comporte donc pas de fond fermé. Des ouvertures 34 allongées suivant l'axe XX sont prévues sur la partie de la paroi de la tubulure 30 qui est tournée vers l'extérieur de l'échangeur interne de manière à envoyer le fluide dans les canaux secondaires 54. Ainsi le fluide à basse pression arrive par le bas de la tubulure 30 avant de remonter le long de celle-ci. Le fluide passe ensuite par les ouvertures 34, comme montré par les flèches indiquées dans la tubulure 30, pour se répandre dans les canaux secondaires 54, au début de l'échange thermique.The secondary inlet tubing 30 partially shown on the Figures 8 and 9 receives fluid at low pressure from bottom to top (arrow F4). It does not have a closed bottom. Apertures 34 elongate along the axis XX are provided on the part of the wall of the pipe 30 which is turned towards the outside of the internal exchanger so as to send the fluid into the secondary channels 54. Thus the fluid at low pressure arrives from the bottom of the tubing 30 before going up along it. The fluid then passes through the openings 34, as shown by the arrows indicated in the tubing 30, to spread in the secondary channels 54, at the beginning of the heat exchange.

La tubulure secondaire d'entrée 30 peut comporter une pluralité de canaux 300 allongés suivant l'axe (XX), pour favoriser une meilleure répartition dans les canaux secondaires 54. Sur les figures des dessins, ces canaux sont au nombre de trois à titre d'exemple non limitatif. Les canaux d'entrées 300 génèrent une bonne distribution du fluide réfrigérant sur le plan vertical.The secondary inlet tubing 30 may comprise a plurality of channels 300 elongate along the axis (XX), to promote a better distribution in the secondary channels 54. In the figures of the drawings, these channels are three in number. non-limiting example. The inlet channels 300 generate a good distribution of the refrigerant on the vertical plane.

Les ouvertures 34 sont agencées sur la tubulure secondaire d'entrée 30 de manière à optimiser la répartition du fluide à basse pression reçu dans tous les canaux secondaires 54. Ainsi, comme le montre les figures 14, 17 et 20, les ouvertures 34 sont allongées et agencées de manière à occuper sensiblement toute la longueur du tube. En particulier, sur l'ensemble des figures, trois ouvertures 34 sont prévues pour la communication fluidique avec chacun des trois canaux 300 de la tubulure secondaire d'entrée 30. Les trois ouvertures sont en outre légèrement décalées de manière à venir en communication avec chacun des canaux 300 de la tubulure secondaire d'entrée 30.The openings 34 are arranged on the secondary inlet pipe 30 so as to optimize the distribution of the low-pressure fluid received in all the secondary channels 54. Thus, as shown in FIGS. figures 14 , 17 and 20 the openings 34 are elongate and arranged to occupy substantially the entire length of the tube. In particular, in all of the figures, three openings 34 are provided for the fluid communication with each of the three channels 300 of the secondary inlet pipe 30. The three openings are furthermore slightly offset so as to come into communication with each one. 300 channels of the secondary inlet tubing 30.

La tubulure secondaire de sortie 7 s'étend selon un axe parallèle à l'axe (XX) et présente un fond fermé. Son raccord fluidique est prévu sur sa partie haute. Par ailleurs une ou plusieurs ouvertures 37 allongées selon l'axe (XX) sont prévues sur la partie de sa paroi tournée vers le centre de l'échangeur interne pour recevoir le fluide qui sort des canaux secondaires. 54. Un exemple de réalisation des ouvertures 37 est représenté sur la figure 21.The secondary outlet tubing 7 extends along an axis parallel to the axis (XX) and has a closed bottom. Its fluidic connection is provided on its upper part. Moreover one or more openings 37 elongated along the axis (XX) are provided on the part of its wall facing the center of the internal exchanger to receive the fluid exiting the secondary channels. 54. An embodiment of the openings 37 is shown in FIG. figure 21 .

Le fluide à basse pression passe ainsi des canaux secondaires 54 à l'intérieur de la tubulure secondaire de sortie 7, à la fin de l'échange thermique, puis remonte le long de la tubulure avant d'être envoyé vers le compresseur 14.The low-pressure fluid thus passes secondary channels 54 inside the secondary outlet pipe 7, at the end of the heat exchange, then goes back up the along the tubing before being sent to the compressor 14.

