EP2937658B1 - Fluide caloporteur interne - Google Patents

Fluide caloporteur interne Download PDF

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Publication number
EP2937658B1
EP2937658B1 EP15164732.8A EP15164732A EP2937658B1 EP 2937658 B1 EP2937658 B1 EP 2937658B1 EP 15164732 A EP15164732 A EP 15164732A EP 2937658 B1 EP2937658 B1 EP 2937658B1
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EP
European Patent Office
Prior art keywords
refrigerant
accumulator
tube
heat exchanger
corrugated fins
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP15164732.8A
Other languages
German (de)
English (en)
Other versions
EP2937658A1 (fr
Inventor
David Mayor Tonda
Dr. Günther Feuerecker
Wolfgang Geiger
Karl-Gerd Krumbach
Klaus FÖRSTER
Martin Kaspar
Thomas Bruder
Uwe FÖRSTER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
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Filing date
Publication date
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Publication of EP2937658A1 publication Critical patent/EP2937658A1/fr
Application granted granted Critical
Publication of EP2937658B1 publication Critical patent/EP2937658B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the invention relates to an internal heat exchanger according to the preamble of the first claim.
  • a heat exchanger is known DE 10 2006 017 432 ,
  • the refrigerant R-134a is in future no longer permitted for use in air conditioning systems.
  • R-744 CO 2
  • the refrigerant R-744 is much more environmentally friendly compared to R-134a and still allows for a higher cooling capacity with a comparable volume of the air conditioning system.
  • COP Coefficient of Performance
  • the inner heat exchanger can be integrated as a separate component or designed as a combination element with the so-called accumulator, which acts as a storage device and / or drying device for the refrigerant.
  • the refrigerant on the high pressure side is guided through a line which is arranged on the accumulator and flows around the refrigerant of the low pressure side.
  • the publication DE 198 30 757 A1 discloses an air conditioner, wherein an internal heat exchanger is provided, which is combined with a condenser and a collector.
  • the inner heat exchanger is arranged in the region of the capacitor, whereby a space-saving solution is generated.
  • the air conditioning system thus produced is particularly suitable for use with the refrigerant R-744 (CO 2 ).
  • the accumulator in this case has an outer wall formed from two hollow-cylindrical shaped elements, which has a plurality of flow channels formed between the hollow cylindrical elements. Through these flow channels, the refrigerant can flow. Thus, a heat transfer can take place between the refrigerant flowing through the flow channels, which are formed in the outer wall, and the refrigerant flowing through the accumulator in the interior.
  • the inner heat exchanger is formed by two hollow cylinders arranged one inside the other. In the space between the inner cylinder and the outer cylinder can flow a vapor refrigerant with low pressure.
  • the inner cylinder is designed as a flat tube with a plurality of microchannels, which can be flowed through by a high-pressure refrigerant. In the cavity formed by the inner cylinder, the refrigerant can be further collected with a low pressure. Between the refrigerant with low pressure and the refrigerant with high pressure can be generated by this arrangement, a heat transfer.
  • an internal heat exchanger which has an integrated accumulator.
  • the cylindrical accumulator which can be flowed through by a refrigerant, is surrounded by a tube formed into a helix. Through the pipe can also flow a refrigerant.
  • the tube is arranged between the outer wall of the accumulator and the inner wall of a likewise hollow cylindrical housing. Preferably, a heat transfer between the refrigerant flowing in the pipe and the refrigerant flowing around the pipe can be achieved.
  • the tube is located at the inner heat exchanger or publication US 2008/0000261 A1 both flat on the outer wall of the accumulator and on the inner wall of the housing.
  • a heat exchanger with accumulator known, the accumulator is wrapped by a helical tube.
  • the tube and the accumulator are arranged in a hollow cylindrical housing.
  • the helical tube is flat both on the outer wall of the accumulator and on the inner wall of the housing.
  • the tube, the accumulator and the gap between the accumulator and the housing can be flowed through by a refrigerant.
  • a disadvantage of the solutions of the prior art is in particular that the higher cooling capacity is accompanied by the inner heat exchanger with a higher pressure drop within the refrigerant circuit, which in turn leads to a negative impact on the cooling capacity.
  • the pressure drop occurs, in particular on the low-pressure side in the region in which the line of the high pressure side is flowed around by the refrigerant of the low pressure side.
