EP3175195B1 - Échangeur de chaleur et procédé de fabrication de l'échangeur de chaleur - Google Patents

Échangeur de chaleur et procédé de fabrication de l'échangeur de chaleur Download PDF

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Publication number
EP3175195B1
EP3175195B1 EP15742244.5A EP15742244A EP3175195B1 EP 3175195 B1 EP3175195 B1 EP 3175195B1 EP 15742244 A EP15742244 A EP 15742244A EP 3175195 B1 EP3175195 B1 EP 3175195B1
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EP
European Patent Office
Prior art keywords
housing
coil
accumulator
heat exchanger
force
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.)
Active
Application number
EP15742244.5A
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German (de)
English (en)
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EP3175195A1 (fr
Inventor
Uwe FÖRSTER
Wolfgang Geiger
Christoph Kästle
Andreas König
Karl-Gerd Krumbach
David Mayor Tonda
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Mahle International GmbH
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Mahle International GmbH
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Publication of EP3175195A1 publication Critical patent/EP3175195A1/fr
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    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/06—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0472—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0472—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled
    • F28D1/0473—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled the conduits having a non-circular cross-section
    • 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
    • F28D7/0016—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 bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/051—Compression system with heat exchange between particular parts of the system between the accumulator and another part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements
    • F28F2275/122—Fastening; Joining by methods involving deformation of the elements by crimping, caulking or clinching

