KR20060130207A - Laminate heat exchanger - Google Patents

Abstract

The present invention relates to a laminate heat exchanger, in particular an oil cooler in a tank, installed in a cooler casing of a vehicle cooler cooler. This heat exchanger comprises a plurality of laminated, interconnected and in particular solder plates (71-77), each of which consists of two half plates, with the medium to be cooled such as oil being half plates. The hollow space part passing in the longitudinal direction of is sealed. Each half plate has a plurality of grooves extending from the longitudinal one side of the half plate to the longitudinal opposite side to produce a laminate heat exchanger that can be economically produced.

Description

Laminated Plate Heat Exchanger {STACKED-PLATE HEAT EXCHANGER}

FIELD OF THE INVENTION The present invention relates to a laminated heat exchanger, in particular consisting of two identical half plates which are laminated together for automotive use, in particular interconnected by soldering and in each case rotated 180 ° from each other and are oil-like in the longitudinal direction of the plates. It relates to an in-tank oil cooler in a tank having a plurality of swash plates enclosing a cavity through which the medium to be cooled.

German publication DE 43 08 858 C2 consists of two identical plate halves rotated at 180 ° at a normal layer, soldered one plate above another, and rotated at 180 ° and provide a cavity for conduction of the medium to be cooled. Disclosed is a plate heat exchanger with enclosing plates. This half plate is provided with embossed edges for soldering the half plate to form the plate and connection faces for soldering the mutual plate. Furthermore, the half plates are provided with truncated conical embossing on the inside and outside. The half plates are formed mirror-symmetrically about the transverse and / or longitudinal axis of the plate. The truncated conical embossings are arranged in a checkerboard manner between the connecting surfaces. Positive embossings intersect with negative embossings. Positive embossings and negative embossings are in the shape of a knob. In the assembled state, the half plates enclose a cavity through which the fluid, for example oil, flows. These cavity protruding knobs are intended to ensure good swirling of the oil and to increase strength as a result of the tie rod function.

It is an object of the present invention to provide an automotive laminated heat exchanger, in particular an in-tank oil cooler in a tank, having a plurality of elongate plates, the elongated plates being laminated to each other, in particular soldered together And in each case consists of two identical half plates rotated by 180 ° to each other and encloses a cavity through which the medium to be cooled, such as oil, in the longitudinal direction of the plates, the laminate heat exchanger being simple in shape and cost-effective Can be produced. Nevertheless, the laminate heat exchanger according to the invention will ensure a good vortex of the medium to be cooled between the cavities formed between the two half plates.

 The elongated plates are composed of two identical half plates stacked on one another, in particular interconnected by soldering, in each case being rotated by 180 ° in each case, and enclosing a cavity enclosing a cavity through which the medium to be cooled, such as oil, in the longitudinal direction of the plates In a laminated heat exchanger for automobiles having an elongated plate, in particular an oil cooler in a tank,

The object of the present invention is achieved by each half plate having a plurality of grooves that are continuous from the longitudinal one side of the half plate to the longitudinal opposite side. The half plate is also shaped into flat tubes or panels. The continuation of the grooves ensures the passage of the refrigerant from the longitudinal one side of the half plate to the longitudinal opposite side. The grooves in the cavity ensure a good swirl of the medium to be cooled.

A preferred embodiment of a laminate heat exchanger is characterized in that in each case the elongated plates consist of two identical half plates rotated 180 ° to each other. The production of the laminate heat exchanger according to the invention is thereby significantly simplified.

Another preferred embodiment of the laminate heat exchanger is characterized in that the grooves continue in a straight line from the longitudinal one side of the half plate to the longitudinal opposite side. This ensures an uninterrupted passage of coolant from the longitudinal one side of the half plate to the longitudinal opposite side.

Another preferred embodiment of the laminate heat exchanger is characterized in that the grooves in each half plate are embossed on one side. The grooves are formed of, for example, rectilinear, elongate, narrow depressions in the form of straight lines that are embossed on one side in thin metal sheet material. The production of the half plates is simplified since the grooves are embossed on only one side.

