JP4944009B2 - Laminated disk heat exchanger - Google Patents

Description

  The present invention relates to a laminated disk heat exchanger for automobiles, in particular an in-tank oil cooler incorporated in a coolant box of a coolant cooler, and a plurality of vertically long stacked and bonded together, particularly brazed. It relates to a disk having disks, each disk being assembled from two disk halves and surrounding a cavity for the passage of a cooled medium such as oil in the longitudinal direction of the disk.

The disk-type heat exchanger known from US Pat. No. 5,697,097 has disks stacked and brazed together, the disks being assembled from two identical disk halves rotated 180 ° relative to each other and for guiding the medium to be cooled Surrounds the cavity. The disk halves have coining edges for brazing the disk halves into a single disk and connecting surfaces for brazing the disks to each other. Further, the disc half is provided with a frustoconical coining portion on the inner surface and the outer surface. The disk half is shaped mirror-symmetrically with respect to its horizontal axis and / or longitudinal axis. The frustoconical coining portions are arranged in a grid pattern between the connection surfaces. Positive coining parts are alternated with negative coining parts. The positive coining portion and the negative coining portion are formed in a protruding shape. When assembled, the disk halves surround a cavity through which fluid, for example oil, flows. Protrusions protruding into the cavity provide good vortexing of the oil and are believed to increase strength due to its tension bar function.
German Patent Invention No. 4308858

  An object of the present invention is a laminated disk heat exchanger for an automobile, particularly an in-tank oil cooler, which has a plurality of vertically long disks stacked and bonded to each other, in particular, brazed to each other. Laminated disk shape that is constructed from two identical disk halves rotated 180 ° and surrounds a cavity for the passage of a cooled medium such as oil in the longitudinal direction of the disk and is simple and inexpensive to manufacture It is to provide a heat exchanger. Nevertheless, the laminated disk heat exchanger according to the invention shall ensure good vortexing of the medium to be cooled in the cavity formed between the disk halves.

  The object is to provide a laminated disk heat exchanger for automobiles, in particular an in-tank oil cooler incorporated in a coolant box of a coolant cooler, which are stacked and joined together, in particular a plurality of longitudinal disks brazed Each of which is assembled from two disk halves and encloses a cavity for the passage of a medium to be cooled, such as oil, in the longitudinal direction of the disk. However, this is solved by the fact that the groove extends from one long side of the disk half to the opposite long side. The disc is also called a flat tube or plate. The transition of the groove ensures the flow of coolant from one long side of the disk half to the opposite long side. Within the cavity, the grooves provide a good vortexing of the cooled medium.

BEST MODE FOR CARRYING OUT THE INVENTION

  A preferred embodiment of the stacked disk heat exchanger is characterized in that the longitudinal disks are assembled from two identical disk halves that are rotated 180 ° from each other. This greatly simplifies the production of the laminated disk heat exchanger according to the invention.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the grooves extend linearly from one long side of the disk half to the opposite long side. This ensures a smooth flow of coolant from one long side of the disk half to the opposite long side.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the grooves are coined on one side of each disk half. The groove is formed by, for example, a linear, vertically long thin depression coined on one side of a thin plate material. Since the groove is coined only on one side, the manufacture of the disk half is simplified.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the groove is limited by a peripheral edge on the long side. The circumferential edge serves to bond, in particular braze, the two disc halves together. This seals the cavity between both disk halves against the surroundings.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that one disk is formed by two adjacent disk halves and the grooves of the disk halves are coined outward. The groove defines the flow path of the cooling medium inside the disk. A cooling medium inlet is mainly provided at one end of the disk, and an outlet is provided at the other end of the disk.

  Another preferred embodiment of a laminated disk heat exchanger is characterized in that the two disks are adjacent to each other at their raised areas formed by the grooves and are joined together by a brazing process. Between the raised areas, coolant, such as water, can reach from one long side of each disk half to the opposite long side. In addition, the discs are equipped with protruding raised areas in the edge areas of the through holes, in which the disks are also brazed to one another.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the grooves extend at an angle of 35 ° to 55 °, in particular 45 °, with respect to the longitudinal axis of the attached disk half. This on the one hand ensures that the medium to be cooled can flow from one end of the disc to the other end in a cavity formed inside the disc. On the other hand, the groove transition according to the invention also ensures that the coolant can flow from one long side to the opposite long side in the two disks.