Definitions

  • the invention relates to a heat exchanger for cooling a fluid, with an accumulator, a housing and a tube shaped into a coil, a gap being formed between the accumulator and the housing, in which the tube shaped into a coil is arranged.
  • the invention also relates to a method for producing a heat exchanger.
  • R-744 CO 2
  • the refrigerant R-744 is much more environmentally friendly than R-134a and, with a comparable volume of the air conditioning system, enables a higher cooling capacity.
  • COP Coefficient of Performance
  • a so-called internal heat exchanger is additionally used in air conditioning systems, the refrigerant in this internal heat exchanger being cooled further by heat transfer between the refrigerant on the low pressure side of the refrigerant circuit and the warmer refrigerant on the high pressure side of the refrigerant circuit.
  • the EP 2 136 160 A2 shows a heat exchanger and a method for producing the heat exchanger.
  • the heat exchanger has a collector which is arranged in a housing.
  • a coiled tubing is arranged between the housing and the collector.
  • An internal high-pressure process is used to produce a contact between the tube coil, the collector and the housing, as a result of which the tube coil is expanded and comes into contact with the collector and the housing.
  • an air conditioning system which has an internal heat exchanger.
  • the internal heat exchanger is combined with the condenser.
  • the inner heat exchanger has a coiled tubing which is arranged between a collector and a housing.
  • a disadvantage of the devices in the prior art is, in particular, that the pipe which carries the refrigerant on the high-pressure side either only has the refrigerant on the low-pressure side flowing around them or achieves the generation of a defined countercurrent between the refrigerant on the high-pressure side and the low-pressure side by means of complex manufacturing processes becomes.
  • the occurrence of leaks can lead to a drastic reduction in the efficiency of the heat exchanger.
  • US-A-4061184 discloses a heat exchanger according to the preamble of claim 1.
  • An embodiment of the invention relates to a heat exchanger for cooling a fluid, with an accumulator, a housing and a tube formed into a coil, wherein a gap is formed between the accumulator and the housing, in which the tube shaped into a coil is arranged, wherein a non-positive connection is formed between the housing and the helix, the non-positive connection being produced by a plastic deformation of the housing.
  • a non-positive connection between the housing and the helix is particularly advantageous in order to prevent the helix from flowing uncontrollably along its turns. Gaps between the coil and the housing can cause leakage currents, which negatively affect the efficiency of the heat exchanger. It is particularly advantageous to generate a force fit by plastically deforming the housing. In particular, compression of the housing is advantageous, as a result of which the diameter of the housing is reduced, as a result of which the helix is brought into contact with the housing.
  • non-positive connection is produced between the housing and the coil and the accumulator, the non-positive connection being produced by plastic deformation of the housing and the coil.
  • both the housing and the coil are plastically deformed, as a result of which a positive connection is generated both between the accumulator and the coil and between the housing and the coil.
  • This is particularly advantageous in order to produce a flow channel that is as fluid as possible, along which a fluid flow can flow along the helix.
  • the housing is compressed until it rests on the coil.
  • the force component then continues to act on the housing so that the housing is further compressed until the coil is also compressed.
  • the helix is advantageously plastically deformed by compression until it comes into frictional engagement with the battery due to a reduction in diameter.
  • plastic deformation is generated by a force component acting radially inwards on the housing.
  • a radial direction always means a direction which is normal to the central axis of the heat exchanger.
  • An axial direction means a direction along the central axis of the heat transfer.
  • a preferred exemplary embodiment is characterized in that the accumulator, the helix and the housing are cylindrical.
  • a cylindrical configuration of the accumulator, the helix and the housing is advantageous in order to achieve a uniform compression of the individual elements that runs around the circumferential direction.
  • oval cross sections or angular cross sections of the elements can also be provided.
  • the application of the force component is preferably adapted to the respective cross sections of the elements in order to produce a force connection that is completely circumferential in the circumferential direction.
  • a non-adapted application of the force component can, for example, cause corrugations and bulges in the elements, thereby preventing a fluid-tight formation of a flow channel between the coil and the accumulator or the housing.
  • a helical flow channel is formed between the accumulator and the housing by the helix, through which a fluid can flow in the circumferential direction with an incline which can be predetermined by the turns of the helix.
  • the helical flow channel is advantageously formed by the free spaces formed between the individual turns.
  • the slope formed in the helix also gives the free spaces a slope, which at the same time also represents the slope of the resulting flow channel.
  • the flow channel is closed by the inner wall of the housing resting on the radially outward side of the coil and by the outer wall of the accumulator resting on the radially inward side of the coil.
  • the formation of such a flow channel allows a fluid to flow in a countercurrent to the fluid in the helix without leakage flows past the helix. This significantly increases the efficiency of the heat exchanger through improved heat transfer.
