Heat exchanger for internal combustion engines with reinforcing elements on the joint area of two partition walls and internal combustion engine with heat exchanger

Abstract

The invention relates to a heat exchanger for an internal combustion engine for transferring heat between fluids, having a housing with a housing wall and a housing interior which is at least partially delimited by the housing wall. The housing interior has a fluid inlet region for introducing a first fluid of the fluids into the housing interior and a fluid outlet region for discharging the first fluid from the housing interior. The heat exchanger comprises at least two partition walls, each of which is at least predominantly accommodated in the housing interior and is connected to the housing wall of the housing at at least one connection region. In order to separate the fluids from one another, the partition walls at least partially delimit a fluid accommodation chamber which can be flowed through by a second fluid of the fluids. The partition walls are connected to one another at least at a joint region which is assigned to the fluid inlet region and which adjoins the fluid accommodation chamber in the fluid main flow direction of the first fluid. Furthermore, the heat exchanger comprises a reinforcing element which is arranged on the joint region in order to reinforce a reinforcing section of the joint region which adjoins the connection region and is designed to support the reinforcing section at least against a bending load which is caused by a length change of the joint region when the joint region is subjected to a temperature-induced length change.

Description

Technical Field

[0001] This invention relates to a heat exchanger for an internal combustion engine, which transfers heat between at least two fluids. Another aspect of the invention relates to an internal combustion engine having a heat exchanger. Background Technology

[0002] Such heat exchangers (also called heat exchangers) are used to transfer heat between fluids. For example, so-called oil-coolant-heat exchangers are commonly used to cool the engine oil in internal combustion engines. During a cold start of the internal combustion engine, the oil-coolant-heat exchanger can also be used to heat the engine oil and thereby accelerate the so-called hot run of the internal combustion engine. Heat exchangers used in internal combustion engines can also directly contribute to the low untreated emissions of the internal combustion engine. An example of this is cooled exhaust gas recirculation (also simply EGR), in which a portion of the exhaust gas emitted during the operation of the internal combustion engine is extracted from the engine's exhaust system, cooled by means of a heat exchanger configured as an AGR cooler, and then supplied to the engine's intake system. The cooled portion of the exhaust gas then reaches the corresponding combustion chamber of the internal combustion engine and is used as so-called ballast gas during the combustion of the air-fuel mixture, thereby significantly reducing untreated NOx emissions.

[0003] A heat exchanger for exchanging heat between a first fluid and a second fluid is disclosed in DE102016210261A1, wherein the heat exchanger for the first fluid is capable of flowing from a first end side to a second end side. The heat exchanger has at least two partition plates that separate flow regions within the heat exchanger for the first fluid and the second fluid from each other. At least two adjacent partition plates each have a connection region on at least one end side of the heat exchanger, in which the partition plates are connected to each other by a connection portion. The connection portion has at least one notch on the end side. Summary of the Invention

[0004] The objective of this invention is to provide heat exchangers and internal combustion engines of the type described at the beginning, which are capable of achieving particularly resistant heat transfer between fluids.

[0005] This task is accomplished by the heat exchanger according to the invention and by the internal combustion engine according to the invention.

[0006] A first aspect of the invention relates to a heat exchanger for an internal combustion engine for transferring heat between at least two fluids, said heat exchanger comprising:

[0007] - At least one housing having at least one housing wall and a housing cavity defined at least partially by means of the housing wall, the housing cavity having a fluid inlet region for introducing a first fluid of the at least two fluids into the housing cavity and a fluid outlet region for discharging the first fluid from the housing cavity;

[0008] - At least two partition walls, which are at least primarily housed within the cavity of the housing and connected to the housing wall at at least one connection region, and which at least partially define a fluid-containing cavity through which a second of the at least two fluids can flow in order to separate the fluids from each other, wherein the at least two partition walls are connected to each other at least in an engagement region disposed in the fluid inlet region and adjacent to the fluid-containing cavity in the main flow direction of the first fluid.

[0009] The fluid can be, for example, exhaust gas and coolant, especially cooling water. The first fluid can be configured as exhaust gas, and the second fluid can be configured as coolant. The fluid discharge region can be opposite the fluid inlet region in the main flow direction of the first fluid. The term "main flow direction" can be understood as the flow direction of the first fluid, which flows primarily in the heat exchanger during conventional use.

