Cooler with two parallel plates

Abstract

The aim is to manufacture compact coolers or coolers with improved heat transfer. [Solution] The present invention relates to a cooler (10) having at least two parallel plates (12, 14, 50, 54) connected to each other and in particular formed by soldering each other, wherein at least one flow path (34) formed in one of the plates (50) is interrupted, and the plate (50) has at least one barrier so that a flow of a first fluid, in particular a flow of a refrigerant, is switched to a flow path formed in another plate (54), and at least two flow paths (34), preferably each flow path (34) is also assigned a separate inlet (26) and preferably an outlet (26), and a closed flow space (56) for a second fluid, such as cooling water, is formed between the plates (12, 14, 50, 54), comprising up to three, preferably two different types of plates (12), of which two, preferably one of which type, has flow paths (34) formed inside the plate.

Description

Technical Field

[0001] The present invention relates to a cooler having two parallel plates, and more particularly to a cooler having two parallel plates that are compact or have improved heat transfer.

Background Art

[0002] For example, Patent Document 1 discloses a cooler having three substantially parallel plates, and the two outer plates of the cooler are basically flat. The middle plate defines a flow path for cooling water or refrigerant, is mechanically coupled to the above plates, and is usually soldered. Patent Document 2 describes a similar cooler through which air flows. Finally, Patent Document 3 relates to a heat exchanger between two liquids, and each liquid is separated by a plurality of flow paths or flow path spaces in the heat exchanger.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Patent Document 2

Patent Document 3

Summary of the Invention

Problems to be Solved by the Invention

[0004] The object of the present invention is to manufacture a cooler that is compact or has improved heat transfer.

Means for Solving the Problems

[0005] A solution to this problem is provided by the invention described in claim 1. The present invention includes two parallel plates connected to each other and in particular soldered to each other, such that at least one flow path formed in one plate is interrupted, wherein the plates are formed to have at least one barrier, such that a fluid flow, in particular a refrigerant flow, is switched to a flow path formed in the other plate.

[0006] In other words, the flow channels are formed in sections, alternating between plates. In the flat regions between the flow channels, the plates are parallel and connected to one another. To ensure the above transition from a flow channel in one plate to a flow channel in the other, the flow channels formed in the corresponding plates overlap each other. Thus, the barriers forming the ends of the flow channel sections formed in the plates function as guide members for the transition and as turbulators to improve heat transfer. At the same time, the cooler, or heat exchanger in general, can be kept compact. As will be described in more detail below, the plates can be connected to one another so that they can withstand particularly high stresses due to internal pressure.

[0007] If the space between two plates is defined as a normal plane, then a normal fluid flow, particularly a refrigerant flow, can be described as a quadratic circle. In contrast, the flow formed in the heat exchanger according to the present invention is three-dimensional, as the fluid, particularly the refrigerant, flows within at least a section of a curved portion, channel, or rise in the first plate, surrounded by adjacent flat regions of the second plate, and within other sections of a rise, curved portion, or channel in the second plate, surrounded by adjacent flat regions of the first plate.

[0008] In other words, if the layout of one or more flow paths is indicated by different colors showing the flow within one plate and at curved sections or similar locations within another plate, then this layout is indicated by different colors along the path of the flow paths. A second fluid, such as cooling water, which heats the refrigerant flowing alternately within the plates, flows within the remaining plate gap surrounded by circumferential side webs. In this case, not only direct and countercurrent flows, but also cross-reverse flows can be formed within the heat exchanger. Furthermore, the cooler preferably has a flat outer plate on the outside, for example, having an inlet and outlet for a fluid heated by a coolant. This provides a means for connecting to the vehicle's fluid system. In principle, the connections can be located on each of the two outer plates and on both sides of the cooler.

[0009] To ensure integrity, at least four plates, including the outer plate, are mechanically connected in an appropriate manner, particularly by soldering, to create a high-strength cooler overall. This relates to resistance to both internal pressure and external mechanical stress. The cooler can also be connected to the vehicle's cooling system. Furthermore, the cooler according to the present invention has low pressure loss and high strength as described above. Depending on the requirements, the outer plate and / or any intermediate or separating plate can be perfectly aligned with the plate in which the flow path is formed, or offset inward on at least one side.