Comme représenté sur les figures 8 et 9, la tubulure principale d'entrée 6 et la tubulure secondaire de sortie 7 peuvent être solidaires d'une plaque de liaison 76 (voir aussi la figure 21). La plaque 76 a une section courbée et une forme adaptée pour venir se loger entre l'avant-dernier enroulement externe du tube et le dernier enroulement du tube. La tubulure secondaire 7 est agencée le long de la paroi de la plaque de liaison sous le dernier enroulement du tube tandis que la tubulure principale d'entrée 6 est agencée au niveau d'un bord de la plaque de liaison, à l'extérieure des enroulements. Comme on peut le voir sur la figure 8, la section de la tubulure secondaire 7 présente une section de faible largeur radiale pour favoriser son insertion sous le dernier enroulement du tube.As shown on Figures 8 and 9 , the main inlet pipe 6 and the secondary outlet pipe 7 may be secured to a connecting plate 76 (see also FIG. figure 21 ). The plate 76 has a curved section and a shape adapted to be housed between the penultimate outer winding of the tube and the last winding of the tube. The secondary tubing 7 is arranged along the wall of the connecting plate under the last winding of the tube while the main inlet tubing 6 is arranged at an edge of the connecting plate, outside the windings. As can be seen on the figure 8 , the section of the secondary tubing 7 has a small radial width section to promote its insertion under the last winding of the tube.

L'échangeur de chaleur comporte également un noyau interne de forme sensiblement cylindrique autour duquel est enroulé le tube 5. Ce noyau 3 permet de rigidifier l'échangeur interne.The heat exchanger also comprises an inner core of substantially cylindrical shape around which the tube 5 is wound. This core 3 makes it possible to stiffen the internal exchanger.

Dans une première forme de réalisation représentée sur les figures 12 à 15, le noyau peut se présenter en trois parties imbriquées 360, 38 et 32, la dernière partie étant constituée par la tubulure principale de sortie tandis que la tubulure secondaire d'entrée 30 fait partie intégrante de la partie 360. L'assemblage des parties 360 et 38 délimite un renfoncement adapté pour loger la tubulure principale de sortie 32 pour la sortie du fluide à haute pression 32.In a first embodiment shown on the Figures 12 to 15 the core may be in three nested parts 360, 38 and 32, the last part being the main outlet pipe while the secondary inlet pipe 30 is an integral part of the 360 part. The assembly of the parts 360 and 38 delimits a recess adapted to house the main outlet pipe 32 for the outlet of the high-pressure fluid 32.

Dans une variante représentée sur les figures 16 et 17, le noyau 3 est monobloc et de forme générale cylindrique. Dans cette variante, la tubulure principale de sortie 32 et la tubulure secondaire d'entrée 30 font partie intégrante du noyau 3. Une tubulure 40 fait également partie intégrante du noyau 3 pour délimiter un passage servant à la réalisation de la spirale.In a variant shown on the Figures 16 and 17 , the core 3 is monobloc and of cylindrical general shape. In this variant, the main outlet pipe 32 and the secondary inlet pipe 30 form an integral part of the core 3. A tubing 40 is also an integral part of the core 3 to define a passage for the realization of the spiral.

Dans une autre variante représentée sur les figures 18 à 20, le noyau peut être constitué de deux parties coaxiales 31 et 33. La partie 33 constitue une structure rigide interne présentant des renfoncements en forme de gorges sur son pourtour tandis que la partie 31 est constituée d'une feuille métallique venant entourer la structure rigide 31 pour définir la tubulure principale de sortie 32 et la tubulure secondaire d'entrée 30.In another variant shown on the Figures 18 to 20 the core may consist of two coaxial portions 31 and 33. The portion 33 constitutes an internal rigid structure having recesses in the form of grooves on its periphery while the portion 31 consists of a metal sheet surrounding the rigid structure 31 to define the main outlet tubing 32 and the secondary inlet tubing 30.

Le tube 5 selon l'invention est réalisé en tant que pièce monobloc profilé et peut être obtenu par extrusion.The tube 5 according to the invention is produced as a profiled monobloc piece and can be obtained by extrusion.

De préférence, le tube 5 est réalisé en alliage d'aluminium, mais d'autres matériaux sont envisageables.Preferably, the tube 5 is made of aluminum alloy, but other materials are possible.

