EP3516319B1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
EP3516319B1
EP3516319B1 EP17755522.4A EP17755522A EP3516319B1 EP 3516319 B1 EP3516319 B1 EP 3516319B1 EP 17755522 A EP17755522 A EP 17755522A EP 3516319 B1 EP3516319 B1 EP 3516319B1
Authority
EP
European Patent Office
Prior art keywords
working medium
heat exchanger
edge
housing
ring seal
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
EP17755522.4A
Other languages
German (de)
English (en)
Other versions
EP3516319A1 (fr
Inventor
Pramod Barhate
Simon HUND
Bernd Krämer
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP3516319A1 publication Critical patent/EP3516319A1/fr
Application granted granted Critical
Publication of EP3516319B1 publication Critical patent/EP3516319B1/fr
Active 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0224—Header boxes formed by sealing end plates into covers
    • F28F9/0226—Header boxes formed by sealing end plates into covers with resilient gaskets
    • 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
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • 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
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1607—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-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
    • F28F2275/08—Fastening; Joining by clamping or clipping
    • F28F2275/085—Fastening; Joining by clamping or clipping with snap connection

Definitions

  • the present invention relates to a heat exchanger for media-separated cooling of a working medium by means of a cooling medium, with the features of the preamble of claim 1.
  • Such heat exchangers which can also be referred to as heat exchangers, are used, for example, in motor vehicles to cool a working medium of the vehicle, preferably an internal combustion engine of the vehicle. Comparatively high temperatures can occur on the side of the working medium to be cooled, for example in a charge air cooler or in an exhaust gas recirculation cooler or in an exhaust gas cooler. It is clear that the cooling of the working medium is accompanied by heating of the cooling medium, so that the respective heat exchanger can also be used for heating the cooling medium, which then corresponds to a working medium, by means of the working medium, which then corresponds to a heating medium.
  • a generic heat exchanger is for example from the WO 2014/006213 A1 known. It has a housing which has a housing jacket, a working medium inlet, a working medium outlet, a cooling medium inlet and a cooling medium outlet. The working medium and the cooling medium can thus be supplied to and removed from the housing. Furthermore, the heat exchanger has a heat exchanger block which is inserted into the housing and which has a front floor facing the working medium inlet and a rear floor facing away from the working medium inlet, as well as a plurality of working medium pipes for guiding the working medium. The working medium pipes penetrate the two trays and are also firmly and tightly connected to the two trays to form the heat exchanger block.
  • a working medium path leads from the working medium inlet inside through the working medium pipes to the working medium outlet. Also introduces Coolant path from the coolant inlet around the outside of the working medium pipes to the coolant outlet.
  • the heat transfer between the working medium flowing inside and the cooling medium flowing outside takes place via the walls of the working medium pipes.
  • the respective base has a circumferential edge which projects radially beyond the working medium tubes and which is axially supported in each case via an axially acting ring seal on a step of the housing which runs around the respective edge.
  • the jacket is formed from two half-shells which are arranged axially between the two bottoms of the heat exchanger block and are attached to one another.
  • the known heat exchanger thus has a housing that has at least four separate components that have to be assembled. Thus, the effort to implement the known heat exchanger is comparatively large.
  • the heat exchanger block outside the housing, in order to subsequently combine the finished heat exchanger block with the housing.
  • the production of the heat exchanger block outside the housing is of particular advantage, since the production of the heat exchanger block often has a high thermal This is accompanied by a load which, for example, cannot be realized in a plastic casing of the housing and / or requires good accessibility, which is not provided within the housing.
  • the working medium pipes must be led through the floors so that soldered connections or welded connections are used there.
  • very high temperatures may also be required for soldering, for example when brazing.
  • plastics and light metal alloys In order to be able to manufacture a heat exchanger as inexpensively as possible, it is necessary to use inexpensive materials, such as plastics and light metal alloys. However, these inexpensive materials cannot be used in all possible temperature ranges. Furthermore, plastics have a significantly lower coefficient of thermal conductivity than metals. In contrast, iron alloys, preferably steel, especially stainless steel, have a very high temperature resistance, but are then comparatively expensive. However, particularly in vehicle applications, the lowest possible weight for the heat exchanger is desirable.
  • a heat exchanger which is inserted laterally into the housing through a housing opening, the housing opening being bordered by an axially protruding projection on which locking lugs are formed radially on the outside.
