HEAT EXCHANGER

Abstract

Heat exchanger, having multiple first flow channels (4) of a cooling medium arranged one over another,second flow channels (5) of a process medium, which are arranged between the first flow channels (4) and are provided on their ends with manifold boxes (7, 8),the first and second flow channels (4, 5) each being formed by partition plates (2) and first and second block profiles (3, 6), which hold these partition plates spaced apart, and lamellae (9, 10) arranged between respective block profiles (3, 6),the first block profiles (3) delimiting the first flow channels (4) being designed as C-shaped,two springy legs (32) extending in the direction of the lamellae (9) from a base (31) of the first block profiles (3) and delimiting a recess (33) open in the direction of the lamellae (9) between them, wherein the base (31) has at least one recess (38, 39) for the flexible design of the base (31) of the first block profiles (3).

Description

BACKGROUND OF THE INVENTION

This application claims benefit of and priority to German Patent Application No. 20 2011 052 186.9, filed Dec. 5, 2011, the content of which Application is incorporated by reference herein. No new matter has been added.

The present invention relates to a heat exchanger that includes a plurality of first flow channels for a cooling medium. The plurality of the first flow channels are configured to be located one over the other. Further included are a plurality of second flow channels for a process medium. One the plurality of the second flow channels is located between two of the plurality of the first flow channels. The plurality of the first and second flow channels each are formed from partition plates, and first and second block profiles are configured to hold the partition plates in a spaced-apart condition. Lamellae are arranged between the first and second block profiles. The first block profiles delimit the first flow channels and are configured to be C-shaped. Two legs are configured to be springy and extend in a direction of the lamellae from a base of the first block profiles and delimit a first recess open in the direction of and between the extended lamellae.

A heat exchanger is known, for example, from DE 202 08 748 U1. The heat exchanger described therein is used, in particular, for high-temperature applications, for example, in charge air coolers or oil coolers of motor vehicles, which are subject to significant thermal and mechanical stresses because of high cyclic temperature differences and cyclically changing flow rate quantities. These cyclic thermal stresses and the cyclic pressure stresses, in particular internal pressure stresses, act in particular on the components in the region of the supply of the hot medium, for example, in the form of undesired material extensions or compressions of the components of the heat exchanger, which are connected to one another by soldering to form a rigid block.

To lengthen the service life of such a heat exchanger, it is proposed, in the above-mentioned publication, that the block profiles of the heat exchanger, which hold spaced apart partition plates, which are arranged parallel to one another, and which block profiles, together with lamellae arranged between the partition plates, form the flow channels of the cooling medium and the flow channels of the process medium to be cooled, be provided on a side facing away from the lamellae with a central recess having legs, which are flexible transversely to the flow directions of the hot and cold medium and have the soldering surfaces, whereby one side of the block profile is implemented flexibly and can thus absorb forces or tensions perpendicularly to the flow directions.

However, it has been shown that in spite of the partially flexibly designed block profile, damage which decreases the lifetime of the heat exchanger block through cyclically occurring stresses cannot be adequately avoided.

Embodiments of the present disclosure provide for a heat exchanger which has a lengthened lifetime and which has even less danger of cracking.

Thus, the present disclosure relates to a heat exchanger including a plurality of first flow channels for a cooling medium. The plurality of the first flow channels are configured to be located one over the other. Further included are a plurality of second flow channels for a process medium. One the plurality of the second flow channels is located between two of the plurality of the first flow channels. The plurality of the first and second flow channels each are formed from partition plates, and first and second block profiles are configured to hold the partition plates in a spaced-apart condition. Lamellae are arranged between the first and second block profiles. The first block profiles delimit the first flow channels and are configured to be C-shaped. Two legs are configured to be springy and extend in a direction of the lamellae from a base of the first block profiles and delimit a first recess open in the direction of and between the extended lamellae. The base includes a second recess.

According to the present disclosure, the first block profiles delimiting the first flow channels are designed as both having C-shaped legs extending from a base of the block profiles in the direction of the lamellae and are also provided with a flexibly designed base.