  • the heat transfer between the high-pressure side refrigerant and the low-pressure side refrigerant is not optimal.
  • a heat exchanger with a calibrated helical finned tube is known.
  • the finned tube is formed into a helix, which comprises an accumulator.
  • the finned tube is formed by a tube which has radially projecting elements. The elements protrude completely circumferentially in the radial direction of the tube from the surface of the tube.
  • the tube is spaced both in the radial direction of the helix to surrounding structures and the individual turns of the tube in the axial direction of the helix to each other.
  • the spiral-shaped tube and the accumulator can be flowed through by a refrigerant. In particular, a heat transfer between the refrigerant flowing inside the helix and the refrigerant flowing around the helix is generated.
  • a disadvantage of this solution from the prior art is in particular that a relative movement of the individual turns of the helix to each other in the axial direction of the helix through the elements is not possible. Also, the elements which protrude into the space between the turns impede fluid flow in this area, thereby creating a higher pressure loss. Furthermore, the handling of finned tubes is particularly complex, since they are difficult to process due to the protruding rib elements. The projecting elements can, for example, interlock with each other, which makes assembly difficult.
  • the object of the present invention to provide an internal heat exchanger, which allows a heat transfer between the refrigerant of the low pressure side and the refrigerant of the high pressure side, wherein the resulting pressure loss should be minimized.
  • the invention relates to an air conditioner with a refrigerant circuit with an internal heat exchanger according to the invention
  • An embodiment of the invention relates to an internal heat exchanger with a cylindrical accumulator, with a cylindrical housing, with a spiral-shaped tube, with first corrugated fins and second corrugated fins, wherein the accumulator compared to the inner diameter of the housing has a smaller outer diameter and within the Housing is arranged, wherein the helix-shaped tube is disposed in the gap between the accumulator and the housing, wherein the first corrugated fins are arranged in the radial direction between the tube and an outer wall of the accumulator and / or the second corrugated fins in the radial direction between the tube and an inner surface of the housing are arranged.
  • the refrigerant flowing through the formed gap can therefore flow through the structure created by the corrugated fins. This causes a much lower pressure loss than the conventional arrangements in which the tube rests directly on the respective inner surfaces and outer surfaces.
  • the refrigerant may only run down the individual turns of the coil on the pipe itself, and more particularly in the optional clearances formed between the adjacent turns.
  • corrugated fins do not fill the free spaces formed between the turns of the helix. Such an arrangement of the corrugated fins is particularly advantageous in order to further reduce the resulting pressure loss.
  • first corrugated ribs and / or in each case a plurality of second corrugated ribs are arranged lined up in the axial direction.
  • the inner jacket and the outer jacket of the corrugated ribs on the helix can be made in one piece in the axial direction or can be formed from a plurality of hollow cylindrical corrugated rib elements, which are successively pushed onto the helix or pushed into the helix. This is particularly advantageous in terms of mounting. Furthermore, in a simple way, a section-wise adaptation of the corrugated ribs can be carried out by using different corrugated rib elements.
  • a preferred embodiment is characterized in that the individual turns of the helix are movable in the axial direction relative to each other, wherein in a relative movement in the axial direction, the helix on inner surfaces of the corrugated fins, which face the tube, or the outer surfaces of the corrugated fins, which the Accumulator or the housing, slide on the outer surface of the accumulator or the inner surface of the housing.
  • the corrugated ribs form a first and a third layer in the radial direction, wherein the tube formed into a helix forms a second layer lying between the two layers.
  • the package of corrugated fins and helix forms a multi-layered in cross-section package.
  • the corrugated ribs thereby form the two outer layers, while the helix is enclosed as a middle layer between the layers of the corrugated ribs.
  • the layers are preferably arranged concentrically to one another. Furthermore, the layers preferably do not protrude into one another in the radial direction but are clearly separated from one another. This is advantageous to produce the corrugated rib-free space between the mutually adjacent turns of the coil. In this way, the pressure loss occurring during the flow is minimized.
  • the accumulator and the gap between the accumulator and the housing with a refrigerant can be flowed through, wherein the pressure level of the refrigerant in the accumulator and in the gap compared to the pressure level of the refrigerant in the helical shaped tube is smaller.
  • the refrigerant in the accumulator and the refrigerant in the gap to each other in countercurrent and / or in the DC are flowable.
