Cooler with two substantially parallel plates

Abstract

A cooler (10) has at least two substantially parallel plates (12, 14, 50, 54) which are shaped and connected to one another, in particular welded to one another, and is characterized in that at least one flow channel (34) formed in one plate (50) is interrupted, and the plate has at least one barrier, according to the invention, the plates (12, 14, 50, 54) are arranged such that a first fluid flow, in particular a refrigerant flow, is deflected into flow channels formed in the other plate (54), individual inlets (26) and preferably also outlets (26) are assigned to at least two flow channels (34), preferably each flow channel (34), and a closed flow space (56) for a second fluid, for example a coolant, is formed between the plates (12, 14, 50, 54).

Description

Technical Field

[0001] The invention relates to a cooler having two substantially parallel plates. Background Art

[0002] For example, DE 10 2021 210 826 A1 discloses a cooler having three substantially parallel plates, the outer two of which are substantially flat. The middle plate defines a flow channel for the coolant or refrigerant and is mechanically connected, usually welded, to the first-mentioned plate.

[0003] JP H 11-287580 A describes a similar cooler around which air flows.

[0004] Finally, DE 11 2021 004 917 T5 relates to a heat exchanger between two liquids, wherein each liquid is divided into a plurality of flow channels or flow spaces within the heat exchanger. Summary of the invention

[0005] Technical issues

[0006] Against this background, the invention is based on the problem of producing a cooler which is compact and / or provides an improved heat transfer.

[0007] Technical Solutions

[0008] The solution to this problem is provided by the subject matter of claim 1 .

[0009] This comprises two essentially parallel plates which are shaped and connected to one another, in particular welded to one another, in such a way that at least one flow channel formed in one plate is interrupted and the plate has at least one barrier so that a fluid flow, in particular a refrigerant flow, is deflected into a flow channel formed in the other plate.

[0010] In other words, the flow channels are formed between one plate and another in segments and in alternating form. With respect to the flat areas between any flow channels, the plates are parallel to each other and connected to each other. In order to ensure the described deflection from the flow channel in one plate to the flow channel in another plate, the flow channels formed in the corresponding plates overlap. The above-mentioned barriers, which essentially form the ends of the flow channel segments formed in the plates, therefore serve as guide elements for deflection and act as turbulators to improve heat transfer. At the same time, the cooler or general heat exchanger can remain compact. As described in more detail below, the plates can also be connected together so that the plates are subjected to particularly high stresses due to internal pressure.

[0011] If the space between two plates is usually defined as a plane, conventional fluid flow, in particular refrigerant flow, can be described as two-dimensional. In contrast, the flow formed in the heat exchanger according to the present invention is three-dimensional, because the fluid, in particular the refrigerant, flows in at least a section in the depression, channel or protrusion of the first plate, bounded by the adjacent flat area of ​​the second plate, and flows in another section in the protrusion, depression or channel of the second plate, bounded by the adjacent flat area of ​​the first plate.

[0012] In other words, if the layout of one or more flow channels is marked with different colors to indicate the flow in a depression or similar area of ​​one plate on the one hand and the flow in a depression or similar area of ​​another plate on the other hand, this will be shown as different colors in the course of the flow channels. A second fluid, for example a coolant, which releases heat to the refrigerant flowing alternately in the plates flows in the remaining plate interspaces delimited by the circumferential lateral webs. In this case, both direct and countercurrent flows as well as cross-countercurrent flows can be formed in the heat exchanger.

[0013] Furthermore, the cooler usually has a substantially flat outer plate on the outer side, which preferably has an inlet and an outlet for a fluid that releases heat to the refrigerant, for example. This essentially provides a way to connect to the fluid system of the vehicle. In principle, the connection piece can be provided on both sides of the cooler and on each of the two outer plates.

[0014] For the sake of completeness, it should be mentioned that at least four plates including the outer plate are mechanically connected, in particular welded, to each other in a suitable manner in order to form a cooler of high overall strength. This involves resistance both to internal pressure and to external mechanical stresses.

[0015] The cooler can also be connected to the cooling system of the vehicle. Furthermore, the cooler according to the invention has low pressure losses and, as mentioned, high strength. Depending on requirements, the outer plates and / or any intermediate plates or separator plates can be completely consistent with the plate in which the flow channel is formed, or offset inwards on at least one side.