Another preferred embodiment of the laminate heat exchanger is characterized in that the grooves are delimited by the longitudinal sides of the longitudinal sides. The circumferential edge serves to interconnect the two half plates, especially in the soldering iron. The cavity between the two half plates is thereby sealed about the perimeter.

Another preferred embodiment of the laminate heat exchanger is formed by two half plates which are mutually supported and outwardly embossed grooves. The grooves define the flow path range of the medium to be cooled inside the half plate. The inlet for the medium to be cooled is preferably provided at one end of the half plate and the outlet for the medium is provided at the other end of the half plate.

Another preferred embodiment of the laminate heat exchanger is characterized in that the two plates are mutually supported by raised areas formed by grooves and interconnected by a soldering process. Refrigerant, such as water, may pass from the longitudinal one side of each half plate between the raised zones to the longitudinal opposite side. Furthermore, the half plates are also mounted in the edge region of the through holes with the cup-shaped raised regions which are soldered together.

Another preferred embodiment of the laminate heat exchanger is characterized by continuous at an angle of 35-55 °, in particular at an angle of 45 ° with respect to the longitudinal axis of the grooved half plate. This ensures, on the one hand, that the medium to be cooled can flow through the cavity formed inside the half plate from one end of the half plate to the multi-part. On the other hand, the continuation of the grooves according to the invention also ensures that the coolant can flow from the longitudinal side to the longitudinal opposite side in the two half plates.

Another preferred embodiment of the laminate heat exchanger is characterized in that the grooves of two mutually supporting half plates are arranged at an angle of 70-110 ° with respect to each other, in particular at an angle of 90 °. This provides a flow passage for the medium to be cooled with a large number of directional changes and vortices inside the half plate. The advantage is that the boundary layers formed in the cavity repeatedly collapse during operation. This results in a sharply degraded heat transition compared to smooth grooves without grooves. Thus, when the medium flows through the cavity, the medium to be cooled is subject to many direction changes. In comparison, the refrigerant can flow in a straight line, in fact, without being disturbed through the grooves between the two half plates which support each other. An angle of 90 ° actually produces a circular soldering meniscus at the connection point of the two grooves. The flow in the longitudinal and transverse directions with respect to the main flow direction of the medium to be cooled is thereby equally affected. The angle is preferably 80-100 degrees.

Another preferred embodiment of the laminate heat exchanger is characterized in that the grooves have a depth of 0.8-1.5 mm, in particular a depth of 1.15 mm. This depth has proved to be particularly advantageous within the scope of the present invention. Especially in the case of fuel coolers, the grooves preferably have a depth of 0.5-1.5 mm.

Another preferred embodiment of the laminate heat exchanger is characterized in that the grooves of the half plates are arranged parallel to each other at intervals of 3-5 mm, in particular at intervals of 4 mm. This dividing dimension proves to be particularly advantageous within the scope of the present invention.

Another preferred embodiment of the laminate heat exchanger is characterized in that the half plates have a width of approximately 20-50 mm. Another preferred embodiment of a laminate heat exchanger has proven that this width is particularly advantageous within the scope of the present invention. In commercial vehicles, the half plates preferably have a width of approximately 20-120 mm. Particular preference is given to a width of 70-80 mm, in particular a width of 76 mm.

Another preferred embodiment of the laminate heat exchanger is characterized in that the hydraulic diameter has a value of 1.5-2.5 mm, in particular of 1.8 mm. This value proves to be particularly advantageous within the scope of the present invention.