Through the flexible design of the base of the block profiles, it is within the scope of the present disclosure to significantly reduce both the effects of pulsing or cyclic internal pressure stresses on the heat exchanger and also the effects of cyclic thermal stresses.

Thus, in the case of cyclic internal pressure stresses, the tensions acting on the lamellae arranged between each two of the first block profiles, for example, the flanks of the lamellae, which may be designed as turbulators in the edge region of the front process passages, are reduced by up to 40% through the flexible design of the first block profiles in relation to the known, or typical embodiment of block profiles. The lifetime of the heat exchanger block in accordance with the present disclosure, is thus increased by a factor of 4 to 5.

The tensions caused by cyclic thermal stresses on the lamellae arranged between each two of the first block profiles are also reduced by the flexible design of the first block profiles by approximately 30% in relation to the known, or typical embodiment of the block profiles.

The tensions caused by cyclic thermal stress on the partition plates at the edge of the first block profiles because of the thermal expansion in the block width direction are reduced to the same extent. That is done by the enlargement of the ratio of bending length to deflection of the partition plate in the event of a deformation of the partition plate and by a reduction of the cyclic temperature difference between the flexible first block profile and the lamellae, which lamellae may, for example, be designed as turbulators. The lifetime of the lamellae, which may be, for example, be designed as turbulators, in the process passages of the heat exchanger block is thus increased by a factor of 3 to 4. The lifetime of the partition plates is thus increased as a function of the thermal tensions caused by the thermal expansion in the block longitudinal direction by a factor of 1.5 to 3.

Embodiments of the present disclosure are discussed herein and in the appended claims.

According to an embodiment of the present disclosure, the base of the block profiles has recesses extending parallel to the running direction of the flow channels of the cooling medium, which are designed to be slotted, for example. Firstly, the flexibility of the block profile is thus increased, and secondly, the mass of the block profile is also reduced by the introduction of the recesses, so that the absorption capacity of the block profile is thus also reduced. Finally, an enlargement of the heat-transfer area on the block profile and therefore a reduction of the thermal tensions is achieved by the introduction of the recesses.

The ends of the recesses in the interior of the base are designed as widened, according to an embodiment of the present disclosure. This results in a further increase of the flexibility of the block profile, on the one hand, and also a further enlargement of the heat-transfer area of the block profile, on the other hand.

According to an embodiment of the present disclosure, the recesses are alternately arranged on the side facing away from the lamellae and the side facing toward the lamellae.

The sum of the length of the alternately arranged recesses may be, for example, greater than the length of the base of the first block profile, so that viewed in a longitudinal extension of the base, the ends of the recesses located in the interior of the base partially overlap.

Embodiments according to the present disclosure are further explained herein.

Other aspects of the present disclosure will become apparent from the following descriptions when considered in conjunction with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows a schematic perspective view of an embodiment of a heat exchanger having a heat exchanger block and laterally arranged manifold boxes, in accordance with the present disclosure.

FIG. 2 shows a perspective view of the heat exchanger block of FIG. 1 having block profiles arranged therein.

FIG. 3 shows an exploded view of a part of the heat exchanger block of FIG. 2.

FIG. 4 shows an embodiment of a turbulator inserted into the processing passages in the block of the heat exchanger, in accordance with the present disclosure.

FIG. 5 shows a sectional view transversely to the flow direction of the cooling medium of the heat exchanger having block profiles arranged therein, in accordance with an embodiment of the present disclosure.

FIG. 6 shows a sectional view of the heat exchanger of FIG. 5 transversely to the flow direction of the medium to be cooled.

FIG. 7 shows a sectional view of the heat exchanger in a plane parallel to the flow direction of the cooling medium and the process medium, in accordance with the present disclosure.

FIG. 8 shows a sectional view of an embodiment of a block profile transversely to the flow direction of the cooling medium having a base designed as springy on one side, in accordance with the present disclosure.

FIG. 9 shows a sectional view of an embodiment of a block profile transversely to the flow direction of the cooling medium having a base designed as springy on both sides, in accordance with the present disclosure.

