EP3516319A1

EP3516319A1 - Heat exchanger

Info

Publication number: EP3516319A1
Application number: EP17755522.4A
Authority: EP
Inventors: Pramod Barhate; Simon HUND; Bernd Krämer
Original assignee: Mahle International GmbH
Current assignee: Mahle International GmbH
Priority date: 2016-09-26
Filing date: 2017-08-24
Publication date: 2019-07-31
Anticipated expiration: 2037-08-24
Also published as: EP3516319B1; CN109791033A; WO2018054643A1

Abstract

The invention relates to a heat exchanger (1) for cooling a working medium (12) by means of a cooling medium (13) with separation of the mediums, comprising a housing (2) having a housing casing (4), a working medium inlet (5), a working medium outlet (6), a cooling medium inlet (7) and a cooling medium outlet (8), and comprising a heat exchanger block (3) which is located in the housing (2) and has a front end cap (9) near the working medium inlet (5) and a rear end cap (10) remote from the working medium inlet (5), as well as multiple working medium pipes (11) for carrying the working medium (12), which pipes pass through the two end caps (9, 10) and are securely connected to the two end caps (9, 10), wherein an axial ring seal (19) is arranged axially between an edge (17) of the rear base (10) and a step (18) on the housing (2). An improved sealing function can be achieved if the housing (2) has at least one clip-in contour (20) in the region of the step (18), which cooperates with a mating clip-in contour (21) on the edge (17) on a rear side (22) of the edge (17) facing away from the ring seal (19).

Description

heat exchangers

The present invention relates to a heat exchanger for media-separate cooling of a working medium by means of a cooling medium, having 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. In this case, comparatively high temperatures can occur on the side of the working medium to be cooled, for example in the case of 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 a heating of the cooling medium, so that the respective heat exchanger for media-separated heating of the cooling medium, which then corresponds to a working medium, by means of the working medium, which then corresponds to a heating medium can be used.

A generic heat exchanger is for example from 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. Thus, the housing, the working medium and the cooling medium can be supplied and discharged therefrom. Further, 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 and a plurality of working medium pipes for guiding the working medium. The working medium pipes pass through the two floors and are also solid and tightly connected to the two floors to form the heat exchanger block. In the heat exchanger, a working medium path leads from the working fluid inlet inside through the working fluid tubes to the working fluid outlet. Further, a coolant path leads from the coolant inlet outside around the working fluid tubes to the coolant outlet. Via the walls of the working medium pipes, the heat transfer between the working medium flowing inside and the outside flowing cooling medium takes place. In the known heat exchanger of the respective bottom has a radially over the working fluid tubes protruding, peripheral edge, which is axially supported in each case via an axially acting ring seal at a circumferential edge of the housing along the respective edge. Further, in the known heat exchanger, the shell is formed of two half-shells, which are arranged axially between the two bottoms of the heat exchanger block and attached to each other. To this jacket are connected to the axial end faces a the Arbeitsmediumeinlass exhibiting inlet housing part or a Arbeitsmediumauslass exhibiting Auslassgehäuseteil, wherein in the respective connection region of the edge of the respective bottom is integrated with the associated ring seal. Accordingly, the housing-side step cooperating with the respective ring seal is formed on the inlet housing part and the outlet housing part, respectively. The known heat exchanger thus has a housing that has at least four separate components that must be assembled. Thus, the cost of implementing the known heat exchanger is relatively large.

From DE 10 2013 221 932 A1 another heat exchanger is known, in which the jacket is made in one piece, so that the heat exchanger block can be inserted axially into the shell. Furthermore, it is provided in this heat exchanger, in each case insert a metallic wall in an inlet region of the shell and in an outlet region of the shell in order to reduce the thermal load of the jacket made of plastic. In the two above-mentioned heat exchangers, it is possible to produce the heat exchanger block outside the housing in order then to 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 is often accompanied by a high thermal load, which is not feasible, for example, in a plastic jacket of the housing, and / or requires good accessibility, which does not exist within the housing is. For example, the working medium pipes must be passed tightly through the bottoms, so that solder joints or welded joints are used there. Depending on the intended use of the heat exchanger, very high temperatures may also be required for soldering, for example during brazing.