[0010] When the heat exchanger is used as specified, the first fluid enters the shell cavity in the fluid inlet area and exits from the shell cavity in the fluid outlet area. Furthermore, the second fluid is guided and thus contained in the fluid containment cavity during conventional use of the heat exchanger. To achieve the highest possible heat transfer coefficient, it is particularly advantageous to guide the fluids through the heat exchanger while creating turbulent flows for both the first and second fluids. Thus, effective heat transfer between the fluid inlet and outlet areas, and between the first fluid and the second fluid guided in the fluid containment cavity, can occur through the respective partition walls.

[0011] The main flow direction of the fluid can be oriented in the longitudinal extension direction of the heat exchanger. Therefore, the fluid discharge area can be opposite the fluid inlet area in the longitudinal extension direction of the heat exchanger. The fluid containment cavity can extend between at least two partition walls, thereby effectively and reliably keeping the second fluid guided in the fluid containment cavity separate from the first fluid. Heat transfer between the two fluids can be achieved, in particular, through the thermal conduction of the respective partition walls. In particular, the first fluid can flow perpendicular to each other in the main flow direction along the opposite sides of the fluid containment cavity, i.e., for example, in the direction of observation along the main flow direction, on the left and right sides of the fluid containment cavity, and exchange heat with the second fluid guided in the containment cavity through the respective partition walls. The expression that the at least two partition walls at least partially define the fluid containment cavity can be understood to mean that the fluid containment cavity can be defined not only by the partition walls but also, for example, partially by the shell walls.

[0012] Assigning a junction area to a fluid inlet area can be understood as the junction area being at least near the fluid inlet area, i.e., facing the fluid inlet area and being additionally or alternatively arranged in the fluid inlet area.

[0013] According to the present invention, the heat exchanger includes at least one reinforcing element, which is arranged on the joint region to at least partially reinforce at least one reinforcing section adjacent to the joint region and is configured to support the reinforcing section at least against bending loads caused by the length change of the joint region due to temperature.

[0014] This is advantageous because it allows for load reduction in the connection area. By supporting the bending load, lateral bending in the reinforced section, for example in the form of warping deformation, can be avoided. To illustrate: a warping deformation, at least partially similar, is known, for example, from Euler buckling bars, where the buckling bar is supported at its two ends.

[0015] The reinforced section can preferably be directly adjacent to the connecting area. Therefore, the reinforcing element of the reinforced section for supporting bending loads can significantly reduce the mechanical stress caused by the length change in the connecting area, thereby causing at most a slight and therefore harmless mechanical load on the connecting area.

[0016] If a temperature-induced length change occurs in the joint area during the operation of the heat exchanger, wherein the first fluid impacts the joint area at the fluid inlet area at a particularly high fluid temperature and / or at a high transient fluid flow velocity of the first fluid and thereby intensely heats the joint area, then a reinforcing element can be used to prevent bending of the reinforcing section due to the length change.

[0017] In particular, even when the temperature of the first fluid is high, when the first fluid impacts the joint area, it is possible to avoid the generation of possible stress cracks and the resulting incomplete sealing in the joint area, thereby enabling a durable and particularly resistant heat transfer between fluids.

[0018] The regions of the at least two partition walls adjacent to the at least one joining region in the main fluid flow direction may be without the at least one reinforcing element. In other words, it may be specified that the reinforcing element extends only at least partially over the joining region, which does not preclude the possibility that other joining regions, such as a second joining region, may not also have such a reinforcing element, i.e., a second reinforcing element, which may be spaced apart from the joining region in the main fluid flow direction and may be provided, for example, for a fluid discharge region.

[0019] The reinforcing element can in principle be constructed as a plate, thereby allowing the reinforcing element to be easily manufactured and sometimes arranged in a space-saving manner on the reinforcing section.

[0020] This invention is based on the understanding that the connection area where the partition wall is at least indirectly, and preferably directly, connected to the shell wall is particularly susceptible to damage due to thermal stress. It is known that the first fluid, in particular, undergoes high transient flow velocity changes and impacts the connection area at high fluid temperatures, and that the associated temperature-induced length changes in the connection area can lead to damage. The invention proceeds from this understanding because a particularly locally restricted and therefore targeted reinforcement is achieved through reinforcing elements, which can specifically prevent undesirable bending due to temperature-induced length changes.