[0010] In the overlapping region between two cooling channel sections within two different plates, a channel height twice as large as the depth of the curved section formed in one plate is generated. This is also true for the channel space for fluids in the remaining plate gap, except for the channel for fluids adjacent to the outer plate. It should be noted that, within the plate gap described, the refrigerant inlet and outlet, for example, has a diameter of 4.0 to 4.4 mm when the plate thickness is 0.6 mm, and a diameter of 2.8 to 3.2 mm when the plate thickness is 0.4 mm.

[0011] The cooler according to the present invention is particularly pressure-stable because stability is more easily ensured, since the fluid flow, in particular the refrigerant flow, is divided into multiple flow paths outside the plate, with a separate inlet and preferably a separate outlet assigned to at least two flow paths, preferably each flow path within each plate. Therefore, an advantage is that heat is efficiently transferred to the second liquid fluid by forming a closed channel space between the plates for a second fluid, such as cooling water. Currently, it is considered preferable that the cooler according to the present invention be applied to cooling water coolers and direct refrigerant evaporators. Further preferred embodiments are described in the dependent claims.

[0012] The design according to the present invention can be advantageously implemented by a single type of plate having flow channels that rotate alternately 180 degrees and are installed within the heat exchanger. This means that only a single type of flow channel pattern or multiple U-shaped patterns, such as U-shaped or winding shapes, can be implemented within the heat exchanger. Therefore, two types of plates are sufficient as an additional plate type in addition to the outer plate. In such a heat exchanger, providing a second type of flow pattern is advantageous in certain applications, and this can also be efficiently achieved in an advantageous manner by using up to two types of plates having flow channels.

[0013] As described above, the flow path according to the present invention can be realized, for example, by interconnecting one plate of the same type that has been rotated 180°. At the same time, the thickness of at least one plate can be favorably reduced to 0.6 mm or less without excessively compromising strength. The plate thickness may vary depending on the manufacturing process and its requirements. A minimum thickness of 0.4 mm is preferred, and initial simulations and tests have shown that a depth of 0.65–0.8 mm is favorable for the channels formed within the plate. This results in a total height or depth of 1.3–1.6 mm in the overlapping region of the two channel sections where the two plates are positioned on top of each other. Such dimensions are currently considered optimal in terms of a robust soldering process, pressure loss, heat transfer performance, and rigidity.

[0014] From a geometrical perspective of flow, initial simulations showed that winding flows and / or, where appropriate, multiple, particularly three-bent U-shaped and / or straight flows are favorable. Because this winding shape is relatively complex, it can be modified depending on the specific requirements. The U-shape essentially includes sections connected at right angles.

[0015] Regarding the mechanical internal pressure resistance of the cooler, it is currently desirable that it be able to withstand an internal pressure matching the maximum operating pressure of the refrigerant R744, in particular, to form a stable cooler. This value can be achieved by minimizing the free expansion area between plates, especially by connecting the plates at multiple points and / or points parallel to multiple flow paths. Thus, internal pressure resistance can be guaranteed despite a plate thickness of less than 0.6 mm.

[0016] Heat transfer can also be improved in a desirable manner by turbulators positioned outside the flow path, i.e., in the cooling water flow space. Turbulators can be formed by circular or elliptical notches, and multiple such turbulators can be provided continuously parallel to the flow path. Preferably, turbulators can be integrally provided in a plate in the form of notches or punches and / or bends. The maximum height of the turbulators can correspond to the height of the flow space, and therefore the turbulators are adjacent to the upper boundary of the flow space.

[0017] From the viewpoint of efficient heat transfer, it is preferable that the second fluid be guided through V-shaped and / or arc-shaped plate gaps. As described above, it is advantageous to provide different flow paths to different regions of the heat exchanger, such that a first shape, e.g., a linear flow path, is formed in the first group of plates, and a second shape, e.g., a U-shape, is formed in the second group of plates. In particular, this can improve performance and at the same time allow as many connections or arbitrary connections as possible to be formed on one side of the heat exchanger.

