EP1725824B1 - Stacked-plate heat exchanger - Google Patents

Description

The invention relates to a stacked plate heat exchanger, in particular a Intank oil cooler, for motor vehicles, with a plurality of stacked and interconnected, in particular soldered, elongated discs, which are composed of two identical, rotated by 180 ° to each other disc halves and a cavity for performing a medium to be cooled, such as oil, enclose in the longitudinal direction of the discs.

From the German patent application DE 43 08 858 C2 is a disc heat exchanger with stacked and mutually soldered discs known, which are composed of two identical, rotated by 180 ° to each other disc halves and enclose a cavity for conducting a medium to be cooled. The disc halves are provided with a distinct rim for soldering the disc halves to a disc and with pads for soldering the discs together. In addition, the disc halves are provided on the inner and on the outer surface with frustoconical characteristics. The disk halves are designed mirror-symmetrically to their transverse and / or longitudinal axis. The frusto-conical shapes are arranged in a checkerboard pattern between the connection surfaces. Positive characteristics alternate with negative characteristics. The positive characteristics and the negative characteristics are knob-like. In the assembled state, the disc halves enclose a cavity, which from a Fluid, such as oil, is flowed through. The protruding into this cavity pimples to ensure good swirling of the oil and increase the strength as a result of their Zugankerfunktion.

The US 2003/0131979 A1 discloses a stacked plate heat exchanger according to the preamble of claim 1.

The object of the invention is a stacked plate heat exchanger, in particular an Intank oil cooler, for motor vehicles, with several stacked and interconnected, in particular soldered, elongated discs, which are composed of two identical, rotated by 180 ° to each other disc halves and a Cavity for performing a medium to be cooled, such as oil, enclose in the longitudinal direction of the discs to create, which is simple and inexpensive to produce. The stacked plate heat exchanger according to the invention should nevertheless ensure a good swirling of the medium to be cooled in the cavity formed between the pan halves.

The object is achieved with the features of claim 1.

In a stacked plate heat exchanger, in particular an Intank oil cooler, for motor vehicles, with a plurality of stacked and interconnected, in particular soldered, elongated discs, which are composed of two disc halves and a cavity for carrying a medium to be cooled, such as oil in Enclose the longitudinal direction of the discs, each of the disc halves on a plurality of grooves which extend from one longitudinal side to the opposite longitudinal side of the disc half. The discs are also referred to as flat tubes or plates. The course of the grooves ensures the passage of coolant from one longitudinal side of the disc half to the opposite longitudinal side. In the cavity, the grooves ensure good turbulence of the medium to be cooled.

A preferred embodiment of the stacked-plate heat exchanger is characterized in that the elongated discs of each two the same, are assembled by 180 ° to each other rotated disc halves. This considerably simplifies the production of the stacked plate heat exchanger according to the invention.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that the grooves extend in a straight line from one longitudinal side to the opposite longitudinal side of the pane half. This ensures an unhindered passage of coolant from one longitudinal side of the disk half to the opposite longitudinal side.

Another preferred embodiment of the stacked-plate heat exchanger is characterized in that the grooves are formed on one side in each disc half. The grooves are formed by straight, elongated, narrow depressions, which are formed on one side, for example, in a sheet material. Since the grooves are pronounced only on one side, simplifies the manufacture of the disc halves.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that the grooves are bounded on the longitudinal sides by a peripheral edge. The peripheral edge serves to connect two disc halves together, in particular to be soldered. As a result, the cavity between the two disc halves is sealed to the environment.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that a disc is formed by two abutting disc halves whose grooves are pronounced outwards. The grooves in the interior of the disc limit the flow path of the medium to be cooled. Preferably, an inlet is provided at one end of the disc and an outlet for the medium to be cooled is provided at the other end of the disc.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that two discs with their abutting portions formed by the grooves abut each other and joined together by a soldering process. Coolant, for example water, can pass between the raised areas from one longitudinal side to the opposite longitudinal side of the respective half of the pane. In addition, the discs are provided in the edge region of through holes with cup-shaped, raised areas where the discs are also soldered together.