  • a flow in countercurrent overall a higher heat transfer can be achieved.
  • a flow in the DC can also be provided.
  • the tube has a plurality of fluidically separated flow channels in the interior. Through a tube with several internal flow channels, the heat transfer due to the larger interfaces between the refrigerant in the interior of the tube and the refrigerant flowing around the pipe can be further increased.
  • first corrugated ribs and / or the second corrugated ribs are designed as ribs which are V-shaped in cross-section and / or ribs which are trapezoidal in cross section and / or ribs provided with bevels.
  • first corrugated ribs and / or second corrugated ribs arranged adjacent to each other in the axial direction have an offset in the circumferential direction relative to each other.
  • first corrugated fins and / or the second corrugated fins are permanently connected to the tube formed into a helix. This can be achieved, for example, by the common joining methods of brazing, welding or gluing. A permanent connection is particularly advantageous in terms of mountability.
  • a further preferred embodiment is characterized in that at the upper end portion of the accumulator, a refrigerant inlet and a refrigerant transfer is arranged, the accumulator can be flowed through in a U-shape, wherein the refrigerant inlet leads from outside the inner heat exchanger through the housing and the gap in the accumulator and a deflection of the refrigerant at the lower end portion of the accumulator is executable, wherein the helical-shaped tube having a first refrigerant port and a second refrigerant port, which pierce the housing to the outside, wherein the housing further comprises a first refrigerant outlet, which from the gap to the outside leads.
  • Such an arrangement is advantageous in order to ensure a guidance of the refrigerant along the low-pressure side through the inner heat exchanger and at the same time a guidance of the refrigerant on the high-pressure side and furthermore a most effective heat exchange between the refrigerants of the two sides.
  • An embodiment of the invention relates to an air conditioning system with a refrigerant circuit and an internal heat exchanger, wherein the accumulator is flowable with a refrigerant, which has a lower pressure level compared to the refrigerant in the tube formed into a helix.
  • An air conditioner with an internal heat exchanger according to the invention is particularly advantageous, since the efficiency of the entire air conditioner can be further increased by, in particular, the cooling capacity can be increased.
  • the Fig. 1 shows a cross section through a bent into a helix tube 3.
  • the tube 3 has a refrigerant port 4, through which a refrigerant can flow into the tube 3 or can flow out of this.
  • first corrugated fins 2 are arranged.
  • second corrugated fins 1 are arranged.
  • the corrugated fins 1, 2 are in each case arranged adjacent to the tube 3 in the radial direction and, in particular, do not engage between the individual turns of the tube 3.
  • the corrugated fins 1, 2 are arranged completely circumferentially on the outer circumference or on the inner circumference of the tube 3.
  • the first corrugated fins 2 thus form an axially extending jacket, which is surrounded by the tube 3, which is shaped as a helix.
  • the second corrugated fins 1 are formed as a jacket, which surrounds the tube 3 on the outer circumference.
  • the Fig. 2 shows a perspective view of a helix-shaped tube 3 with a refrigerant port 4, as already in Fig. 1 was shown. At least a portion of the tube 3 is surrounded with first corrugated fins 2 on the inner circumference and surrounded with second corrugated fins 1 on the outer circumference.
  • the corrugated fins 1, 2 may extend over the entire axial extent of the helix or be formed of a plurality of subregions, which are successively inserted in the axial direction of the helix or in the helix.
  • the corrugated fins 1, 2 can be pushed onto the helix without further locking or permanently connected thereto by joining methods, such as joining, soldering, welding or gluing.
  • the tube 3 forms with the corrugated fins 1, 2 a three-layer structure, wherein the middle layer is formed by the tube 3 and both corrugated fins 1, 2 are arranged both on the outer circumference and in the inner circumference.
  • the resulting in the helix free spaces in the axial direction between adjacent turns are not filled in particular by the corrugated fins 1, 2.
  • This is particularly advantageous in terms of mounting, since the corrugated fins can be formed into cylindrical bodies and can be inserted into the coil without great installation effort or can be pushed over the coil. Alternatively, it may also be advantageous if these clearances are not present and touch the windings.
  • tube 3 in particular simple smooth tubes can be used, which are formed in a corresponding shaping process into a helix.
  • special tubes can be used, which will be discussed in the following figures.