From DE 10 2006 051 000 A1 another heat exchanger is known in which the heat exchanger block is completed within the shell of the housing. In this case, during welding or soldering of the working medium pipes with the respective bottom cooling of the jacket in the region of the respective floor must be carried out in order to prevent damage to the shell. In other words, the production of the heat exchanger block within the housing is associated with increased effort.

In order to produce a heat exchanger as inexpensively as possible, the use of inexpensive materials, such as plastics and light alloys, is required. However, these inexpensive materials can not 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, in particular stainless steel, have a very high temperature resistance, but are then comparable. way expensive. However, the lowest possible weight for the heat exchanger is desirable in particular in vehicle applications.

Furthermore, it has been found that the use of axially acting annular seals between the edge of the respective bottom of the heat exchanger block and the respective stage of the housing is problematic because the heat exchanger block and housing during operation of the heat exchanger due to the different temperatures and the different coefficients of thermal expansion are different expand. In this case, the heat exchanger block and the housing relative to each other in the region of the respective bottom axially so far adjusted that the respective ring seal can no longer fulfill their sealing function.

The present invention is concerned with the problem of providing for a heat exchanger of the type mentioned an improved or at least another embodiment, which is characterized on the one hand by an inexpensive manufacturability and on the other hand by increased reliability in the ring seal.

This problem is solved according to the invention by the subject matter of the independent claim. Advantageous embodiments are the subject of the dependent claims.

The invention is based on the general idea to lock the heat exchanger block in the housing, such that in the region of the ring seal an axial contact and preferably an axial bias can be permanently ensured. In detail, the invention proposes to realize such a latching between housing and heat exchanger block in the region of the rear floor in order to axially bias the first ring seal provided there, art, that the first ring seal rests axially biased both at the edge of the rear floor and at the associated, formed on the housing stage. Thus, the sealing function of the first ring seal is guaranteed under all expected temperatures and operating situations.

For this purpose, the housing expediently has at least one latching contour in the region of the step, which cooperates with a counter-latching contour of the edge on a rear side of the edge of the rear base facing away from the first ring seal. The respective locking contour causes an axial positioning of the edge on the housing. This axial positioning on the one hand causes an axial fixation of the edge on the housing, which prevents the edge of an axial movement directed away from the step. On the other hand, this axial positioning for the edge defines an axial position relative to the housing, in which the first ring seal rests axially biased on the edge and on the step.

Suitably, a plurality of latching contours are provided, which are spaced apart 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 floor is improved on the housing.

In another embodiment, the respective latching contour can interact directly with the rear side of the edge, in which case the rear side of the edge itself forms the counter-latching contour together for all latching contours. This simplifies the production of the rear floor. In particular, the respective latching contour encompasses a radially outer edge of the edge.

Suitably, the respective latching contour may have a ramp on a side facing the working medium inlet. The ramp facilitates the axial insertion of the heat exchanger block passing over the respective locking contour by the edge of the rear floor, which precedes when inserting the heat exchanger block in the housing. After passing over the ramp, a substantially radially oriented locking lug adjoining the ramp of the latching contour engages behind the respective counter-latching contour and thus secures the edge against axial withdrawal from the housing counter to the direction of insertion.

In a further embodiment, the edge can be supported axially with a front side facing the first ring seal directly on the step. Thus, the edge is in the direction of insertion on the step and in the extension direction of the respective locking contour. As a result, a particularly efficient axial positioning of the heat exchanger block is achieved within the housing.