  • Elastic springbacks can result in minimal gaps between the coil and the housing. Due to their small gap width, these gaps lead to a very high pressure loss in the gap and thus to a high heat transfer. This column is therefore not to be regarded as disadvantageous.
  • the spacing of the turns from one another in the axial direction creates the free spaces between the turns which form the flow channel.
  • the size of the free spaces is mainly determined by the selected pitch of the individual turns.
  • the individual windings can also have slopes which differ from one another, as a result of which differently sized free spaces are created along the axial direction of the helix.
  • the tube from which the helix is formed has a round cross section or an oval cross section or an angular cross section.
  • An oval tube can be particularly advantageous if the broad sides of the tube extend in a radial direction, while the narrow sides extend in the axial direction. By compressing the tube in the radial direction, a tube with an approximately circular cross section can thus be produced. Deformation from the oval tube to the round tube can cause the material to work harden, which increases the strength of the tube. Nevertheless, the round shape created ensures an optimal flow cross-section.
  • the tube has an internal rib and / or an external rib. Ribs are advantageous in order to influence the fluids flowing through the heat exchanger in a targeted manner. In particular, the generation of a turbulent flow is advantageous in order to increase the heat transfer.
  • a method which provides for plastic deformation of the housing in order to produce a frictional connection between the coil and the inner surface of the housing is particularly advantageous since it is easy to use and can be easily adapted to a large number of differently dimensioned heat exchangers.
  • different outside diameters of the heat exchangers can be taken into account by correspondingly adapting the device in which the heat exchanger is accommodated for deformation.
  • the accumulator is preferably arranged in the center of the heat exchanger.
  • the coil is plugged onto the accumulator, so that the accumulator is arranged in the interior space formed within the coil.
  • the housing is placed over the coil so that the coil and the accumulator are arranged in the housing.
  • the accumulator, the filament and the housing preferably have the same cross sections, which differ only in the respective inner diameter and outer diameter.
  • a deformation, in particular a compression, of the housing is generated by a force component which acts inwards in the radial direction and is applied to the housing.
  • the force component is preferably removed from the housing when a certain predetermined deformation has been reached or other predetermined control values have been reached. For example, a measured force or a distance traveled can be considered as a control value.
  • the individual work steps of the method lead to an arrangement of an accumulator within a coil, the coil itself being arranged within the housing.
  • the force acting on the housing creates a force fit between at least the housing and the coil. After reaching a predefined frictional connection, the force is finally removed from the housing, which creates the heat exchanger with the non-positively connected elements.
  • the helix with the radially inward side abuts the radial outer surface of the accumulator and / or the helix with the radially outward side on the radial inner surface of the housing is applied.
  • the helix can rest on the accumulator and / or on the housing. This is particularly advantageous to facilitate assembly. In particular, if the helix only rests on one of the other two elements, assembly is particularly simple. If the accumulator and the housing bear against the helix, different fits can be provided between the helix and the accumulator and / or the housing, which enables assembly with greater or lesser expenditure of force.
  • a gap is formed between the housing and the helix in order to enable assembly.
  • a gap between the coil and the housing is particularly advantageous if the accumulator and the coil are already preassembled as a structural unit and a fit with small tolerances is formed between the coil and the accumulator. The assembly can then be easily installed in the housing.
  • a gap is advantageous in order to first achieve only a deformation of the housing during the plastic deformation before the housing comes into contact with the Wendel is coming. As a result, the housing can be transferred in a targeted manner beyond the elastic deformation area into the plastic deformation area without already having an effect on the coil or the accumulator.
  • Cold forming is particularly advantageous in order to achieve increased stability of the heat exchanger.
  • Cold forming changes the lattice structure of the materials of the individual elements, thereby strengthening the individual elements and thus the entire heat exchanger.
  • the force component is generated by a pressing device on the radial outer surface of the housing.
  • a pressing device can be formed, for example, by one or more punches which can be moved radially inwards in order to be able to apply a force component to the housing.
  • the surfaces of the stamp facing the heat exchanger can be easily adapted to the cross section of the housing of the heat exchanger, as a result of which different heat exchangers can also be manufactured in a simple manner.
  • the pressing device can act on the housing in the axial direction over the entire length of the housing or only along a partial region.
  • Another preferred exemplary embodiment is characterized in that the application of the force component is controlled away and the duration of the force application and / or the nominal force is dependent on the deformation of the housing generated by the force component or in that the application of the force component is force-controlled and the duration of the Force application and / or the nominal force is dependent on a measured or predefined force.