  • the Fig. 3 shows a cross section through an inner heat exchanger 21.
  • This is essentially formed by a cylindrical housing 6, which has mutually parallel outer walls, which form the long side of the housing 6 and two opposite narrow sides, which act as a lid and the housing 6 complete.
  • Inside the housing 6 is an accumulator 7 is arranged, which is also formed cylindrically.
  • the accumulator is used primarily for storing and / or drying and / or filtering a refrigerant which can flow through the accumulator 7.
  • the accumulator 7 has a smaller outer diameter than the inner diameter of the housing 6. In this way arises between the housing 6 and the accumulator 7, a gap 9. Within this gap is in the Fig.
  • the accumulator 7 is supported via spacer elements 8 in the right region of the figure with respect to an inner surface of the housing 6. In this way, a completely circumferential gap between the accumulator 7 and the housing 6 is generated.
  • the pipe 3 has a first refrigerant connection 4 and a second refrigerant connection 5.
  • the refrigerant connections 4, 5 serve as a fluid inlet or as a rempliidablauf.
  • the helix, which is formed from the tube 3, is in each case completely flowed through by the refrigerant.
  • an end portion of the housing 6 can be separated to realize a insertion opening.
  • the Fig. 4 shows a further sectional view through the inner heat exchanger 21.
  • the inner heat exchanger 21 has a refrigerant inlet 10 at the left end region, via which a refrigerant can flow through the housing 6 into the accumulator 7 along the flow direction 12.
  • the refrigerant in the right area of the Fig. 4 flow and are deflected along the arrow 13, before it flows back to the left end of the accumulator 7 again.
  • an overflow region is shown, through which the refrigerant from the accumulator 7 can flow into the gap 9 between the housing 6 and the accumulator 7.
  • the refrigerant can flow along the entire circumference in the gap 9 and from left to right, the tube 3 and the corrugated fins 1, 2 flow around.
  • the refrigerant flows at a pressure which is higher than the pressure of the refrigerant, which flows through the accumulator 7 and the gap 9.
  • a refrigerant outlet 11 is further arranged, via which the refrigerant can flow out of the housing 6 after the flow through the gap 9.
  • the pipe 3 is supplied along the flow direction 17 through the refrigerant port 5 with a refrigerant. Via the refrigerant connection 4, the refrigerant can flow out of the tube 3 in the direction of the flow arrow 18.
  • Fig. 4 a flow through the inner heat exchanger is shown, wherein the refrigerant flows in the pipe 3 in a counterflow to the refrigerant in the gap 9. This is particularly advantageous in order to realize a higher heat transfer.
  • the Fig. 5 shows a sectional view through an internal heat exchanger 21 analogous to Fig. 4 ,
  • the reference numerals therefore come, as far as the same elements are designated, match.
  • the refrigerant of the higher pressure which flows through the pipe 3
  • the refrigerant finally flows out along the flow arrow 20 from the refrigerant connector 5 at the right end region.
  • the flow through the accumulator 7 and the gap 9 has not changed thereby.
  • the tube 3 and the gap 9 are flowed through in direct current.
  • the Fig. 6 shows a perspective view of a coil, which is formed from the circularly wound tube 3, which further comprises the refrigerant port 4 at the left end portion and the refrigerant port 5 at the right end portion.
  • the Fig. 7 shows by the reference numeral 30, an alternative cross-sectional shape for the tube 3.
  • the reference numeral 30 in particular an oval or elliptical cross-sectional shape of the tube 3 is shown.
  • a slot-like cross-sectional shape is shown, which is formed essentially of two mutually parallel broad sides, which are completed by rounded semicircular narrow sides to a closed pipe contour.
  • the Fig. 8 shows two cross sections of flat tubes 32, 34.
  • the flat tube 32 has in its interior a plurality of circular cross-sectional flow channels 33, which are arranged in a row adjacent to each other.
  • the flat tube 34 which is arranged underneath, has an alternative embodiment, in which a plurality of flow channels 35, which have a square cross section, are arranged in a row next to one another.
  • the flat tubes 32, 34 may also form the base material for forming the helix, which is arranged in the gap 9 of the inner heat exchanger 21.
  • the number of flow channels 33, 35 in the flat tubes 32, 34 of the in Fig. 8 differ from the example shown.