The first ring seal may for example be designed as a plastic seal. Plastic seals are characterized by a particularly high density. The two floors of the heat exchanger block the cooling medium path axially, so that the back of the edge is exposed directly to the cooling medium and cooled accordingly. The first ring seal thus cooperates with an actively cooled edge, whereby the thermal load of the ring seal is reduced.

If the first ring seal is designed as a plastic seal, the stage may expediently have a receiving groove, in which the first ring seal is inserted axially. In this way, the axial compression of the first ring seal can be limited to a permissible or predetermined extent. Furthermore, an efficient radial fixation or positioning for the first ring seal is made possible with the aid of the receiving groove.

In another embodiment, it can be provided that the edge is supported axially exclusively via the first ring seal at the step. This The design is characterized by a particularly simple geometry in the area of the step, which simplifies the production.

Another embodiment provides that the first ring seal is designed as a disk-shaped metal bead seal. Although such metal bead seals are not as dense as plastic seals, they have a significantly higher thermal resistance.

According to another advantageous embodiment, the working medium inlet can be formed integrally 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 connection flange can be a one-piece, integrally manufactured casting. This makes it possible to produce the connection flange and the jacket made of different materials. For example, the jacket may be a plastic part, while the connection flange is a metal part. The front bottom also has a radially over the working fluid tubes projecting, circumferential edge which is disposed axially between an axial shell end face of the shell and an axial Flanschstirnseite of the connection flange, so that he achieved with the attachment achieved by the attachment of the flange on the jacket in turn on the housing is fixed. Suitably, the edge of the front floor extends radially into the attachment, so that it is integrated into this attachment. In this way, the heat exchanger block is axially fixed in the region of the front floor by the attachment between the connection flange and jacket on the housing. In the area of the rear floor, the heat exchanger block is axially fixed by the latching on the housing.

Suitably, the coolant inlet and the coolant outlet as well as the respective catch contour and the step are integrally formed on the jacket. This simplifies the production of the housing is successful. Furthermore, the jacket can be made in one piece or in one piece, in particular as an integral casting.

In another embodiment, the heat exchanger can be configured in U-current construction. In this case, the Arbeitsmediumauslass is 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 deflection chamber to the working medium outlet. Furthermore, the housing is closed in the region of the deflection chamber by a housing bottom, which is expediently integrally formed on the jacket. This gives the housing a particularly inexpensive to manufacture, since it ultimately only the connection flange with working medium inlet and Arbeitsmediumauslass and the jacket with housing bottom, coolant inlet and coolant outlet comprises. The diverting chamber may be bounded directly by the shell and the housing bottom or bounded by a metal body which is inserted into the housing. Such a metal body can be used especially when the housing is made in the region of the jacket and housing bottom made of plastic and the expected temperatures in the deflection chamber are still relatively high.

However, an alternative embodiment in which the heat exchanger is designed in I-current design is particularly advantageous. In this case, the working fluid outlet is disposed axially opposite the working fluid inlet and may be further conveniently integrally formed on the shell. In this construction, too, the housing in an advantageous embodiment comprises only two components, namely the jacket with working medium outlet, coolant inlet, coolant outlet and the connection flange with working medium inlet. It is noteworthy that the presented here heat exchanger allows both in the U-current design as well as in the I-current construction, a production of the heat exchanger block outside the housing, which greatly simplifies the production of the heat exchanger block. The finished heat exchanger block can then be inserted into the housing by being axially inserted in the jacket in the absence of flange on the mantle end face. In this case, the heat exchanger block is inserted so far into the shell until the preceding during insertion preceding rear bottom latched edge with the respective locking contour. Subsequently, the connecting flange can be fastened to the jacket, whereby the heat exchanger block is fixed at the edge in the area of the front floor.

According to an advantageous development may be provided axially between the edge of the front bottom and the mantle end side an axially acting second ring seal. Additionally or alternatively, an axially acting third ring seal may be provided axially between the edge of the front floor and the flange face. In this case, the second ring seal and the third ring seal can optionally be configured 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 in each case as a plastic seal. Likewise, the second ring seal and the third ring seal may each be designed as a metal bead seal. It is also conceivable to carry out 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 carry out the second ring seal as a metal bead seal, while the third ring seal is designed as a plastic seal.