FIGS. 10 to 21 show sectional views of embodiments of a block profile transversely to the flow direction of the cooling medium, in accordance with the present disclosure.

FIGS. 22 and 23 show perspective views of embodiments of block profiles having recesses transversely to the flow directions, in accordance with the present disclosure.

FIGS. 24 to 28 show sectional views of embodiments of a block profile transversely to the flow direction of the cooling medium, in accordance with the present disclosure.

DETAILED DESCRIPTION

In the following description of the Figures and discussion of the embodiments of the present disclosure, terms such as top, bottom, left, right, front, rear, for example, relate to the exemplary illustrations and the positions selected in the respective Figures of the heat exchanger, the block profile, the manifold box, and other elements shown, according to the present disclosure. These terms are not to be understood as restrictive, that is, these references may change through different work positions or the mirror-symmetric design, for example.

In FIG. 1, a heat exchanger block is identified by the reference numeral 1. Heat exchanger block 1 has multiple partition plates 2 arranged one over another, and has first flow channels 4 of a cooling medium, which are arranged one over another, interposed. Heat exchanger block 1 also has second flow channels 5, which are arranged between the first flow channels 4 and are provided on their end with manifold boxes 7, 8, of a process medium to be cooled, and respectively, an upper and lower end plate 14 arranged parallel to the partition plates 2 to border the heat exchanger block 1 from the top and bottom. The manifold boxes 7, 8 are designed, in a known way, as hood-shaped or box-shaped and are provided on their side facing toward the end plate 14 with, for example, a semicircular recess. The recess is closable by a correspondingly shaped front wall 13. The front wall 13 is connected by weld seams 12 to the end plate 14 and the housing of the respective manifold box 7, 8. Side walls 73, shown in FIGS. 1 and 6, of the manifold boxes 7, 8 are connected via weld seams 15 to the front sides of the heat exchanger block 1, through which the medium to be cooled enters and exits.

The length L and the depth T of the heat exchanger block 1 are defined by the dimensions of the rectangular partition plates 2.

As shown in FIGS. 1 to 3, the flow channels 4 of the coolant are formed in a flow direction Y by lamellae 9 arranged between the partition plates 2, the flow channels 4 extending parallel to the front sides of the heat exchanger block 1, on which the manifold boxes 7, 8 are arranged.

Between the manifold boxes 7, 8 and the lamellae 9, first block profiles 3 are arranged between the partition plates 2 on their frontal ends, in order to suitably equip the heat exchanger block 1 in the inlet region of the hot process medium to be cooled and the thermal and mechanical stresses accompanying this.

The flow channels 5 of the medium to be cooled are also formed by lamellae 10, which are arranged between each two partition plates 2, having second block profiles 6 terminating the flow channels 5 at the side edges. The second block profiles 6, as may be recognized in FIG. 3, for example, being formed essentially rectangular in the region of the contact surfaces with the partition plates 2 and the outward facing surface, while the side facing toward the lamellae 10 may be, for example, formed as a triangle tapering toward the lamellae 10.

The lamellae 10 forming flow channels 5 of the medium to be cooled may be, as shown in FIG. 4, designed as turbulators having cams 101 and a cam pitch t(T) and flanks 102 having a material thickness s(T). This is in order to ensure sufficient strength in the event of large thermal and mechanical alternating stresses, the turbulators essentially being used for the purpose of swirling the hot medium in the flow channels 5. The second block profiles 6 can, accordingly, also be designated as turbulator profiles in accordance with the present disclosure.

Both the components of the heat exchanger block 1, and also the partition plates 2, the lamellae 9 and 10, and the first and second block profiles 3 and 6 may, for example, include aluminum and are fixedly connected to one another by soldering to form a rigid block. Other heat exchanger active materials such as copper, copper alloys, and steel are within the scope of the present disclosure.

In order to reduce the effects of cyclic internal pressure stresses on the heat exchanger and also the effect of cyclic thermal stresses, the first block profiles 3 may, for example, be designed to be springy. For this purpose, on the one hand, such a block profile 3 is designed on an end facing toward the lamellae 9 as C-shaped, as is known from the prior art, as shown in FIG. 8, for example, in order to be able to compensate for cyclically occurring stresses by spring deflection of legs 32 forming the C-shaped formation.

