Laminated plate heat exchanger

Abstract

The present invention suppresses the tendency of flow imbalance between stages in a plate-laminated heat exchanger. An inlet (10) for the first fluid (3) is formed at one end of the plates (1, 2) in the stacking direction, an outlet (11) for the first fluid (3) is formed at the other end of the plates (1, 2), the inlet (10) is connected to the first communication hole (7), the outlet (11) is connected to the second communication hole (8), and a bypass from the second communication hole (8) at the one end to the outlet (11) is formed in this case.

Description

Technical Field

[0001] The present invention relates to a plate stacking-type heat exchanger, and more particularly to a structure for suppressing flow rate imbalance (biased flow) in each section of a flow channel through which a fluid flows (circulates). Background Art

[0002] As a conventional type of plate stacking type heat exchanger, there is a heat exchanger in which first flow channels through which a first fluid flows and second flow channels through which a second fluid flows are alternately formed on every other plate in the stacking direction of the plates. Fig.13A and Fig.14A This is an example of a conventional plate stack type heat exchanger, and the arrangements of the inlet and outlet of the first fluid are different. exist Fig.13A In the heat exchanger, an inlet for the first fluid is formed at one end portion in the stacking direction of the plates, and an outlet for the first fluid is arranged at the other end portion (I-shaped inlet and outlet arrangement). exist Fig.14A In the heat exchanger, an inlet and an outlet for a first fluid are arranged at one end portion in the stacking direction of the plates (U-shaped inlet and outlet arrangement). Summary of the invention [Technical problem to be solved by the invention]

[0003] exist Fig.13A In the case of an I-shaped inlet and outlet configuration, due to the inertia of the fluid, such as Fig. 13B As shown in the example, there is a tendency for the flow rate distribution between the stages to become uneven (flow rate imbalance). In addition, Fig.14A In the case of a U-shaped inlet and outlet configuration, the influence of the flow path length inside the core is dominant, resulting in Fig. 14B The flow rate imbalance tendency illustrated in the example produces an opposite flow rate imbalance tendency under the condition where the influence of inertia is dominant. Therefore, the technical problem to be solved by the present invention is to suppress the tendency of flow rate imbalance between stages in a plate stack type heat exchanger having an I-shaped or U-shaped inlet and outlet arrangement. [Technical solutions for solving technical problems]

[0004] The first invention for solving the above-mentioned technical problems is a plate stack type heat exchanger having a core 9 in which a plurality of disk-shaped plates 1 and 2 are stacked. In the stacking direction of the plates 1 and 2, first flow channels 4 through which the first fluid 3 flows and second flow channels 6 through which the second fluid 5 flows are alternately formed on every other plate. A first communicating hole 7 and a second communicating hole 8 are provided separately from each other on each of the plates 1 and 2. The core 9 is used to guide the first fluid 3 from the first communicating hole 7 to the second communicating hole 8 through the first flow channel 4, wherein: An inlet 10 for the first fluid 3 is formed at one end of the plates 1 and 2 in the stacking direction, and an outlet 11 for the first fluid 3 is formed at the other end. The inlet 10 is connected to the first communicating hole 7, and the outlet 11 is connected to the second communicating hole 8. A bypass from the second communication hole 8 at the one end portion to the outlet 11 is formed through the inside or outside of the core 9 .

[0005] The second invention for solving the above-mentioned technical problems is a plate stack type heat exchanger having a core 9 in which a plurality of disk-shaped plates 1 and 2 are stacked. In the stacking direction of the plates 1 and 2, first flow channels 4 through which the first fluid 3 flows and second flow channels 6 through which the second fluid 5 flows are alternately formed on every other plate. A first communicating hole 7 and a second communicating hole 8 are provided separately from each other on each of the plates 1 and 2. The core 9 is used to guide the first fluid 3 from the first communicating hole 7 to the second communicating hole 8 through the first flow channel 4, wherein: An inlet 10 for the first fluid 3 is formed at one end of the plates 1 and 2 in the stacking direction, and an outlet 11 for the first fluid 3 is formed at the other end. The inlet 10 is connected to the first communicating hole 7, and the outlet 11 is connected to the second communicating hole 8. A bypass from the inlet 10 to the first communication hole 7 at the other end is formed through the inside or outside of the core 9 .