Particularly advantageous is an embodiment in which the heat exchanger block is made of an iron alloy, while the jacket of a Plastic or made of a light metal alloy. Since, in the heat exchanger presented here, the heat exchanger block can be completed outside the housing, the two floors and the working medium pipes can be joined with high accessibility, even at high temperatures, for example to solder or weld the working medium pipes to the floors. The jacket can be manufactured as an inexpensive casting made of plastic or light metal alloy and thereby integrally molding depending on the degree of integration and depending on the design with the coolant inlet, with the coolant outlet, the step and the respective locking contour. If the abovementioned connection flange is provided, this may likewise be made of an iron alloy or of a light metal alloy, depending on the expected thermal load of the hot working medium to be cooled. In an exhaust gas cooler, the connection flange is preferably made of an iron alloy.

In another embodiment, the edge of the rear floor may be axially raised radially inward from the step at ambient temperature and axially abut radially against the step at the operating temperature. This can be realized for example by a corresponding shaping of the soil in the region of the edge. For example, the edge of the rear floor with respect to a direction perpendicular to the axial direction plane to the rear, so directed away from the front floor, be inclined. During operation of the heat exchanger, the heat exchanger block expands axially stronger than the housing, whereby the above-mentioned inclination of the edge is always lower until the edge comes to rest axially at the operating temperature and radially inward at the stage.

Likewise, an embodiment is conceivable in which the edge of the rear floor has, radially inward, an axial distance from the step, which, in the case of a surrounding temperature is greater than at operating temperature. This means that the said axial distance decreases with increasing temperature and in extreme cases can assume the value zero, but does not have to. Thus, at high temperatures, especially in the upper range of the possible operating temperatures, radially inward axial contact between the edge and the step can occur, while at lower temperatures, which may still be in the operating temperature range, such an axial contact is omitted. This too can be realized by a corresponding shaping of the rear floor in the region of the edge.

Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components.

Show, in each case schematically,

1 is an isometric view of a heat exchanger,

2 shows an axial section of the heat exchanger, 3 is an enlarged detail III of Fig. 2,

4 to 5 each show a detailed view as in FIG. 3, but in other embodiments,

6 is an enlarged detail VI of FIG. 2,

7 to 9 each show a detailed view as in FIG. 6, but in other embodiments,

10 is a greatly simplified schematic representation of a heat exchanger in

I-flow design,

Fig. 1 1 is a greatly simplified schematic diagram of a heat exchanger in

U-flow design.

Referring to Figures 1 and 2, a heat exchanger 1 comprises a housing 2 and a heat exchanger block 3, which is located in the interior of the housing 2 and therefore is not visible in Fig. 1. 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. Furthermore, the heat exchanger block 3 a plurality of working fluid tubes 1 1 for guiding a working fluid 12, wherein the working fluid tubes 1 1 pass axially through the two floors 9, 10 and are firmly and tightly connected to the two floors 9, 10. In the example presented here, the working medium inlet 5 comprises an associated inlet nozzle and has a fastening flange which serves to connect the heat exchanger 1 to a working medium line carrying the working medium, such as a charge air line, an exhaust gas return line or an exhaust line. Also, the Arbeitsmediumauslass 6 here has an associated outlet nozzle and a mounting flange, which serves to connect the heat exchanger 1 to the working medium line. The cooling medium inlet 7 here comprises an associated inlet pipe which serves to connect the heat exchanger 1 to a cooling circuit leading to a coolant 13. Finally, here also the Kühlmediumauslass 8 has an associated outlet port, which serves to connect the heat exchanger 1 to the cooling circuit.