[0018] Finally, to ensure secure connection of the plates, it has been proven advantageous to join the plates in the inlet and outlet regions and / or the outer edge regions, particularly by soldering. Alternatively or additionally, folds can be provided in at least one reinforcing plate and / or at least one section or location on the outer edge. Reinforcing plates may be provided particularly in the refrigerant inlet and outlet regions, or tie rods may be configured such that tie rods are inserted into additional holes including collars and soldered to each plate. This configuration distributes downward tensile force from the upper plate to multiple plates, including the bottom plate, to all plates. Such tie rods may be circular, elliptical, rectangular, or any other shape. Also, multiple tie rods may be provided. Alternatively or additionally, the plate stack forming the heat exchanger may be surrounded by strips, for example, strips of aluminum material which may be soldered to the plate stack, particularly in areas where the greatest mechanical stress is applied. Finally, one or more C-shaped brackets may be provided on the outside of the plate stack to support the plate stack together. Since at least one bracket has at least one connection, and in any case this is a critical area where pressure stress may occur, it is preferable that at least one bracket be provided in the connection area.

[0019] Considering the advantageous properties, it is more preferable that all inlets and outlets for the first fluid have a plate thickness of approximately 0.6 mm and a diameter of 4.0 to 4.4 mm, or a plate thickness of approximately 0.4 mm and a diameter of 2.8 to 3.2 mm. Furthermore, if all inlets and outlets of the first fluid are surrounded by rising or curved sections formed by plates, this is also advantageous for the stability of the plate stack.

[0020] This point is similarly applicable to the desirable measure of making the ascending part or the recessed part that forms the flow path adjacent to the ascending part or the recessed part. All ascending parts and recessed parts can be efficiently configured, and this structure promotes the flow into and within the channel. If all ascending parts or recessed parts have the same height or depth, the manufacture and connection of the plates are particularly easy. This point is applicable to the preferred measure for making the sections of the flow paths formed in different plates have at least partially the same length. This configuration also improves the flow pattern. In particular, when the flow paths in each plate are adjacent to each inlet and outlet, particularly excellent characteristics are expected so that the fluid flow does not immediately switch after the fluid flows into the adjacent plate.

Brief Description of the Drawings

[0021] [Figure 1] This is the basic structure of the cooler according to the present invention. [Figure 2] This is a plan view of the first type of plate of the cooler shown in FIG. 1. [Figure 3] This is a plan view of the second type of plate of the cooler shown in FIG. 1. [Figure 4] This is a view showing a part of an additional embodiment of the cooler according to the present invention. [Figure 5] This is a part of an additional embodiment of the cooler according to the present invention. [Figure 6] This is a view showing a part of an additional embodiment of the cooler according to the present invention. [Figure 7] This is a part of an additional embodiment of the cooler according to the present invention. [Figure 8] This is a view showing the plates used in the examples of FIGS. 4 to 7. [Figure 9] This is a view showing the plates used in the examples of FIGS. 4 to 7. [Figure 10] This is a view showing the plates used in the examples of FIGS. 4 to 7. [Figure 11]This figure shows the plates used in the embodiments shown in Figures 4 to 7. [Figure 12] This figure shows the plates used in the embodiments shown in Figures 4 to 7. [Figure 13] This is a detailed diagram of the cooler according to the present invention. [Figure 14] This figure shows an additional embodiment of a plate used in a cooler. [Figure 15] This is a diagram showing the plate shown in Figure 14 rotated 180°. [Figure 16] Figures 14 and 15 show cross-sectional views of two sets of plates having volumes according to the diagrams, with the cross-sections perpendicular to the flow path. [Figure 17] Figures 14 and 15 show cross-sectional views of two sets of plates having volumes according to the diagram, with the cross-sections parallel to the flow path. [Figure 18] Figures 14 and 15 show cross-sectional views of two sets of plates having volumes according to the diagram, with the cross-sections parallel to the flow path. [Figure 19] This is a cross-sectional view that penetrates the outer plate and the two sets of plates. [Figure 20] This figure shows the flow on the first plate, the second plate, and the plate formed by combining both the first and second plates. [Figure 21] This figure shows the flow on the first plate, the second plate, and the plate formed by combining both the first and second plates. [Figure 22] This figure shows the flow on the first plate, the second plate, and the plate formed by combining both the first and second plates. [Figure 23] This figure shows a further embodiment of the plate. [Figure 24] Figure 23 is a first cross-sectional view of a plate stack consisting of multiple plates. [Figure 25] This is a second cross-section that penetrates the plate stack, which consists of multiple plates as shown in Figure 23. [Modes for carrying out the invention]