[0016] In the overlap region between two cooling channel sections in two different plates, this results in a flow channel height that is twice the depth of the recess formed in one plate. The same applies to the flow space for the fluid in the remaining plate gap, with the exception of the fluid flow space adjacent to the outer plate.

[0017] It should also be mentioned that for the refrigerant inlet and outlet, ie in the described plate interspaces, for example for a plate thickness of 0.6 mm, a diameter of 4.0 to 4.4 mm is preferred and for a plate thickness of 0.4 mm, a diameter of 2.8 to 3.2 mm is preferred.

[0018] The cooler according to the invention is particularly pressure-stable due to the fact that at least two flow channels, preferably each flow channel in a respective plate, are assigned a separate inlet and preferably also a separate outlet, in other words, the fluid flow, in particular the refrigerant flow, has been divided into a plurality of channels outside the plate, where stability can be more easily ensured.

[0019] Advantageously, therefore, heat is effectively transferred to the second fluid, a liquid fluid, by forming a closed flow space between the plates for the second fluid, such as a coolant.

[0020] At present, preferred fields of application of the cooler according to the invention are coolant coolers and direct refrigerant evaporators.

[0021] Preferred further developments are described in the dependent claims.

[0022] The design according to the invention can advantageously be realized by a single type of plate with flow channels, which is alternately rotated through 180° and installed in the heat exchanger. This means that only a single type of flow pattern can be realized inside the heat exchanger, for example a U-shaped or meandering flow pattern, or a plurality of U-shaped flow patterns. Two types of plates are therefore sufficient, in addition to the outer plates being another plate type. Since providing a second flow pattern in such a heat exchanger can provide advantages in certain applications, this can also be effectively achieved in an advantageous manner by using a maximum of two different types of plates with flow channels.

[0023] As mentioned above, the flow channel according to the present invention can be realized by connecting plates of one and the same type to each other, for example, by rotating one of the plates of one and the same type through 180°.

[0024] At the same time, the thickness of at least one plate can be advantageously reduced to 0.6 mm or less without excessively reducing strength. The plate thickness can vary depending on the manufacturing process and the corresponding requirements. A minimum thickness of 0.4 mm is currently preferred, and preliminary simulations and tests have shown that a depth of 0.65 mm to 0.8 mm is advantageous for the flow channels formed in the plates. This results in a total height or depth of 1.3 mm to 1.6 mm in the overlapping area of ​​the two flow channel sections, where the two plates are placed one on top of the other. Such dimensions are currently considered optimal in terms of robust welding processes, pressure losses, heat transfer performance, and strength.

[0025] Regarding the geometry of the flow, preliminary simulations have shown that meandering flows and / or, where appropriate, multiple, in particular three U-shaped flows and / or straight flows are advantageous. The meanders can be relatively complex and are therefore particularly suitable for the requirements. The U-shape essentially has sections connected at right angles.

[0026] With regard to the mechanical resistance to internal pressure of the cooler, it is currently preferred that the cooler should withstand an internal pressure corresponding to the maximum operating pressure of the refrigerant R744 in order to form a particularly stable cooler. Such values ​​can be achieved in particular by minimizing the free span area between the plates by connecting the plates to one another at multiple points and / or in parallel with multiple flow channels. The internal pressure resistance can then be ensured despite a plate thickness of 0.6 mm or less.

[0027] The heat transfer can also be improved in an advantageous manner by means of turbulators, which are preferably arranged outside the flow channel, in other words in the coolant flow space. The turbulators can be formed by recesses, which can be circular or oval, and a plurality of such turbulators can be arranged in series substantially parallel to the flow channel. The turbulators are preferably arranged as one piece in the plate in the form of the recesses or punchings and / or bends. The maximum height of such turbulators can correspond to the height of the flow space, in other words, so that the turbulators abut the upper boundary of the flow space.