[0006] The third invention for solving the above-mentioned technical problems is a plate stack type heat exchanger having a core 9 in which a plurality of disk-shaped plates 1 and 2 are stacked. In the stacking direction of the plates 1 and 2, first flow channels 4 through which the first fluid 3 flows and second flow channels 6 through which the second fluid 5 flows are alternately formed on every other plate. A first communicating hole 7 and a second communicating hole 8 are provided separately from each other on each of the plates 1 and 2. The core 9 is used to guide the first fluid 3 from the first communicating hole 7 to the second communicating hole 8 through the first flow channel 4, wherein: An inlet 10 and an outlet 11 for the first fluid 3 are formed at one end of the plates 1 and 2 in the stacking direction. The inlet 10 is connected to the first communicating hole 7, and the outlet 11 is connected to the second communicating hole 8. A bypass from the second communication hole 8 at the other end portion of the plates 1 , 2 in the stacking direction to the outlet 11 is formed through the inside or outside of the core 9 .

[0007] The fourth invention for solving the above-mentioned technical problems is a plate stack type heat exchanger having a core 9 in which a plurality of disk-shaped plates 1 and 2 are stacked. In the stacking direction of the plates 1 and 2, first flow channels 4 through which the first fluid 3 flows and second flow channels 6 through which the second fluid 5 flows are alternately formed on every other plate. A first communicating hole 7 and a second communicating hole 8 are provided separately from each other on each of the plates 1 and 2. The core 9 is used to guide the first fluid 3 from the first communicating hole 7 to the second communicating hole 8 through the first flow channel 4, wherein: An inlet 10 and an outlet 11 for the first fluid 3 are formed at one end of the plates 1 and 2 in the stacking direction. The inlet 10 is connected to the first communicating hole 7, and the outlet 11 is connected to the second communicating hole 8. A bypass path from the inlet 10 to the first communication hole 7 at the other end portion of the plates 1 and 2 in the stacking direction is formed inside or outside the core 9 .

[0008] A fifth invention for solving the above-mentioned technical problems is a plate stack type heat exchanger which is the plate stack type heat exchanger according to the above-mentioned first invention and is also the plate stack type heat exchanger according to the above-mentioned second invention.

[0009] The sixth invention for solving the above-mentioned technical problems is a plate stack type heat exchanger which is the plate stack type heat exchanger described in the third invention and is also the plate stack type heat exchanger described in the fourth invention. [Effects of the invention]

[0010] The above-mentioned first invention is a plate stacked heat exchanger, in which an inlet 10 for the first fluid 3 is formed at one end in the stacking direction of the plates 1 and 2, and an outlet 11 for the first fluid 3 is formed at the other end, and a bypass from the second connecting hole 8 at the one end to the outlet 11 is formed inside or outside the core 9. A flow path directly connected from the inlet 10 at one end to the outlet 11 at the other end is a main flow path, and a flow path from the second communication hole 8 at one end to the outlet 11 via a bypass to the outlet 11 is a secondary flow path. By such an arrangement, in the secondary flow channel, the distance of the layer on one side through the second connecting hole 8 is shorter. Since the flow channel length inside the core 9 is shortened, the flow imbalance tendency caused by the flow channel length and the flow imbalance tendency caused by the inertia in the main flow channel are offset, thereby suppressing the flow imbalance between the sections.

[0011] The above-mentioned second invention is a plate stacked heat exchanger, in which an inlet 10 for the first fluid 3 is formed at one end in the stacking direction of the plates 1 and 2, and an outlet 11 for the first fluid 3 is formed at the other end, and a bypass from the inlet 10 to the first connecting hole 7 at the other end is formed inside or outside the core 9. A flow path directly connected from the inlet 10 at one end to the outlet 11 at the other end is a main flow path, and a flow path from the inlet 10 to the outlet 11 via a bypass to the first communication hole 7 at the other end is a secondary flow path. By setting in this way, the flow rate imbalance tendency due to the inertia of the first fluid 3 in the secondary flow channel and the flow rate imbalance tendency due to the inertia in the primary flow channel are offset, thereby suppressing the flow rate imbalance between the stages.