A further preferred embodiment of the stacked plate heat exchanger is characterized in that the grooves extend at an angle of 35 ° to 55 °, in particular of 45 °, to the longitudinal axis of the associated pane half. This ensures, on the one hand, that the medium to be cooled can flow from one end to the other end of the disc through the cavity formed in the interior of the disc. On the other hand, it is also ensured by the course of the grooves according to the invention that the coolant can flow in two disks from one longitudinal side to the opposite longitudinal side.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that the grooves of two abutting disc halves are arranged at an angle of 70 ° to 110 °, in particular of 90 ° to each other. As a result, a flow path is created for the medium to be cooled in the interior of the discs, which has many changes of direction and vortex. This has the advantage that during operation in the cavity forming boundary layers are repeatedly torn. This leads to a greatly diluted heat transfer compared to a smooth channel without grooves. The medium to be cooled is thus subjected to many changes of direction as it flows through the cavity. In contrast, the coolant can flow almost unhindered and straight through the grooves between two adjacent discs. The angle of 90 ° gives a nearly circular solder meniscus at the Verbiridungsstelle of the two grooves. As a result, the flow is influenced in the same way longitudinally and transversely to the main flow direction of the medium to be cooled. Preferably, the angle is 80 ° to 100 °.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that the grooves have a depth of 0.8 to 1.5 mm, in particular of 1.15 mm. This depth has proven to be particularly advantageous in the context of the present invention. In particular, in fuel coolers, the grooves preferably have a depth of 0.5 mm to 1.5 mm.

Another preferred embodiment of the stacked-plate heat exchanger is characterized in that the grooves of a half-disc are arranged parallel to each other at a distance of 3 to 5 mm, in particular of 4 mm, to each other. This pitch has proven to be particularly advantageous in the context of the present invention.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that the disc halves have a width of about 20 to 50 mm. This width has proven to be particularly advantageous in the context of the present invention. For commercial vehicles, the disc halves preferably have a width of about 20 to 120 mm. Particularly preferred is a width of 70 to 80 mm, in particular of 76 mm.

A further preferred embodiment of the stacked plate heat exchanger is characterized in that the hydraulic diameter has a value of 1.5 to 2.5 mm, in particular of 1.8 mm. This value has proved to be particularly advantageous in the context of the present invention.

The hydraulic diameter between two adjacent disc halves along the main flow direction of the medium to be cooled represents the ratio between the permeable channel cross section and the heat exchange surface. The hydraulic diameter is defined as four times the ratio of the area ratio to the area density. The area ratio is determined as the ratio of the free channel cross-section to the total end face of the channel between two adjacent pane halves. The area density is determined by the Ratio between the heat transfer surface to the block volume. The hydraulic diameter should preferably remain as constant as possible over the entire main flow direction of the medium to be cooled. As a result, a uniform flowability of the cavity between two disc halves is achieved.

A further preferred embodiment of the stacked plate heat exchanger is characterized in that the disc halves are formed from a metallic material, in particular aluminum or stainless steel. The discs are preferably joined together by brazing. Stainless steel is preferably used in commercial vehicles.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that at least one side of the disc halves is coated with soldering auxiliary material. Thereby, the manufacturing process of the stacked plate heat exchanger according to the invention can be simplified.

The disc halves each have a pair of through holes as inflow and outflow conduits. About the through holes, the medium to be cooled enters the cavity between two disc or a flat tube forming disc halves. The discs may also be referred to as discs and the disc halves as disc halves.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that the edge region of the through holes is formed raised. Preferably, the edge region of the through holes is raised as far as the grooves or waves. Two adjoining raised edge regions of different disk halves seal the through holes and the cavity communicating with the through holes between two disk halves with respect to the environment through which coolant flows.

Indentations are provided in the edge area of the through holes. The indentations serve to reinforce the disc halves in the area of the through holes.

The impressions are, viewed in section, wave-shaped in the inlet area with wave crests and wave troughs. The wave crests and wave troughs essentially create punctiform contacts between two adjacent pane halves.