[0021] In an advantageous improvement of the invention, the reinforcing element at least partially surrounds the at least two partition walls in the reinforced section. This is advantageous because partial enclosure provides particularly reliable support against bending loads, especially because bending toward the opposing sides can be effectively suppressed.

[0022] In another advantageous improvement of the invention, the reinforcing element clamps at least two partition walls onto the reinforcing section. This is advantageous because clamping provides a particularly tight fit of the reinforcing element against the partition walls. Thus, the reinforcing element can be mounted on the partition walls with particular care to prevent loss and, if necessary, additionally connected to the partition wall material in a locking manner, for example, by brazing. The reinforcing element can, in particular, have an undersized dimension, so that the reinforcing element can be tensioned by the two partition walls when it is arranged on the reinforcing section.

[0023] In another advantageous improvement of the invention, the joint region includes a joint region segment without reinforcing elements. Advantageously, this allows for targeted deformation of the joint region segment caused by length variations. The joint region segment can then deform with particularly low resistance, resulting in a reduction in load on the joint area. Therefore, deformation can be specifically limited to the joint region segment by means of reinforcing elements, and the reinforced segment can be protected against deformation by means of the reinforcing elements. The statement "without reinforcing elements" can be understood as meaning that the joint region segment can be reinforced without the aid of reinforcing elements. In other words, the joint region segment is thus not reinforced by means of reinforcing elements and therefore not supported by reinforcing elements.

[0024] In another advantageous improvement of the invention, the reinforcing element has a tapered region in which it tapers towards the joint region segment without a reinforcing element. This is advantageous because the tapering eliminates or at least significantly reduces possible abrupt changes in stiffness along the joint region. This improves durability to some extent in the case of length variations caused by temperature. The tapering can be configured such that the reinforcing element tapers, for example, towards the joint region segment.

[0025] In another advantageous improvement of the invention, the reinforcing element material is locked to at least one of the at least two partition walls. This allows for particularly high rigidity of the joint area and a reliable connection between the reinforcing element and the joint area. If the reinforcing element is locked to both partition wall materials, particularly by brazing, a particularly durable connection can be achieved.

[0026] Typically, gaps constructed between partition walls and extending along the joint area can have a uniform, easily sealed gap width. For example, the gaps can be filled with metal solder (e.g., solder) and thereby join the partition walls together at the joint area.

[0027] In another advantageous improvement of the invention, the at least two partition walls are connected to the housing wall in a T-shaped joint manner at the connection area. This is advantageous because the T-shaped joint connection can be manufactured at a particularly low manufacturing cost. The T-shaped joint connection can be understood as the two partition walls and the housing wall forming a T-shape with each other in the connection area in a cross-section oriented perpendicular to the main fluid flow direction.

[0028] Each partition wall may have at least one partition wall region oriented along the shell wall, preferably away from the joint area, on which a corresponding partition wall may preferably be material-locked to the shell wall. Particularly preferably, each partition wall may have at least two partition wall regions opposite each other, which may be brazed to the shell wall.

[0029] In another advantageous improvement of the invention, the reinforcing element is material-locked to at least one of the at least two partition walls and / or to the shell wall in the connection area. This allows for particularly high stiffness in the connection area. By material-locking the partition walls, preferably two partition walls, to the connection area using the reinforcing element, one or more partition walls can be directly supported in the connection area by the reinforcing element, thus imparting particularly high stiffness to the connection area. Through the material-locking connection of the reinforcing element to the shell wall, bending loads can be at least partially supported on the shell wall by the reinforcing element, thereby reducing the load on the connection area. When the reinforcing element is material-locked to both partition walls and to the shell wall in the connection area, a correspondingly high stiffness can be achieved.

[0030] A second aspect of the invention relates to an internal combustion engine having a heat exchanger according to a first aspect of the invention. In an internal combustion engine equipped with this heat exchanger, particularly resistant heat transfer between fluids can be achieved.

[0031] In an advantageous improvement of the invention, the heat exchanger is configured as an exhaust cooler for an internal combustion engine. By means of a heat exchanger configured as an exhaust cooler, especially an AGR cooler, particularly failure-resistant heat transfer can be achieved between the exhaust gas as a first fluid and the coolant as a second fluid.