The working medium 12, which is indicated by arrows in FIGS. 1 and 2, may preferably be a gas, such as, for example, charge air, recirculated exhaust gas and exhaust gas. The heat exchanger 1 serves for media-separated cooling of the working medium 12 by means of a cooling medium , The cooling medium 13, which is indicated by arrows in FIGS. 1 and 2, can be a liquid, such as, for example, a cooling liquid of a cooling circuit of an internal combustion engine or of a motor vehicle equipped therewith. For the media-separated and heat-transmitting coupling, a working medium path 14 indicated by arrows and a cooling medium path 15 also 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 tubes 1 1 through the Arbeitsmediumauslass 6. The coolant path 15 leads from Kühlmitte- leinlass 7 outside around the working medium tubes 1 1 around the coolant outlet 8. The working medium tubes 1 1 are configured in the example shown each straight and parallel to each other and side by side, ie arranged radially next to each other, wherein radially between adjacent working medium tubes 1 1 Ranges 16 are formed, which are also flowed through by the cooling medium 13 of the cooling medium path 15.

FIG. 2 also shows that the working medium inlet 5 is expediently configured as a diffuser in order to distribute the supplied working medium 12 onto the working medium pipes 11.

According to FIGS. 2 to 5, the rear floor 10 has a circumferential edge region or edge 17 projecting radially beyond the working medium pipes 11. Along the edge 17, the housing 2 has a circumferential step 18. Axially between the edge 17 and the step 18 Now, a first ring seal 19 is arranged, which acts axially and thus seals the edge 17 relative to the step 18. The housing 2 now has at least one, but preferably several latching contours 20 in the region of this step 18. The respective latching contour 20 acts together with a counter-latching contour 21, which is located at the edge 17, wherein the latching contour 20 is axially supported on a rear side 22 of the edge 17 facing away from the first ring seal 19 on the counter-latching contour 21. Generally, with the aid of the respective catch contour 20, a catch 23 is provided for axially fixing the edge 17 to the step 18. The latching 23 prevents the edge 17 at an axial movement directed away from the step 18. Further, 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 biased on both the step 18 and the edge 17. In summary, this means that an axial positioning of the heat exchanger block 3 in the housing 2 is realized by the annular circumferential step 18. With the aid of the latching 23, an axial fixation of the heat exchanger block 3 in the region of the rear floor 10 is realized. Both measures make it possible to produce the heat exchanger block 3 outside of the housing 2. If, as here, a plurality of latching contours 20 are provided, these are spaced apart in the circumferential direction and 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.

As can be seen in particular from the enlarged views of FIGS. 3 to 5, the respective latching contour 20 preferably interacts directly with the rear side 22 of the edge 17, so that the edge 17 itself forms the counter-latching contour 21, specifically in the region of its radially outside lying outer edge. Accordingly, the locking contour 20 surrounds the edge 17 in the region of its outer edge.

In Figures 2 to 5, 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 and the edge 17 passes. It is clear that in reality instead the first ring seal 19 abuts axially on the edge 17, wherein a corresponding elastic deformation of the first ring seal 19 takes place.

In the example of Figure 3, the edge 17 is supported with its front side 25, which faces the first ring seal 19, directly on the step 18 axially. In this case, a receiving groove 26 is formed for the first ring seal 19 in the stage 18, in which the first ring seal 19 is inserted axially. In the example of Figure 3, the first ring seal 19 is designed as a plastic seal.

In the example of Figure 4, the edge 17 is supported exclusively on the first annular seal 19 on the step 18 axially. In this case, 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 Figure 3, in which the first ring seal 19 is designed as a plastic seal and is inserted into a receiving groove 26. However, it is also conceivable to apply the variant of FIG. 4 here as well, in which the first ring seal 19 is configured as a metal seal and in which the receiving groove 26 can be dispensed with. The peculiarity of the embodiment shown in Figure 5 is that the edge 17 is inclined relative to a plane extending perpendicular to the axial direction, so that it touches the step 18 only at the ambient temperature radially outward, while it lifts off radially from the step 18. This situation is shown in FIG. 5 by a solid line. At the same time, a situation is shown with a broken line, which sets at operating temperature. At operating temperature, the edge 17 is now also radially inward on the step 18 axially. In general, the edge 17 of the rear floor 10 radially inwardly may have an axial distance 27 from the step 18 which is greater at ambient temperature than at operating temperature.