Another preferred embodiment of the laminate heat exchanger is that the hydraulic diameter between two adjacent half plates along the main flow direction of the medium to be cooled constitutes the ratio between the through-hole pipe cross section and the heat exchange zone. This hydraulic diameter is defined as four times the ratio of area ratio to area density. This area ratio is determined by the ratio of the free duct cross section to the total end surface area of the pipe between adjacent half plates. Area density is determined from the ratio of heat transfer area to block volume. The hydraulic diameter should preferably be kept as constant as possible throughout the main flow direction of the medium to be cooled. Uniform throughflow capability of the cavity between the two half plates is thereby achieved.

Another preferred embodiment of the laminate heat exchanger is characterized in that the two half plates are formed of metal material, in particular aluminum or high grade steel. These half plates are preferably interconnected by hard soldering. High grade steel is preferably used in commercial vehicles.

Another preferred embodiment of the laminate heat exchanger is characterized in that at least one side of the half plates is coated with a soldering aid material. The production process of the laminate heat exchanger according to the invention can thereby be simplified.

Another preferred embodiment of the laminate heat exchanger is characterized in that the half plate has in each case a pair of through holes as inflow lines and outflow lines. The medium to be cooled is passed through the through hole into a cavity between two half plates or flat tubes forming a plate. These half plates may also be designated as panels and half plates as half panels.

Another preferred embodiment of the laminate heat exchanger is characterized in that the edge region of the through hole is raised. It is preferable that the edge region of the through hole is raised to the same size as the grooves or the wave shape. The two raised edge zones of the mutually supported half plates plate seal the through-holes and the cavity between the two half plates which are connected to the through holes with respect to the flow around the refrigerant.

Another preferred embodiment of the laminate heat exchanger is characterized in that the embossings are provided in the edge region of the through hole. Embossing serves to reinforce the two half plates in the region of the through hole.

Another preferred embodiment of a laminate heat exchanger is that the wavy crests and wavy troughs, as can be seen in cross section, essentially provide a close contact between two adjacent half plates. .

Another preferred embodiment of the laminate heat exchanger is characterized in that in each case a plurality of half plates are soldered in the inlet zone in a substantially straight line to adjacent half plates which are inside and outside. In each case the internal pressure resistance of the tube formed of two half plates rises sharply.

Another preferred embodiment of the laminate heat exchanger is characterized in that the embossing is at least partially continuous around the through hole in a serpentine manner, as seen from above. The area of contact between the two half plates is thereby increased in each case.

Another preferred embodiment of a laminate heat exchanger is in each case two half plates being integrally interconnected by bending edges which are continuous in the longitudinal or transverse direction to form a conducting device for the medium to be cooled. Is characteristic. Since the two half plates are already integrally connected at the bending edges, the two plates only have to be soldered together on one side. The cross section through which the medium to be cooled is increased thereby. Furthermore, the number of individual parts required is reduced by half because only one part is needed for each conducting device.

Another preferred embodiment of a laminate heat exchanger is characterized in that the conducting device is formed of a substantially rectangular elongated panel subdivided into two elongated halves which are folded together by the bending edges. The panel is preferably embossed stamping made of a metal material which can be simply reduced in cost. In the folded state, the half panels consequently lay the other half panel on one side half panel.

Another preferred embodiment of the laminate heat exchanger is characterized in that the half panel has a perimeter edge raised relative to the panel surface. The half panel is embossed in the circumferential edge, with the depth of the embossed surface being preferably half the width of the conducting device.

Another preferred embodiment of the laminate heat exchanger is characterized in that the peripheral edge is obstructed at the intersection with the bending edge. The half panels in the region of the bend edge have the same depth over the entire length of the bend edge. This prevents undesirable damage to the panel material in the region of the bending edge during the folding operation.

Another preferred embodiment of the laminate heat exchanger is characterized in that the half panels are mutually supported with the peripheral edge in the folded state. The half panels are preferably soldered together at the perimeter.

In a vehicle cooler having at least a waterbox, the object specified above is achieved by installing the laminated heat exchanger described above in the waterbox.

Further advantages, features and details of the present invention may be obtained from the following detailed description in which the embodiments are described in detail with reference to the drawings. In this case the features mentioned in the claims and in the description may be essential to the invention in each case individually or in other combinations.