  Another preferred embodiment of the stacked disk heat exchanger is characterized in that the grooves of two adjacent disk halves are arranged at an angle of 70 ° to 110 °, in particular 90 ° to each other. This provides a flow path inside the disk for the medium to be cooled, which flow path has many turnings and vortices. The advantage of this is that the boundary layer that forms in the cavity during operation is chopped again and again. As a result, heat transfer is significantly improved compared to smooth passages without grooves. In other words, the medium to be cooled is subjected to many changes in direction when it flows through the cavity. On the other hand, the coolant can flow almost linearly in the groove between two adjacent disks. An angle of 90 ° results in a substantially circular wax meniscus at the junction of the two grooves. This causes the flow to be affected the same along and across the main flow direction of the medium to be cooled. The angle is mainly 80 ° to 100 °.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the grooves have a depth of 0.8 to 1.5 mm, in particular 1.15 mm. This depth has proven particularly advantageous within the framework of the invention. Particularly in the case of a fuel cooler, the groove has a depth of mainly 0.5 mm to 1.5 mm.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the grooves of one disk half are arranged parallel to each other at a mutual distance of 3-5 mm, in particular 4 mm. This pitch dimension has proven particularly advantageous within the framework of the invention.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the disk halves have a width of about 20-50 mm. This width has proven particularly advantageous within the framework of the invention. In the case of commercial vehicles, the disk halves mainly have a width of about 20 to 120 mm. The particularly preferred width is 70 to 80 mm, in particular 76 mm.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the hydraulic diameter has a value of 1.5 to 2.5 mm, in particular 1.8 mm. This value proved to be particularly advantageous within the framework of the present invention.

  The hydraulic diameter between two adjacent disk halves along the main flow direction of the medium to be cooled represents the ratio between the flowable cross section and the heat transfer surface. The hydraulic diameter is defined as 4 times the ratio of area ratio to surface density. The area ratio is calculated as the ratio of the free path crossing area and the total positive area of the path between two adjacent disk halves. The areal density is calculated from the ratio between the heat transfer surface and the block volume. The hydraulic diameter will have to be as constant as possible mainly throughout the main flow direction of the medium to be cooled. This achieves a uniform flow of cavities between the two disk halves.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the disk halves are made of a metallic material, in particular aluminum or special steel. The disks are connected to each other mainly by hard soldering. Special steel is preferably used in the case of commercial vehicles.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that at least one side of the disk half is coated with a brazing flux. Thereby, the manufacturing process of the laminated disk type heat exchanger according to the present invention can be simplified.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the disk halves have a pair of through holes as inflow and outflow lines, respectively. The medium to be cooled reaches through the through hole into a cavity between two disk halves forming one disk or one flat tube. The disc may be referred to as a plate, and the disc half may be referred to as a plate half.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the edge region of the through-hole is raised. Mainly the edge region of the through hole is raised just like a groove or corrugation. Two adjacent raised edge regions of different disk halves seal the through hole and the cavity connected to the through hole between the two disk halves against the environment around which the coolant flows.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that irregularities are provided in the edge region of the through holes. The irregularities help to reinforce the disk half in the area of the through holes.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the irregularities are formed in a corrugated shape with a wave front and wave valley in the inlet region when viewed in cross section. The wave front and wave valley provide a substantially point-like contact between two adjacent disk halves.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that a plurality of disk halves are brazed substantially linearly with adjacent disk halves, both on their inner and outer surfaces in the inlet region. This significantly increases the resistance to internal pressure of the tube formed by each two disk halves.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the irregularities extend at least partly around the through-holes in a serpentine shape when viewed in plan view. This enlarges the contact surface between each two disk halves.

  In another preferred embodiment of the laminated disk heat exchanger, each two disk halves are joined together by a bending ridge extending in the longitudinal or lateral direction to form a cooling medium conduit mechanism. It is characterized by that. Since both disc halves are already joined together at the bending ridges, the disc halves still only have to be brazed together on one side. Thereby, the cross section which distribute | circulates a to-be-cooled medium increases. Furthermore, since only one part is required per pipeline mechanism, the number of required individual parts is reduced by half.