[0028] For efficient heat transfer, it is also preferred that the second fluid is guided through the V-shaped and / or arc-shaped plate interspaces. As already indicated above, it may be advantageous to provide different flows in different areas of the heat exchanger so that in the first set of plates the flow channels are formed in a first shape, e.g. a straight shape, and in the second set of plates the flow channels are formed in a second shape, e.g. a U shape. In particular, this may improve performance and at the same time any connection or as many connections as possible may be formed on a single side of the heat exchanger.

[0029] Finally, for the stable connection of the plates, it has been proven to be advantageous to connect the plates together, in particular to weld the plates, in the region of the inlet and outlet and / or on the outer edges. In addition, alternatively or additionally, at least one reinforcing plate and / or folding portion can be provided at least partially or at certain positions on at least one outer edge. In particular, reinforcing plates can be provided in the region of the refrigerant inlet and outlet, and / or the tie rods can be configured so that the tie rods are inserted through the additional holes formed by the collars and welded to each plate. This distributes the tension from the top plate to a plurality of plates, downward to all plates including the bottom plate. Such tie rods can be circular, oval or rectangular or have any other shape. In addition, a plurality of such tie rods can be provided. Alternatively or additionally, the plate stacks forming the heat exchanger can be enclosed by strips, such as aluminum, which can be welded to the plate stacks, in particular to the plate stacks in the regions subject to the greatest mechanical stress. Finally, one or more C-shaped brackets can be provided on the outside of the plate stacks to hold the plate stacks together. At least one such bracket may comprise one or more connections; in any case, at least one such bracket is preferably arranged in the region of the connections, since these regions are crucial for the resulting pressure stresses.

[0030] To obtain advantageous properties it is further preferred that all inlets and outlets for the first fluid have a diameter of 4.0 mm to 4.4 mm, in particular a floor thickness of about 0.6 mm, or a diameter of 2.8 mm to 3.2 mm, in particular a floor thickness of about 0.4 mm.

[0031] It is also advantageous for the stability of the plate stack if all inlets and outlets for the first fluid are surrounded by elevations or depressions formed by the plate material.

[0032] The same applies to the preferred measure in which a projection or depression adjoins a projection or depression forming a flow channel. All projections and depressions can be constructed effectively and the structure facilitates flow to and within the channel.

[0033] The production and connection of the panels is particularly easy if all elevations or depressions have the same height or depth.

[0034] This also applies to the preferred measure in which the sections of the flow channels formed in the different plates have at least partially the same length. This also improves the flow pattern.

[0035] Particularly good performance can also be expected if in each plate the flow channels adjoin each inlet and outlet, in other words so that the fluid flow is not deflected immediately after entering an adjacent plate. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] The present invention is explained in more detail below with reference to exemplary embodiments. It is shown as follows:

[0037] Figure 1 : The basic structure of the cooler according to the present invention.

[0038] Figure 2 : Figure 1 A plan view of a first type of plate in a cooler is shown.

[0039] Figure 3 : Figure 1 A plan view of the second type of plate in the cooler is shown.

[0040] Figure 4 : A part of another embodiment of the cooler according to the present invention.

[0041] Figure 5 : A part of another embodiment of the cooler according to the present invention.

[0042] Figure 6 : A part of another embodiment of the cooler according to the present invention.

[0043] Figure 7 : A part of another embodiment of the cooler according to the present invention.

[0044] Figures 8 to 12 : Figures 4 to 7 A plate used in an embodiment of the present invention.

[0045] Fig.13 : Details of the cooler according to the invention.

[0046] Fig.14 : Another embodiment of a plate used in a cooler.

[0047] Fig.15 : Fig.14 The plate is shown rotated through 180°.

[0048] Figures 16 to 18 : Passing through including according to Fig.14 and Fig.15 The volume of the cross-section of the two plate pairs, where Fig.16 A cross section perpendicular to the flow channel is shown, and Fig.17 and Fig.18 A cross section parallel to the flow channel is shown.

[0049] Fig.19 : Section through two plate pairs and the outer plate.

[0050] Figure 20 to Figure 22 : Flow in the first plate, the second plate and the two plates combined.

[0051] Fig.23 : Another embodiment of the board.

[0052] Fig.24 : Pass through Fig.23 A first cross section of a plate stack having a plurality of plates is shown.