A further preferred embodiment of the stacked-plate heat exchanger is characterized in that a plurality of pane halves are soldered in the entry region, both on its inside and on its outside substantially linearly with the respective adjacent pane halves. As a result, the internal pressure strength of the tubes formed from two disc halves increases sharply.

A stacked-plate heat exchanger according to the invention is characterized in that the indentations, seen in plan view, extend in a meandering manner at least partially around the through-holes. As a result, the contact area between two disc halves is increased.

A further preferred embodiment of the stacked-plate heat exchanger is characterized in that in each case two disc halves are integrally connected to each other by a longitudinally or transversely extending bending edge, to form a conduit means for the medium to be cooled. Since the two disc halves are already connected in one piece to the bending edge, they only need to be soldered together on one side. As a result, the cross-section through which the medium to be cooled flows increases. In addition, the number of required individual parts is reduced by half, since one part is still required per line device.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that the conduit means is formed by an elongate, in particular substantially rectangular, plate which is divided by the bending edge into two elongate halves which are folded together. The plate is preferably an embossed stamped part made of a metallic material which can be produced simply and inexpensively. In the folded state, the plate halves are congruent to each other.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that the plate has a relative to the plate surface raised peripheral edge. Preferably, the plate is embossed within the peripheral edge, wherein the depth of the embossed surface is half the width of the conduit means.

Another preferred embodiment of the stacked plate heat exchanger is characterized in that the peripheral edge is interrupted at the intersections with the bending edge. In the area of the bending edge, the plate has the same depth over the entire length of the bending edge. This avoids undesirable damage to the plate material in the area of the bending edge during folding.

Another preferred embodiment of the stacked-plate heat exchanger is characterized in that the two plate halves lie in the folded state with the peripheral edge to each other. Preferably, the plate halves are soldered to each other at the peripheral edge.

In a vehicle radiator with at least one water tank, the above-mentioned object is achieved in that a previously described stacked plate heat exchanger is installed in the water tank.

Figur 1

eine perspektivische Darstellung einer Scheibenhälfte;

Figur 2

ein Ende der Scheibenhälfte aus Figur 1 in der Untersicht;

Figur 3

die Ansicht eines Schnitts entlang der Linie III-III in Figur 2;

Figur 4

eine perspektivische Darstellung von zwei Scheibenhälften;

Figur 5

einen vergrößerten Ausschnitt aus Figur 4;

Figur 6

eine perspektivische Darstellung von sieben Scheiben, die zu einem erfindungsgemäßen Stapelscheiben-Wärmetauscher zusammengebaut sind;

Figur 7

eine vergrößerte, perspektivische Darstellung einer Abschlussscheibe des in Figur 6 dargestellten Stapelscheiben-Wärmetauschers;

Figur 8

die Ansicht eines Querschnitts durch ein Ende des in Figur 6 dargestellten Stapelscheiben-Wärmetauschers,

Figur 9

ein Ende des in Figur 6 dargestellten Stapelscheiben-Wärmetauschers in der Seitenansicht;

Figur 10

eine perspektivische Darstellung eines Wasserkastens mit einem eingebauten Stapelscheiben-Wärmetauscher;

Figur 11

einen Kühler mit einem eingebauten Wasserkasten, wie er in Figur 10 dargestellt ist;

Figur 12

eine Darstellung der Lötmenisken im Kanalschnitt;

Figur 13

eine Darstellung von nahezu kreisrunden Lötmenisken in der Draufsicht;

Figur 14

einen Stapelscheibenwärmetauscher gemäß einem weiteren Ausführungsbeispiel der Erfindung in der Draufsicht;

Figur 15

den Stapelscheibenwärmetauscher aus Figur 14 in der Seitenansicht;

Figur 16

die Ansicht eines Schnitts entlang der Linie XVI-XVI in Figur 14;

Figur 17

die Ansicht eines Schnitts entlang der Linie XVII-XVII in Figur 14;

Figur 18

die Ansicht eines Schnitts entlang der Linie XVIII-XVIII in Figur 14;

Figur 19

eine vergrößerte Darstellung der Einzelheit XIX aus Figur 14;