1 shows a perspective view of a half plate;

FIG. 2 shows a bottom view of one end of the half plate of FIG. 1; FIG.

3 shows a cross section along line III-III in FIG. 2;

4 shows a perspective view of two half plates;

5 shows an enlarged detail of FIG. 4;

6 shows a perspective view of seven plates assembled to form a laminate heat exchanger according to the invention;

FIG. 7 shows an enlarged perspective view of a closing-off plate of the laminate heat exchanger illustrated in FIG. 6;

8 shows a cross section through one end of the laminate heat exchanger illustrated in FIG. 6;

9 shows a side view of one end of the laminate heat exchanger illustrated in FIG. 6;

10 shows a perspective view of a waterbox with a laminated plate heat exchanger installed;

FIG. 11 shows a chiller with an installed waterbox as illustrated in FIG. 10;

12 is a sectional view showing an example of solder unevenness in the pipe portion;

13 actually shows a plan view of circular solder unevenness;

14 shows a top view of a laminate heat exchanger according to another embodiment of the present invention;

FIG. 15 shows a side view of the laminate heat exchanger of FIG. 14;

FIG. 16 shows a cross sectional view along line VI-VI of FIG. 14; FIG.

17 shows a sectional view along the line VII-VII of FIG. 14;

18 shows a sectional view along the line VII-VII of FIG. 14;

19 shows a detailed enlarged view of VII of FIG. 14;

20 is a plan view showing an open state of the folded state of the conducting device according to the present invention;

FIG. 21 is a plan view showing a state in which the conductor of FIG. 20 is folded in half;

FIG. 22 shows a top view of a laminate heat exchanger having a closed conductor in the closed state as illustrated in FIGS. 20 and 21;

FIG. 23 shows a side view of the laminate heat exchanger of FIG. 22, and

24 is a cross-sectional view taken along the line XIV-XIV of FIG. 22.

1 shows a perspective view of a plate half 1. This half plate 1 has the form of an elongated panel consisting of an aluminum sheet with two straight longitudinal sides 2, 3 arranged in parallel with each other. The half plate 1 is rounded in a semicircle at the ends 4, 5 of the plate. The through holes 8, 9 are provided in the ends 4, 5. The edge regions 10, 11 of the through holes 8, 9 are embossed in a concave manner, so that the edge regions 10, 11 are raised below the half plate 1.

The plurality of grooves 12 are embossed in the half plate 1 between the through holes 8, 9. The grooves 12 continue in a straight line from the longitudinal one side 2 of the half plate 1 to the longitudinal opposite side 3. The grooves take the form of an elongated recess which rises below the half plate 1. However, the grooves may also be continuous in a non-linear fashion, for example in a wavy or zigzag fashion.

2 shows a bottom view of the end 4 of the half plate 1 of FIG. 1. The edge region 10 and the ten grooves 21-30 are raised out of the drawing plane. The ends of the grooves 21-30 are rounded towards the longitudinal sides 2, 3. The longitudinal axis of the half plate 1 is represented by 31. The grooves 21-30 are arranged at an angle α of 45 ° with respect to the longitudinal axis 31.

As can be seen in cross-section in Figure 3 it can be seen that the half plate (1) has a corrugated form. The shape of the corrugated cross section is formed by grooves embossed on one side of the half plate 1.

4 shows two half plates 1, 42 in a perspective view. The sides of the half plates 1, 42, in which the grooves are raised, are raised away from each other.

In FIG. 5, it can be seen that the half plate 42 is exactly the same shape as the half plate 1. However, the half plate 42 is arranged to rotate 180 ° with respect to the half plate 1. One end having a through hole 48 and an edge region 50 which rises out of the plane of the drawing is disposed above the through hole 8 of the end 4 of the half plate 1, The cup-shaped edge region 10 is raised to the drawing plane. Grooves 52 which are raised in the drawing plane are formed in the half plate 42. The grooves 52 are arranged at an angle β of 90 ° with respect to the grooves 12 which rise to the drawing plane. The two half plates 1, 42 are soldered together at the contact points of the grooves and at the edge regions 2, 3 to form a plate or flat tube.