  • the front bottom of the heat exchanger projects radially beyond the working medium pipe and forms a circumferential collar which has latching openings which match the latching lugs, engages around the projection and latches with the latching lugs in order to fix the heat exchanger to the housing.
  • a circumferential seal is arranged axially between the projection and the collar.
  • the present invention is concerned with the problem of specifying an improved or at least another embodiment for a heat exchanger of the type mentioned at the outset, which is distinguished on the one hand by inexpensive manufacture and on the other hand by increased functional reliability in the area of the ring seal.
  • the invention is based on the general idea of locking the heat exchanger block in the housing in such a way that axial contact and preferably axial pretension can be permanently ensured in the area of the ring seal.
  • the invention proposes realizing such a latching between the housing and the heat exchanger block in the area of the rear floor in order to axially prestress the first ring seal provided there, such that that the first ring seal bears axially biased both at the edge of the rear floor and at the associated step formed on the housing. This ensures the sealing function of the first ring seal at all expected temperatures and operating situations.
  • the housing expediently has at least one latching contour in the area of the step, which cooperates with a counter-latching contour of the rim on a rear side of the edge of the rear base facing away from the first ring seal.
  • the respective locking contour brings about an axial positioning of the edge on the housing.
  • this axial positioning causes the edge to be axially fixed to the housing, which prevents the edge from moving axially away from the step.
  • this axial positioning for the edge defines an axial position relative to the housing in which the first ring seal bears axially preloaded on the edge and on the step.
  • a plurality of latching contours are expediently provided, which are spaced apart from one another in the circumferential direction and which are arranged distributed along the edge. In this way, the axial fixation or axial positioning of the edge of the rear base on the housing is improved.
  • the respective latching contour can interact directly with the rear of the edge, in which case the rear of the edge itself forms the counter-latching contour together for all latching contours. This simplifies the manufacture of the rear floor.
  • the respective locking contour encompasses a radially outer outer edge of the edge.
  • the respective latching contour can expediently have a ramp on a side facing the working medium inlet.
  • the ramp makes it easier to drive over the respective locking contour through the edge of the rear floor, which precedes when the heat exchanger block is inserted into the housing.
  • an essentially radially oriented latching lug of the latching contour adjoining the ramp engages behind the respective counter-latching contour and thus secures the edge against axial pulling out of the housing against the direction of insertion.
  • the edge can be axially supported directly on the step with a front side facing the first ring seal.
  • the edge lies against the step in the direction of insertion and against the respective latching contour in the pull-out direction. This results in a particularly efficient axial positioning of the heat exchanger block within the housing.
  • the first ring seal can be configured, for example, as a plastic seal.
  • Plastic seals are characterized by a particularly high level of tightness.
  • the two bottoms of the heat exchanger block axially delimit the cooling medium path, so that the rear of the edge is directly exposed to the cooling medium and is cooled accordingly.
  • the first ring seal thus interacts with an actively cooled edge, which reduces the thermal load on the ring seal.
  • the step can expediently have a receiving groove into which the first ring seal is inserted axially. In this way, the axial compression of the first ring seal can be limited to an allowable or predetermined amount. Furthermore, with the aid of the receiving groove, an efficient radial fixation or positioning for the first ring seal is made possible.
  • the edge is supported axially on the step exclusively via the first ring seal.
  • This embodiment is characterized by a particularly simple geometry in the area of the step, which simplifies production.
  • the first ring seal is designed as a disk-shaped metal bead seal.
  • metal bead seals are not as tight as plastic seals, but have a significantly higher thermal resistance.
  • the working medium inlet can be integrally formed on a connecting flange which is a separate component with respect to the jacket and which is fastened to the jacket by means of a fastening.
  • the connecting flange can be a one-piece, integrally produced cast part. This makes it possible to manufacture the connecting flange and the jacket from different materials.
  • the jacket can be a plastic part, while the connecting flange is a metal part.
  • the front base also has a circumferential edge which projects radially beyond the working medium pipes and is arranged axially between an axial jacket end face of the jacket and an axial flange front side of the connecting flange, so that it in turn fixes the connecting flange on the jacket to the housing by means of fastening is fixed.
  • the edge of the front base expediently extends radially into the fastening so that it is integrated into this fastening.