  • the Fig. 9 shows a sectional view through a corrugated fin 36, wherein the rib elements are each arranged W-shaped, in particular, the kink of the corrugated fins, which are arranged in the upper end region or in the lower end of the corrugated fins 36, provided with a Kire 37.
  • the material of the corrugated rib is pressed against one another.
  • the Fig. 10 shows a turbulence insert 38, which can be used as an alternative to the corrugated fins 1 and 2.
  • the turbulence insert 38 in this case has first flow channels 39, 40 and 41, which are also found in the right adjacent elements of the turbulence insert 38 each.
  • the flow channels 39, 40 and 41 are formed in particular by an offset of the sections 42 and 43 of the turbulence insert to each other.
  • the turbulence insert 38 can be produced in particular by a partial deflection of partial regions from one plane only.
  • various methods for producing a corresponding turbulence insert are known in the prior art.
  • Fig. 1 to 10 Embodiments shown are merely exemplary and serve to illustrate the inventive concept.
  • the choice of materials and the arrangement of the individual elements to each other have the Fig. 1 to 10 no limiting character.
  • the tube formed into a helix is surrounded both on the outer circumference and on the inner periphery by a sheath-like corrugated rib structure, whereby the tube can be spaced to inner surfaces or outer surfaces of the housing or the accumulator.
  • the gap generated by the corrugated fins between the tube 3 and the inner walls or outer walls of the housing 6 and the accumulator 7 is preferably flowed through by the refrigerant, whereby in particular a lower pressure drop is generated than in the known in the prior art solutions which no spacing of Provide pipe to the inner wall of the housing or to the outer wall of the accumulator.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (14)

  1. Echangeur de chaleur intérieur (21) comprenant un accumulateur (7) en forme de cylindre, comprenant un carter (6) en forme de cylindre, comprenant un tube (3) formé en spirale, comprenant des premières ailettes ondulées (2) et comprenant des deuxièmes ailettes ondulées (1), où l'accumulateur (7) présente un diamètre extérieur plus petit, par comparaison avec le diamètre intérieur du carter (6), et est disposé à l'intérieur du carter (6), où le tube (3) formé en spirale est disposé dans l'intervalle (9) compris entre l'accumulateur (7) et le carter (6), caractérisé en ce que les premières ailettes ondulées (2) sont disposées, dans la direction radiale, entre le tube (3) et une paroi extérieure de l'accumulateur (7) et / ou les deuxièmes ailettes ondulées (1) sont disposées, dans la direction radiale, entre le tube (3) et une surface intérieure du carter (6).
  2. Echangeur de chaleur intérieur selon la revendication 1, caractérisé en ce que les espaces libres configurés dans la direction axiale, entre les différentes spires du tube (3), sont formés en étant exempts d'ailettes ondulées.
  3. Echangeur de chaleur intérieur selon la revendication 1, caractérisé en ce que les différentes spires du tube sont au contact les unes des autres, sans former d'espaces libres.
  4. Echangeur de chaleur intérieur (21) selon la revendication 1, 2 ou 3, caractérisé en ce qu'à chaque fois plusieurs premières ailettes ondulées (2) et / ou à chaque fois plusieurs deuxièmes ailettes ondulées (1) sont disposées en rangées juxtaposées les unes à côté des autres, dans la direction axiale.
  5. Echangeur de chaleur intérieur (21) selon l'une quelconque des revendications précédentes, caractérisé en ce que les différents tours de la spirale peuvent être déplacés les uns par rapport aux autres, où, au cours d'un mouvement relatif se produisant dans la direction axiale, les spires se trouvant sur des surfaces intérieures des ailettes ondulées (1, 2), qui sont tournées vers le tube (3), glissent, ou bien les surfaces extérieures des ailettes ondulées (1, 2), qui sont tournées vers l'accumulateur (7) ou vers le carter (6), glissent sur la surface extérieure de l'accumulateur (7) ou sur la surface intérieure du carter (6).
  6. Echangeur de chaleur intérieur (21) selon l'une quelconque des revendications précédentes, caractérisé en ce que les ailettes ondulées (1, 2) forment, dans la direction radiale, une première et une troisième couche, où le tube (3) formé en spirale constitue une deuxième couche se trouvant entre les deux couches.