[0053] Fig.25 : Pass through Fig.23 A second cross section of a plate stack with a plurality of plates is shown. DETAILED DESCRIPTION

[0054] As from Figure 1 As can be seen, the cooler 10 according to the invention comprises a number of plates, which are described in more detail below. All plates are generally substantially rectangular, and the outer plate 14 is substantially flat at least on its outer side. The middle plate 12 has a structure described in more detail below to form a flow channel. In the illustrated case, the top outer plate in the drawings also has inlets and outlets 16-22, which are also described in more detail below and can be adapted to customer requirements.

[0055] In particular, in the case shown, the top outer plate 14 has an inlet 16 and an outlet 18, for example for a coolant that is cooled by the cooler 10 according to the invention. As indicated by arrows A and B, the coolant flows substantially in the orientation shown from the top to the bottom through all the plate interstices described in more detail below, and from the bottom of the cooler 10 upwards to the outlet 18. In particular, the coolant is distributed to all the plate interstices by passages 36 formed in all the plates, in which the coolant flows in a U-shape substantially from the front left to the rear right, from the rear right to the front right, and finally to the front left, in order to flow to the outlet 18 through the passages 36, which can again be seen. Figure 2 and Figure 3 Interrupted flow channels 34 for the refrigerant are shown, which are described in more detail below. The coolant flows substantially between the flow channels 34, in particular in a U-shape due to the central boundary 58. The inlet 16 and the outlet 18 are substantially cylindrical, have a tapered section approximately in the middle and can be welded to the outer plate 14.

[0056] The same applies to the block 24 which will be seen, with the inlet 20 and the outlet 22 for the refrigerant. In view of the higher pressure loads in this area, the block 24 can be formed by milling, for example.

[0057] In the right region of the outer plate 14, a number of openings 26 can be seen, through which the refrigerant enters a number of flow channels which are described in more detail below. Figure 1On the basis of FIG. 2 , it is explained that the refrigerant initially flows to the front left in the left region of the plate stack 28 along the arrow C that can be seen. As can be seen from the vertical arrow C, this occurs in parallel throughout the plate stack 28. For the sake of clarity, only the two lowest plates in this plate stack 28 are shown separated from each other. The parts of the plate stack 28 that can be seen above them consist of identical plates that are nevertheless shown as stacked.

[0058] The same applies to the lower plate stack 30 which is separated from the upper plate stack 28 by a partition plate or intermediate plate 32. For the upper plate stack 28, a straight-line flow is described along the arrow C pointing from the rear right to the front left. In contrast, a U-shaped flow is formed in the lower plate stack 30, so that the refrigerant flows in parallel in all flow channels of the plate stack 30, first along the arrow D from the front left to the rear right, then along the arrow E from the rear left to the rear right, and then along the arrow F from the rear right to the front left. The refrigerant flows upward from the lower plate stack, now enters the right side portion of the upper plate stack 28, and in the upper plate stack, the refrigerant flows again along the arrow G from the front left to the rear right and thus in parallel in all flow channels in a straight line, and flows from the upper plate stack along the arrow H to the outlet 22 of the refrigerant.

[0059] Since the coolant entering through the inlet 16 flows from the front left to the rear right in the upper plate stack in the left area of ​​the upper plate stack, the coolant flows in a countercurrent manner to the refrigerant. A parallel U-shaped flow is generated in the lower plate stack. A countercurrent is also formed in the right part of the upper plate stack 28. This extends the flow path in an advantageous manner and improves heat transfer. This applies in particular to the countercurrent in the right area of ​​the upper plate stack 28, which is particularly advantageous for cooling the coolant that subsequently leaves the cooler 10. At the same time, Figure 1 In the case of the cooler 10 shown, all inlets and outlets 16 , 18 , 20 and 22 can advantageously be arranged on one side, which offers advantages for example for connecting the cooler to a cooling system of a vehicle.

[0060] like Figure 2 As shown, the plates 12 of the upper plate stack 28 have openings 26 for the refrigerant on the one hand and interrupted flow channels 34 and passages 36 described in more detail below on the other hand, for example, four to six parallel flow channels 34 for the refrigerant on the one hand and passages 36 for the coolant on the other hand. Figure 2 The plates shown are configured for straight flow, in the case shown, from right to left at the top and from left to right at the bottom with respect to the refrigerant. Furthermore, in the example given, turbulators 38 are shown in the upper region between the flow channels, which will be described in more detail below. Figure 2As can be seen in FIG. 1 , in this case the turbulator 38 is elongated in the flow direction of the refrigerant and is connected in series with the flow channel 34 for the refrigerant.