In FIG. 6, the plurality of plates 60 are soldered to each other. The through holes of the plurality of plates 60 are sealed at the lower side by the sealing plates 61 and 62. On top of the plurality of plates 60, connecting parts 67, 68 are placed in the through holes at the ends. The medium to be cooled can be introduced into the interior of the plurality of plates 60 through one of the connecting parts 67, 68. The medium to be cooled may flow out of the plurality of plates 60 out of the other connecting piece 67, 68.

7 shows the sealing plate 61 in an enlarged perspective view. The sealing plate 61 has the form of a circular plate 64 having a circular central elevation 65. The outer diameter of the circular center projection 65 is adapted to the inner diameter of the engaging through hole of each half plate.

8 and 9, it can be seen that the laminate heat exchanger illustrated in perspective view in FIG. 6 includes seven plates 71-77 in which another plate is stacked on one plate. In each case the medium to be cooled inside the seven consecutive plates 71-77 in a straight line between the seven plates 71-77 through a concave section between one side and the opposite side of the corresponding half plate. Multiple flow paths are formed that are essentially zigzag in shape.

FIG. 10 shows a waterbox 78 installed with the laminate heat exchanger illustrated in FIG. 6. Multiple plates 60 are disposed within waterbox 78. The connecting parts 67, 68 protrude out of the waterbox 78.

In FIG. 11, the waterbox 78 of FIG. 10 is installed on one side of the cooling network 79. Another water box 80 is installed on the other side of the cooling network 79. The two water boxes 78, 80 and the cooling network 79 together form a refrigerant cooler 81 for a vehicle (not shown).

Profiling of the half plates 1, 42 is designed such that the wave profiles are in intimate contact with each other when the plates are stacked on each other. This causes a change in direction repeatedly inside the plates for the through-flowing cooling medium. The multiple contact points at which the two half plates are soldered ensure good pressure stability. The leg angle of the shape is 45 ° with respect to the main flow direction of the medium to be cooled. The hydraulic diameter is 1.8 mm. Embossing angles range from 20-60 ° with respect to the main flow direction. The hydraulic diameter may vary between 1.5-2.5 mm.

Large area embossing in the inlet and outlet zones enables leaktight plate connections without the use of additional components. The half plate has horizontal soldering surfaces and thus ensures sufficient passage of refrigerant outside of the cooler. It is preferable that the half plate has a slight angle at the peripheral edge of the plate. The planeness of the plate in the unsoldered state is thereby improved. The edge angle is 5-20 degrees, preferably 10 degrees. The half plate consists of aluminum and is connected to the other half plate by a wheel-soldering process.

In FIG. 12, it can be seen that in each case the two half plates are connected to the other half plate by soldering concave-convex 101, 102; 103, 104. In FIG. 13, it can be seen that the solder bumps 101-104 are actually of circular design, as can be seen from the plan view.

Figure 14 shows a further embodiment of a half plate 1 of a laminate heat exchanger according to the invention. The same reference numerals as the embodiment illustrated in FIG. 1 are used to denote the same parts. The above description of FIG. 1 is made to prevent repetition. Only the differences between the embodiments are described below.

In the half plate 1 illustrated in FIG. 14, the edge regions 110, 111 of the through holes 8, 9 are provided with embossing. At the end 5 of the half plate 1, the edge region 111 has a serpentine embossing 115 which is connected by connecting beads. At the end 4 of the half plate 1 the edge region 110 has a serpentine embossing 118 which is connected to the other half plate by a connecting bead 120. The two half plates 1 as shown in FIG. 14 also form a plate or flat tube, represented by a conducting device, in each case at the contact point of the groove 12 and the edge region 2 as described above. In 3) and also in the embossings 118 and 119 to the other half plate.