L'invention a été décrite en référence à une section circulaire pour les canaux principaux 52. Toutefois, l'invention n'est pas limitée à cette forme de réalisation.The invention has been described with reference to a circular section for the main channels 52. However, the invention is not limited to this embodiment.

L'invention permet d'obtenir un encombrement diamétral réduit pour l'échangeur interne, grâce à l'alternance de canaux principaux chauds 52 et de canaux secondaires froids 54.The invention makes it possible to obtain a reduced diametral bulk for the internal exchanger, thanks to the alternation of hot main channels 52 and cold secondary channels 54.

Par ailleurs, la séparation étanche entre, d'une part, les canaux secondaires 54, et d'autre part, entre les canaux secondaires 54 et les canaux principaux voisins 52, permet de limiter les risques d'accumulation de liquide au fond de l'échangeur et les risques d'interférence thermique.Moreover, the sealed separation between, on the one hand, the secondary channels 54, and on the other hand, between the secondary channels 54 and the neighboring main channels 52, makes it possible to limit the risks of accumulation of liquid at the bottom of the exchanger and the risks of thermal interference.

La structure de l'échangeur interne selon l'invention garantit de plus une bonne isolation thermique entre les canaux principaux 52 et les canaux secondaires 54, sans qu'il soit nécessaire d'interposer des feuilles d'isolation. L'invention permet donc de réduire le nombre de composants dans l'échangeur, ce qui simplifie le procédé de fabrication de l'échangeur et permet de réduire ses coûts.The structure of the internal exchanger according to the invention further ensures good thermal insulation between the main channels 52 and the secondary channels 54, without it is necessary to interpose insulation sheets. The invention therefore reduces the number of components in the exchanger, which simplifies the manufacturing process of the exchanger and reduces its costs.

Le profil du ou des tubes est défini de telle façon que les canaux formés par enroulement de celui-ci ne comportent pas de formes convexes afin d'éviter tout remplissage de la forme précédemment citée par de l'huile et donc d'augmenter la surface d'échange.The profile of the tube or tubes is defined in such a way that the channels formed by winding thereof do not comprise convex shapes in order to avoid any filling of the form previously mentioned with oil and therefore to increase the surface area. exchange.

L'invention concerne aussi l'utilisation d'un échangeur de chaleur, tel que défini ci-dessus, en tant qu'échangeur interne, dans laquelle le premier fluide est un fluide à haute pression et le deuxième fluide est un fluide à basse pression.The invention also relates to the use of a heat exchanger, as defined above, as an internal exchanger, in which the first fluid is a high-pressure fluid and the second fluid is a low-pressure fluid. .

L'invention propose en outre un ensemble intégré comprenant un accumulateur et l'échangeur interne 9 décrit ci-dessus.The invention further provides an integrated assembly comprising an accumulator and the internal exchanger 9 described above.

La figure 1 montre schématiquement un circuit de climatisation incorporant un tel ensemble intégré 100.The figure 1 schematically shows an air conditioning circuit incorporating such an integrated assembly 100.

L'ensemble intégré comporte un boîtier externe 115 dans lequel est agencé l'échangeur interne 9 et un accumulateur 17. Le boîtier 115 est délimité par un fond et est fermé par un couvercle, non représenté, afin de former une chambre interne étanche. Le couvercle et le boîtier peuvent être fixés entre eux par brasage. Le couvercle et le boîtier peuvent être formés de tout matériau adapté.The integrated assembly comprises an outer casing 115 in which the internal exchanger 9 and an accumulator 17 are arranged. The casing 115 is delimited by a bottom and is closed by a cover, not shown, in order to form a sealed internal chamber. The lid and the housing can be fixed together by soldering. The lid and the housing may be formed of any suitable material.