Figur 20

eine erfindungsgemäße Leitungseinrichtung im aufgeklappten Zustand in der Draufsicht;

Figur 21

die Leitungseinrichtung aus Figur 20 im halb zusammengeklappten Zustand;

Figur 22

einen Stapelscheiben-Wärmetauscher mit einer geschlossenen Leitungseinrichtung, wie sie in den Figuren 20 und 21 dargestellt ist, im geschlossenen Zustand in der Draufsicht;

Figur 23

den Stapelscheiben-Wärmetauscher aus Figur 22 in der Seitenansicht und

Figur 24

die Ansicht eines Schnitts entlang der Linie XXIV-XXIV in Figur 22.

Further advantages, features and details of the invention will become apparent from the following description in which with reference to the drawing an embodiment is described in detail. Show it:

FIG. 1

a perspective view of a disc half;

FIG. 2

one end of the disc half FIG. 1 in the lower view;

FIG. 3

the view of a section along the line III-III in FIG. 2 ;

FIG. 4

a perspective view of two disc halves;

FIG. 5

an enlarged section FIG. 4 ;

FIG. 6

a perspective view of seven discs, which are assembled to form a stacked plate heat exchanger according to the invention;

FIG. 7

an enlarged, perspective view of a lens of the in FIG. 6 illustrated stacked plate heat exchanger;

FIG. 8

the view of a cross section through one end of the in FIG. 6 illustrated stacked plate heat exchanger,

FIG. 9

an end to the in FIG. 6 illustrated stacked-plate heat exchanger in side view;

FIG. 10

a perspective view of a water box with a built-in stacked plate heat exchanger;

FIG. 11

a cooler with a built-in water tank, as in FIG. 10 is shown;

FIG. 12

a representation of the solder meniscus in the channel section;

FIG. 13

a representation of nearly circular Lötmenisken in plan view;

FIG. 14

a stacked plate heat exchanger according to another embodiment of the invention in plan view;

FIG. 15

off the stacked plate heat exchanger FIG. 14 in the side view;

FIG. 16

the view of a section along the line XVI-XVI in FIG. 14 ;

FIG. 17

the view of a section along the line XVII-XVII in FIG. 14 ;

FIG. 18

the view of a section along the line XVIII-XVIII in FIG. 14 ;

FIG. 19

an enlarged view of the detail XIX FIG. 14 ;

FIG. 20

a conduit device according to the invention in the unfolded state in plan view;

FIG. 21

the conduit device FIG. 20 in the half-folded state;

FIG. 22

a stacked plate heat exchanger with a closed conduit means, as in the FIGS. 20 and 21 is shown, in the closed state in plan view;

FIG. 23

off the stacked plate heat exchanger FIG. 22 in the side view and

FIG. 24

the view of a section along the line XXIV-XXIV in FIG. 22 ,

In FIG. 1 a disc half 1 is shown in perspective. The disc half 1 has the shape of an elongated plate made of aluminum sheet with two straight longitudinal sides 2 and 3, which are arranged parallel to each other. At their ends 4 and 5, the disc half 1 is rounded in a semicircle. In the ends 4 and 5 through holes 8 and 9 are provided. The edge regions 10, 11 of the through holes 8, 9 are recessed, so that the edge regions 10, 11 on the underside of the disc half 1 are raised.

Between the through holes 8 and 9, a plurality of grooves 12 are formed in the disc half 1. The grooves 12 extend in a straight line from one longitudinal side 2 to the opposite longitudinal side 3 of the disc half 1. The grooves have the shape of elongated recesses, which are raised on the underside of the disc half 1. The grooves can not be straight, for example, wavy or zig-zag shaped.

In FIG. 2 is the end 4 of the disc half 1 from FIG. 1 shown in the subview. The edge region 10 and ten grooves 21 to 30 rise from the plane of the drawing. The ends of the grooves 21 to 30 are rounded to the longitudinal sides 2, 3 out. The longitudinal axis of the disc half 1 is denoted by 31. The grooves 21 to 30 are arranged at an angle α of 45 ° to the longitudinal axis 31.

