JP2009517625A - Cooling device used for internal combustion engine - Google Patents

Abstract

  A cooling device is proposed. This cooling device can be manufactured by die casting and has a heat transfer unit (1; 27, 28) surrounded by an outer shell (14; 31). In this case, a jacket (20) through which a refrigerant flows is formed between the heat transfer unit (1; 27, 28) and the outer shell (14; 31). In this jacket (20), a passage (21; 33) through which refrigerant flows is formed between the outer shell (14; 31) and the outer housing (2) of the heat transfer unit (1; 27, 28). Thus, it is divided by the web (3, 4, 5, 6; 29, 30, 34, 35, 36, 37). For this purpose, the webs (3, 4, 5, 6; 29, 30, 34, 35, 36, 37) are arranged so that the circulation is performed in a meander shape. Thereby, the freedom degree regarding arrangement | positioning of a refrigerant | coolant inlet (12; 32) and a refrigerant | coolant outlet (13; 38) is acquired compared with a spiral flow. Furthermore, this type of cooling device can be manufactured and assembled at low cost, and has high efficiency.

Description

  The present invention relates to a cooling device, particularly an exhaust gas cooling device used for an internal combustion engine, wherein an outer shell is provided, and at least one heat transfer unit is disposed in the outer shell. The outer housing has a jacket formed between the outer shell and the heat transfer unit, which is formed between the outer shell and the heat transfer unit, and is formed in the heat transfer unit. In which the web is disposed between the outer shell and the outer housing of the heat transfer unit, and the web partitions the passage through which the refrigerant flows in the jacket. About.

  This type of cooling device is used in an internal combustion engine as an exhaust gas cooling device for reducing harmful substance emissions by, for example, cooling exhaust gas, mixing it with newly sucked air, and supplying it to a cylinder. used. This temperature drop of the cylinder filling reduces harmful substance emissions. For this purpose, different configurations of the cooling device have been filed.

  In many of these cooling devices, a dead zone or vortex in the jacket through which the refrigerant flows is a problem. In this dead zone, refrigerant replacement is not performed. This significantly reduces the efficiency of the cooling device. In addition, the boiling of the refrigerant can cause damage to the cooling device.

  In order to avoid such dead water areas and increase the efficiency of the heat exchanger, a cooling device having forced refrigerant guidance has been developed.

  Thus, German Offenlegungsschrift 20 474 474 discloses a separating wall for use in a cooling device. This separation wall is arranged in the refrigerant jacket and defines a passage through which it flows. This cooling device is formed in a cylindrical shape. In this case, the web for forcibly guiding the refrigerant flow is formed from a separating plate that is disposed supplementarily to the heat exchanger unit located inside. The separator plate spirally surrounds the inner heat exchanger unit, thereby providing a spiral-shaped forced guide around the heat exchanger unit.

  A similar arrangement is also known from German Offenlegungsschrift 20 2004008737. This known specification also discloses a cylindrical heat exchanger. The separation wall of the heat exchanger is arranged in a spiral shape, that is, spirally around the inner passage. This separation wall is formed by a wire. This wire is approximately square. This wire is then fixed in material connection to the inner tube, ie the heat exchanger unit.

  In such a configuration, it is disadvantageous that the heat exchanger unit is defined with respect to the arrangement of the refrigerant inlet and the refrigerant outlet at the time of such a helical forced guide. During the spiral recirculation of the inner heat exchanger unit, the inlet and outlet for the refrigerant must be located at the axial end of the heat exchanger.

  Further, it is extremely technically difficult to manufacture the inner heat exchanger unit in a rectangular shape, for example, in a rectangular parallelepiped shape or from a plurality of parts, or to arrange a plurality of heat exchanger units in one outer shell. It is disadvantageous that it is possible only with difficulty and effort. In this case, it is desirable that each heat exchanger unit be as forcedly refluxed as possible. In such a case, the helical courses of the webs separating the passages provided in both parts can correspond exactly to each other, so that there are no tears or voids between the individual members. It becomes.

  Therefore, the subject of this invention is providing the cooling device with a refrigerant | coolant forced guide which has a high freedom degree regarding arrangement | positioning of a refrigerant | coolant inlet and a refrigerant | coolant outlet. In this case, it is desirable that the multi-division property of the inner heat exchanger unit can be easily obtained at the same time. Furthermore, it is desirable to be able to arrange, for example, a plurality of heat exchanger units that are individually forced to reflux as completely as possible in one housing.