  Another preferred embodiment of the laminated disk heat exchanger is that the ducting mechanism is formed by a longitudinal, in particular substantially rectangular plate, which is divided into two longitudinal halves by a bending ridge, which halves It is characterized by being folded. The plate is an embossed stamped part mainly made of a metal material, and can be manufactured easily and inexpensively. When folded, the plate halves overlap completely.

  Another preferred embodiment of the stacked disk heat exchanger is characterized in that the plate has a raised peripheral edge compared to the plate surface. Mainly, the plate is roughened inside the peripheral edge, and the depth of the roughened surface is half the inner width of the pipe mechanism.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that the circumferential edge is interrupted at the intersection with the bending ridge. In the area of the bending ridge, the plate has the same depth over the entire length of the bending ridge. This prevents undesirable breakage of the plate material in the area of the bending ridge when folded.

  Another preferred embodiment of the laminated disk heat exchanger is characterized in that both plate halves are adjacent to one another at the circumferential edge when folded. Mainly the plate halves are brazed to each other at the peripheral edge.

  In the vehicular cooler having at least one water box, the above problem is solved by incorporating the laminated disk heat exchanger into the water box.

  Other advantages, features and details of the invention will become apparent from the following description, in which one embodiment is described in detail with reference to the drawings. Each feature recited in the claims and specification can be essential to the invention either individually or in any combination.

  FIG. 1 shows one disc half 1 in a perspective view. The disk half 1 is in the form of a vertically long plate made of an aluminum thin plate, and has two linear long sides 2 and 3 arranged in parallel to each other. The disk half 1 has its ends 4 and 5 rounded into a semicircle. Through holes 8 and 9 are provided at the ends 4 and 5. The edge regions 10 and 11 of the through-holes 8 and 9 are recessed and coined, and the edge regions 10 and 11 are raised on the lower surface of the disk half 1.

  A number of grooves 12 are coined in the disk half 1 between the through holes 8, 9. The groove 12 extends linearly from one long side 2 of the disk half 1 to the opposite long side 3. The groove has a shape of a vertically long bulge raised on the lower surface of the disk half 1. However, the grooves are not linear but can be extended, for example, in a corrugated or zigzag manner.

  FIG. 2 shows the end 4 of the disk half 1 of FIG. 1 in a bottom view. The edge grooves 21 to 30 of the edge regions 10 and 10 are raised from the illustrated plane. The ends of the grooves 21 to 30 are rounded on the long sides 2 and 3. Reference numeral 31 denotes a longitudinal axis of the disk half 1. The grooves 21 to 30 are arranged at an angle α of 45 ° with respect to the longitudinal axis 31.

  As can be seen in FIG. 3, the disk half 1 has a waveform profile when viewed in cross section. The corrugated cross-sectional profile is formed by grooves that are coined on one side of the disk half 1.

  FIG. 4 shows two disc halves 1 and 42 in perspective view. The side surfaces of the disk halves 1 and 42 where the grooves are raised face each other.

  As can be seen in FIG. 5, the disk half 42 has exactly the same shape as the disk half 1. However, the disk half 42 is arranged to be rotated 180 ° with respect to the disk half 1. A distal end 44 having a through hole 48 whose edge region 50 is raised from the illustrated plane is disposed over the through hole 8 in the distal end 4 of the disk half 1, and the protruding edge region 10 of the through hole 8 is in the illustrated plane. It is raised. The groove 52 formed in the disk half 42 protrudes outward from the illustrated plane. The groove 52 is arranged at an angle β of 90 ° with respect to the groove 12 raised in the illustrated plane. Both disc halves 1, 42 are brazed together at the groove contact point and the edge regions 2, 3 to form one disc or flat tube.

  In FIG. 6, a large number of disks 60 are brazed to each other. On the bottom surface, the through hole of the disk 60 is closed by termination disks 61 and 62. Connection fitting tubes 67 and 68 are placed in the through holes at the end of the upper surface of the disk 60. The medium to be cooled can be introduced into the disk 60 through one of the connection fitting pipes 67 and 68. The medium to be cooled can flow out of the disk 60 through the other connection fitting pipes 68 and 67.

  FIG. 7 shows the termination disk 61 in an enlarged perspective view. The termination disk 61 is in the shape of a circular disk 64 and has a circular ridge 65 at the center. The outer diameter of the circular raised portion 65 is adapted to the inner diameter of the through hole attached to each disk.