L'ensemble intégré comporte également une tubulure auxiliaire 4 prévue pour recevoir le fluide à basse pression en provenance de l'évaporateur et l'acheminer vers le fond du boîtier, comme représenté sur les figures 8 et 9. La tubulure auxiliaire 4 a une forme générale cylindrique et est agencée à l'extérieur des enroulements du tube comme le montre la figure 9. Le fluide qui arrive dans la tubulure 4 est reçu dans le fond du boîtier 115, de sorte que la partie liquide du fluide réfrigérant à basse pression reste au fond du boîtier, tandis que seule la partie vaporisée du fluide passe dans la tubulure secondaire d'entrée 30 dont le fond est ouvert. Le fluide à basse pression est alors envoyé dans les canaux secondaires 54 grâce aux ouvertures 34. Parallèlement, la tubulure principale externe 6 reçoit le fluide à haute pression qui est envoyé dans les canaux principaux 52 pour circuler en sens inverse de celui du fluide à basse pression dans les canaux secondaires 54. Les fluides échangent ainsi de la chaleur avant de ressortir par leurs tubulures de sortie respectives 32 et 7.The integrated assembly also comprises an auxiliary pipe 4 designed to receive the low-pressure fluid from the evaporator and convey it towards the bottom of the housing, as shown in FIGS. Figures 8 and 9 . The auxiliary tubing 4 has a general shape cylindrical and is arranged outside the windings of the tube as shown in FIG. figure 9 . The fluid that arrives in the tubing 4 is received in the bottom of the casing 115, so that the liquid portion of the low-pressure refrigerant remains at the bottom of the casing, while only the vaporized portion of the fluid passes into the secondary tubing of the casing. entry 30 whose bottom is open. The low pressure fluid is then sent into the secondary channels 54 through the openings 34. In parallel, the main external tubing 6 receives the high pressure fluid that is sent into the main channels 52 to flow in the opposite direction to that of the low pressure fluid. pressure in the secondary channels 54. The fluids exchange heat before exiting through their respective outlet pipes 32 and 7.

Le nombre de canaux principaux 52 peut varier en fonction de l'échange de chaleur à réaliser.The number of main channels 52 may vary depending on the heat exchange to be performed.

Les différents composants de l'ensemble intégré 100 sont avantageusement réalisés en un alliage d'aluminium et sont brasés ensuite au moyen d'un plaquage de brasure. L'ensemble peut être brasé en une seule fois par passage dans un four de brasage. L'ensemble étant ainsi réalisé, il suffit ensuite de le relier aux branches du circuit comme indiqué ci-dessus.The various components of the integrated assembly 100 are advantageously made of an aluminum alloy and are then brazed by means of solder plating. The assembly can be brazed at one time by passing through a brazing furnace. The assembly being thus realized, it is then sufficient to connect it to the branches of the circuit as indicated above.

Un tel ensemble intégré permet de réduire l'encombrement général du circuit de climatisation tout en offrant des performances frigorifiques satisfaisantes.Such an integrated assembly reduces the overall size of the air conditioning circuit while providing satisfactory cooling performance.

Bien que l'invention s'applique à tout type d'échangeurs de chaleur, elle est particulièrement avantageuse pour un échangeur de chaleur interne d'un circuit de climatisation fonctionnant avec un fluide supercritique.Although the invention applies to any type of heat exchanger, it is particularly advantageous for an internal heat exchanger of an air conditioning circuit operating with a supercritical fluid.

L'invention n'est pas limitée aux modes de réalisation décrits ci-dessus. Elle englobe toutes les variantes de réalisation qui pourront être envisagées par l'homme du métier, notamment en ce qui concerne les tubulures de connexion fluidique 6, 7, 30 et 32, et le noyau 3.The invention is not limited to the embodiments described above. It encompasses all the embodiments that may be envisaged by those skilled in the art, in particular as regards the fluidic connection pipes 6, 7, 30 and 32, and the core 3.

L'invention s'applique en particulier aux circuits de climatisation des véhicules automobiles.The invention applies in particular to air conditioning circuits of motor vehicles.

Claims (18)