[0032] The preferred embodiments and advantages described in relation to one of these aspects are applicable accordingly to the corresponding other aspects of the invention, and vice versa.

[0033] The features and combinations of features mentioned above in the specification, as well as the features and combinations of features mentioned below in the description of the drawings and / or shown separately in the drawings, can be used not only in the combinations given separately, but also in other combinations or individually, without departing from the scope of the invention.

[0034] Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the accompanying drawings. Attached Figure Description

[0035] The invention will now be explained again with the aid of specific embodiments. For this purpose, the following is shown:

[0036] Figure 1 A three-dimensional cross-sectional view of a heat exchanger partially shown in an internal combustion engine is provided for transferring heat between two fluids, the first of which is configured as the exhaust gas of the internal combustion engine and the second fluid is configured as the coolant of the internal combustion engine, wherein the internal combustion engine, shown in a highly abstract manner, is configured for a motor vehicle, also shown in a highly abstract manner.

[0037] Figure 2 Show Figure 1 Enlarged view of a segment of the heat exchanger shown; and

[0038] Figure 3 Shown in Figure 2 An enlarged view of region A, outlined by a dashed line, showing the reinforcing element in a magnified 3D view. Detailed Implementation

[0039] Figure 1 A schematic diagram of a motor vehicle K is shown, having an internal combustion engine 100, also schematically shown, configured to drive the motor vehicle K. The internal combustion engine 100 includes a heat exchanger 10 configured as an exhaust gas cooler, specifically an AGR cooler for the internal combustion engine 100. Therefore, during operation of the internal combustion engine 100, so-called cooled exhaust gas recirculation can be achieved by means of the heat exchanger 10. Figure 2 Show Figure 1 An enlarged view of a segment of the heat exchanger shown.

[0040] The heat exchanger 10 is used to transfer heat between two fluids. The first fluid is configured as an exhaust gas, while the second fluid is configured as a coolant, for example, in the form of a water-antifreeze mixture.

[0041] The heat exchanger 10 (here: AGR cooler) includes a housing 20 having at least one housing wall 22. The housing wall 22 is configured as a plate and may also be referred to as a cooling jacket.

[0042] The housing wall 22 defines a housing cavity 24 on its circumferential side. The housing cavity 24 has a fluid inlet region 30 for introducing a first fluid into the housing cavity 24 and a fluid outlet region for discharging the first fluid from the housing cavity 24. The fluid outlet region, not shown further here, is arranged downstream of the fluid inlet region in the main flow direction x of the first fluid. The main flow direction x corresponds to the longitudinal extension direction of the heat exchanger 10. In other words, when the heat exchanger 10 is used as intended, the first fluid flows through the housing cavity 24 in the longitudinal extension direction of the heat exchanger 10.

[0043] Similarly, by means of Figure 1 and Figure 2 It can be seen that the heat exchanger is constructed as a plate heat exchanger under the current circumstances.

[0044] The plates of the heat exchanger 10 are formed by pairs of interconnected partition walls 40, 50 (i.e., the first partition wall 40 and the second partition wall 50 configured here as corresponding plate half-shells). Thus, plates are formed by the first partition wall 40 and the second partition wall 50, wherein the heat exchanger 10 has a plurality of such plates, as by means of... Figure 1As can be seen, the following discussion will focus only on the single plate formed by the two partition walls 40 and 50, but the following description also applies in principle to the other plates of the heat exchanger 10.

[0045] Partition walls 40 and 50 are housed within the housing cavity 24 and are connected to the housing wall 22 via connection regions 60 and 62 that are opposed to each other in the height direction z of the heat exchanger 10. Here, the first partition wall 40 has corresponding partition wall regions 42 that are opposed to each other in the height direction z, while the second partition wall 50 has partition wall regions 52 that are opposed to each other in the height direction z. Each partition wall region 42 and 52 is formed onto the housing wall 22. In other words, the partition wall regions 42 and 52 extend at least substantially parallel to the housing wall 22 at their respective connection regions 60 and 62, and in this case also extend relative to each other, and are material-locked to the housing wall 22 at the connection regions 60 and 62, particularly by brazing.