[0061] The same applies to Figure 3 The plate 40 of the lower plate stack 30 is shown. As can be seen in particular in the right-hand area, the refrigerant is deflected in its flow channel 34, resulting in an overall U-shaped flow.

[0062] exist Figure 4 In the alternative embodiment shown, the flow is essentially three U-shaped, as explained in more detail below. Here, the middle U is inverted and the two legs of the middle U coincide with the inner legs of the outer U. In this case, the refrigerant inlet 20 and outlet 22 are separate, and the refrigerant first flows along arrows C into the various flow channels, then flows to the right along arrows D in a three-U-shaped or serpentine form as described, and flows from there to the outlet 22. The coolant inlet and outlet can again be regarded as essentially cylindrical and can be used in a parallel and countercurrent manner with the refrigerant.

[0063] Figure 5 Basically it shows Figure 4 The flow situation shown is replicated in that the flow in the two upper plates is essentially from left to right and the flow in the two lower plates is from right to left after the flow from the second plate is directed from above to the third plate. Figure 4 After the other plate pair shown below, the return flow to the outlet 22 is indicated by arrow H.

[0064] Figure 6 It is shown how the refrigerant inlet 20 and outlet 22 can be advantageously arranged on one side of the cooler, namely by using a lower set 42 in the top plate for the inlet (see Figure 8 ) opening, where the refrigerant Figure 7 The upper plate alignment shown flows from left to right, Figure 7 The center plate pair shown flows from right to left and Figure 7 The lower plate alignment is shown with flow again from left to right. Arrow H indicates flow through Figure 6 The plate pair shown below then produces a total backflow to the outlet 22. Figures 4 to 7 The concepts shown emphasize that they advantageously allow all inlets and outlets 16-22 to be arranged on one side. This makes it easier to integrate the cooler into the cooling system of the vehicle, for example, without requiring external deflection of the refrigerant, for example. Figure 4 and Figure 5 The combination allows an odd number of deflections, and Figure 6 and Figure 7 The combination allows an even number of deflections.

[0065] like Figure 8 In more detail, according to Figure 7 The top plate in each plate pair is Figure 8 The first plate type shown corresponds to. Fig. 9 The second panel type shown forms the bottom panel of the top panel pair and the bottom panel pair, and Fig.10 The plate type shown forms the base plate of the intermediate plate pair. Figures 8 to 12 , Fig.14 and Fig.15 The arrow I in the figure shows a substantially inverted V-shaped flow of the second fluid in the flow space between the two plates from one passage 36 to the other in the orientation shown. The flow space extends to the outer boundary 60 on all sides. The second fluid, usually a coolant, in particular water, is cooled and releases heat to the refrigerant, which in this case flows in a countercurrent manner and, according to the figure, flows substantially in three U-shaped ways from the upper left to the upper right, so that the refrigerant evaporates. Ideally, the heat is transferred uniformly along the corresponding flow paths.

[0066] Fig.11 and Fig.12 The remaining plate types shown correspond to Figure 4 and Figure 6 The lower part of the plate shown, where Fig.12 The plate type shown forms the upper plate. In addition, Figure 7 The two upper plates in Figure 5 The plate pairs shown correspond to each other and Figure 4 In the lower part of Fig.11 The board type is the upper board and Fig.12 The plate type in is the lower plate. Figures 8 to 12 As can be seen in FIG. 1 , different openings 26 are closed in different plate types in order to achieve the flow paths described above using the plates shown. Figure 8 The groups 42 shown in the figure form a collector area that can be advantageously used for heat transfer. For all plate types, it can be seen that their respective flow channels for the refrigerant are interrupted, and the operation of the resulting cooler will be described in more detail below. Due to the corresponding central boundary 58, the coolant flows from one passage 36 to another in a substantially inverted V-shaped or arc-shaped manner.