  • a path-controlled device preferably captures the working path of the pressing device or the deformation distance of the housing. From this, it can be concluded that the deformation has already taken place, whereby a very precise deformation can be achieved.
  • a force is measured in particular on the stamps, which occurs in response to the applied force component. This changes depending on whether only the housing is deformed or also the coil and / or the accumulator. In this way, the deformation can be carried out in a targeted manner without direct insight into the interior of the housing.
  • the nominal force means the force component and in particular its amount, which is applied to the housing for the purpose of deformation.
  • the deformation of the housing and optionally of the coil and / or of the accumulator has an elastic component, micro-gaps between the housing and the coil and / or between the coil and the after the action of the radially inward force component Train the accumulator.
  • micro-gaps increases the surface of the accumulator, the tube and the housing that is active for heat transfer. This is done by an upstream deformation of the individual elements and a subsequent expansion of the elements in the elastic range of the overall deformation. The deformed areas then have in particular a larger surface.
  • the microgaps are preferably so small that the disadvantages due to the microgaps are smaller than the advantages achieved by increasing the surface area.
  • the Figure 1 shows a perspective view of a helix 1.
  • the helix 1 is generated by a tube 2 which has been wound up to form a helix 1.
  • the helix 1 has a plurality of turns 3, which are spaced apart from one another in the axial direction of the helix 1 and each form a free space 4 between the turns 3 adjacent to one another.
  • the axial direction runs along the central axis, which extends from top to bottom through the interior space 7 formed within the turns 3 of the helix 1.
  • the radial direction runs from this central axis to the windings 3.
  • the tube 2 has two tube end regions 5, 6, which are arranged at the top and bottom at the end of the helix 1 and serve as fluid connections for the flow through the tube 2.
  • FIG. 2 shows a further view of the helix 1, as already shown in Figure 1 was shown.
  • the free spaces 4 can be seen, which are formed between two mutually adjacent turns 3.
  • the turns 3 each have an identical outside diameter and an identical inside diameter. This is in the embodiment of Figures 1 and 2 , which show a cylindrical helix 1, a cylindrical interior 7 and a cylindrical outer surface on the outside diameter of the turns 3.
  • the Figure 3 shows a detailed view of the upper end region of the helix 1.
  • the upper tube end region 5 can be seen, which is formed by a bend of approximately 90 ° from the upper turn 3 upwards.
  • the tube end region 5 can also be at different angles to the rest of the coil 1 or have additional connection elements.
  • the cylindrical interior 7 is shown in the interior of the helix 1 and furthermore the free spaces 4 between the mutually adjacent turns 3.
  • the Figure 4 shows a plan view of the helix 1 along the central axis, which is formed centrally in the cylindrical interior 7.
  • all the turns 3 are in alignment with one another and have identical inside and outside diameters, as a result of which a cylindrical inner lateral surface and a cylindrical outer lateral surface are formed on the helix 1.
  • the Figure 5 shows a sectional view through a heat exchanger 20. Inside the heat exchanger 20, the coil 1 is arranged, which according to the embodiments of FIG Figures 1 to 4 is executed. In the cylindrical interior 7 of the helix 1 there is also a cylindrical body 10 which forms an accumulator. This accumulator 10 is used in particular for the storage and / or filtering and / or drying of a refrigerant which can flow through the heat exchanger 20.
  • the accumulator 10 has a nozzle at its upper end region, which is in fluid communication with a fluid connection 16.
  • This fluid connection 16 is formed in the housing 11, which accommodates both the coil 1 and the accumulator 10.
  • the accumulator 10 has a radially outwardly directed surface 14, on which in the exemplary embodiment the Figure 5 the radially inward side 13 of the helix 1 rests.
  • the surface 14 can have any contour, ie for example be cylindrical, as shown, or be designed as a single or multiple thread.
  • the coil 1 is accordingly dimensioned such that the accumulator 10 can be accommodated in the cylindrical interior 7 with a precise fit.
  • a press fit, a clearance fit or a transition fit can preferably be provided between the accumulator 10 and the helix 1. Accordingly, the helix 1 can be pushed over the accumulator 10 with or without effort.
  • contact points 15 are formed on the individual windings 3.
  • the upper tube end region 5 of the coil 1 is in fluid communication with a further fluid connection 25, which is also formed in the housing 11 , whereby the coil 1 can be flowed through with a fluid.
  • the housing 11 is also cylindrical and has a radially inward surface 21.
  • the inside diameter of the housing 11 is larger than the outside diameter of the helix 1. This creates a gap 12 between the helix 1 and the housing 11.
  • the cylindrical wall of the housing 11 is rectilinear in the area of the helix in the axial direction and has no depressions or indentations.
  • the Figure 5 shows an assembled state of the heat exchanger 20 before the final processing, which provides for fixing the coil 1 between the accumulator 10 and the housing 11.
  • the cavity 17 formed between the accumulator 10 and the housing 11 or half of the accumulator 10 can also have a fluid flowing through it.
  • the filament 1 would only be flowed around since the gap 12 is located between the filament 1 and the housing 11.
  • a defined flow channel which is formed in particular by the free spaces 4 between the windings 3