[0046] Partition walls 40 and 50 are used to separate the fluids from each other and at least partially define a fluid receiving cavity 70 through which the second fluid (here: coolant) flows when the heat exchanger 10 is used as intended. The fluid receiving cavity 70 is also partially defined by means of the shell wall 22, i.e., in the height direction z of the heat exchanger 10 perpendicular to the main fluid flow direction x. The fluid receiving cavity 70 is defined in all... Figures 1 to 3 The fluid containment cavity 70 is covered and therefore not visible by the partition walls 40 and 50, however it is clear how the partition walls 40 and 50, which are constructed as corresponding plate half-shells, can define the fluid containment cavity 70. Thus, each of the plate half-shells (partition walls 40 and 50) can limit approximately one half of the fluid containment cavity 70.

[0047] The paired partition walls 40 and 50 are respectively connected and brazed to each other at least in a joint area 80 adjacent to the fluid receiving cavity 70 and disposed in the fluid inlet area 30 along the main flow direction x of the first fluid. Here, the gap 84 extending between the partition walls 40 and 50 in the joint area 80 is filled with solder, thereby brazing the partition walls 40 and 50 together and sealing the gap 84 against undesired outflow of the second fluid (coolant, especially cooling water) from the fluid receiving cavity 70 extending between the partition walls 40 and 50. Additionally, the partition walls 40 and 50 are also connected to each other at another joint area opposite the joint area 80 along the main flow direction x and disposed in the fluid outlet area; however, this... Figures 1 to 3 It is not visible, especially because the fluid discharge area is not shown.

[0048] At the common joining area 80, the corresponding partition walls 40 and 50 are oriented at an angle, currently a right angle (90° angle), relative to the corresponding partition wall areas 42 and 52. Thus, the partition walls 40 and 50 are connected to the shell wall 22 in a T-joint manner at the joining areas 60 and 62, as is particularly clearly seen in… Figure 2 As can be seen in the text.

[0049] With the help of Figure 2 and Figure 3 As can be seen, the heat exchanger 10 includes a plurality of reinforcing elements 90, which are arranged on the joining region 80 to at least partially reinforce the reinforcing sections 86 adjacent to the connecting regions 60, 62 of the joining region 80. The reinforcing elements 90 are configured to support each reinforcing section 86 against bending loads caused by temperature-induced length changes in the joining region 80. Supporting bending loads particularly prevents lateral bending in the region of the reinforcing section 86 in the form of warping or wavy deformation. Figure 1 The illustration of reinforcing element 90 has been omitted for clarity.

[0050] Currently, for each joining region 80 and therefore for each plate (which includes partition walls 40, 50), two reinforcing elements 90 are arranged on reinforcing sections 86 that are opposite each other along the height direction z. One reinforcing section 86 is assigned to the connecting region 60 and the other reinforcing section 86 is assigned to the second connecting region 62. Thus, one reinforcing element 90 is located on the connecting region 60 and one reinforcing element 90 (opposite each other along the height direction z in this example) is located on the connecting region 62.

[0051] The reinforcing element 90 partially surrounds the partition walls 40 and 50 on the corresponding reinforcing section 86, thereby achieving effective reinforcement on the two partition walls 40 and 50.

[0052] In addition, the reinforcing element 90 clamps the partition walls 40 and 50 at the reinforcing section 86. In other words, the reinforcing element 90 thus applies clamping force to the partition walls 40 and 50 respectively.

[0053] With the help of Figure 2 As can be seen, the joining region 80 includes a joining region segment 82 without reinforcing elements. The joining region segment 82 extends between reinforcing segments 86 that are opposite each other.

[0054] If a temperature-induced length change occurs in the joint area 80 during normal use of the heat exchanger 10, then by designing the joint area section 82 without reinforcing elements, possible deformations, such as wavy bends, caused by the length change can be locally and thus specifically contained in the joint area section 82. Conversely, bending and associated mechanical stress loads can be prevented in the area of ​​the reinforcing section 86 and in the joint areas 60, 62 by means of reinforcing elements 90.