  • the heat exchanger block is axially fixed to the housing in the region of the front base by the fastening between the connecting flange and the jacket. In the area of the rear floor, the heat exchanger block is axially fixed to the housing by the catch.
  • the coolant inlet and the coolant outlet as well as the respective locking contour and the step are expediently formed integrally on the jacket. This simplifies the manufacture of the housing. Furthermore, the jacket can be made in one piece or in one piece, in particular as an integral casting.
  • the heat exchanger can be designed in a U-current construction.
  • the working medium outlet is also integrally formed on the connection flange, while a deflection chamber is provided in the housing.
  • the working medium path now leads through at least one of the working medium pipes from the working medium inlet to the deflection chamber and through at least one other of the working medium pipes from the deflecting chamber to the working medium outlet.
  • the housing is closed in the region of the deflection chamber by a housing base which is expediently integrally formed on the casing. This gives the housing a particularly inexpensive construction, since it ultimately only comprises the connecting flange with working medium inlet and working medium outlet and the casing with the housing base, coolant inlet and coolant outlet.
  • the deflection chamber can be delimited directly by the jacket and the housing base or by a metal body which is inserted into the housing.
  • a metal body can be used above all if the housing in the area of the casing and housing base is made of plastic and the expected temperatures in the deflection chamber are still relatively high.
  • the heat exchanger is designed in an I-current design.
  • the working medium outlet is arranged axially opposite the working medium inlet and can also advantageously be integrally formed on the jacket.
  • the housing comprises only two components, namely the jacket with the working medium outlet, coolant inlet, coolant outlet and the connecting flange with the working medium inlet.
  • the finished heat exchanger block can then be inserted into the housing by axially inserting it into the jacket if there is no connecting flange on the jacket end face.
  • the heat exchanger block is inserted into the jacket until the rear floor preceding it when inserted is locked on the edge with the respective locking contour.
  • the connecting flange can then be attached to the jacket, which means that the heat exchanger block is also fixed in the area of the front floor.
  • an axially acting second ring seal can be provided axially between the edge of the front base and the jacket end face.
  • an axially acting third ring seal can be provided axially between the edge of the front base and the flange end face.
  • the second ring seal and the third ring seal can optionally be designed as a plastic seal or as a metal bead seal. In particular, it is thus possible to design the second ring seal and the third ring seal each as a plastic seal. Likewise, the second ring seal and the third ring seal can each be designed as a metal bead seal. It is also conceivable to design the second ring seal as a plastic seal, while the third ring seal is designed as a metal bead seal. Finally, it is also possible to design the second ring seal as a metal bead seal, while the third ring seal is designed as a plastic seal.
  • the heat exchanger block is made of an iron alloy
  • the jacket is made of an Plastic or made of a light alloy. Since the heat exchanger block can be finished outside of the housing in the heat exchanger presented here, the two floors and the working medium pipes can be joined at high temperatures, for example in order to solder or weld the working medium pipes to the floors.
  • the jacket can be produced as an inexpensive cast part made of plastic or light metal alloy and, depending on the degree of integration and depending on the design, form integrally with the coolant inlet, with the coolant outlet, the step and the respective locking contour.
  • the connection flange is provided, it can also be made of an iron alloy or a light metal alloy, depending on the thermal load to be expected from the hot working medium to be cooled. In the case of an exhaust gas cooler, the connection flange is preferably made of an iron alloy.
  • the edge of the rear floor can lift off radially inwardly from the step at ambient temperature and bear axially inward on the step at operating temperature.
  • This can be achieved, for example, by appropriate shaping of the base in the area of the edge.
  • the edge of the rear floor can be inclined to the rear relative to a plane running perpendicular to the axial direction, that is to say directed away from the front floor.
  • the heat exchanger block expands axially more than the housing, as a result of which the above-mentioned inclination of the edge becomes less and less until the edge also comes into axial contact with the step radially on the inside at operating temperature.
  • edge of the rear bottom has an axial distance from the step radially on the inside, which is at ambient temperature is greater than at operating temperature. This means that the axial distance decreases with increasing temperature and in extreme cases can, but does not have to, be zero.
  • axial contact between the edge and the step can occur radially on the inside, while at lower temperatures, which can still be in the operating temperature range, such axial contact does not occur.
  • This can also be achieved by appropriate shaping of the rear floor in the area of the edge.