It is also noteworthy that the rear floor 10 in the embodiments of Figures 2 to 5 is spatially shaped so that the cooperating with the step 18 and the first ring seal 19 edge 17 is axially offset to a bordered by the edge 17 area, with the Working medium tubes 1 1 is firmly connected. This offset takes place at the rear floor 10 to the outside, ie axially directed away from the working fluid pipes 1 first

According to Figures 1 and 2, the working medium inlet 5 is integrally formed on a connecting flange 28, which represents a separate component with respect to the jacket 4. In the example, the above-mentioned diffuser is thus formed in the connecting flange 28. This connection flange 28 is fastened by means of a fastening 29 on the jacket 4. The attachment 29 is here as Flanschverbin- Made with multiple screw 30 realized. According to FIGS. 2 and 6 to 9, the front bottom 9 has a circumferential edge 31 protruding radially over the working medium pipes 11. This edge 31 is arranged axially between an axial jacket end face 32 of the jacket 4 and an axial flange face 33. Furthermore, the edge 31 extends radially into the attachment 29. As a result, the edge 31 of the front bottom 9 is integrated into the attachment 29, so that by means of the attachment 29 on the one hand, the connecting flange 28 on the shell 4 and on the other hand, the heat exchanger block 3 are fixed to the housing 2.

While the working medium inlet 5 is integrated into the connecting flange 28, the coolant inlet 7 and the coolant outlet 8 as well as the latching contours 20 and the step 18 are integrated in the jacket 4.

In the example of Figures 1 and 2, the heat exchanger 1 is designed in I-flow design, which is characterized according to Figure 10 in that the working medium outlet 6 the working medium inlet 5 is axially opposite. In contrast, FIG. 11 shows a heat exchanger 1 in a U-flow design, which is characterized in that the working medium inlet 5 and the working medium outlet 6 are located at the same axial end of the housing 2 and are axially opposite a deflection chamber 34.

In the example of Figures 1 and 2, in which the heat exchanger 1 is designed in the I-flow design, it is also provided that the Arbeitsmedi- umauslass 6 is integrally formed on the jacket 4. In this case, the jacket 4 passes over a convergence region 35 in the Arbeitsmediumauslass 6. In the convergence region 35, a collecting chamber 36 is formed, in which the partial streams of the working medium 12 guided through the separate working medium tubes 11 are reunited and jointly flow to the working medium outlet 6. If, on the other hand, the heat exchanger 1 is configured in the U-current design, the working medium outlet 6 can also be formed integrally on the connection flange 28 in accordance with a preferred embodiment. The housing 2 then contains the deflection chamber 34. The working medium path 14 leads through at least one of the working medium tubes 1 1 from the working medium inlet 5 to the deflection chamber 34 and through at least one other of the working medium tubes 1 1 from the deflection chamber 34 to Arbeitsmediumauslass 6. The housing 2 is then in the area the deflection chamber 34 closed by a housing bottom 37. The housing bottom 37 is integrally formed on the jacket 4 in a preferred embodiment. The deflection chamber 34 may be limited by a metal housing, not shown here, which is inserted into the housing 2 and the casing 4 and the housing bottom 37 to the deflection chamber 34 out and protects against contact with the working medium 12.

According to FIGS. 2 and 6 to 9, an axially acting second annular seal 38 can be provided in the region of the front bottom 9 between the associated edge 31 and the jacket end face 32. Furthermore, axially between the edge 31 of the front bottom 9 and the flange face 33, an axially acting third ring seal 39 may be provided. The second ring seal 38 and the third ring seal 39 may be configured as a plastic seal or as a metal bead seal.