According to an embodiment of the present disclosure, a side facing away from the lamellae 9 and facing toward the inflow region of the medium to be cooled, which is designated hereafter as the base 31 of the first block profiles 3, is also designed to be springy.

As shown in FIGS. 5, 7, and 8, the entire block profile 3 has a length a in the direction of the longitudinal axis L of the block profile, which is divided into a length b of the base and a length c of the legs 32, which make the base 31 springy, and which extend in the direction of the lamellae 9 and delimit a recess 33 open in the direction of the lamellae 9. Through the recess 33, existing between the legs 32, having passage 34 between the legs 32 of a width e, a force acting perpendicularly to the partition plates 2 as a result of the entry of the hot medium from the first block profile 3, can be compensated for, without the connection between the upper or lower side of the block profiles 3, which faces toward the partition plates 2, and the partition plates 2 detaching.

In order to keep the force, which is exerted from the base 31 of the first block profile 3, on the second lamellae 10, which are, for example, designed as turbulators, and the partition plates 2, as a result of the cyclic heating and cooling by entry of the medium to be cooled into the front manifold boxes 7 and into the second flow channels 5 or as a result of the cyclic internal pressure stresses as small as possible, the base 31 of the block profiles is also designed to be springy on a side facing away from the lamellae 9 forming the flow channels 4 of the cooling medium.

The springy design is performed, for example, by recesses 38, which extend parallel to the flow direction X of the flow channels 4 of the cooling medium, and by which the base 31 of the first block profile 3 is divided on the side facing away from the lamellae 9 into outer webs 36 and at least one inner web 37. These recesses 38 may, for example, be designed as slots having a slot depth m, the slot depth m being in a ratio of 0.4≦m/b≦0.9 in relation to the width b of the base 31.

The slot depth m may, for example, be additionally at least 1 mm less than the seam thickness of the weld seam 15, which is designated as the a dimension, or height of the triangle insertable into an arbitrary seam shape, via which the manifold boxes 7, 8 are connected to the front sides of the heat exchanger block 1 on the entry or exit side of the process medium, respectively.

The width h 1 of these slotted recesses 38 may, for example, be in a ratio to the total width h of the first block profile 3 of: 0.1≦h1/h≦0.3.

The recesses 33 between the legs 32 of the first block profile 3 may, for example, be designed as circular having a diameter d. The circular recess 33 opens toward the lamellae 9 to form an opening gap 34 having a width e.

An embodiment according to the present disclosure, in relation to the embodiment of the first block profile 3 shown in FIG. 8, having further increased flexibility, is shown in FIG. 9. That is, the approximately 90% flexibility in the longitudinal extension of the block profile 3 of FIG. 8 is in relation to the 100% flexibility in the longitudinal extension of the block profile 3 according to FIG. 9. The block profile 3 shown in FIG. 9 is distinguished in that in addition to the recesses 38 from the side facing away from the lamellae 9, recesses 38 are also provided from the side of the base 31 facing toward the lamellae 9. The recess 38 penetrating from the side facing toward the lamellae 9 into the base 31 may, for example, start centrally in the recess 33 between the legs 32 and is formed substantially corresponding to the recess 38 starting from the side facing away from the lamellae 9.

In the embodiment shown in FIG. 9, the recess 38 penetrating from the side facing toward the lamellae 9 into the base 31 has a length n, which may, for example, correspond to the equation n=m*(0.1−0.9)+(b−m). The width h2 of this recess 38 may, for example, correspond to a ratio of 0.1≦h2/h≦0.3.

Further embodiments of the first block profile 3, according to the present disclosure, are described hereafter and are shown in FIGS. 10 to 23. The embodiment of the legs 32 and the recesses 33 provided between the legs and the opening gap 34 are essentially maintained.