  As can be seen in FIGS. 8 and 9, the stacked disk heat exchanger shown in perspective view in FIG. 6 includes seven disks 71-77 stacked. A large number of substantially zigzag flow paths for the medium to be cooled are formed inside the disks 71 to 77, and the flow paths are between the disks 71 to 77 in a recessed area between the two grooves. Thus, it extends linearly from one side of the corresponding disc half to the opposite side.

  FIG. 10 shows a water box 78, and the laminated disk heat exchanger shown in FIG. 6 is incorporated in this water box. The disk 60 is disposed inside the water box 78. The end fitting pipes 67 and 68 project outward from the water box 78.

  In FIG. 11, the water box 78 of FIG. 10 is attached to one side of the cooling net 79. Another water box 80 is attached to the opposite side of the cooling net 79. Both water boxes 78, 80 and the cooling net 79 together form an automotive coolant cooler 81 (not shown).

  The profile of the disk halves 1 and 42 is designed so that the waveform profile contacts in a dot-like fashion when the disks are stacked. As a result, a change in three directions occurs for the medium to be circulated inside the disk. The large number of contact points where both disc halves are brazed together ensure good compressive strength. The leg angle of the profile is 45 ° with respect to the main flow direction of the medium to be cooled. The hydraulic diameter is 1.8 mm. The unevenness angle is in the range of 20 ° to 60 ° with respect to the main flow direction. The hydraulic diameter can be varied between 1.5 mm and 2.5 mm.

  Large area coinings in the inlet and outlet regions allow for tight coupling of the disks without the need for additional members. The disk halves have a horizontal brazing surface, which ensures a sufficient flow of coolant through the outside of the cooler. The peripheral edge of the disk half is mainly bent slightly. This improves the flatness of the disc when it is unbrazed. The chamfer angle is 5 ° to 20 °, mainly 10 °. The disc halves are made of aluminum and joined together by a wheel brazing process.

  As can be seen in FIG. 12, each two disk halves are joined together by wax meniscus 101, 102 and 103, 104. As can be seen in FIG. 13, the wax meniscus 101 to 104 is configured in a substantially circular shape in a plan view.

  FIG. 14 shows a disk half 1 of a laminated disk heat exchanger according to the present invention according to another embodiment. The same reference numerals are used to represent the same parts as in the embodiment shown in FIG. To avoid repetition, it is instructed to refer to the above description for FIG. In the following, only the differences between the examples will be mentioned.

In the disk half 1 shown in FIG. 14, the edge regions 110 and 111 of the through holes 8 and 9 are provided with irregularities. The disk half 1 has meandering irregularities 115 and 116 in the edge region 111 of the end 5, and the irregularities are coupled by a coupling groove 117. The disk half 1 has serpentine irregularities 118 and 119 in the edge region 110 of the end 4, and the irregularities are coupled to each other by a coupling groove 120. Each of the two disk halves 1 as shown in FIG. 14 is, as described above, the contact point of the groove 12, the edge regions 2, 3, to form one disk or flat tube, also referred to as a conduit mechanism. And rugged portions 118, 119 are brazed to each other.

  The cooler block shown in a side view in FIG. 15 includes a plurality of stacked flat tubes.

  16 is a cross-sectional view taken along line XVI-XVI in FIG. As can be seen from this cross-sectional view, the various flat tubes of one cooler block are linearly connected to each other by means of the meandering irregularities 115, 116 and the irregularities 118, 119 in a stacked manner.

  FIG. 17 is a cross-sectional view taken along line XVII-XVII in FIG. As can be seen in this cross-sectional view, the number of substantially linear contact surfaces is increased by meandering irregularities 116. The serpentine irregularities 116 are also referred to as reinforcing groove portions. It can be seen here how the irregularities are brazed together at the end of the disk, both inside and outside the laminated disk heat exchanger.

  18 is a cross-sectional view taken along line XVIII-XVIII in FIG. Here it can be seen how the irregularities 119 are brazed to each other at the disk end 4 on both the inner and outer surfaces of the laminated disk heat exchanger.