  • an installation must be made between the inwardly facing surface 21 of the housing 11 and the radially outwardly facing surface Page 22 of the helix 1 are generated.
  • this is intended to reduce a leakage flow past the windings 3 or to exclude it entirely.
  • a fluid flowing through the cavity 17 can then only flow between the windings 3 in a screw-like channel structure which is formed by the free spaces 4, as a result of which an improved heat transfer between the fluid flowing in the coil 1 and the fluid flowing through the cavity 17 can be generated.
  • the Figure 6 shows the heat exchanger 20 of the Figure 5 , whereby deformation of the housing 11 in a radially inward direction creates a contact between the radially inward surface 21 of the housing 11 and the radially outward side 22 of the helix 1. This can be seen in particular in the partial region 18 of the housing 11, which is deflected out of the plane of the original wall 19 by the action of a radially inward force component.
  • the embodiment of the Figure 6 lies both the radially outward surface of the accumulator 10 on the helix 1 and the radially inward surface of the housing 11.
  • the flow channel is thus defined in particular by the free spaces 4 between the turns 3.
  • a deformation of the housing 11, as in Figure 6 is shown, for example, can be generated by a press ram which is arranged cylindrically around the housing 11 and which generates a radially inward force on the outer surface of the housing 11.
  • the heat exchanger 20 in the state of Figure 5 For example, be inserted into a press device and then a force component is exerted on the housing 11.
  • the Figure 7 shows an alternative embodiment of the heat exchanger 20.
  • an embodiment shown which represents a partially assembled state of the heat exchanger 20.
  • the partially assembled state there is both between the inward side 13 of the coil 1 and the radially outward surface 14 of the accumulator 10 and between the radially outward outer side 22 of the coil 1 and the radially inward surface 21 of the housing 11 each have a gap 12 and 24 respectively.
  • a structure of the heat exchanger 20, as in Figure 7 is achieved in particular in that the inner diameter of the coil 1 is larger than the outer diameter of the accumulator 10, while the inner diameter of the housing 11 is larger than the outer diameter of the coil 1.
  • a spacing as shown in FIG Figure 7 is particularly advantageous in order to achieve a simpler assembly of the heat exchanger 20.
  • the Figure 8 shows the heat exchanger as already in Figure 7 was shown, wherein the housing 11 is caused by a force component, which has acted radially inward on the outer surface of the housing 11, a deformation in the housing region 18.
  • the deformation in the area 18 of the housing 11 is in comparison to the deformation of the Figure 6 stronger, so that in addition to the housing 1 being in contact with the coil 1, the coil 1 was also in contact with the battery 10.
  • the housing 11 not only is the housing 11 deformed, but also the helix 1 is compressed in the radially inward direction.
  • the accumulator 10 can also experience compression due to the action of the radially inward force component.
  • the deformation of the housing 11 and, optionally, the coil 1 and / or the accumulator 10 results in strain hardening in the respective elements, which is particularly advantageous for producing a higher stability of the heat exchanger 20.
  • the elastic component of the deformation of the individual elements 1, 10 and 11 that is present in each case can lead to the formation of micro-gaps between the coil 1 and the accumulator 10 or the housing 11.
  • these micro-gaps are so small that the leakage currents generated are extremely low.
  • the efficiency of the heat exchanger 20 is influenced only slightly.
  • micro-gaps that arise due to the deformation of the individual elements are advantageous because they lead to an increase in the surface area of the individual elements, as a result of which an improved heat transfer can be generated.
  • the increased efficiency due to the improved heat transfer is to be preferred over the efficiency reduction due to the microgaps.
  • a tube 2 is shown with a circular cross section.
  • tubes with an oval, elliptical or angular cross section can also be used.
  • the shape of cylindrical cross sections of the helix 1, the accumulator 10 and the housing 11 shown in each case are also only examples. Different cross sections can also be used here without deviating from the basic idea of the invention.
  • the tube can also have inner ribs or outer ribs, through which the flow in the individual flow channels can be influenced.
  • the free spaces 4 between the windings 3 can be designed with turbulence-generating rib elements.
  • the Figure 9 shows a block diagram illustrating the steps of the method in a sequence.
  • the accumulator 10 is inserted into the coil.
  • the helix 1 forms an interior space 7 which is arranged in the center of the helix 1.
  • the accumulator 10 is inserted into this interior.
  • the helix 1 can also be pushed over the accumulator 10.
  • the block 31 represents the work step in which the housing 11 is plugged onto the helix 1.
  • the housing 11 is preferably tubular, the cross section of the housing 11 being matched to the cross section of the helix 1 and / or the accumulator 10.
  • a force component is applied to the radial outer surface of the housing 11. This can preferably be done by a pressing device which provides movable punches which generate a force in the radial direction by a method.
  • the work step which is represented by block 33, corresponds to the plastic deformation of the housing 11 as a result of the force component applied to the housing 11 in block 32.
  • the force component After reaching a certain predetermined deformation of the housing 11 and optionally the coil 1 and / or the accumulator 10, the force component is finally removed from the housing 11, so that no further plastic deformation takes place. This step is shown in block 34.