  • a heat exchanger 1 comprises a housing 2 and a heat exchanger block 3, which is located inside the housing 2 and therefore in FIG Fig. 1 is not visible.
  • the housing 2 has a housing jacket 4, a working medium inlet 5, a working medium outlet 6, a cooling medium inlet 7 and a cooling medium outlet 8.
  • the heat exchanger block 3 has a front floor 9 facing the working medium inlet 5 and a rear floor 10 facing away from the working medium inlet 5.
  • the heat exchanger block 3 has a plurality of working medium tubes 11 for guiding a working medium 12, the working medium tubes 11 leading axially through the two trays 9, 10 and being firmly and tightly connected to the two trays 9, 10.
  • the working medium inlet 5 comprises an associated inlet connector and has a fastening flange which is used to connect the heat exchanger 1 to a working medium line carrying the working medium, such as e.g. a charge air line, an exhaust gas recirculation line or an exhaust gas line.
  • the working medium outlet 6 here also has an associated outlet connector and a fastening flange, which is used to connect the heat exchanger 1 to the working medium line.
  • the coolant inlet 7 here comprises an associated inlet connection piece, which is used to connect the heat exchanger 1 to a cooling circuit carrying a coolant 13.
  • the cooling medium outlet 8 here also has an associated outlet connector, which is used to connect the heat exchanger 1 to the cooling circuit.
  • the heat exchanger 1 is used for media-separated cooling of the working medium 12 with the aid of a cooling medium 13.
  • a working medium 12 which in the Figures 1 and 2 is indicated by arrows, it can preferably be a gas, such as charge air, recirculated exhaust gas and exhaust gas.
  • the cooling medium 13 which in the Figures 1 and 2 is indicated by arrows, it can be a liquid, such as a cooling liquid of a cooling circuit of an internal combustion engine or a motor vehicle equipped with it.
  • a working medium path 14 indicated by arrows and a cooling medium path 15 likewise indicated by arrows are formed in the heat exchanger 1.
  • the working medium path 14 leads from the working medium inlet 5 inside through the working medium pipes 11 to the working medium outlet 6.
  • the coolant path 15 leads from the coolant inlet 7 outside around the working medium pipes 11 to the coolant outlet 8.
  • the working medium pipes 11 are each linear and parallel to one another and to the side arranged side by side, ie radially next to each other, with 11 spaces radially between adjacent working medium tubes 16 are formed, which are also traversed by the cooling medium 13 of the cooling medium path 15.
  • FIG. 2 it can further be seen that the working medium inlet 5 is expediently designed as a diffuser in order to distribute the working medium 12 supplied to the working medium pipes 11.
  • the rear base 10 has a circumferential edge region or edge 17 projecting radially beyond the working medium pipes 11.
  • the housing 2 has a circumferential step 18.
  • a first ring seal 19 is now arranged, which acts axially and thus seals the edge 17 with respect to the step 18.
  • the housing 2 now has at least one, but preferably a plurality of latching contours 20 in the region of this step 18.
  • the respective latching contour 20 interacts with a counter-latching contour 21 which is located on the edge 17, the latching contour 20 being axially supported on the counter-latching contour 21 on a rear side 22 of the rim 17 facing away from the first ring seal 19.
  • a latching 23 for axially fixing the edge 17 to the step 18 is created.
  • the latch 23 prevents the edge 17 from axially moving away from the step 18.
  • the catch 23 causes the edge 17 to be positioned relative to the step 18 in an axial position in which the first ring seal 19 bears axially pretensioned both on the step 18 and on the edge 17.
  • the heat exchanger block 3 is axially fixed in the region of the rear floor 10. Both measures make it possible to be able to manufacture the heat exchanger block 3 outside the housing 2.
  • a plurality of latching contours 20 are provided, these are spaced apart from one another in the circumferential direction and are distributed along the edge 17.
  • the circumferential direction runs with respect to a longitudinal central axis 24 of the housing 2, which defines the axial direction, which extends parallel to the longitudinal central axis 24.
  • the respective locking contour 20 preferably interacts directly with the rear side 22 of the edge 17, so that the edge 17 itself forms the counter-locking contour 21, specifically in the region of its radially outer outer edge. Accordingly, the locking contour 20 encompasses the edge 17 in the region of its outer edge.