  1. Heat exchanger (1) for air conditioning circuits, comprising at least one tube (5) delimiting a path for the circulation of a first fluid and of a second fluid, the tube being wound about an axis so as to define successive windings, the successive windings of the tube are closely packed together so as to delimit fluidtight ducts known as secondary ducts (54) for the circulation of the second fluid, the said secondary ducts (54) being situated between projecting regions of the said tube (5), and in that the said tube (5) has ducts known as main ducts (52) at the projecting regions, these being intended to have the first fluid passing through them, characterized in that the tube (5) comprises a profile section, and in that the profile section of the tube (5) comprises on one of its faces ribs formed by the main ducts (52) and grooves (51) between the main ducts, while the other face is substantially planar, and in that each secondary duct (54) for the second fluid is delimited by a groove (51) between two adjacent ribs of a given winding and the planar face of the next winding.
  2. Heat exchanger according to Claim 1, characterized in that the ends of the main ducts are housed between a main inlet manifold (6) able to receive the first fluid, and a main outlet manifold (32) able to deliver the first fluid out of the exchanger, and in that the ends of the secondary ducts (54) are in fluidic communication with a secondary inlet manifold (30) able to receive the second fluid and a secondary outlet manifold (7) able to deliver the second fluid out of the exchanger.
  3. Heat exchanger according to Claim 2, characterized in that each main manifold is of substantially cylindrical shape about an axis parallel to the axis of the exchanger and has an opening (60, 320) designed to accept one of the ends of the tube (5).
  4. Heat exchanger according to one of Claims 2 and 3, characterized in that each secondary manifold has elongate openings (34, 37) over part of its wall for fluidic communication with the secondary ducts (54).
  5. Heat exchanger according to one of Claims 2 to 4, characterized in that it comprises a connecting plate (76) of curved cross section with a shape suited to being housed between the penultimate external winding of the tube and the last external winding of the tube, and in that the main inlet manifold (6) and the secondary outlet manifold (7) are attached to the connecting plate (76).
  6. Heat exchanger according to one of Claims 2 to 5, characterized in that it comprises an internal core (3) of substantially cylindrical shape.
  7. Heat exchanger according to Claim 6, characterized in that the core (3) is of one piece.
  8. Heat exchanger according to Claim 6, characterized in that the core (3) consists of several imbrocated parts (360, 38, 32) which provides supply and distribution for the primary circuit and the secondary circuit as well as the winding of the tube or tubes (5).
  9. Heat exchanger according to Claim 6, characterized in that the core (3) is made up of two coaxial parts (33, 31), the first part comprising a rigid structure provided with channels on its periphery and the second part comprising a metal sheet wound around the first part in such a way as to define the main outlet manifold (32) and the secondary inlet manifold (30).
  10. Heat exchanger according to one of Claims 2 to 9, characterized in that the secondary inlet and outlet manifolds comprise one or more elongate openings which are elongated along the axis of the exchanger so as to be in fluidic communication with the secondary ducts.
  11. Heat exchanger according to Claim 10, characterized in that the openings (34) are offset radially and along the axis of the exchanger in relation to one another.
  12. Heat exchanger according to Claim 11, characterized in that the secondary inlet manifold (30) comprises one or more openings (34), and in that it is divided into one or more inlet ducts (300) so that each inlet duct communicates with at least one of the openings.
  13. Heat exchanger according to one of the preceding claims, characterized in that the tube (5) is formed as a profiled component made of one or more pieces.
  14. Heat exchanger according to one of the preceding claims, characterized in that the tube (5) is obtained by extrusion.
  15. Heat exchanger according to one of the preceding claims, characterized in that the main ducts (52) of the tube are of substantially circular cross section.
  16. Use of a heat exchanger according to one of the preceding claims as an internal exchanger, in which the first fluid is a high-pressure fluid and the second fluid is a low-pressure fluid.
  17. Integrated assembly for an air conditioning circuit operating using a refrigerant, characterized in that it comprises an internal exchanger (9) according to one of Claims 2 to 15 and a housing (115) in which the internal exchanger is housed, the housing (115) delimiting an end wall, and in that the housing comprises an auxiliary manifold (4) positioned on the outside of the windings of the tube (5), the auxiliary manifold being able to accept the second fluid and convey it towards the end wall of the housing so that only the vaporized portion of the second fluid is sent into the secondary inlet manifold (30).
  18. Air conditioning circuit operating using a refrigerant, comprising a compressor (14), a condenser (11), an expansion valve (12) and an evaporator (13), characterized in that it comprises an integrated assembly according to Claim 17, the main inlet manifold (6) being connected to the compressor (14), and the auxiliary manifold (7) being connected to the evaporator, whereas the main outlet manifold (32) is connected to the expansion valve (12) and the secondary outlet manifold (30) is connected to the bottom part of an accumulator (17) and receives the vaporized portion of the fluid.
EP08717605A 2007-03-12 2008-03-11 Heat exchanger and built-in assembly including such exchanger Active EP2118608B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0701758A FR2913764B1 (en) 2007-03-12 2007-03-12 HEAT EXCHANGER AND INTEGRATED ASSEMBLY INCORPORATING SUCH EXCHANGER
PCT/EP2008/052858 WO2008113714A1 (en) 2007-03-12 2008-03-11 Heat exchanger and built-in assembly including such exchanger