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

Claims (15)

  1. Echangeur de chaleur (20) servant au refroidissement d'un fluide, ledit échangeur de chaleur comprenant un accumulateur (10), un carter (11) et un tube (2) produit pour former un serpentin (1), où un interstice est configuré entre l'accumulateur (10) et le carter (11), interstice dans lequel est disposé le tube (2) produit pour former un serpentin (1), où un assemblage par action de force est réalisé entre le carter (11) et le serpentin (1), caractérisé en ce que l'assemblage par action de force est produit par une déformation plastique du carter (11).
  2. Echangeur de chaleur (20) selon la revendication 1, caractérisé en ce qu'un assemblage par action de force est produit entre le carter (11), le serpentin (1) et l'accumulateur (10), où l'assemblage par action de force est produit par une déformation plastique du carter (11) et du serpentin (1).
  3. Echangeur de chaleur (20) selon l'une des revendications précédentes, caractérisé en ce que la déformation plastique est produite par un composant de force agissant sur le carter (11), vers l'intérieur dans le sens radial.
  4. Echangeur de chaleur (20) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'accumulateur (10), le serpentin (1) et le carter (11) sont configurés en étant de forme cylindrique.
  5. Echangeur de chaleur (20) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un conduit d'écoulement de forme hélicoïdale est formé par le serpentin (1), entre l'accumulateur (10) et le carter (11), conduit d'écoulement à travers lequel un fluide ayant une pente prédéfinissable peut s'écouler à travers les spires (3) du serpentin (1), suivant la direction circonférentielle.
  6. Echangeur de chaleur (20) selon l'une quelconque des revendications précédentes, caractérisé en ce que les différentes spires (3) du serpentin (1) sont configurées en étant espacées les unes des autres dans la direction axiale.
  7. Echangeur de chaleur (20) selon l'une quelconque des revendications précédentes, caractérisé en ce que le tube (2), à partir duquel le serpentin (1) est formé, présente une section ronde ou une section ovale ou une section angulaire.
  8. Echangeur de chaleur (20) selon l'une quelconque des revendications précédentes, caractérisé en ce que le tube (2) présente un ensemble de nervures intérieures et / ou un ensemble de nervures extérieures.
  9. Procédé de fabrication d'un échangeur de chaleur (20) selon au moins l'une quelconque des revendications précédentes, ledit échangeur de chaleur comprenant un accumulateur (10), un carter (11) et un tube (2) produit pour former un serpentin (1), où le procédé comprend les étapes suivantes consistant :
    • à introduire l'accumulateur (10) dans le serpentin (1),
    • à emboîter un carter (11) de forme tubulaire, sur le serpentin (1),
    • à appliquer, sur le carter (11), une force dirigée vers l'intérieur dans le sens radial,
    • à procéder à la déformation plastique du carter (11) et, facultativement, du serpentin (1) et / ou de l'accumulateur (10) dans une direction orientée vers l'intérieur dans le sens radial,
    • à démonter le composant de force, du carter (11).
  10. Procédé selon la revendication 9, caractérisé en ce que, avant l'application du composant de force tourné vers l'intérieur dans le sens radial, le serpentin (1) vient en appui, par le côté (13) tourné vers l'intérieur dans le sens radial, sur la surface extérieure radiale (14) de l'accumulateur (10), et / ou le serpentin (1) vient en appui, par le côté (22) tourné vers l'extérieur dans le sens radial, sur la surface intérieure radiale (21) du carter (11).
  11. Procédé selon l'une des revendications précédentes 9 ou 10, caractérisé en ce qu'un interstice (12) est formé entre le carter (11) et le serpentin (1) avant l'application du composant de force tourné vers l'intérieur dans le sens radial.
  12. Procédé selon l'une quelconque des revendications précédentes 9 à 11, caractérisé en ce qu'une déformation à froid du carter (11) et, facultativement, du serpentin (1) et / ou de l'accumulateur (10) est produite par l'application du composant de force tourné vers l'intérieur dans le sens radial.
  13. Procédé selon l'une quelconque des revendications précédentes 9 à 12, caractérisé en ce que le composant de force est produit par un dispositif de compression agissant sur la surface extérieure radiale du carter (11).
  14. Procédé selon l'une quelconque des revendications précédentes 9 à 13, caractérisé en ce que l'application du composant de force est à commande proportionnelle à la course, et la durée de l'application de la force et / ou la force nominale est fonction de la déformation du carter (11), ladite déformation étant produite par le composant de force, ou bien caractérisé en ce que l'application du composant de force est à commande servomotrice, et la durée de l'application de la force et / ou la force nominale est fonction d'une force mesurée ou prédéfinie.
  15. Procédé selon l'une quelconque des revendications précédentes 9 à 14, caractérisé en ce que la déformation du carter (11) et, facultativement, du serpentin (1) et / ou de l'accumulateur (10) présente une proportion élastique, où après l'action du composant de force tourné vers l'intérieur dans le sens radial, des micro-interstices se forment entre le carter (11) et le serpentin (1) et / ou entre le serpentin (1) et l'accumulateur (10).
EP15742244.5A 2014-07-29 2015-07-24 Échangeur de chaleur et procédé de fabrication de l'échangeur de chaleur Active EP3175195B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014110718.7A DE102014110718A1 (de) 2014-07-29 2014-07-29 Wärmeübertrager und Verfahren zur Herstellung des Wärmeübertragers
PCT/EP2015/067057 WO2016016143A1 (fr) 2014-07-29 2015-07-24 Échangeur de chaleur et procédé de fabrication de l'échangeur de chaleur