  This problem is solved by disposing a web that partitions the passage through which the refrigerant flows, so that the heat transfer unit is forcedly circulated in a meander shape. With this meander-shaped recirculation, the arrangement of the inlet and outlet can be freely selected as well as the shape of the cooling device and the heat exchanger unit. Even in the multi-partition nature of the heat exchanger unit, the web can be made with the heat transfer unit easily and without misalignment.

  In an advantageous configuration, an axially extending first web is arranged between the outer shell and the outer housing of the heat transfer unit, from which a circumferentially extending web is connected to the axially extending web. Alternately extending from both sides around the heat transfer unit, the circumferentially extending web is advantageously at the front of the axially extending web, with a spacing corresponding to the spacing between the circumferentially extending webs. It's over. In such a configuration, there are only webs arranged perpendicular to each other. These webs can be placed easily and accurately with respect to each other even in the case of the multi-partition of the heat transfer unit, so that the dead zone is completely avoided. In such a type of cooling device, the refrigerant inlet is disposed at the first axial end portion of the cooling device, and the refrigerant outlet is disposed at the axially opposite end portion. . There is a high efficiency and thus high efficiency of the heat transfer unit over the entire circumference.

  In an alternative configuration, two axially extending webs arranged on opposite sides are formed between the outer shell and the outer housing of the heat transfer unit. The first web ends in front of the last axial section of the cooling device, and from both webs, alternately in the axial direction, the first web extending in the axial direction and the second extending in the axial direction. A web extending circumferentially from the web extends around the heat transfer unit from both sides of each axially extending web, and the circumferentially extending web is advantageously at a distance between the circumferentially extending webs. It ends in front of the other web, each extending in the axial direction, with a corresponding spacing. With such a configuration, the refrigerant inlet and the refrigerant outlet can be arranged at the same end in the axial direction of the cooling device, whereby the cooling device is first circulated in a meander shape at the first half thereof. Then, it is circulated in a meander shape in its second half. In this type of configuration, the flow of the heat transfer unit can also be selected correspondingly in a u-shape, so that the cooling device can be operated in both countercurrent and parallel flow. The web-to-web arrangement remains easily formable, and a dead space is avoided.

  In another alternative configuration, two heat transfer units are arranged in one outer shell, and between each heat transfer unit, each heat transfer unit is forced through the entire surface as viewed in cross section. As is, the web is formed. In such cases, it is a two-stage cooler. This cooler is formed with a smaller length in the axial direction, which again has the advantage that there is a significantly higher degree of freedom with respect to the construction space compared to a cooler that is forced to recirculate in a spiral manner. is doing.

  Such a full recirculation is achieved by the fact that both heat transfer units are recirculated in the form of the numeral 8 as viewed in cross section. Thus, additional forward and reverse flows are avoided and the refrigerant inlet passage and the refrigerant outlet passage can be arranged on opposite sides of the heat transfer unit in the axial direction.

  In an advantageous configuration of this type, one axially extending web is arranged between the outer shell and each heat transfer unit, the two axially extending webs being opposite to each other of the jacket. Webs extending in the circumferential direction are alternately extended around the heat transfer unit from both sides of the web extending in the axial direction, and first webs extending in the circumferential direction are arranged on the circumferential surface located on the side. Ends in front of the first web extending in the axial direction with a predetermined spacing, and each second web extending in the circumferential direction is in front of the second web extending in the axial direction with a predetermined spacing It ends with. Such a configuration ensures a particularly simple recirculation of the two-stage heat exchanger in the form of the numeral 8.

  In an advantageous configuration, the heat transfer unit is manufactured by a die casting process, which makes the heat transfer unit lighter, for example when using aluminum die casting or magnesium die casting, but nevertheless can be manufactured inexpensively. At the same time, the heat transfer unit is suitable for high temperatures.

  In an advantageous configuration, the heat transfer unit is formed from an upper part and a lower part, both parts being connected to each other by welding, in particular friction stir welding. This friction stir welding is particularly suitable for use with a magnesium die cast cooler or an aluminum die cast cooler. An additional bulge or eyelet for screw fastening, as is known for joining the two parts together in another cooling device, is not necessary here, so that despite being very small, Close assembly is ensured without additional sealing elements.

  Advantageously, the web is at least partly arranged in the outer housing of the heat transfer unit, so that no additional insertion members are necessary to ensure a working forced guide. In this case, in the die casting method, these webs can be produced together with the heat transfer unit in a single production step.