[0022] As shown in Figure 1, the cooler 10 according to the present invention includes a plurality of plates, which are described below. All plates are generally basically rectangular, and the outer plate 14 is basically flat at least on the outside. The intermediate plate 12 includes the structure described below to form a flow path. In the illustrated embodiment, the illustrated upper outer plate has an inlet 16 and an outlet 22, which can be adjusted according to customer requirements, as will be further described below.

[0023] Specifically, in the illustrated embodiment, the upper outer plate 14 includes, for example, an inlet 16 and an outlet 18 for cooling water to be cooled by the cooler 10 according to the present invention. In the illustrated orientation, as indicated by arrows A and B, the cooling water flows basically from top to bottom through all the plate gaps described below, and then from bottom to top of the cooler 10 towards the outlet 18. Specifically, the cooling water is distributed through all the plate gaps, flowing in a U-shape through the illustrated passage 36, basically from front left to back right, then to front right, and finally to front left, in order to pass through the illustrated passage 36 to the outlet 18.

[0024] Figures 2 and 3 show the interrupted flow path 34 for the refrigerant, which is detailed below. The refrigerant essentially flows between the U-shaped flow path 34, particularly as a result of the formation of the central boundary 58. The inlet 16 and outlet 18 are basically cylindrical, with a nearly conical shape in the center, and can be soldered to the outer plate 14. This also applies to the block 24 having a refrigerant inlet 20 and outlet 22, which will be described later. Taking into account the higher pressure load in this region, the block 24 can be formed, for example, by milling.

[0025] Multiple openings 26 through which the refrigerant enters the multiple flow paths described below can be seen in the right-hand region of the outer plate 14. Based on Figure 1, the refrigerant is described as initially flowing to the front left along arrow C in the left-hand region of the plate stack 28. As indicated by the vertical arrow C, this flow occurs parallel to the entire plate stack 28. For clarity, the two bottom plates of this plate stack 28 are shown separately from each other. The portion of the plate stack 28 above these two bottom plates is composed of identical plates that appear to be stacked.

[0026] This point also applies to the lower plate stack 30, which is separated from the upper plate stack 28 by a separator or intermediate plate 32. In the case of the upper plate stack 28, a linear flow is illustrated along arrow C, which points from the rear right to the front left. In contrast, in the lower plate stack 30, a U-shaped flow is formed in the lower plate stack 30, so that the refrigerant flows parallel in all the flow paths of the plate stack 30, first from the front left to the rear right along arrow D, then from the rear left to the rear right along arrow E, and then from the rear right to the front left along arrow F. From here, the refrigerant flows upward, into the right-hand portion of the upper plate stack 28, then flows parallel in all the flow paths along arrow G, from the front left to the rear right, and thus linearly, and from there flows to the outlet 22 along arrow H.

[0027] The coolant flowing in from inlet 16 flows from front left to rear right in the left region of the upper plate stack, so the coolant flows in the opposite direction to the refrigerant. In the lower plate stack, a parallel U-shaped flow is generated. A reverse flow is also formed in the right portion of the upper plate stack 28. This reverse flow extends the flow path in an advantageous manner and improves heat transfer. This is particularly advantageous for the reverse flow in the right region of the upper plate stack 28, which is especially beneficial for cooling the coolant flowing out of the cooler 10. At the same time, in the case of the cooler 10 shown in Figure 1, all inlets and outlets (16, 18, 20, 22) can be advantageously positioned on one side, which provides an advantage, for example, when connecting the cooler to a vehicle's cooling system.