In FIG. 3 it can be seen that the disc half 1 viewed in cross-section, a wave-shaped profile aufinreist. The wave-shaped cross-sectional profile is formed by the grooves, which are formed on one side in the half-disc 1.

In FIG. 4 two disc halves 1 and 42 are shown in perspective. The sides of the disc halves 1 and 42 on which rise the grooves are facing away from each other.

In FIG. 5 it can be seen that the disc half 42 has exactly the same shape as the disc half 1. However, the disc half 42 is arranged rotated relative to the disc half 1 by 180 °. An end 44 with a through-hole 48, the edge region 50 of which rises from the plane of the drawing, is arranged above the through-hole 8 of the end 4 of the half-pane 1, the bowl-shaped edge region 10 of the through-hole 8 rising into the plane of the drawing. In the disc half 42 grooves 52 are formed, which rise out of the plane of the drawing. The grooves 52 are arranged at an angle β of 90 ° to the grooves 12, which rise into the plane of the drawing. The two disc halves 1 and 42 are soldered together to form a disc or a flat tube at the contact points of the grooves and in the edge region 2 and 3.

In FIG. 6 is a plurality of discs 60 soldered together. At the bottom, the through-holes of the disks 60 are closed by cover disks 61, 62. At the top of the discs 60 are at the ends of the through holes connecting pieces 67, 68 placed. Through one of the connecting pieces 67, 68, the medium to be cooled can be introduced into the interior of the discs 60. From the other connection piece 68, 67, the medium to be cooled from the discs 60 exit.

In FIG. 7 the lens 61 is shown enlarged in perspective. The lens 61 has the shape of a circular disk 64, which has a circular, central elevation 65. The outer diameter of the circular elevation 65 is adapted to the inner diameter of the associated through-hole of the respective disc.

In the FIGS. 8 and 9 you can see that in FIG. 6 stacked disc heat exchanger shown in perspective comprises seven discs 71 to 77, which are stacked on top of each other. Inside the discs 71 to 77, a plurality of substantially zigzag-shaped flow paths for the medium to be cooled are formed, which between the discs 71 to 77 rectilinearly pass through the recessed portions between every two grooves from one side to the opposite side corresponding disc half run.

In FIG. 10 a water box 78 is shown in which the in FIG. 6 installed stacked plate heat exchanger is installed. The discs 60 are disposed within the water box 78. The end stoppers 67, 68 protrude from the water box 78 out.

In FIG. 11 the water box 78 is off FIG. 10 attached to one side of a cooling network 79. To the other side of the cooling network 79, a further water tank 80 is grown. The two water boxes 78 and 80 and the cooling network 79 together form a coolant radiator 81 of a (not shown) motor vehicle.

The profiling of the disc halves 1 and 42 is designed so that the wave profiles when stacking the discs touch selectively. This results in the interior of the discs again and again changes in direction for the flowing medium to be cooled. The large number of contact points at which the two halves of the disc are soldered together ensures good pressure stability. The leg angle of the profiling is 45 ° to the main flow direction of the medium to be cooled. The hydraulic diameter is 1.8 mm. The embossing angle is in a range between 20 ° and 60 ° to the main flow direction. The hydraulic diameter can vary between 1.5 mm and 2.5 mm.

The large-area design in the inlet and outlet area enables a dense pane connection without the need for additional components. The disc halves have horizontal solder surfaces, whereby a sufficient flow passage of the coolant is ensured on the outside of the radiator. The disc halves are preferably slightly angled at its peripheral edge. As a result, the flatness of the disc is improved in the unsoldered state. The bending angle is between 5 ° and 20 °, preferably 10 °. The disc halves are made of aluminum and are connected by a Radlötprozess.

In FIG. 12 it can be seen that in each case two disc halves are connected to one another by solder menisci 101, 102 and 103, 104. In FIG. 13 it can be seen that the solder menisci 101 to 104 are almost circular in plan view.