  • the first ring seal 19 is shown in the usual manner in the relaxed state, so that the first ring seal 19 supposedly penetrates into the edge 17 or penetrates the edge 17. It is clear that, in reality, the first ring seal 19 lies axially against the edge 17, with a corresponding elastic deformation of the first ring seal 19 taking place.
  • the edge 17 is axially supported with its front side 25, which faces the first ring seal 19, directly on the step 18.
  • a receiving groove 26 is formed for the first ring seal 19 in step 18, in which the first ring seal 19 is inserted axially.
  • the first ring seal 19 is designed as a plastic seal.
  • the edge 17 is supported axially on the step 18 exclusively via the first ring seal 19.
  • the first ring seal 19 is designed as a disk-shaped metal bead seal. In this case, no receiving groove 26 is required.
  • Figure 5 shows an embodiment similar to in Figure 3 , in which the first ring seal 19 is designed as a plastic seal and is inserted into a receiving groove 26.
  • the variant of Figure 4 to be used in which the first ring seal 19 is designed as a metal bead seal and in which the receiving groove 26 can be dispensed with.
  • the peculiarity of the in Figure 5 The embodiment shown shows that the edge 17 is inclined with respect to a plane running perpendicular to the axial direction, so that at ambient temperature it only touches the step 18 radially on the outside, while it lifts radially on the inside from the step 18.
  • This situation is in Figure 5 shown with a solid line.
  • a broken line shows a situation that occurs at operating temperature.
  • the edge 17 now also axially lies radially on the inside of the step 18.
  • the edge 17 of the rear base 10 can have an axial distance 27 from the step 18 radially inside, which is greater at ambient temperature than at operating temperature.
  • the rear floor 10 in the embodiments of FIGS Figures 2 to 5 is spatially shaped in such a way that the edge 17 cooperating with the step 18 and the first ring seal 19 is axially offset from an area enclosed by the edge 17, which is firmly connected to the working medium pipes 11. This offset occurs at the rear floor 10 to the outside, that is to say axially away from the working medium pipes 11.
  • the working medium inlet 5 is integrally formed on a connecting flange 28, which represents a separate component with respect to the jacket 4.
  • the diffuser mentioned above is thus formed in the connecting flange 28.
  • This connecting flange 28 is fastened to the jacket 4 by means of a fastening 29.
  • the attachment 29 is here as a flange connection realized with several screw connections 30.
  • the front base 9 has a peripheral edge 31 which projects radially beyond the working medium tubes 11. This edge 31 is arranged axially between an axial jacket face 32 of the jacket 4 and an axial flange face 33. Furthermore, the edge 31 extends radially into the fastening 29.
  • the edge 31 of the front base 9 is integrated into the attachment 29, so that with the aid of the attachment 29 on the one hand the connecting flange 28 on the jacket 4 and on the other hand the heat exchanger block 3 are fixed to the housing 2.
  • FIG. 1 In the example of the Figures 1 and 2 is the heat exchanger 1 designed in I-current construction, which according to Figure 10 characterized in that the working medium outlet 6 is axially opposite the working medium inlet 5.
  • Figure 11 shows Figure 11 a heat exchanger 1 in a U-current design, which is characterized in that working medium inlet 5 and working medium outlet 6 are located at the same axial end of the housing 2 and axially opposite a deflection chamber 34.
  • the working medium outlet 6 is integrally formed on the jacket 4.
  • the jacket 4 merges into the working medium outlet 6 via a convergence region 35.
  • a collecting chamber 36 is formed in the convergence area 35, in which the partial flows of the working medium 12 which are passed through the separate working medium pipes 11 are recombined and flow together to the working medium outlet 6.
  • the working medium outlet 6 can also be integrally formed on the connection flange 28.
  • the housing 2 then contains the deflection chamber 34.
  • the working medium path 14 leads through at least one of the working medium pipes 11 from the working medium inlet 5 to the deflection chamber 34 and through at least one other of the working medium pipes 11 from the deflection chamber 34 to the working medium outlet 6.
  • the housing 2 is then in the region of the deflection chamber 34 closed by a housing base 37.
  • the housing base 37 is integrally formed on the casing 4.
  • the deflection chamber 34 can be delimited by a metal housing (not shown here) which is inserted into the housing 2 and lines the casing 4 and the housing base 37 towards the deflection chamber 34 and protects it from contact with the working medium 12.
  • an axially acting second ring seal 38 can be provided in the region of the front base 9 between the associated edge 31 and the jacket end face 32.