  7. Echangeur de chaleur intérieur (21) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'accumulateur (7) et l'intervalle (9) compris entre l'accumulateur (7) et le carter (6) peuvent être traversés par un fluide frigorigène, où le niveau de pression du fluide frigorigène contenu dans l'accumulateur (7) et dans l'intervalle (9) est plus bas, par comparaison avec le niveau de pression du fluide frigorigène contenu dans le tube (3) formé en spirale.
  8. Echangeur de chaleur intérieur (21) selon l'une quelconque des revendications précédentes, caractérisé en ce que le fluide frigorigène contenu dans l'accumulateur (7) et le fluide frigorigène contenu dans l'intervalle (9) peuvent s'écouler l'un par rapport à l'autre, en flux inversé et / ou en flux de même sens.
  9. Echangeur de chaleur intérieur (21) selon l'une quelconque des revendications précédentes, caractérisé en ce que le tube (32, 34) présente, à l'intérieur, plusieurs conduits d'écoulement (33, 35) séparés fluidiquement les uns des autres.
  10. Echangeur de chaleur intérieur (21) selon l'une quelconque des revendications précédentes, caractérisé en ce que les premières ailettes ondulées (2) et / ou les deuxièmes ailettes ondulées (1) sont configurées comme des ailettes ayant, en section, une forme en V et / ou comme des ailettes ayant, en section, une forme de trapèze et / ou comme des ailettes dotées d'arêtes saillantes.
  11. Echangeur de chaleur intérieur (21) selon l'une quelconque des revendications précédentes, caractérisé en ce que les premières ailettes ondulées (2) et / ou les deuxièmes ailettes ondulées (1) disposées en étant à chaque fois contiguës entre elles présentent un décalage les unes par rapport aux autres, dans la direction circonférentielle.
  12. Echangeur de chaleur intérieur (21) selon l'une quelconque des revendications précédentes, caractérisé en ce que les premières ailettes ondulées (2) et / ou les deuxièmes ailettes ondulées (1) sont assemblées de façon permanente avec le tube (3) formé en spirale.
  13. Echangeur de chaleur intérieur (21) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une entrée de fluide frigorigène (10) et une sortie de trop-plein du fluide frigorigène sont disposées au niveau de la zone d'extrémité supérieure de l'accumulateur (7), où l'accumulateur (7) peut être traversé en forme de U, où l'entrée de fluide frigorigène (10) conduit dans l'accumulateur (7) à partir de l'extérieur de l'échangeur de chaleur intérieur (21) et en traversant le carter (6) et l'intervalle (9), et un retour de flux (13) du fluide frigorigène peut être réalisé au niveau de la zone d'extrémité inférieure de l'accumulateur (7), où le tube (3) formé en spirale présente un premier raccord (4) pour le fluide frigorigène et un deuxième raccord (5) pour le fluide frigorigène, raccords qui passent à l'extérieur à travers le carter (6), où le carter (6) présente en outre une première sortie de fluide frigorigène (11) qui conduit vers l'extérieur en partant de l'intervalle (9).
  14. Système de climatisation comprenant un circuit de fluide frigorigène et un échangeur de chaleur intérieur (21) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'accumulateur (7) peut être traversé par un fluide frigorigène qui présente un niveau de pression plus bas, par comparaison avec le fluide frigorigène contenu dans le tube (3) formé en spirale.
EP15164732.8A 2014-04-23 2015-04-22 Fluide caloporteur interne Not-in-force EP2937658B1 (fr)

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WO2019161785A1 (fr) * 2018-02-24 2019-08-29 三花控股集团有限公司 Séparateur gaz-liquide et système d'échange de chaleur
CN109556325A (zh) * 2018-12-19 2019-04-02 珠海格力电器股份有限公司 换热器和空调器
CN113928574A (zh) * 2021-11-19 2022-01-14 中国直升机设计研究所 一种直升机冷却系统的热交换器

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FR2875894B1 (fr) * 2004-09-24 2006-12-15 Valeo Climatisation Sa Dispositif combine d'echangeur de chaleur interne et d'accumulateur pour un circuit de climatisation
DE102005021787A1 (de) * 2005-05-11 2006-11-16 Modine Manufacturing Co., Racine Vorrichtung zur Behandlung des Kältemittels
JP4251172B2 (ja) * 2005-10-14 2009-04-08 パナソニック株式会社 ヒートポンプ給湯装置
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