FIG. 15 shows the side of a cooler block, which comprises a plurality of flat tubes with one tube stacked on top of another.

FIG. 16 is a cross-sectional view taken along the line VI-VI of FIG. 14. In cross section, the various flat tubes of the cooler block are connected in a straight line to each other in the region of the serpentine embossing 115, 116 and in a stacked structure at the embossing 118, 119.

17 is a cross-sectional view taken along the line VII-VII of FIG. 14. In this cross section the number of essentially straight contact surfaces is increased as a result of the embossing 116 of the serpentine shape. The serpentine form of embossing 116 is also represented by reinforcing beads. Here it can be seen how the embossings at the end of the plate are soldered to each other inside and outside the laminate heat exchanger.

18 is a cross-sectional view taken along the line VII-VII of FIG. 14. Here it can be seen how the embossings 119 at the plate end 4 are soldered to each other inside and outside the laminate heat exchanger.

FIG. 19 shows a detailed enlarged view of part “XIV” of FIG. 14. The form of the embossings 118 and 119 is designed such that the plates on which the other plate is stacked on one plate are soldered in a straight line to the inside and the outside. The internal pressure resistance of the tube formed from the two half plates is thereby sharply raised, the plate connection is illustrated in the serpentine manner of FIG. 19.

20 shows the conducting device 140, which is also represented as a flat tube or short tube in a folded-open state. The flat tube 140 is formed by a panel 142 that is essentially rectangular in shape and has rounded corners. This (rectangular) panel 142 is a stamping consisting of sheet aluminum having a bend edge 143, whereby the panel 142 is also made of two half plates 145 of the same size represented by half plates. 146) in the longitudinal direction. The two half plates 145, 146 coincide with the half plates of this embodiment in addition to being integrally shaped. The (rectangular) panel 142 serves to solder the two half plates 145 and 146 to each other in a state where the outer side is defined by the peripheral edge 148 and the peripheral edge is folded together. The half panels 145, 146 are provided with an embossed groove in the circumferential edge 148 as described above.

21 shows the tube 140 in a slightly sealed state.

22 shows the closed state of the tube 140 in a plan view. Tube 140 is the topmost flat tube of a laminate heat exchanger having a plurality of flat tubes stacked on top of each other.

FIG. 23 shows a side view of the laminate heat exchanger of FIG. 22. The laminate heat exchanger also includes six other flat tubes 150-155 in addition to the flat tubes 140, which are soldered together in a stacked structure.

24 is a cross-sectional view taken along the line XIV-XIV of FIG. 22. It can be seen from the cross section that the laminate heat exchanger is formed of folded flat tubes 140, 150-155. With flat tubes produced in one piece, the number of parts needed to make a laminate heat exchanger is reduced by half. Folded flat tubes have the advantage that the length of the sealed solder seam is actually reduced by half.

Claims (27)