  • an axially acting third ring seal 39 can be provided axially between the edge 31 of the front base 9 and the flange end face 33.
  • the second ring seal 38 and the third ring seal 39 can be designed as a plastic seal or as a metal bead seal.
  • FIGS. 2 and 6 show an embodiment in which the second ring seal 38 is designed as a plastic seal and in which the third ring seal 39 is also designed as a plastic seal.
  • Figure 7 shows an embodiment in which the second ring seal 38 is designed as a metal bead seal and in which the third ring seal 39 is also designed as a metal bead seal.
  • Figure 8 shows an embodiment in which the second ring seal 38 is designed as a plastic seal, while the third ring seal 39 is designed as a metal bead seal.
  • Figure 9 an embodiment in which the second ring seal 38 is designed as a metal bead seal, while the third ring seal 39 is designed as a plastic seal.
  • the jacket end face 32 contains an associated receiving groove 40, in which the second ring seal 38 is inserted axially.
  • the flange end 33 contains a corresponding receiving groove 41, in which the third ring seal 39 is inserted axially.
  • the second ring seal 38 and the third ring seal 39 are also shown in FIGS Figures 2 and 6 to 9 each shown in the relaxed state, so that they seem to protrude into the edge 31 of the front base 9 or into the flange face 33. In reality, this is not the case, rather the second ring seal 38 and the third ring seal 39 are then elastically deformed in a corresponding manner and lie axially on the edge 31 or on the flange end face 33.
  • the front base 9 is three-dimensionally shaped such that the edge 31 is axially offset with respect to an inner region of the front base 9 which is bordered by the edge 31, the inner region is firmly connected to the working medium pipes 11.
  • the axial offset takes place inwards, that is in a direction facing the working medium pipes 11.
  • the metal bead seals shown are each formed by a metal disk which extends in a ring along the respective edge 17 or 31 and which has at least one axially projecting, closed circumferential sealing contour 42 which bears axially against the respective edge 17, 31 or on the flange end face 33 .
  • the respective sealing contour 42 is integrally formed on the metal disk in the manner of a bead by reshaping.
  • This sealing contour 42 can or several such sealing contours 42 can be arranged radially between an inner edge and an outer edge of the respective metal bead seal. In the examples shown here, only one such sealing contour 42 is formed on each metal bead seal, specifically by an S-shaped angled area on the inner edge.
  • the heat exchanger block 3 that is to say the bases 9, 10 and the working medium tubes 11, are each made of an iron alloy. Different iron alloys can also be used. As a result, the heat exchanger block 3 can have a high thermal resistance. Furthermore, the individual components of the heat exchanger block 3 can be joined outside the housing 2, that is to say in particular they can be welded or soldered.
  • the jacket 4 can be made of a plastic or a light metal alloy. The jacket 4 integrally has the locking contours 20 and the step 18. Furthermore, the jacket 4 preferably also has the coolant inlet 7 and the coolant outlet 8 integrally. In the I-current construction shown here, the working medium outlet 6 is optionally integrally formed on the jacket 4 with the transition region 35.
  • the connecting flange 28 is preferably made of a metal. Depending on the area of application of the heat exchanger 1, a light metal alloy or an iron alloy can also be used. In the I-current design, the working medium inlet 5 is integrally formed on the connecting flange 28. In the U-current design, the connection flange 28 can additionally have the working medium outlet 6.
  • the respective ring seal 19, 38, 39 runs in a ring-shaped manner in the circumferential direction, but can in principle have any cross section transverse to its direction of rotation.