  In a subsequent or alternative configuration, the outer shell is formed from at least two parts and is manufactured by die casting, and the web is formed at least partially on the inner wall of the outer shell. Of course, in such a configuration, the web may be completely formed in the outer shell and reach the outer wall of the heat transfer unit. Intermediate dissociation is also possible, whereby a web is formed partly on the outer housing of the heat transfer unit and partly on the inner wall of the outer shell made from two parts. In both cases, additional inserts and thus manufacturing steps are avoided.

  In a subsequent configuration, the web is mainly formed in the outer housing of the heat transfer unit and has a break in the coupling area between the upper part and the lower part. In the closed state, the outer shell is closed by a corresponding web. Such a configuration is particularly advantageous in a heat transfer unit consisting of several parts. The heat transfer unit is then welded. This usually requires a space in order to be able to apply a corresponding welding tool in the area between the individual members of the heat transfer unit. Nevertheless, in order to avoid refrigerant overflow in the assembled state at this point, the interrupting part is consciously cut out in the heat transfer unit and a corresponding web placed on the inner wall of the outer shell. In the assembled state, it is filled again, so that there is no region with a stationary refrigerant.

  On the other hand, in an alternative configuration, the web is formed with a smooth passage in the cross-section in the connection region between the upper part and the lower part of the heat transfer unit. This certainly causes a slight pressure loss in the refrigerant jacket, since the cross section is no longer equal over the course, but this type of configuration provides a reliable separation of the passageway by the web. It is possible to guide the welding tool through a web gently formed in this area without breaking.

  The cooling device according to the invention has a high efficiency. In this case, the structure size and the arrangement of the refrigerant inlet and the refrigerant outlet can be selected almost freely. This type of cooling device can be easily and inexpensively manufactured and assembled without the need to use additional components.

  Three examples are shown in the drawings and are described below.

  1 to 3 show a heat transfer unit 1 of a cooling device usually surrounded by an integral outer shell (not shown). The heat transfer unit 1 has an outer housing 2. In the outer housing 2, webs 3, 4, 5, and 6 are formed. The webs 3, 4, 5 and 6 serve for forced circulation of the heat transfer unit 1. The height of the webs 3, 4, 5 and 6 corresponds to the distance between the inner wall of the outer shell and the outer housing 2 of the heat transfer unit 1, whereby heat transfer with the outer shell (not shown). The jacket formed between the unit 1 is divided by the webs 3, 4, 5, 6 into a continuously extending passage 7.

  Inside the heat transfer unit 1, a passage through which exhaust gas flows is formed. In this passage, for example, ribs for better heat transfer may be arranged. In this embodiment, the heat transfer unit 1 is formed in a u-shape. This is because at least one web extending in the axial direction is formed inside the heat transfer unit 1, this web being interrupted in the rear region, thus enabling a change of the exhaust gas flow. It means that. Correspondingly, the exhaust gas inlet 8 and the exhaust gas outlet 9 are formed at the same axial end of the heat transfer unit 1.

  Now, mainly in order to be able to guide the refrigerant flow in the opposite direction to the exhaust gas flow or along with the exhaust gas flow along the heat exchanger unit 1, the webs 3, 4, 5, 6 are connected to the heat transfer unit 1. Is first forcedly circulated in a meander shape in the first half 10 and then forcedly circulated in a meander shape in the opposite direction in the second half 11, whereby the refrigerant inlet 12 and the refrigerant outlet 13 Are arranged at the same end in the axial direction of the heat transfer unit 1.

  For this purpose, two webs 3, 4 extending in the axial direction are formed in the outer housing 2 of the heat transfer unit 1. Of the two webs 3, 4, the first web 3 extending in the axial direction is located on the upper surface of the heat transfer unit 1 shown in FIG. 1, and the second web 4 extending in the axial direction is heat transfer. The unit 1 is located on the lower surface shown in FIG. The webs 5 and 6 extend alternately from both webs 3 and 4 extending in the axial direction in the circumferential direction on both sides of both webs 3 and 4 when viewed in the axial direction. The webs 5 and 6 terminate in front of axially extending webs 4 and 3 arranged on opposite sides. In this case, the distance between the ends of the circumferential webs 5, 6 and the associated axial webs 3, 4 respectively corresponds to the distance between two successive webs 5, 6 extending in the circumferential direction. As a result, only a slight pressure loss is generated.