[0055] Each reinforcing element 90 has a tapering region 98, in which the corresponding reinforcing element 90 tapers towards the joining region segment 82 without reinforcing elements. (By means...) Figure 3 It can be seen that the reinforcing element 90 tapers sharply towards the joining region segment 82 due to its taper. The taper region 98 can preferably extend along the entire length of the reinforcing element 90, which is achieved by means of... Figure 3 It can be seen that, Figure 3 In the middle, the tapered region 98 extends along the entire length of the reinforcing element 90 in the height direction z.

[0056] The reinforcing element 90 is designed, at least partially, as a hollow square. Each reinforcing element 90 has two sidewall regions 92, 94 facing each other in a direction y, different from the main fluid flow direction x. In these sidewall regions 92, 94, the first sidewall region 92 supports the first partition wall 40 along the reinforcing section 86 and preferably also supports one of the connecting regions 60, 62. The second sidewall region 94, facing the first sidewall region 92 along the y-direction, supports the second partition wall 50 along the reinforcing section 86 and preferably also supports one of the connecting regions 60, 62, as if by means of… Figure 3 As can be seen, sidewall regions 92 and 94 are integrally connected to each other via endwall regions 96 of corresponding reinforcing elements 90. Endwall regions 96 have end faces 97 facing the main fluid flow direction x (see...). Figure 3 The direction y here corresponds to the lateral direction of the heat exchanger 10.

[0057] The direction y is oriented perpendicular to the central plane M, and the partition walls 40 and 50 can be oriented at least substantially parallel to this central plane. The central plane M is formed here by the main fluid flow direction x and the height direction z.

[0058] The main flow direction of the fluid, x (the longitudinal extension direction of the heat exchanger 10), y (the transverse direction of the heat exchanger 10), and z (the height direction) are oriented perpendicularly to each other.

[0059] The reinforcing element 90 is connected to the partition walls 40 and 50 by means of material locking, especially by brazing.

[0060] The corresponding reinforcing element 90 is material-locked to the partition walls 40 and 50 in the corresponding connection regions 60 and 62, and at least indirectly connected to the housing wall 22. The connection at least indirectly can be understood here as the reinforcing element 90 being material-locked to the partition walls 40 and 50 in the partition wall regions 42 and 52, wherein the partition wall regions 42 and 52 are in turn material-locked to the housing wall 22.

[0061] The reinforcing elements 90 are respectively provided and constructed to prevent possible bending caused by mechanical stress resulting from length changes in the joint areas 60 and 62 due to temperature-induced length changes in the joint area 80, for example in the form of corrugated portions or bulges. Therefore, particularly resistant heat transfer between fluids can be achieved by means of the reinforcing elements 90.

[0062] The partition walls 40 and 50 are connected to each other in a material-locking manner along the entire joint area 80, i.e., brazed.

[0063] In manufacturing the current heat exchanger 10, the partition walls 40, 50 (plate half-shells) can be joined to each other on the one hand at the joining region 80 and to the shell wall 22 on the other hand at the connecting regions 60, 62. Due to the minimum brazing width in the design of the heat exchanger 10, the connecting regions 60, 62 exhibit particularly rigid zones of the heat exchanger 10, especially in the fluid inlet region 30.

[0064] The reinforcing element 90 prevents unacceptably high mechanical loads, such as those in the form of temperature-alternating loads, on the connection areas 60, 62. The reinforcing element 90 prevents the partition walls 40, 50, which are connected to the housing wall 22 in a T-joint manner, from bending in the reinforced section 86, thereby preventing excessive loads on the connection areas 60, 62 even under high transient flow conditions of particularly hot exhaust gas (first fluid) through the housing cavity 24. The reinforcing element 90 can form a targeted localized reinforcement, where bending does not occur even under temperature-induced length variations.

[0065] By adjusting the geometry of the reinforcing element 90, a targeted, localized increase in the stiffness of the plate half-shells (partition walls 40, 50) is achieved in the joining region 80. Thus, the brazed plate half-shells are locally and limitedly reinforced by the reinforcing element 90, resulting in minimal deformation in the reinforced section 86 under alternating temperature loads. The reinforced section 86 is the corresponding edge region of the joining region 80 adjacent to the connecting regions 60, 62. The connecting regions 60, 62 are generally unloaded under alternating temperature loads.