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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 servant au refroidissement avec séparation de milieux d'un milieu de travail (12) au moyen d'un milieu de refroidissement (13),
    - avec un boîtier (2) qui présente une enveloppe de boîtier (4), une entrée de milieu de travail (5), une sortie de milieu de travail (6), une entrée de milieu de refroidissement (7) et une sortie de milieu de refroidissement (8),
    - avec un bloc échangeur de chaleur (3) qui est inséré dans l'intérieur du boîtier (2) et qui présente un fond avant (9) tourné vers l'entrée de milieu de travail (5) et un fond arrière (10) détourné de l'entrée de milieu de travail (5) ainsi que plusieurs tubes de milieu de travail (11) servant à guider le milieu de travail (12), lesquels traversent les deux fonds (9, 10) et sont reliés fixement aux deux fonds (9, 10),
    - dans lequel un trajet de milieu de travail (14) passe de l'entrée de milieu de travail (5) en traversant l'intérieur des tubes de milieu de travail (11) jusqu'à la sortie de milieu de travail (6),
    - dans lequel un trajet de milieu de refroidissement (15) passe de l'entrée de milieu de refroidissement (7) à l'extérieur autour des tubes de milieu de travail (11) jusqu'à la sortie de milieu de refroidissement (8),
    - dans lequel est disposé axialement entre un bord (17) périphérique du fond arrière (10) dépassant radialement au-dessus des tubes de milieu de travail (11) et un échelon (18) du boîtier (2) périphérique le long du bord (17) un premier joint d'étanchéité annulaire (19) agissant axialement,
    caractérisé en ce que
    le boîtier (2) présente dans son intérieur dans la plage de l'échelon (18) au moins un contour d'encliquetage (20) qui coopère au niveau d'un côté arrière (22) du bord (17) détourné du premier joint d'étanchéité annulaire (19) avec un contour d'encliquetage complémentaire (21) du bord (17).
  2. Echangeur de chaleur selon la revendication 1,
    caractérisé en ce que
    plusieurs contours d'encliquetage (20) sont prévus, qui sont disposés de façon répartie à distance les uns des autres dans la direction périphérique le long du bord (17).
  3. Echangeur de chaleur selon la revendication 1 ou 2,
    caractérisé en ce que
    le contour d'encliquetage respectif (20) coopère directement avec le côté arrière (22) du bord (17) en tant que contour d'encliquetage complémentaire (21).
  4. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    le bord (17) s'appuie axialement avec un côté avant (25) tourné vers le joint d'étanchéité annulaire (19) directement à l'échelon (18).
  5. Echangeur de chaleur selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que
    le premier joint d'étanchéité (19) est conçu comme un joint d'étanchéité en matière plastique.
  6. Echangeur de chaleur selon la revendication 5,
    caractérisé en ce que
    l'échelon (18) présente une rainure de réception (26) dans laquelle le premier joint d'étanchéité annulaire (19) est inséré.
  7. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que
    le bord (17) ne s'appuie axialement à l'échelon (18) que sur le premier joint d'étanchéité annulaire (19).
  8. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3 et 7, caractérisé en ce que
    le premier joint d'étanchéité annulaire (19) est conçu comme un joint d'étanchéité en gouttière métallique en forme de disque.
  9. Echangeur de chaleur selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce que
    - l'entrée de milieu de travail (5) est constituée d'un seul tenant au niveau d'une bride de raccordement (28) qui est une pièce séparée par rapport à l'enveloppe (4) et qui est fixée à l'enveloppe (4) au moyen d'une fixation (29),
    - le fond avant (9) présente un bord périphérique (31) dépassant radialement au-dessus des tubes de milieu de travail (11) qui est disposé axialement entre un côté frontal d'enveloppe (32) axial de l'enveloppe (4) et un côté frontal de bride axial (33) de la bride de raccordement (28) et qui peut être intégré dans la fixation (29).
  10. Echangeur de chaleur selon l'une quelconque des revendications 1 à 9,
    caractérisé en ce que
    l'entrée de milieu de refroidissement (7) et la sortie de milieu de refroidissement (8) ainsi que le contour d'encliquetage respectif (20) et l'échelon (18) sont formés d'un seul tenant au niveau de l'enveloppe (4).
  11. Echangeur de chaleur selon les revendications 9 et 10,
    caractérisé en ce que
    - l'échangeur de chaleur (1) est conçu dans une structure à écoulement en U,
    - la sortie de milieu de travail (6) est formée d'un seul tenant au niveau de la bride de raccordement (28),
    - une chambre de dérivation (34) est prévue dans le boîtier (2)
    - le trajet de milieu de travail (14) passe à travers au moins un tube de milieu de travail (11) de l'entrée de milieu de travail (5) à la chambre de dérivation (34) et passe à travers au moins un autre tube de milieu de travail (11) de la chambre de dérivation (34) à la sortie de milieu de travail (6),
    - le boîtier (2) est fermé dans la zone de la chambre de dérivation (34) par un fond de boîtier (37) qui est formé d'un seul tenant au niveau de l'enveloppe (4).