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EP2118608A1 EP2118608A1 (en) 2009-11-18
EP2118608B1 true EP2118608B1 (en) 2011-04-06

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EP (1) EP2118608B1 (en)
AT (1) ATE504793T1 (en)
DE (1) DE602008006034D1 (en)
ES (1) ES2363053T3 (en)
FR (1) FR2913764B1 (en)
WO (1) WO2008113714A1 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2522633C1 (en) * 2013-01-09 2014-07-20 Общество с ограниченной ответственностью Научно-производственное предприятие "Донские технологии" Wet-vapour condenser of microturbine
DE102017217313A1 (en) * 2017-09-28 2019-03-28 Franz Josef Ziegler Heat exchanger
CN110857823A (en) * 2018-08-23 2020-03-03 杭州三花研究院有限公司 Gas-liquid separator, air conditioning system, and method for manufacturing gas-liquid separator
US11892212B2 (en) 2018-08-23 2024-02-06 Zhejiang Sanhua Intelligent Controls Co., Ltd. Gas-liquid separator and air conditioning system

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FR2928997B1 (en) 2008-03-20 2014-06-20 Valeo Systemes Thermiques HEAT EXCHANGER AND INTEGRATED AIR CONDITIONING ASSEMBLY COMPRISING SUCH AN EXCHANGER.
FR2939187B1 (en) * 2008-12-01 2013-02-22 Valeo Systemes Thermiques SPIRE HEAT EXCHANGER AND AIR CONDITIONING DEVICE COMPRISING SUCH A HEAT EXCHANGER
DE102008060699A1 (en) * 2008-12-08 2010-06-10 Behr Gmbh & Co. Kg Evaporator for a refrigeration circuit
FR2940419B1 (en) * 2008-12-22 2010-12-31 Valeo Systemes Thermiques COMBINED DEVICE COMPRISING AN INTERNAL HEAT EXCHANGER AND AN ACCUMULATOR, AND PROVIDED WITH A MULTIFUNCTIONAL INTERNAL COMPONENT
FR2940420B1 (en) * 2008-12-22 2010-12-31 Valeo Systemes Thermiques COMBINED DEVICE COMPRISING AN INTERNAL HEAT EXCHANGER AND AN ACCUMULATOR COMPRISING A CLIMATEING MOUTH
JP2015034663A (en) * 2013-08-08 2015-02-19 サンデン株式会社 Heat exchanger and heat cycle apparatus including heat exchanger
JP2015034662A (en) * 2013-08-08 2015-02-19 サンデン株式会社 Heat exchanger
JP2015034661A (en) * 2013-08-08 2015-02-19 サンデン株式会社 Heat exchanger and heat exchanger manufacturing method
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RU2522633C1 (en) * 2013-01-09 2014-07-20 Общество с ограниченной ответственностью Научно-производственное предприятие "Донские технологии" Wet-vapour condenser of microturbine
DE102017217313A1 (en) * 2017-09-28 2019-03-28 Franz Josef Ziegler Heat exchanger
CN110857823A (en) * 2018-08-23 2020-03-03 杭州三花研究院有限公司 Gas-liquid separator, air conditioning system, and method for manufacturing gas-liquid separator
CN110857823B (en) * 2018-08-23 2020-11-06 杭州三花研究院有限公司 Gas-liquid separator, air conditioning system, and method for manufacturing gas-liquid separator
US11892212B2 (en) 2018-08-23 2024-02-06 Zhejiang Sanhua Intelligent Controls Co., Ltd. Gas-liquid separator and air conditioning system

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FR2913764A1 (en) 2008-09-19
ES2363053T3 (en) 2011-07-19
WO2008113714A1 (en) 2008-09-25
DE602008006034D1 (en) 2011-05-19
FR2913764B1 (en) 2009-12-11
EP2118608A1 (en) 2009-11-18
ATE504793T1 (en) 2011-04-15

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