  Now, the course of the refrigerant becomes clear with reference to FIGS. Via the refrigerant inlet 12, the refrigerant flows in the direction of the axial web 3 that can be seen in FIG. 1 and passes between the end of the web 6 extending in the circumferential direction and the web 3 extending in the axial direction. And flows between the webs 5 and 6 extending in the circumferential direction. From here, the refrigerant flows to the lower surface of the heat transfer unit 1 shown in FIG. 3 along the side wall shown in FIG. Here, the flow is again redirected in the axial direction, so that the refrigerant is redirected again by 90 ° between the end of the web 5 extending in the circumferential direction and the end of the web 4 extending in the axial direction. And return to the upper surface between the two webs 5 and 6. Now, this meandering motion continues to the other end of the heat transfer unit 1 in the axial direction by repeated turning. Thus, the refrigerant can flow on the opposite side of the heat transfer unit 1 on the upper surface of the heat transfer unit 1 that can be seen in FIG. This is because the web 3 extending in the axial direction is interrupted in this region. From now on, meander-like movements are subsequently carried out to the outlet 13 around each half of the cross section of the heat transfer unit 1.

  4 and 5 show a similar cooling device. In this case, the outer shell 14 opened in FIG. 4 is also shown here. A double web 15 is formed on the inner wall of the outer shell 14. The double web 15 engages the webs 3, 4, 5, 6 so as to surround the webs 3, 4, 5, 6 so that a reliable sealing is achieved. In order to be able to accomplish this, the outer shell is formed from an upper part 16 and a lower part 17, as can be seen in FIG.

  As is clear from FIGS. 1 to 3, the heat exchanger unit 1 is also formed by an upper part 18 and a cover-like lower part 19 from two parts. The recirculation of the cooling device shown in FIGS. 4 and 5 is performed in the same manner as the recirculation described in conjunction with FIGS. In this case, the jacket 20 can also be recognized in this figure, and the inner passage 21 through which the exhaust gas flows can be recognized in FIG. In the passage 21, ribs 22 extend from both portions 18 and 19 into the passage 21. The intermediate rib 23 is also apparent. The rib 23 separates the first half 10 that is initially flowed from the second half 11 that is flowed in the opposite direction.

  As apparent from FIG. 4, webs 5, 6 extending in the circumferential direction have interruption portions 24 in the region of the outer edge portion of the cover-like lower portion 19 of the heat transfer unit 1. The interrupting portion 24 exists because the welding tool performs welding that requires a sufficient free space when the lower portion 19 is fixed to the upper portion 18. The discontinuous course of the ribs 5 and 6 at this point will probably make accurate and dense welding impossible without breaking the ribs 5 and 6. For this reason, this existing interruption 24 is blocked during the assembly of the cooling device by a short web 25 arranged on the outer shell 14. Such a web can be seen especially in FIG.

  In the heat transfer unit shown in FIGS. 1 to 3, this problem is that the area between the upper part 18 and the lower part 19 of the heat transfer unit 1, which is required as a free passage for the tool during the welding process, is outside. This was solved in another form by being formed continuously and smoothly around the ribs 5 and 6 arranged in the housing 2. As a result, a wavy cross section apparent in FIG. 2 is formed on the lower surface. This has the advantage that, for example, a friction stir welding process can be performed without interruption of the ribs 5 and 6, but in order to avoid a flow loss, the refrigerant passage 20 can flow. The cross-section must be kept equal, which has the disadvantage that an accurate calculation of the existing surface must be carried out and must be realized in the casting.

  Further, as can be seen in FIGS. 4 and 5, the cooling device is secured to the original cooling device by means of mounting members 26. An exhaust gas inlet 8 and an exhaust gas outlet 9 are formed in the mounting member 26.

  It is clear that a reliable forced circulation in the meander shape of the heat transfer unit 1 is achieved by both configurations. In this case, the refrigerant inlet 12 and the refrigerant outlet 13 are disposed at the same end in the axial direction of the heat exchanger unit 1. As a precaution, it is also possible to arrange the refrigerant inlet 12 and the exhaust gas inlet 8 and the refrigerant outlet 13 and the exhaust gas outlet 9 at the end of the cooling device that is located on the opposite side in the axial direction. This is possible during reflux. Perhaps only one axial web is required in this case, and it is only necessary to have circumferentially extending webs extending alternately on both sides from this axial web, respectively to the axial web. It only needs to be finished before another collision.

  Another configuration of a cooling device according to the present invention is shown in FIG. The progress of the refrigerant is illustrated by arrows. The component or flow present on the back side is characterized by a dashed line.