In an embodiment of the first block profile according to FIGS. 10, 11, 13, 18 to 20, and 22, differently formed recesses 38 are introduced from the side facing away from the lamellae 10 into the base 31 of the block profile. In contrast to the embodiment shown in FIG. 8, in which three recesses 38 are arranged one below another in the direction of the depth B of the heat exchanger block 1, which protrude parallel and linear from the side facing away from the lamellae 9 into the base 31 in the direction of the longitudinal extension L of the heat exchanger block 1 into the base 31 of the first block profile 3, in the embodiment according to FIG. 10, the ends of the recesses 38 are widened in the interior of the base 31 and are designed, for example, as circular widened areas 381. The diameter d1 of these circular widened areas 381 may be, for example, 1.5 to 3 times the width h1 of the slotted recesses 38. The embodiment of the block profile 3 shown in FIG. 11 differs from that of the block profile shown in FIG. 10 in that in the block profile 3 of FIG. 11, only two, instead of three, recesses 38 are provided and the center of the circular widened areas 381 in the embodiment shown in FIG. 10 is located on an imaginary centerline of the recess 38, while the circular widened area 381 of FIG. 11 is positioned so that an inner side of the recesses 38 formed by an outer web 36 merges tangentially into the circular widened area 381.

In the embodiment shown in FIG. 13, again having three recesses 38 positioned one under another, with circular widened areas 381 having a diameter d1, the recesses 38 are conically widened toward the manifold boxes 7, 8, the smallest width of the recesses 38 being dimensioned with h1. The width h3 on the outer edge of the base 31 of the block profile may, for example, be dimensioned so that 1≦h3/h1≦3.

The length of all recesses 38 extending from the side facing away from the lamellae 9 into the base 31 of the block profiles 3 may, for example, always correspond to the above-mentioned length m.

In the embodiment of the first block profile 3 shown in FIG. 18, the recesses 38 are designed corresponding to the embodiment shown in FIG. 8. In addition, depressions 361 having a length t in the direction of the longitudinal extension L of the heat exchanger block 1 are provided on the top and bottom sides of the block profile 3 facing toward the partition plates 2.

The length t of the depressions 361 in the direction of the longitudinal extension L of the heat exchanger block 1 may, for example, correspond to the difference of the length b of the base 31 of the first block profile 3 and the length m of the recesses 38 multiplied by a factor of 1.1 to 3.

The depression 361 may, for example, be designed as a trough in the form of a circular section, whose radius of curvature R may, for example, correspond to the equation R=0.5+(0.15−1.15)*(b−m)².

In the embodiment shown in FIG. 19, additional recesses 39, in the form of boreholes having a diameter d3, are provided in addition in extension of the recesses 38 in the base 31. This is done in order to also make it easier to press in the block profile 3 in the direction of the width B of the heat exchanger block 1 in the region of the base 31 of the first block profile 3 close to the attachment of the leg 32. The diameter d3 may, for example, correspond to 1.5 to 5 times the internal height h1 of the essentially slotted recesses 38.

In the embodiment of the first block profile 3 shown in FIG. 20, two recesses 38 are provided from the side facing away from the lamellae, which are delimited by two outer webs 36 and one inner web 37, the recesses 38 tapering into the base 31, having a narrowest point h1 and a widest point h3 at the entry of the recess 38. In addition, a further recess 39, which is designed as an oblong hole extending through the entire depth T of the block profile 3, is formed between the two recesses 38. The length of the oblong hole k may, for example, correspond to 0.4 to 0.6 times the length b of the base 31 of the first block profile 3.

In the embodiment of the first block profile 3 shown in FIG. 22, additional recesses 38a are introduced into the base 31 of the block profile 3, which are again designed as slotted having a length of s1, the length s1 of these slotted recesses 38 which may, for example, correspond to approximately 0.6 to 0.8 times the length b of the base 31 of the block profile 3. The width r1 of these recesses 38 may for example, correspond to a ratio of 0.01≦r1/T≦0.03. These recesses 38a, considered in the direction of the depth T of the heat exchanger block 1, are provided approximately every one-twentieth to three-tenths of the depth T of the heat exchanger block.