[0066] In the current heat exchanger 10, the reinforcing element 90 helps to prevent stress cracks caused by possible temperature-induced length changes in the connection regions 60, 62. Furthermore, the reinforcing element 90 significantly reduces potential abrupt changes in stiffness in the T-joint-shaped connection and extends the possible crack propagation path.

[0067] The reinforcing element 90 can also be configured as a reinforcing clip for ease of installation. The reinforcing clip can then lock, for example, onto the reinforcing section 86 with at least one or both of the partition walls 40, 50.

[0068] The reinforcing element 90 can be connected to the joint area 80 during the manufacture of the heat exchanger 10, preferably by brazing.

[0069] List of reference numerals

[0070] 10 Heat Exchanger

[0071] 20. Housing

[0072] 22 Shell wall

[0073] 24. Inner cavity of the shell

[0074] 30 Fluid entry area

[0075] 40 First partition wall

[0076] 42. Separator Area

[0077] 50 Second partition wall

[0078] 52. Separator Area

[0079] 60 Connection Area

[0080] 62 Second Connection Area

[0081] 70 Fluid Reception Chamber

[0082] 80 Joint area

[0083] 82 Joint area section

[0084] 84 gaps

[0085] 86 Reinforced Section

[0086] 90 Reinforcing Components

[0087] 92 Sidewall area

[0088] 94 Second sidewall region

[0089] 96 End Wall Region

[0090] 97 End Face

[0091] 98 Gradual contraction region

[0092] 100 Internal Combustion Engine

[0093] K Motor Vehicle

[0094] M center plane

[0095] x Main flow direction of fluid

[0096] y direction

[0097] z represents the height direction.

Claims

1. A heat exchanger (10) for an internal combustion engine (100) for transferring heat between at least two fluids, said heat exchanger comprising: - At least one housing (20), the housing having at least one housing wall (22) and a housing cavity (24) defined at least partially by means of the housing wall (22), the housing cavity having a fluid inlet region (30) for introducing a first fluid of the at least two fluids into the housing cavity (24) and a fluid outlet region for discharging the first fluid from the housing cavity (24); - At least two partition walls (40, 50), each partition wall being at least primarily housed in the housing cavity (24) and connected to the housing wall (22) of the housing (20) at at least one connection region (60), and each partition wall defining at least partially, in order to separate the fluids from each other, a fluid receiving cavity (70) through which a second of the at least two fluids can flow, wherein the at least two partition walls (40, 50) are connected to each other at least in a junction region (80) provided to the fluid inlet region (30) and adjacent to the fluid receiving cavity (70) along the main flow direction (x) of the first fluid; Its features are, The heat exchanger (10) includes at least one reinforcing element (90) arranged on the joint region (80) to at least partially reinforce at least one reinforcing section (86) adjacent to the connecting region (60), and the reinforcing element is configured to support the reinforcing section (86) at least against bending loads caused by the length change of the joint region (80) due to temperature, and the reinforcing element (90) at least partially surrounds the at least two partition walls (40, 50) on the reinforcing section (86).

2. The heat exchanger (10) according to claim 1, characterized in that, The reinforcing element (90) clamps the at least two partition walls (40, 50) onto the reinforcing section (86).

3. The heat exchanger (10) according to claim 1 or 2, characterized in that, The joining region (80) includes a joining region segment (82) without reinforcing elements.

4. The heat exchanger (10) according to claim 3, characterized in that, The reinforcing element (90) has a tapered region (98) in which the reinforcing element (90) tapers toward the joint region segment (82) without a reinforcing element.

5. The heat exchanger (10) according to claim 1 or 2, characterized in that, The reinforcing element (90) is materially locked to at least one of the at least two partition walls (40, 50).

6. The heat exchanger (10) according to claim 1 or 2, characterized in that, The at least two partition walls (40, 50) are connected to the housing wall (22) in a T-shaped joint manner in the connection area (60).

7. The heat exchanger (10) according to claim 1 or 2, characterized in that, The reinforcing element (90) is material-locked to at least one of the at least two partition walls (40, 50) and / or to the housing wall (22) in the connection area (60).

8. An internal combustion engine (100) having a heat exchanger (10) according to any one of claims 1 to 7.

9. The internal combustion engine (100) according to claim 8, characterized in that, The heat exchanger (10) is configured as an exhaust cooler for the internal combustion engine (100).

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