Multiple sheets stacked together for automotive use, in particular interconnected by soldering, in each case consisting of two plate halves and enclosing a cavity through a medium to be cooled like oil in the longitudinal direction of the plates. In a laminated plate heat exchanger in an oil cooler in a tank provided in a refrigerant box of a refrigerant cooler having a plate, Laminated heat exchanger, characterized in that each of the half plates 1, 42 has a plurality of grooves 21-30 continuous from the longitudinal one side 2 of the half plate 1 to the longitudinally opposite side 3. group. The method of claim 1, Stacked heat exchanger, characterized in that the elongate plates consist of two identical half plates (1, 42) which in each case are rotated by 180 ° to each other. The method of claim 1, wherein Laminated heat exchanger, characterized in that the grooves continue in a straight line from the longitudinal one side of the half plate to the longitudinal opposite side. The method of claim 1, wherein Stacked heat exchanger, characterized in that the grooves (21-30) are embossed on one side in each half plate (1). The method of claim 1, wherein Laminated heat exchanger, characterized in that the grooves (21-30) is delimited on the longitudinal side by the peripheral edge. The method of claim 1, wherein A plate heat exchanger, characterized in that it is formed by two half plates (1, 42) which are mutually supported and grooves (12, 52) which are embossed outwardly. The method of claim 1, wherein Stacked heat exchanger, characterized in that the two plates (71, 72) are mutually supported and soldered to each other with the raised zone formed by the grooves. The method of claim 1, wherein Stacked heat exchanger, characterized in that the grooves (21-30) are continuous at an angle of 35-55 °, in particular at an angle of 45 ° with respect to the longitudinal axis (31) of the combined half plate (1). The method of claim 1, wherein Stacked heat exchanger, characterized in that the grooves (12, 52) of two mutually supported half plates (1, 42) are arranged at an angle of 70-110 ° to each other, in particular at an angle of 90 °. The method of claim 1, wherein Stacked heat exchanger, characterized in that the grooves 21-30 have a depth of 0.5-1.5 mm, in particular a depth of 1.15 mm. The method of claim 1, wherein Laminated heat exchanger, characterized in that the grooves (21-30) of the half plates (1) are arranged parallel to each other at intervals of 3-5 mm, in particular at intervals of 4 mm. The method of claim 1, wherein Stacked heat exchanger, characterized in that the half plates (1, 42) have a width of 20-120 mm, in particular 20-50 mm. The method of claim 1, wherein Stacked heat exchanger, characterized in that the hydraulic diameter is 1.5-2.5 mm, in particular 1.8 mm. The method of claim 1, wherein Laminated heat exchanger, characterized in that the half plates (1, 42) are formed of a metallic material, in particular aluminum or high grade steel. The method of claim 1, wherein Laminated heat exchanger, characterized in that at least one side of the half plate (1, 42) is coated with a soldering aid material. The method of claim 1, wherein The half-plate (1) is a stacked heat exchanger, characterized in that in each case has a pair of through holes (8, 9) as inflow lines and outflow lines. The method of claim 16, Stacked heat exchanger, characterized in that the edge region (10, 11; 110, 111) of the through hole (8, 9) is of an elevated shape. The method according to claim 16 or 17, An embossing (115-120) is provided in the edge region (110; 111) of the through holes (8, 9). The method of claim 18, Stacked heat exchanger, characterized in that the embossing (115, 116, 118, 119) is a wave design having wave crests and wave troughs. The method of claim 19, A multi-layer heat exchanger, characterized in that the plurality of half plates (1) are in each case essentially straight soldered to adjacent half plates on the inside and outside of the plate. The method of claim 19 or 20, Stacked heat exchanger, characterized in that the embossing (115, 116, 118, 119) is continuous at least in part in a meandering manner around the through holes (8, 9) as seen from above. The method of claim 1, wherein In each case the two half plates 145, 146 are integrally interconnected by bending edges 143 which are continuous in the longitudinal or transverse direction to form the conductor 140 for the medium to be cooled. Stacked heat exchanger, characterized in that. The method of claim 22, A conductive heat exchanger (140) characterized in that it is formed of an essentially rectangular panel (142) subdivided by a bend edge (143) into two elongated half plates (145, 146) which are folded together. The method of claim 23, wherein A rectangular heat exchanger, characterized in that the rectangular panel (142) has a circumferential edge (148) raised relative to the panel surface. The method of claim 24, The circumferential edge portion (148) is a laminated heat exchanger, characterized in that blocked by the bending edge portion (143) at the intersection point. The method of claim 24 or 25, Stacked heat exchanger, characterized in that the two half panels (145, 146) are mutually supported with the peripheral edge (148) in the folded state. In a car cooler with at least one waterbox, Automobile heat cooler, characterized in that the laminated heat exchanger according to any one of the above is installed in the water box.

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