[0028] As shown in Figure 2, the plate 12 of the upper plate stack 28 includes, on the one hand, an opening 26 for the refrigerant, and on the other hand, interrupted flow paths 34 and passages 36, such as 4 to 6 parallel flow paths 34 and passages 36 for the refrigerant and cooling water, as described below. In the illustrated example, the plate shown in Figure 2 is configured so that the refrigerant flows linearly from top to right to left and from bottom to left to right. In the presented example, the turbulator 38 is shown in the upper region between the flow channels, as described below. As shown in Figure 2, in this case the turbulator has an elongated shape in the direction of refrigerant flow and is connected in series with the flow paths 34 for the refrigerant.

[0029] This point also applies to the plates 40 of the lower plate stack 30 shown in Figure 3. In particular, as shown in the right-hand region, the refrigerant switches its flow path within the flow path 34, resulting in an overall U-shaped flow.

[0030] In the alternative embodiment shown in Figure 4, the flow essentially bends three times in a U-shape, as will be described in more detail below. Here, the central U is inverted, and its two legs coincide with the inner legs of the outer U. In this case, the refrigerant inlet 20 and outlet 22 are separated, and the refrigerant first flows into individual channels along arrow C, then to the right along arrow D as described, and from there flows in a U-shape or winding pattern with three bends towards the outlet 22. The cooling water inlet and outlet can be considered essentially cylindrical and can be used parallel to the refrigerant and as a backflow to the refrigerant.

[0031] Figure 5 is essentially twice the flow shown in Figure 4. After the flow originating from the second plate is guided from above to the third plate, it flows basically from left to right within the two upper plates and from right to left within the two lower plates. For example, as shown in the example in Figure 4, the return flow that passes through another plate pair and returns to outlet 22 is indicated by arrow H.

[0032] Figure 6 shows that the refrigerant inlet 20 and outlet 22 are favorably positioned on one side of the cooler, utilizing the lower group of openings 42 in the upper plate (see Figure 8), so that the refrigerant flows from left to right in the upper plate pair shown in Figure 7, from right to left in the intermediate plate pair, and again from left to right in the lower plate pair shown in Figure 7. The resulting overall recirculation after flowing through the plate pair in Figure 6 to the outlet 22 is indicated by arrow H. In the concepts shown in Figures 4 to 7, it is emphasized that it is advantageous to have all inlets and outlets (16-22) positioned on one side. This makes it easier to integrate the cooler into a vehicle's cooling system, for example, without requiring external switching of the refrigerant. The combination of Figures 4 and 5 allows for odd-numbered switching, and the combination of Figures 6 and 7 allows for even-numbered switching.

[0033] As shown in more detail in Figure 8, the upper plate of each plate pair according to Figure 7 corresponds to the first plate type shown in Figure 8. The second plate type shown in Figure 9 forms the lower plate of the upper and lower plate pair, and the plate type shown in Figure 10 forms the lower plate of the intermediate plate pair. Arrows I in Figures 8-12, 14, and 15 indicate, in the illustrated orientation, the basically inverted V-shaped flow of the second fluid in the fluid space between the two plates from one passage 36 to the other passage. The fluid space extends in all directions to the outer boundary 60. Generally, the second fluid, which is cooling water, in particular water, is cooled and, in this case, flows in reverse, dissipating heat to the coolant which flows in a U-shape that basically bends three times, from the upper left to the upper right, according to the drawing, and evaporates. The heat is transferred evenly along the fluid passage.

[0034] The remaining plate types shown in Figures 11 and 12 correspond to the plates shown at the bottom of Figures 4 and 6, while the plate type shown in Figure 12 forms the upper plate. Furthermore, the two upper plate pairs in Figure 7 correspond to the plate pair shown in Figure 5, and at the bottom of Figure 4, the plate type in Figure 11 is the upper plate, and the plate type in Figure 12 is the lower plate.

[0035] As shown in Figures 8 to 12, the different openings 26 are closed with different plate types to realize the flow paths described above using the illustrated plates. Groups of openings, such as group 42 shown in Figure 8, form collector regions that can be used favorably for heat transfer. In all plate types, the flow paths of each refrigerant in the plate type are interrupted, and how the resulting cooler functions will be described in more detail below.