In FIG. 14 a disc half 1 of a stacked-plate heat exchanger according to the invention is shown according to a further embodiment. To designate the same parts, the same reference characters are used as in the FIG. 1 illustrated embodiment. To avoid repetition, the preceding description of the FIG. 1 directed. In the following, only the differences between the exemplary embodiments will be discussed.

At the in FIG. 14 shown half disc 1, the edge portions 110, 111 of the through holes 8, 9 provided with indentations. The edge region 111 at the end 5 of the disc half 1 has meander-shaped indentations 115 and 116, which are connected by a connecting bead 117. The edge region 110 at the end 4 of the disc half 1 has meander-shaped indentations 118 and 119, which are interconnected by a connecting bead 120. In each case two disc halves 1, as in FIG. 14 are, as described above, to form a disc or a flat tube, which is also referred to as a conduit means, soldered to each other at the contact points of the grooves 12 and in the edge regions 2 and 3 and at the indentations 118, 119.

In FIG. 15 a side view of a radiator block is shown, comprising a plurality of stacked flat tubes.

In FIG. 16 is the view of a section along the line XVI-XVI in FIG. 14 shown. In the sectional view it can be seen that various flat tubes of a radiator block in a stacked construction in the region of the meander-shaped indentations 115, 116 as well as on the indentations 118, 119 are connected to one another in a line-shaped manner.

In FIG. 17 is the view of a section along the line XVII-XVII in FIG. 14 shown. In the sectional representation, it can be seen that the number of substantially linear contact surfaces is increased by the meander-shaped impressions 116. The meander-shaped impressions 116 are also referred to as reinforcement beads. Here you can see how the Indentations are soldered to each other on the disc end both on the inside and on the outside of the stacked plate heat exchanger.

In FIG. 18 is the view of a section along the line XVIII-XVIII in FIG. 14 shown. Here you can see how the indentations 119 are soldered to each other on the disc end 4 both on the inside and on the outside of the stacked plate heat exchanger.

In FIG. 19 is an enlarged view of the detail XIX FIG. 14 shown. The shape of the indentations 118, 119 is designed so that discs stacked one above the other are soldered to each other in a line on both the inside and on the outside. As a result, the internal pressure strength of a tube formed from two disc halves increases sharply. The disc connections are in FIG. 19 shown meandering.

In FIG. 20 is a conduit means 140, which is also referred to as a flat tube or short tube, in the unfolded state -dargestellt. The flat tube 140 is formed by a plate 142, which has substantially the shape of a rectangle whose corners are rounded. The plate 142 is an aluminum sheet stamping having a bending edge 143 which divides the plate 142 longitudinally into two equal halves 145, 146, also referred to as disc halves. The two disc halves 145, 146 correspond, apart from their one-piece design, the disc halves of the preceding embodiments. The plate 142 is bounded on the outside by a peripheral edge 148, which serves to solder the two plate halves 145, 146 in the folded or folded state together. Within the peripheral edge 148, the plate halves 145, 146 provided with embossed grooves, as described above.

In FIG. 21 the pipe 140 is shown in the partially closed state.

In FIG. 22 the tube 140 is shown in the closed state in plan view. The tube 140 is the uppermost flat tube of a Stacking plate heat exchanger with several stacked flat tubes.

In FIG. 23 is a side view of the stacked plate heat exchanger FIG. 22 shown. In the side view, it can be seen that the stacked-plate heat exchanger, in addition to the flat tube 140, also comprises six further flat tubes 150 to 155, which are soldered together in a stacked construction.

In FIG. 24 is the view of a section along the line XXIV-XXIV in Figure 22 dargestelit. The sectional view shows that the stacked-plate heat exchanger is formed from folded flat tubes 140, 150 to 155. By integrally forming the flat tubes, it reduces the number of parts necessary for the construction of the stacked plate heat exchanger in half. The folded flat tubes have the advantage that the length of the Dichtlötnaht reduced by almost half.