  FIG. 19 shows an enlarged view of the detail XIX in FIG. The shapes of the unevenness 118 and 119 are implemented such that the disks stacked one above the other are linearly brazed to each other on the inner surface and the outer surface. Thereby, the internal pressure strength of one pipe formed by two disk halves is remarkably increased. The disk coupling is shown in a meandering manner in FIG.

  FIG. 20 shows the pipe mechanism 140, also called a flat or short pipe, in an open state. The plate 142 forming the flat tube 140 has a substantially rectangular shape, and the corners of the rectangle are rounded. The plate 142 is a stamped part made of an aluminum thin plate, and has a bent ridge 143. The bent ridge divides the plate 142 into two equal-sized halves 145 and 146 in the longitudinal direction, and these halves are both disc halves. Called. Both disk halves 145, 146 are identical to the disk halves of the previous embodiment except for their integral configuration. A circumferential edge 148 defining the plate 142 on the outside serves to braze both plate halves 145, 146 together when folded or closed. Inside the peripheral edge 148, the plate halves 145, 146 are provided with concave and convex grooves as described above.

  FIG. 21 shows the tube 140 partially closed.

  In FIG. 22, the pipe 140 is shown in a plan view in a closed state. The tube 140 is the uppermost flat tube of the laminated disk heat exchanger having a plurality of flat tubes stacked one above the other.

  FIG. 23 shows the laminated disk heat exchanger of FIG. 22 in a side view. As can be seen in this side view, in addition to the flat tube 140, the laminated disk heat exchanger still includes six other flat tubes 150-155 that are brazed together in a stacked manner.

  24 is a cross-sectional view taken along line XXIV-XXIV in FIG. As can be seen from this cross-sectional view, the laminated disk heat exchanger is formed of folded flat tubes 140 and 150 to 155. The integral configuration of the flat tube reduces the number of parts required to construct a laminated disk heat exchanger by half. A folded flat tube has the advantage that the length of the sealing wax joint is reduced by almost half.

It is a perspective view of a disk half piece. FIG. 2 is a bottom view of the end of the disk half piece of FIG. 1. FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2. It is a perspective view of two disk half pieces. FIG. 5 is an enlarged partial view of FIG. 4. FIG. 6 is a perspective view of seven disks assembled into a laminated disk heat exchanger according to the present invention. It is an expansion perspective view of the termination | terminus disk of the lamination | stacking disk type heat exchanger shown in FIG. It is a cross-sectional view of the terminal of the laminated disk type heat exchanger shown in FIG. The end of the laminated disk heat exchanger shown in FIG. 6 is shown in a side view. It is a perspective view of a water box incorporating a laminated disk heat exchanger. The cooler incorporating the water box as shown in FIG. 10 is shown. FIG. 3 is a diagram of a wax meniscus in a passage area. 1 is a plan view of a substantially circular wax meniscus. FIG. FIG. 4 is a plan view of a laminated disk heat exchanger according to another embodiment of the present invention. The laminated disk type heat exchanger of FIG. 14 is shown with a side view. It is sectional drawing along the XVI-XVI line of FIG. It is sectional drawing along the XVII-XVII line | wire of FIG. It is sectional drawing along the XVIII-XVIII line | wire of FIG. FIG. 15 is an enlarged view of detail XIX in FIG. 14. The pipe line mechanism concerning the present invention is shown with the top view in the state where it opened. The pipe line mechanism of FIG. 20 is shown in a half-folded state. FIG. 22 is a plan view showing a stacked heat exchanger with a closed pipe mechanism as shown in FIGS. 20 and 21 in a closed state. The laminated disk type heat exchanger of FIG. 22 is shown with a side view. FIG. 23 is a cross-sectional view taken along line XXIV-XXIV in FIG. 22.