[0036] Due to the respective central boundaries 58, the refrigerant flows from one passage 36 to the other passage in basically an inverted V-shape or arc shape. First, Figure 13 shows how a block 24 having a refrigerant inlet 20 and / or outlet 22 is connected to an outer plate 14, how the outer plate 14 is connected to an intermediate plate 12, and how multiple intermediate plates 12 are connected to each other. This connection is advantageously achieved by soldering, and it is emphasized that the resulting circumferential and double soldering of the plates in the indicated region 44 particularly ensures rigidity. Rigidity can be further increased optionally by lateral folds, as shown by the folded edges 46. The double circumferential soldering in the indicated region 44 is applied outward toward the left side of the soldering sufficient to perform the function of the cooler, as shown in Figure 13, in the region of the mutually aligned bulging portions of the plates 12, and provides additional protection against corrosion. Since the soldering required to perform the function of the cooler is applied inward from that region 44, corrosion in that region 44 will not lead to leakage of refrigerant or fluid.

[0037] The above also applies to the method shown in Figure 14, where local recesses (dimples, 48) that are soldered continuously to each other on all plates can be provided at one or more corners of plate 12.

[0038] Figure 15 shows the plate shown in Figure 14 rotated 180° around a vertical axis parallel to the plane of the plate along the drawing, which has interrupted flow channels. However, when the plate shown in Figure 14 is soldered to the plate shown in Figure 15 in the illustrated orientation, a continuous flow channel is formed in one of the two plates within a specific region. Here, the refrigerant can flow from one plate to the other within the region where the flow channels of the two plates overlap. The ends of the flow channel sections form barriers for transition into the interior of the other plate.

[0039] Figure 16 shows, in an exemplary manner based on a cross-sectional view, the refrigerant entering the second opening 26 from the left side and initially flowing only within the upper plate 50. However, in the next course, the formed flow path 34 ends, and the refrigerant flows into a flow path 34 formed in the lower plate 54 in the shape of a curved section within the overlapping region. In the illustrated example, each flow path 34 is assigned an opening 26 formed in an additional plate (50, 54), and from this viewpoint, each flow path 34 functions as a distribution section on the flow path 34 of multiple plates (50, 54).

[0040] The overlap shown in Figure 16 illustrates the second channel 34 from the right and the leftmost channel 34 in an exemplary manner. In this region, the refrigerant flows through channels in both plates (50, 54). In the case of the rightmost channel 34, in this region, the refrigerant flows only through the channel 34 formed in the lower plate 54, while the limited channel 34 formed in the upper plate 50 appears to be shown above it.

[0041] As shown in Figure 17, in this case, the refrigerant begins to flow only within the upper plate 50 in the overlap region 52, passes through the flow path of the lower plate 54, and then alternately enters and exits the flow path in the upper plate 50 again in another overlap region 52. This is also shown in Figure 18, which uses the same reference numerals. Figure 18 shows the flow of the cooling water that is to be cooled, as can be seen in the plate gap.

[0042] Figure 19 shows an additional flow space 56 for cooling water adjacent to the outer plate 14, illustrating how the arrangement of the two plate pairs, the upper plate 50 and the lower plate 54, is enclosed by the essentially flat outer plate 14. In the illustrated cross-section, the leftmost flow path 34 is located only within the upper plate 50, the second flow path 34 from the left is located only within the lower plate 54, and the third flow path from the left is located in both the upper plate 50 and the lower plate 54.

[0043] Figure 20 shows the interrupted region in the upper plate 50 where the refrigerant flows, corresponding to the flow path of the upper plate 50 shown in Figure 14. Figure 21 shows the interrupted region in the lower plate 54 through which the refrigerant flows, corresponding to the flow path shown in Figure 15, and Figure 22 shows the resulting flow that alternates between the two plates through different hatching of the flow paths in the different plates. Figure 23 shows, as an example, how the turbulator 38 is formed continuously and parallel to the flow path 34 in the case of a plate with a U-shaped flow that bends three times as described.