  12. Echangeur de chaleur selon les revendications 9 et 10,
    caractérisé en ce que
    - l'échangeur de chaleur (1) est conçu dans une structure à écoulement en I,
    - la sortie de milieu de travail (6) est opposée axialement à l'entrée de milieu de travail (5) et est formée d'un seul tenant au niveau de l'enveloppe (4).
  13. Echangeur de chaleur selon l'une quelconque des revendications 9 à 12,
    caractérisé en ce que
    - un deuxième joint d'étanchéité annulaire (38) agissant axialement est prévu axialement entre le bord (31) du fond avant (9) et le côté frontal d'enveloppe (32),
    - un troisième joint d'étanchéité annulaire (39) agissant axialement est prévu axialement entre le bord (31) du fond avant (9) et le côté frontal de bride (33).
  14. Echangeur de chaleur selon l'une quelconque des revendications 1 à 13,
    caractérisé en ce que
    - le bloc d'échangeur de chaleur (3) est fabriqué en un alliage de fer,
    - l'enveloppe (4) est fabriquée en une matière plastique ou en un alliage de métal léger.
  15. Echangeur de chaleur selon l'une quelconque des revendications 1 à 14,
    caractérisé en ce que
    le bord (17) est incliné par rapport à un plan évoluant verticalement par rapport à la direction axiale, de sorte qu'il ne touche l'échelon (18) à température ambiante que radialement à l'extérieur, tandis qu'il se décolle radialement à l'intérieur de l'échelon(18).
EP17755522.4A 2016-09-26 2017-08-24 Échangeur de chaleur Active EP3516319B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IN201631032705 2016-09-26
PCT/EP2017/071269 WO2018054643A1 (fr) 2016-09-26 2017-08-24 Échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP3516319A1 EP3516319A1 (fr) 2019-07-31
EP3516319B1 true EP3516319B1 (fr) 2020-07-22

Family

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Application Number Title Priority Date Filing Date
EP17755522.4A Active EP3516319B1 (fr) 2016-09-26 2017-08-24 Échangeur de chaleur

Country Status (3)

Country Link
EP (1) EP3516319B1 (fr)
CN (1) CN109791033A (fr)
WO (1) WO2018054643A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3564613A1 (fr) * 2018-05-03 2019-11-06 Mann+Hummel GmbH Échangeur de chaleur, système d'admission d'air avec échangeur de chaleur et procédé de montage d'un échangeur de chaleur
DE102018211807A1 (de) * 2018-07-16 2020-01-16 Mahle International Gmbh Abgasrückführ-Anordnung für eine Brennkraftmaschine
CN113566614A (zh) * 2020-04-28 2021-10-29 杭州科百特科技有限公司 一种换热设备及其制造方法

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Publication number Priority date Publication date Assignee Title
DE102006051000A1 (de) 2005-10-26 2007-07-12 Behr Gmbh & Co. Kg Wärmetauscher, Verfahren zur Herstellung eines Wärmetauschers
US20110056652A1 (en) * 2006-01-23 2011-03-10 Behr Gmbh & Co. Kg Heat exchanger
WO2008003486A1 (fr) * 2006-07-06 2008-01-10 Behr Gmbh & Co. Kg Dispositif de refroidissement des gaz d'échappement destiné en particulier à un véhicule à moteur
DE202009018892U1 (de) * 2009-01-15 2014-04-17 Halla Visteon Climate Control Corporation Wärmetauscher für den Abgasstrang eines Kraftfahrzeugs mit verbessertem Temperaturausgleich im Kühlmittel
DE102012211857A1 (de) * 2012-07-06 2014-01-09 Behr Gmbh & Co. Kg Wärmeübertrager
DE102013205316A1 (de) * 2013-03-26 2014-10-02 Behr Gmbh & Co. Kg Frischluftanlage
DE102014204272A1 (de) * 2013-04-25 2014-10-30 MAHLE Behr GmbH & Co. KG Wärmeübertrager
DE102013221932A1 (de) 2013-10-29 2015-04-30 MAHLE Behr GmbH & Co. KG Wärmetauscher und Verfahren zur Herstellung eines Wärmetauschers

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Publication number Publication date
EP3516319A1 (fr) 2019-07-31
WO2018054643A1 (fr) 2018-03-29
CN109791033A (zh) 2019-05-21

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