Claims (24)

A laminated disk heat exchanger for automobiles, in particular, an in-tank oil cooler incorporated in a coolant box of a coolant cooler, and has a plurality of vertically long disks (71 to 77) stacked and coupled to each other. These discs are each assembled from two disc halves and surround a cavity for passing a medium to be cooled, such as oil, in the longitudinal direction of the disc, and each of the disc halves (1, 42) has a number of grooves ( 21 to 30), and the groove extends from one long side (2) of the disk half (1) to the opposite long side (3), and has two irregularities (115 , 116, 118). 119 ) are provided in a meandering manner along the respective edge regions (110, 111) of the through holes (8, 9), and these two concaves and convexes (115, 116 , 118, 119 ) are connected to the coupling groove portion (117). 120), Disc halves (1), to the adjacent disks halves (1), the laminated disk type heat exchanger, characterized in that are brazed linearly at an outer surface not only the inner surface of the disc halves (1).   2. Laminated disk heat exchanger according to claim 1, characterized in that the longitudinal disk is assembled from two identical disk halves (1, 42) which are rotated 180 [deg.] From each other.   The laminated disk heat exchanger according to any one of claims 1 to 2, wherein the groove extends linearly from one long side of the disk half to the opposite long side.   The laminated disk heat exchanger according to any one of claims 1 to 3, wherein the groove (21-30) is coined on one side of each disk half (1).   The laminated disk heat exchanger according to any one of claims 1 to 4, characterized in that the grooves (21 to 30) are limited by a peripheral edge on the long side.   A disk is formed by two adjacent disk halves (1, 42), and the grooves (12, 52) of the disk halves are coined outwardly. A laminated disk heat exchanger according to any one of the above.   Lamination according to any one of the preceding claims, characterized in that two discs (71, 72) are adjacent to each other in their raised areas formed by grooves and are brazed to each other. Disc type heat exchanger.   A groove (21-30) extending at an angle of 35 ° to 55 °, in particular 45 °, with respect to the longitudinal axis (31) of the attached disk half (1), The laminated disk heat exchanger according to any one of 7.   9. A groove according to claim 1, characterized in that the grooves (12, 52) of two adjacent disk halves (1, 42) are arranged at an angle of 70 ° to 110 °, in particular 90 ° to each other. A laminated disk heat exchanger according to any one of the preceding claims.   The laminated disk heat exchanger according to any one of claims 1 to 9, characterized in that the grooves (21-30) have a depth of 0.5-1.5 mm, in particular 1.15 mm.   11. The groove (21-30) of one disc half (1) is arranged parallel to each other at a mutual distance of 3-5 mm, in particular 4 mm. Laminated disk type heat exchanger.   Laminated disk heat exchanger according to any one of the preceding claims, characterized in that the disk halves (1, 42) have a width of about 20-120 mm, in particular 20-50 mm.   The laminated disk heat exchanger according to any one of claims 1 to 12, characterized in that the hydraulic diameter has a value of 1.5 to 2.5 mm, in particular 1.8 mm.   14. Laminated disc heat exchanger according to claim 1, characterized in that the disc halves (1, 42) are made of a metal material, in particular aluminum or special steel.   15. A laminated disk heat exchanger according to claim 14, characterized in that at least one side of the disk half (1, 42) is coated with a brazing flux.   16. Laminated disc heat exchange according to any one of the preceding claims, characterized in that the disc half (1) has a pair of through-holes (8, 9) as inflow and outflow conduits, respectively. vessel.   The stacked disk heat exchanger according to claim 16, characterized in that the edge regions (10, 11; 110, 111) of the through holes (8, 9) are raised. Irregularities (115,116,118,119), characterized in that is constituted in the waveform has a crest and wave troughs viewed in cross section, the laminated disc shaped according to any one of claims 1 to 17 Heat exchanger. Each of the two disk halves (145, 146) is integrally connected to each other by a bending ridge (143) extending in the longitudinal direction or the lateral direction to form a cooling medium conduit mechanism (140). The laminated disk heat exchanger according to any one of claims 1 to 18 . The conduit mechanism (140) is formed by a substantially rectangular plate (142), which is divided into two longitudinal halves (145, 146) by a bending ridge (143), which are folded. The laminated disk heat exchanger according to claim 19, wherein 21. Laminated disk heat exchanger according to claim 20 , characterized in that the plate (142) has a raised peripheral edge (148) compared to the plate surface. The laminated disk heat exchanger according to claim 21 , characterized in that the circumferential edge (148) is interrupted at the intersection with the bending ridge (143). 23. Laminated disk heat exchanger according to claim 21 or 22 , characterized in that in the folded state both plate halves (145, 146) are adjacent to each other at a circumferential edge (148). An automotive cooler having at least one water box, wherein the laminated disk heat exchanger according to any one of claims 1 to 21 is incorporated in the water box.

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