Figures 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. In contrast, FIG. 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 likewise configured as a metal bead seal.

By contrast, FIG. 8 shows an embodiment in which the second ring seal 38 is designed as a plastic seal, while the third ring seal 39 is configured as a metal bead seal.

Finally, FIG. 9 shows an embodiment in which the second ring seal 38 is designed as a metal bead seal, while the third ring seal 39 is configured as a plastic seal.

If the second ring seal 38 is designed as a plastic seal, as in the examples of FIGS. 2, 6 and 8, the shell end face 32 contains an associated receiving groove 40 into which the second ring seal 38 is inserted axially. If the third ring seal 39 is designed as a plastic seal, as in FIGS. 2, 6 and 9, the flange end face 33 contains a corresponding receiving groove 41 into which the third ring seal 39 is inserted axially.

The second ring seal 38 and the third ring seal 39 are also shown in the relaxed state in FIGS. 2 and 6 to 9, so that they seemingly protrude into the edge 31 of the front floor 9 or into the flange front side 33. In reality, this is not the case, but 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 and on the flange face 33 at.

It is also noteworthy that the front bottom 9 is shaped three-dimensionally, such that the edge 31 is offset axially relative to an inner region of the front bottom 9 that is annularly enclosed by the edge 31, wherein the internal rich firmly connected to the working fluid pipes 1 1. The axial offset takes place inwardly, ie in a working medium tubes 1 1 facing direction.

The metal bead seals shown in FIGS. 4 and 7 to 9 are each formed by a metal disc which extends annularly along the respective edge 17 or 31 and which has at least one axially projecting, closed circumferential sealing contour 42 which is pretensioned at the respective edge 17 , 31 or axially abuts the flange face 33. The respective sealing contour 42 is formed integrally on the metal disk in the manner of a bead by deformation. This sealing contour 42 may be arranged radially between an inner edge and an outer edge of the respective metal seal. In the examples shown here, only a single such sealing contour 42 is formed on each metal seal, in each case by an S-shaped angled region on the inner edge.

Preferred is now an embodiment in which the heat exchanger block 3, so the bottoms 9, 10 and the working medium tubes 1 1 are each made of an iron alloy. In this case, different iron alloys can certainly 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 added outside the housing 2, ie, in particular, welded or soldered. In contrast, the jacket 4 may be made of a plastic or a light metal alloy. The jacket 4 has integrally the latching 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 case of the I-current construction shown here, the working medium outlet 6 is optionally integrally formed with the transition region 35 on the jacket 4. The connecting flange 28 is preferably made of a metal. Depending on the field of application of the heat exchanger 1, a light metal alloy or likewise an iron alloy can be used. At the connection flange 28, the working medium inlet 5 is integrally formed in the I-flow construction. In the U-current construction, the connection flange 28 may additionally have the working medium outlet 6.

The respective annular seal 19, 38, 39 runs closed in the circumferential direction in an annular manner, but can, in principle, have any desired cross section transverse to its direction of rotation.

Claims

claims

1 . Heat exchanger for media-separated cooling of a working medium (12) by means of a cooling medium (13),

a housing (2) having 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),

- With a heat exchanger block (3) which is inserted into the housing (2) and a the working medium inlet (5) facing the front bottom (9) and a working medium inlet (5) facing away from the rear floor (10) and a plurality of working medium tubes (1 1 ) for guiding the working medium (12), which pass through the two floors (9, 10) and are firmly connected to the two floors (9, 10),

wherein a working medium path (14) leads from the working medium inlet (5) inside through the working medium tubes (1 1) to the working medium outlet (6),

wherein a coolant path (15) leads from the coolant inlet (7) on the outside around the working medium pipes (1 1) to the coolant outlet (8),

- Axially between a radially above the working fluid tubes (1 1) protruding, circumferential edge (17) of the rear floor (10) and along the edge (17) circumferential step (18) of the housing (2) an axially acting first annular seal ( 19) is arranged,

characterized,

in that the housing (2) has at least one latching contour (20) in the region of the step (18), which on a rear side (22) of the edge (17) remote from the first ring seal (19) has a counter-latching contour (21) of the edge (17). 17) cooperates.