As may be inferred from FIG. 22, and in accordance with the present disclosure, multiple such recesses 38a are provided, the distance p1 between the individual recesses 38a in the direction of the depth T of the heat exchanger block 1 may, for example, correspond to 0.05 to 0.3 times the depth T of the heat exchanger block.

FIGS. 12, 14 to 17, 21, and 23 show embodiments of the first block profile 3, as shown in principle in FIG. 9. These embodiments share the feature that, in addition to the recesses 38 from the side facing away from the lamellae 9, recesses 38 are also provided from the side of the base 31 facing toward the lamellae 9.

In the embodiments according to FIGS. 12 and 14, in which the recess 38 introduced from the side facing toward the lamellae 9 into the base 31 is provided with a circular widened area 381, the diameter d2 of this circular widened area 381 may, for example, correspond to approximately 1.5 to 5 times the width h2 of the slotted recesses 38.

In the embodiment of the first block profile 3 shown in FIG. 15, the recesses 38 are designed as widening conically from the outside to the inside, the end of the recesses 38 being designed as semicircular. The narrowest point of the recesses introduced from the side facing away from the lamellae 9 into the base 31 may be, for example, h1, in the recess 38 introduced from the opposite side into the base 31, the narrowest point may be, for example, h2. The diameter of the first-mentioned recesses may be, for example, d1, that of the second-mentioned recesses may be, for example, d2.

In another embodiment of the first block profile 3, according to the present disclosure, the recesses 38 are designed as double cones in the direction of their longitudinal extension m, the narrowest point having a width h1 and being approximately in the middle in the direction of the longitudinal extension m of the recesses 38. Accordingly, the recess 38 is designed as originating from the recess 33 between the legs 32, the smallest width of this recess 38 in the direction of the longitudinal extension n may be, for example, h2, and the widest point at the entry being h4, the width h4 may, for example, correspond to the equation 1≦h4/h2≦3 having a smallest width h2, which corresponds to the equation 0.1≦h2/h≦0.3.

Finally, in the embodiment according to FIG. 23, additional slotted recesses 38b are introduced into the block profile 3 from the side facing toward the lamellae 9, which correspond in the alignment to the recesses 38a according to FIG. 22. The slotted recesses 38b also extend here through the legs 32. The length s2 of these slotted recesses 38b may, for example, correspond to 1.2 to 1.8 times the length b of the base 31 of the first block profile 3. The width r2 of these slotted recesses 38b may, for example, correspond to the equation 0.01≦r2/T≦0.03.

As may be inferred from FIG. 23, in accordance with the present disclosure, multiple such slotted recesses 38b are provided, the spacing p2 between the individual recesses 38b in the direction of the depth T of the heat exchanger block 1 may, for example, correspond to 0.05 to 0.3 times the depth T of the heat exchanger block.

To further relieve the partition plates and the turbulators, it is within the scope of the present disclosure to produce the first and/or second block profiles 3, 6 from a spring-elastic material.

In the embodiment of the first block profile 3 shown in FIG. 24, the recesses 38 are designed in different lengths. The central recess has a length f being longer than the vertically observed outer recesses 38 having a length m.

In the embodiment according to FIGS. 25 and 26, the base 31 of the block profile 3 has recesses 38 extending diagonally to the flow direction X of the flow channels 4 of the cooling medium, whereby, for example, the outer webs 36 are designed as reinforced because of their changing width. The diagonal extension of the recesses can, according to the present disclosure, be designed as tapering both from the outside, on the left as shown in FIG. 25 to the inside on the right, as shown in FIG. 25, and also spreading out from the outside to the inside, as shown in FIG. 26.