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EP3175195A1 EP3175195A1 (fr) 2017-06-07
EP3175195B1 true EP3175195B1 (fr) 2020-02-12

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EP (1) EP3175195B1 (fr)
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4071431A1 (fr) * 2021-04-06 2022-10-12 Vaillant GmbH Échangeur de chaleur

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Publication number Priority date Publication date Assignee Title
FR3051037B1 (fr) * 2016-05-04 2018-11-09 Valeo Systemes Thermiques Echangeur thermique compact
JP2021014971A (ja) * 2019-07-16 2021-02-12 ダイキン工業株式会社 貯留タンクユニット

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US4061184A (en) * 1976-10-28 1977-12-06 Ebco Manufacturing Company Heat exchanger for a refrigerated water cooler
US4379390A (en) * 1977-02-28 1983-04-12 Bottum Edward W Ice-making evaporator
FR2547896B1 (fr) * 1983-06-24 1985-11-29 Air Liquide Procede de fabrication d'une virole pour recipient de stockage de fluide cryogenique et virole ainsi obtenue
DE19830757A1 (de) 1998-07-09 2000-01-13 Behr Gmbh & Co Klimaanlage
DE102008028853A1 (de) 2008-06-19 2009-12-24 Behr Gmbh & Co. Kg Integrierte, einen Sammler und einen inneren Wärmeübertrager umfassende Baueinheit sowie ein Verfahren zur Herstellung der Baueinheit
NL2004147C2 (en) * 2010-01-26 2011-07-27 Daalderop Bv Heat exchanger.

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Publication number Priority date Publication date Assignee Title
EP4071431A1 (fr) * 2021-04-06 2022-10-12 Vaillant GmbH Échangeur de chaleur

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WO2016016143A1 (fr) 2016-02-04
DE102014110718A1 (de) 2016-02-04

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