  This cooling device has two heat transfer units 27 and 28 inside. Both the heat transfer units 27 and 28 are forcibly recirculated over their peripheral surfaces. This reflux takes place in the form of the number 8. For this purpose, each heat transfer unit 27, 28 has a web 29, 30 extending in the axial direction. The webs 29 and 30 extend from one end in the axial direction to the other end. Both webs 29, 30 extending in the axial direction are located on the circumferential surface located on the opposite side of the cooling device after assembly into the outer shell 31, whereby the web 29 extending in the axial direction is broken. It is shown by.

  The refrigerant inlet 32 is again located on the surface located on the opposite side of the drawing. From there, the refrigerant flows around the first heat transfer unit 27 in the circumferential direction. From here, the refrigerant continues to flow between the first heat transfer unit 27 and the second heat transfer unit 28. This is because the subsequent path is interrupted by the web 30. Subsequently, the refrigerant flows on the surface of the cooling device on the side opposite to the drawing, and flows in the circumferential direction around the second heat transfer unit 28. A side partition of the passage 33 through which the refrigerant flows is formed by a web 34 extending in the circumferential direction and a web 35 extending in the circumferential direction. The web 34 extends around the entire heat transfer unit 27. Although the web 35 extends around the entire heat transfer unit 28, it terminates prior to the collision with the axial web 30. Accordingly, the circumferential flow ends at the axial web 30. Therefore, the direction of the refrigerant is changed, and this refrigerant continues to flow in the axial direction between the web 30 extending in the axial direction and the web 35 extending in the circumferential direction. Now, the refrigerant undergoes a change again. This is because the axial flow is interrupted by the web 36. The web 36 extends around the heat transfer unit 28 in the circumferential direction. The refrigerant is partitioned by the webs 35, 36 and flows around the second heat transfer unit 28, and from here, based on the resistance of the second web 29 in the axial direction, the both heat transfer units 27, 28 are now again. Flows through the plane corresponding to the drawing.

  In this way, the further progress of the refrigerant is also performed toward the refrigerant outlet 38 through the web 37 provided in the first heat transfer unit 27 and ending in front of the web 30 on the back side again. The web 42 between the two heat transfer units 27, 28, which is required for this purpose, may optionally be formed on one or both of the heat transfer units 27, 28. In the embodiment shown in FIGS. 6 and 7, the heat transfer units 27 and 28 have a common housing 39. The housing 39 is closed on the opposite side by cover elements 40 and 41, respectively, whereby a web 42 between the heat transfer units 27 and 28 is formed integrally with the housing 39. .

  Therefore, when the exhaust gas outlet of the first heat transfer unit 27 and the exhaust gas inlet of the second heat transfer unit 28 are connected, there is no need to extend the cooling device in the axial structural length, and a cooling section for the exhaust gas is formed. Can be doubled.

  For the sake of clarity, such meandering forced circulation of the cooling device ensures the advantage of a completely freely selectable arrangement of the refrigerant inlets 12, 32 and the refrigerant outlets 13, 38. Due to this forced circulation, a high efficiency of the cooling device thus formed is obtained. The assembly and production costs compared to known configurations are significantly reduced. To what extent it is free whether the existing web is formed in the outer shell or in the outer housing of the heat transfer unit or possibly applied as an individual component. The external shape of the heat transfer unit is also sufficiently free by such an arrangement of the passage for guiding the refrigerant by the web.

It is a top view of the heat transfer unit of the cooling device by this invention. It is a side view of the heat transfer unit shown in FIG. It is the figure which looked at the heat-transfer unit of FIG. 1 and FIG. 2 from the downward direction. FIG. 2 is a view from below of an alternative cooling device with a two-part outer housing, in which part of the outer shell is shown cut away. It is a figure which cuts and shows the front view of the cooling device shown in FIG. It is a figure which partially cuts and shows the top view of the 3rd structure of the cooling device by this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Heat transfer unit, 2 Outer housing, 3 Web, 4 Web, 5 Web, 6 Web, 7 Passage, 8 Exhaust gas inlet, 9 Exhaust gas outlet, 10 Half, 11 Half, 12 Refrigerant inlet, 13 Refrigerant outlet, 14 Outer Shell, 15 Double web, 16 Upper part, 17 Lower part, 18 Upper part, 19 Lower part, 20 Jacket, 21 Passage, 22 Rib, 23 Rib, 24 Interruption part, 25 Web, 26 Mounting member, 27 Heat Transfer unit, 28 heat transfer unit, 29 web, 30 web, 31 outer shell, 32 refrigerant inlet, 33 passage, 34 web, 35 web, 36 web, 37 web, 38 refrigerant outlet, 39 housing, 40 cover element, 41 cover element 42 web