In the embodiment of the first block profile 3 shown in FIGS. 27 and 28, a wall section 35, which is in the form of one or multiple, for example, three circular arcs in cross-section and delimits the recess 33 between the legs 32 of the first block profile 3, is designed as arched toward the lamellae 9. This has the advantage, according to the present disclosure, that more space is available at the base 31 of the block profile 3 for the weld seam. The wall section 35 may, for example, be formed from multiple wall sections 351, 352, 353, which merge into one another, having radii R1, R2, R3 different from one another. A first, middle wall section 351 has a first radius R1, which is 1.1 to 5 times greater than a second radius R2 of a second wall section 352 adjacent to the middle wall section 351. Furthermore, the second radius R2 of the second wall section 352 adjacent to the middle wall section 351 may, for example, be 1.1 to 5 times greater than a third radius R3 of a third wall section 353 adjacent to one of the springy legs 32. The flexibility of the legs 32 is thus once again increased in relation to that of the base 31 of the block profile 3.

All of the above-mentioned dimensions of the lengths, depths, widths, or diameters of the recesses, depressions, for example, of the first block profiles may be, for example, selected in accordance with the above-mentioned equations. This is to achieve, through the above described possibility for increasing the flexibility or enlarging the heat-transferring area of the first block profiles to the partition plates and the second lamellae 10, a significant stress reduction, for example, on the cyclically stressed components inside the heat exchanger.

Although the present disclosure has been described and illustrated in detail, it is to be clearly understood that this is done by way of illustration and example only and is not to be taken by way of limitation. The scope of the present disclosure is to be limited only by the terms of the appended claims.

Claims

1. A heat exchanger, having: multiple first flow channels (4) of a cooling medium arranged one over another,second flow channels (5) of a process medium, which are arranged between the first flow channels (4) and are provided on their ends with manifold boxes (7, 8),the first and second flow channels (4, 5) each being formed by partition plates (2) and first and second block profiles (3, 6), which hold these partition plates spaced apart, and lamellae (9, 10) arranged between respective block profiles (3, 6),the first block profiles (3) delimiting the first flow channels (4) being designed as C-shaped,two springy legs (32) extending in the direction of the lamellae (9) from a base (31) of the first block profiles (3) and delimiting a recess (33) open in the direction of the lamellae (9) between them,

2. The heat exchanger (1) according to claim 1, characterized in that the base (31) of the block profiles (3) is designed as flexible on a side facing away from the lamellae (10).

3. The heat exchanger (1) according to claim 1 or 2, characterized in that the base (31) of the block profiles (3) is designed as flexible on a side facing toward the lamellae (10).

4. The heat exchanger (1) according to one of the preceding claims, characterized in that the base (31) of the block profiles (3) has recesses (38) extending parallel to the flow direction (X) of the flow channels (4) of the cooling medium.

5. The heat exchanger (1) according to claim 4, characterized in that the recesses (38) are designed as slotted.

6. The heat exchanger (1) according to claim 5, characterized in that the ends of the recesses (38) are widened in the interior of the base (31).

7. The heat exchanger (1) according to claim 6, characterized in that the ends of the recesses (38) are widened circularly in cross-section.

8. The heat exchanger (1) according to one of preceding claims 5 to 7, characterized in that the walls of webs (36, 37) of the base, which face toward the slotted region of the recesses (38), extend parallel to one another.

9. The heat exchanger (1) according to one of preceding claims 5 to 7, characterized in that the walls of webs (36, 37) of the base, which face toward the slotted region of the recesses (38), extend conically to one another.

10. The heat exchanger (1) according to one of preceding claims 5 to 9, characterized in that the recesses (38) are alternately arranged on the side facing away from the lamellae (10) and the side facing toward the lamellae (10).

11. The heat exchanger (1) according to claim 10, characterized in that the sum of the length (m, n) of the alternately arranged recesses (38) is greater than the length (b) of the base (31) of the first block profile (3).

12. The heat exchanger (1) according to one of the preceding claims, characterized in that the first block profile (3) consists of a spring-elastic material.

13. The heat exchanger (1) according to one of the preceding claims, characterized in that the ratio of length (m) of the recesses (38) to length (b) of the base (31) of the first block profile (3) is between 0.4 and 0.9.

14. The heat exchanger (1) according to one of the preceding claims, characterized in that the ratio of narrowest width (h1, h2) of the recesses (38) to the width (h) of the base (31) of the first block profile (3) is between 0.1 and 0.3.