[0067] Fig.13 Firstly, it is shown how a block 24 with a refrigerant inlet 20 and / or outlet 22 is connected to an outer plate 14, an outer plate 14 to an intermediate plate 12, and a plurality of intermediate plates 12 to each other. This is advantageously achieved by welding, and it is emphasized that the circumferential and double-sided welding of the plates in the shown area 44 ensures a particular strength. The strength can optionally be further increased by transverse folding, as indicated by the folded edge 46. According to Fig.13 The double circumferential welds in the illustrated areas 44 provide additional corrosion protection because the double circumferential welds are applied to the outside, the left side of the welds being sufficient to allow the cooler to operate in the mutually aligned convex areas of the plates 12. Corrosion in the areas 44 will not lead to any leakage of refrigerant or fluid because the aforementioned welds required for the operation of the cooler are applied further inwards than these areas 44.

[0068] The same applies to Fig.14 The measure shown makes it possible to provide local recesses 48 in one or more corners of the plates 12 , which recesses can be welded together continuously for all the plates.

[0069] Fig.15 Pictured Fig.14 The plate shown is rotated through 180° about a vertical axis parallel to the plane of the plate according to the drawing, which therefore also has an interrupted flow channel. Fig.14 The plates are shown welded in this orientation to Fig.15 The plates shown, also welded in the orientation shown, then the overall result is that a continuous flow channel is formed in certain areas only in one of the two plates. Here, the refrigerant can flow from one plate to the other in the area where the flow channels of the two plates overlap. The ends of the flow channel sections form barriers for deflection to the other plate.

[0070] Fig.16 By way of example based on a cross section, it is shown that the refrigerant initially flows only in the upper plate 50 after entering the second opening 26 from the left. However, in the further course, the flow channel 34 formed in the upper plate ends and the refrigerant enters the flow channel 34 formed in the lower plate 54 in the form of a recess in the overlap region. In the case shown, each flow channel 34 is assigned an opening 26 which is formed in the other plates 50, 54 and in this respect acts as a distributor over the flow channels 34 of a plurality of plate pairs 50, 54.

[0071] This overlap in Fig.16 54. In the figure, the second flow channel 34 from the right and the leftmost flow channel 34 are shown as examples. In this area, the refrigerant thus flows in the channels of the two plates 50, 54. For the flow channel 34 arranged on the rightmost side, it can be seen that in this area, the refrigerant flows only in the channel 34 formed in the lower plate 54, while the restricted flow channel 34 formed in the upper plate 50 can be seen above it.

[0072] If you can also Fig.17As can be seen in the figure, in the case shown, the refrigerant flows alternately, starting with the flow only in the upper plate 50 in the area of ​​the overlap 52, entering the flow channel of the lower plate 54, and returning from the flow channel of the lower plate 54 to the flow channel in the upper plate 50 in the area of ​​another overlap 52.

[0073] This can also be Fig.18 Seen in Fig.18 The same reference numerals are used. The flow of the coolant to be cooled is also indicated here, which can be seen in the remaining plate interspaces 56 .

[0074] Fig.19 Also shown is an example of how an arrangement of two plate pairs, each with an upper plate 50 and a lower plate 54, can be closed by a substantially flat outer plate 14, which also has a flow space 56 for the coolant adjacent to the outer plate 14. In the cross section shown, the flow channel 34 located farthest to the left is located only in the respective upper plate 50, the second flow channel 34 from the left is located only in the lower plate 54, and the third flow channel 34 from the left is located in both plates 50, 54.

[0075] Fig. 20 The interruption area of ​​the refrigerant flow in the upper plate 50 is shown, corresponding to Fig.14 The flow passages of the upper plate 50 are shown.

[0076] Fig.21 Shown with Fig.15 The flow channel seen in FIG. 1 corresponds to the flow in the lower plate 54, and Fig. 22 The overall flow is shown alternating between the two plates via the different shading of the flow channels in the different plates.

[0077] Fig.23 By way of example it is shown how turbulators 38 can also be formed in series and in parallel with the flow channels 34 for a plate with the three U-shaped flows.