Claims (23)

1. A stacked-plate heat exchanger, in particular in-tank oil cooler, which can be installed in a coolant box of a coolant cooler, for motor vehicles, with a plurality of elongate plates (71-77) which are stacked one on the other and are connected, in particular soldered, to one another and which are composed in each case of two plate halves and surround a cavity for leading through a medium to be cooled, such as oil, in the longitudinal direction of the plates, wherein each of the plate halves (1, 42) has a multiplicity of grooves (21-30) which run from one longitudinal side (2) of the plate half (1) to its opposite longitudinal side (3), wherein the plate halves (1) have in each case a pair of through-holes (8, 9) as inflow lines and outflow lines and embossings (115-120) are provided in the edge region (110; 111) of the through-holes (8, 9) and, as seen in section, the embossings (115, 116, 118, 119) are of wavy design with wave crests and wave troughs, characterised in that, as seen in a top view, the embossings (115, 116, 118, 119) run in a meander-like manner at least partially around the through-holes (8, 9).
2. The stacked-plate heat exchanger as claimed in claim 1, characterised in that the elongate plates are composed in each case of two identical plate halves (1, 42) rotated through 180° with respect to one another.
3. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that the grooves run rectilinearly from one longitudinal side of the plate half to its opposite longitudinal side.
4. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that the grooves (21-30) are embossed on one side in each plate half (1).
5. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that the grooves (21-30) are delimited on the longitudinal sides by a peripheral edge.
6. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that a plate is formed by two plate halves (1, 42) which bear against one another and the grooves (12, 52) of which are embossed outwardly.
7. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that two plates (71, 72) bear against one another and are soldered to one another with their raised regions formed by the grooves.
8. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that the grooves (21-30) run at an angle of 35° to 55°, in particular of 45°, with respect to the longitudinal axis (31) of the associated plate half (1).
9. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that the grooves (12, 52) of two plate halves (1, 42) bearing against one another are arranged at an angle of 70° to 110°, in particular of 90°, with respect to one another.
10. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that the grooves (21-30) have a depth of 0.5 to 1.5 mm, in particular of 1.15 mm.
11. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that the grooves (21-30) of a plate half (1) are arranged parallel to one another at a distance of 3 to 5 mm, in particular of 4 mm, from one another.
12. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that the plate halves (1, 42) have a width of about 20 to 120 mm, in particular of 20 to 50 mm.
13. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that the hydraulic diameter between two adjacent plate halves along the main flow direction of the medium to be cooled has a value of 1.5 to 2.5 mm, in particular of 1.8 mm.
14. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that the plate halves (1, 42) are formed from a metallic material, in particular from aluminium or high-grade steel.
15. The stacked-plate heat exchanger as claimed in claim 14, characterised in that at least one side of the plate halves (1, 42) is coated with soldering aid material.
16. The stacked-plate heat exchanger as claimed in one of claims 1 to 15, characterised in that the edge region (10, 11; 110, 111) of the through-holes (8, 9) is of raised design.
17. The stacked-plate heat exchanger as claimed in one of claims 1 to 16, characterised in that a plurality of plate halves (1) are soldered essentially linearly to the in each case adjacent plate halves both on their inside and on their outside.
18. The stacked-plate heat exchanger as claimed in one of the preceding claims, characterised in that in each case two plate halves (145, 146) are connected to one another in one piece by means of a bending edge (143) running in the longitudinal direction or in the transverse direction, in order to form a conduction device (140) for the medium to be cooled.
19. The stacked-plate heat exchanger as claimed in claim 18, characterised in that the conduction device (140) is formed by an essentially rectangular panel (142) which is subdivided by means of the bending edge (143) into two elongate halves (145, 146) which are folded together.
20. The stacked-plate heat exchanger as claimed in claim 19, characterised in that the panel (142) has a peripheral edge (148) which is raised with respect to the panel surface.
21. The stacked-plate heat exchanger as claimed in claim 20, characterised in that the peripheral edge (148) is interrupted at the intersection points with the bending edge (143).
22. The stacked-plate heat exchanger as claimed in claim 20 or 21, characterised in that the two panel halves (145, 146) bear against one another with the peripheral edge (148) in the folded-together state.
23. A motor vehicle cooler with at least one water box, characterised in that a stacked-plate heat exchanger as claimed in one of the preceding claims is installed in the water box.

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