2. Heat exchanger according to claim 1,

characterized,

in that a plurality of latching contours (20) are provided, which are distributed in the circumferential direction at a distance from one another along the edge (17).

3. Heat exchanger according to claim 1 or 2,

characterized,

the respective latching contour (20) interacts directly with the rear side (22) of the edge (17) as a counter-latching contour (21).

4. Heat exchanger according to one of claims 1 to 3,

characterized,

in that the edge (17) is axially supported directly on the step (18) by means of a front face (25) facing the first ring seal (19).

5. Heat exchanger according to one of claims 1 to 4,

characterized,

that the first ring seal (19) is designed as a plastic seal.

6. Heat exchanger according to claim 5,

characterized,

the step (18) has a receiving groove (26) into which the first ring seal (19) is inserted.

7. Heat exchanger according to one of claims 1 to 3,

characterized,

in that the edge (17) is axially supported only on the first ring seal (19) on the step (18).

8. Heat exchanger according to one of claims 1 to 3 and 7, characterized

that the first ring seal (19) is designed as a disc-shaped metal bead seal.

9. Heat exchanger according to one of claims 1 to 8,

characterized,

that the working medium inlet (5) is formed integrally on a connecting flange (28) which is a separate component with respect to the jacket (4) and which is fastened to the jacket (4) by means of a fastening (29),

- that the front bottom (9) has a radially over the working medium tubes (1 1) projecting, circumferential edge (31) axially between an axial jacket end face (32) of the shell (4) and an axial Flanschstirnseite (33) of the connecting flange ( 28) is arranged and which can be incorporated into the attachment (29).

10. Heat exchanger according to one of claims 1 to 9,

characterized,

the cooling medium inlet (7) and the cooling medium outlet (8) and the respective latching contour (20) and the step (18) are formed integrally on the jacket (4).

1 1. Heat exchanger according to claims 9 and 10,

characterized,

- That the heat exchanger (1) is designed in U-current construction,

- That the Arbeitsmediumauslass (6) is integrally formed on the connecting flange (28),

- That in the housing (2) a deflection chamber (34) is provided, - That the working medium path (14) through at least one Arbeitsmediunnrohr (1 1) from the working medium inlet (5) leads to the deflection chamber (34) and through at least one other working medium tube (1 1) from the deflection chamber (34) to the working medium outlet (6) .

- That the housing (2) in the region of the deflection chamber (34) by a housing bottom (37) is closed, which is integrally formed on the jacket (4).

12. Heat exchanger according to claims 9 and 10,

characterized,

- That the heat exchanger (1) is designed in I-current construction,

- That the Arbeitsmediumauslass (6) axially opposite the working medium inlet (5) and is integrally formed on the jacket (4).

13. Heat exchanger according to one of claims 9 to 12,

characterized,

- That axially between the edge (31) of the front bottom (9) and the mantle end face (32) is provided an axially acting second annular seal (38),

- that axially between the edge (31) of the front floor (9) and the

Flange end face (33) an axially acting third ring seal (39) is provided.

14. Heat exchanger according to one of claims 1 to 13,

characterized,

that the heat exchanger block (3) is made of an iron alloy,

- That the jacket (4) is made of a plastic or a light metal alloy.

15. Heat exchanger according to one of claims 1 to 14,

characterized, - That the edge (17) of the rear floor (10) at ambient temperature radially inwardly from the step (18) axially lifts and at the operating temperature radially inwardly of the step (18) axially abuts, and / or

- That the edge (17) of the rear floor (9) radially inward an axial distance (27) from the step (18) which is greater at ambient temperature than at the operating temperature.