[0044] Finally, as shown in Figures 24 and 25, which show cross-sections positioned perpendicular to each other, the turbulator 38 can extend across the entire height of the flow gap and, as a result, be adjacent to each upper or outer plate 14. As shown in the right-hand region of Figure 25, the turbulator 38 can extend in both directions, and the plates can be punched out such that when the two plates are joined, the thickness of one plate becomes the area of ​​the turbulator 38, and in other regions, particularly between the flow channels 34, the thickness of the plate is doubled. Industrial Applicability The present invention relates to a cooler having two substantially parallel plates. [Explanation of symbols]

[0045] 10 Cooler 12 Intermediate plate 14 Outer plate 16 Entrance Exit 18, 22 20 Refrigerant inlet 24 blocks 26 Opening 28 Upper plate stack 30 Lower plate stack 32 Intermediate plate 34 U-shaped channel 36 aisles 38 Turbulator 40 plates 42 Opening of the upper plate 44 areas 50 Upper plate 54 Lower plate 58 Central boundary 60 Outer boundary

Claims

1. A cooler (10) having at least two parallel plates (12, 14, 50, 54) connected to each other and in particular formed by soldering each other, At least one flow path (34) formed in one of the plates (50) is interrupted, and the plate (50) has at least one barrier such that the flow of a first fluid, in particular the flow of a refrigerant, is switched to a flow path formed in another plate (54). A cooler (10) characterized in that at least two flow paths (34), preferably each flow path (34) is assigned a separate inlet (26) and preferably an outlet (26), and a closed flow space (56) for a second fluid, such as cooling water, is formed between the plates (12, 14, 50, 54).

2. The cooler (10) according to claim 1, comprising up to three, preferably two different types of plates (12), two of which, preferably one of which types, have flow channels (34) formed inside the plate.

3. The cooler (10) according to claim 1, characterized in that at least one type of plate (12) is installed in at least two different orientations, preferably rotated by 180°.

4. The cooler (10) according to claim 1, characterized in that at least one plate (12, 14) has a thickness of 0.4 to 0.6 mm, and / or at least one flow path within the plate (12, 14) has a depth of 0.65 to 0.8 mm.

5. The cooler (10) according to claim 1, characterized in that the first fluid is guided in a curved and / or U-shaped and / or straight manner, which is curved at least once, particularly three times, so as to penetrate the cooler (10) and / or the flow path.

6. The cooler (10) according to claim 1, characterized in that it has a mechanical internal pressure resistance equivalent to the maximum operating pressure of the refrigerant R744.

7. The cooler (10) according to claim 1, characterized in that it is provided with a turbulator (38) outside the flow path (34) for the refrigerant.

8. The cooler (10) according to claim 1, characterized in that the second fluid is guided to pass through a V-shaped and / or arc-shaped plate gap.

9. The cooler (10) according to claim 1, characterized in that in the first group (28) of the plates (12, 14, 50, 54), the flow path is formed in a first shape, for example, a straight line, and in the second group (30) of the plates (12, 14, 50, 54), the flow path is formed in a second shape, for example, a U-shape.

10. The cooler (10) according to claim 1, wherein the plates (12, 14, 50, 54) are connected to each other in the inlet and outlet (16-22) regions and / or the outer ends, and at least one reinforcing plate and / or at least one folding portion (46) is provided at least in sections or locations on the outer ends.

11. The cooler (10) according to claim 1, characterized in that all inlets and outlets (26) for the first fluid have a diameter of 4.0 to 4.4 mm, especially in the case of a plate thickness of about 0.6 mm, or a diameter of 2.8 to 3.2 mm, especially in the case of a plate thickness of about 0.4 mm.

12. The cooler (10) according to claim 1, characterized in that all inlets and outlets (26) for the first fluid are surrounded by risers or inlets formed of the plate.

13. The cooler (10) according to claim 12, characterized in that the rising portion or inlet portion is adjacent to the rising portion or inlet portion that forms the flow path (34).

14. The cooler (10) according to claim 12, characterized in that all of the aforementioned rising or recessed portions are of the same height or depth.

15. The cooler (10) according to claim 1, characterized in that the sections of the flow path (34) formed on the different plates (12, 14, 50, 54) are at least partially the same length.

16. The cooler (10) according to claim 1, characterized in that, within each plate (12, 14, 50, 54), the flow path (34) is positioned adjacent to the inlet and outlet (26), respectively, so that the fluid flow to an adjacent plate (12, 14, 50, 54) does not immediately switch after the fluid enters the adjacent plate (12, 14, 50, 54).

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