[0078] Finally, as can be seen in the cross-sections which are shown perpendicular to each other Fig.24 and Fig.25 As can be seen in FIG. 1 , the turbulators 38 can extend over the entire height of the flow gap and thus abut against the corresponding upper or outer plate 14. Fig.25 The right-hand area of ​​also shows that the turbulator 38 can extend in two directions and can be punched out of the plate material so that in the case of two connected plates a single plate thickness is produced in the area of ​​the turbulator 38, while in other areas, and in particular in the areas between the flow channels 34, a double plate thickness is present.

[0079] Industrial Applicability

[0080] The invention relates to a cooler having two substantially parallel plates.

Claims

1. A cooler (10) comprising at least two substantially parallel plates (12, 14, 50, 54), which are shaped and connected to one another, in particular welded to one another, at least one flow channel (34) formed in one of the plates (50) being interrupted and the plate (50) having at least one barrier so that a first fluid flow, in particular a refrigerant flow, is deflected into a flow channel formed in the other of the plates (54), a separate inlet (26) and preferably also an outlet (26) being assigned to at least two flow channels (34), preferably to each flow channel (34), and a closed flow space (56) for a second fluid, for example a coolant, being formed between the plates (12, 14, 50, 54).

2. The cooler (10) according to claim 1, characterized in that A maximum of three different types of plates (12), preferably two different types of plates (12) are provided, two types of plates, preferably one type of plate, having flow channels (34) therein.

3. The cooler (10) according to claim 1 or 2, characterized in that: At least one type of plate (12) is mounted in at least two different orientations, preferably rotated through 180°.

4. The cooler (10) according to any one of claims 1 to 3, characterized in that: The thickness of at least one plate (12, 14) is 0.4 mm to 0.6 mm and / or the depth of at least one flow channel in the plate (12, 14) is 0.65 mm to 0.8 mm.

5. The cooler (10) according to any one of claims 1 to 4, characterized in that The first fluid is guided through the cooler (10) and / or the flow channel in a meandering manner and / or in at least a single U-shaped manner, in particular in a triple U-shaped manner and / or in a straight line.

6. The cooler (10) according to any one of claims 1 to 5, characterized in that The cooler (10) has mechanical resistance to internal pressure corresponding to the maximum working pressure of the refrigerant R744.

7. The cooler (10) according to any one of claims 1 to 6, characterized in that In particular, a turbulator (38) is arranged outside the flow channel (34) for the refrigerant.

8. The cooler (10) according to any one of claims 1 to 7, characterized in that The second fluid is guided through the V-shaped and / or arc-shaped plate gaps.

9. The cooler (10) according to any one of claims 1 to 8, characterized in that In the plates (12, 14, 50, 54) of the first group (28), the flow channels are formed into a first shape, such as a straight line, and in the plates (12, 14, 50, 54) of the second group (30), the flow channels are formed into a second shape, such as a U shape.

10. The cooler (10) according to any one of claims 1 to 9, characterized in that The plates (12, 14, 50, 54) are connected to one another in the region of the inlet and outlet (16-22) and / or at the outer edges and / or are provided at least partially or at certain locations with at least one reinforcing plate and / or at least one fold (46) at the outer edges.

11. The cooler (10) according to any one of claims 1 to 10, characterized in that All inlets and outlets (26) for the first fluid have a diameter of 4.0 mm to 4.4 mm, in particular a floor thickness of about 0.6 mm, or a diameter of 2.8 mm to 3.2 mm, in particular a floor thickness of about 0.4 mm.

12. The cooler (10) according to any one of claims 1 to 11, characterized in that All inlets and outlets (26) for the first fluid are surrounded by projections or depressions formed by the plate material.

13. The cooler (10) according to claim 12, characterized in that The projections or depressions are adjacent to projections or depressions forming the flow channel (34).

14. The cooler (10) according to claim 12 or 13, characterized in that All of the protrusions or depressions have the same height or depth.

15. The cooler (10) according to any one of claims 1 to 14, characterized in that Sections of the flow channels (34) formed in different plates (12, 14, 50, 54) have at least partially the same length.

16. The cooler (10) according to any one of claims 1 to 15, characterized in that In each plate (12, 14, 50, 54), the flow channel (34) is adjacent to each inlet and outlet (26), in other words, so that the fluid flow is not deflected immediately after entering the adjacent plate (12, 14, 50, 54).

Images