Claims (12)

  A cooling device, particularly an exhaust gas cooling device used in an internal combustion engine, wherein an outer shell is provided, and at least one heat transfer unit is disposed in the outer shell, and the heat transfer unit includes an outer housing. The outer housing has a jacket formed between the outer shell and the heat transfer unit that is circulated by the refrigerant, formed in the heat transfer unit, from a passage through which a fluid to be cooled flows. In a separate type, a web is arranged between the outer shell and the outer housing of the heat transfer unit, the web partitioning a passage through which the coolant flows in the jacket. The webs (3,4,5,6; 29,30,34,35,36) so that the units (1; 27,28) are forced to recirculate in a meander shape. Characterized in that 37) is arranged a cooling device.   A first web extending in the axial direction is disposed between the outer shell and the outer housing of the heat transfer unit, from which the circumferentially extending web is heated alternately from both sides of the axially extending web. The circumferentially extending webs extending around the transmission unit advantageously end in front of the axially extending webs with a spacing corresponding to the spacing between the circumferentially extending webs. Item 2. The cooling device according to Item 1.   Between the outer shell (14) and the outer housing (2) of the heat transfer unit (1), two axially extending webs (3, 4) arranged on opposite sides are formed. Of the webs (3, 4), the first web (3) ends in front of the last axial section of the cooling device, from both webs (3, 4) alternately in the axial direction, A web (5, 6) extending circumferentially from a first web (3) extending in the axial direction and a second web (4) extending in the axial direction is provided for each web (3, 4) extending in the axial direction. The webs (5, 6) extending around the heat transfer unit (1) from both sides and extending in the circumferential direction preferably have a distance corresponding to the distance between the webs (5, 6) extending in the circumferential direction. 2 and ending in front of the other web (4, 3), each extending axially. Mounting the cooling device.   Two heat transfer units (27, 28) are arranged in one outer shell (31), and between the heat transfer units (27, 28), each heat transfer unit (27, 28) The cooling device according to claim 1, wherein the web (29, 30, 34, 35, 36, 37) is formed so as to be forced to circulate over the entire surface as viewed in cross section.   5. Cooling device according to claim 4, wherein both heat transfer units (27, 28) are circulated in the form of the numeral 8 as viewed in cross section.   One web (29, 30) extending in the axial direction is arranged between the outer shell (31) and each heat transfer unit (27, 28), and both webs (29, 30) extending in the axial direction are arranged. Are arranged on the circumferential surfaces of the passages (33) located on opposite sides of the passage (33), and the circumferentially extending webs (34, 35, 36, 37) of the axially extending webs (29, 30) First webs 34, 35 extending in the circumferential direction alternately from both sides and extending in the circumferential direction are spaced apart from each other by the first webs extending in the axial direction. Ending in front of (30), each second web (36, 37) extending in the circumferential direction ends in front of the second web (29) extending in the axial direction at a predetermined interval. The cooling device according to claim 4 or 5.   The cooling device according to any one of claims 1 to 6, wherein the heat transfer unit (1, 27, 28) is manufactured by a die casting method.   A heat transfer unit (1, 27, 28) is formed from an upper part (18) and a lower part (19), both parts (18, 19) being joined by welding, in particular friction stir welding. The cooling device according to any one of claims 1 to 7.   Webs (3, 4, 5, 6; 29, 30, 34, 35, 36, 37) are at least partially formed in the outer housing (2) of the heat transfer unit (1; 27, 28), The cooling device according to any one of claims 1 to 8.   The outer shell (14) is made of at least two parts and is made by die casting, and the web (15, 25) is at least partly formed on the inner wall of the outer shell (14); The cooling device according to any one of claims 1 to 9.   The webs (3,4,5,6) are mainly formed in the outer housing of the heat transfer unit (1) and are interrupted in the connection area between the upper part (18) and the lower part (19). 11. The device according to any one of claims 1 to 10, wherein the suspension (24) is closed by the corresponding web (25) of the outer shell (14) in the assembled state. The cooling device according to claim 1.   A web (5, 6) is formed in the joining region between the upper part (18) and the lower part (19) of the heat transfer unit (1), with a gentle passage as seen in cross section, The cooling device according to claim 9.

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