[0012] The technical solution described in the above-mentioned third invention is a plate stacked heat exchanger, in which an inlet 10 and an outlet 11 of the first fluid 3 are formed at one end of the plates 1 and 2 in the stacking direction, and a bypass from the second connecting hole 8 at the other end of the plates 1 and 2 in the stacking direction to the outlet 11 is formed inside or outside the core 9. A flow path directly connected from the inlet 10 at one end to the outlet 11 is a main flow path, and a flow path from the second communication hole 8 at the other end of the plates 1 and 2 in the stacking direction to the outlet 11 via a bypass is a secondary flow path. By setting in this way, the flow rate imbalance tendency caused by the inertia of the first fluid 3 in the secondary flow channel and the flow rate imbalance tendency caused by the flow channel length in the primary flow channel are offset, thereby suppressing the flow rate imbalance between the stages.

[0013] The fourth invention is a plate stacked heat exchanger, in which an inlet 10 and an outlet 11 of the first fluid 3 are formed at one end of the plates 1 and 2 in the stacking direction, and a bypass of the first connecting hole 7 from the inlet 10 to the other end of the plates 1 and 2 in the stacking direction is formed inside or outside the core 9. The flow path directly connected from the inlet 10 at one end to the outlet 11 is the main flow path, and the flow path from the inlet 10 to the outlet 11 via the first communication hole 7 at the other end in the stacking direction of the plates 1 and 2 is the secondary flow path. By setting in this way, the flow rate imbalance tendency due to the inertia of the first fluid 3 in the secondary flow channel and the flow rate imbalance tendency due to the inertia in the primary flow channel are offset, thereby suppressing the flow rate imbalance between the stages.

[0014] The fifth invention is a plate stack type heat exchanger, which is the plate stack type heat exchanger described in the first invention and is also the plate stack type heat exchanger described in the second invention. Since the effects of the first and second inventions are combined, the flow imbalance tendency in the secondary flow channel, whether caused by the flow channel length or by inertia, is offset by the flow imbalance tendency in the main flow channel, thereby suppressing the flow imbalance between each section.

[0015] The sixth invention is a plate stack type heat exchanger, which is the plate stack type heat exchanger described in the third invention and is also the plate stack type heat exchanger described in the fourth invention. Since the effects of the third invention and the fourth invention are combined, the flow imbalance tendency in the main channel, whether caused by the channel length or by inertia, is offset by the flow imbalance tendency in the secondary channel, thereby suppressing the flow imbalance between the sections. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1A is a cross-sectional view of a plate stack type heat exchanger according to a first embodiment of the present invention. Figure 1C AA section view. Figure 1B This is a schematic diagram of the flow path of the heat exchanger. Figure 1C yes Figure 1A Top view of the . Figure 2A It is a cross-sectional view showing another example of the first embodiment of the present invention. Figure 2B This is a schematic diagram of the flow path of the heat exchanger. Figure 3A It is a cross-sectional view of a plate stack type heat exchanger according to a second embodiment of the present invention. Figure 3B This is a schematic diagram of the flow path of the heat exchanger. Figure 4A It is a cross-sectional view showing another example of the second embodiment of the present invention. Figure 4B This is a schematic diagram of the flow path of the heat exchanger. Figure 5A It is a cross-sectional view of a plate stack type heat exchanger according to a third embodiment of the present invention. Figure 5B This is a schematic diagram of the flow path of the heat exchanger. Fig. 6A It is a cross-sectional view showing another example of the third embodiment of the present invention. Figure 6B This is a schematic diagram of the flow path of the heat exchanger. Fig. 7A It is a cross-sectional view of a plate stack type heat exchanger according to a fourth embodiment of the present invention. Figure 7B This is a schematic diagram of the flow path of the heat exchanger. Fig. 8A It is a cross-sectional view showing another example of the fourth embodiment of the present invention. Figure 8B This is a schematic diagram of the flow path of the heat exchanger. Fig. 9A It is a cross-sectional view of a plate stack type heat exchanger according to a fifth embodiment of the present invention. Fig. 9B This is a schematic diagram of the flow path of the heat exchanger. Fig. 10A It is a cross-sectional view showing another example of the fifth embodiment of the present invention. Fig. 10B This is a schematic diagram of the flow path of the heat exchanger. Fig.11A It is a cross-sectional view of a plate stack type heat exchanger according to a sixth embodiment of the present invention. Fig. 11B This is a schematic diagram of the flow path of the heat exchanger. Fig. 12A It is a cross-sectional view showing another example of the sixth embodiment of the present invention. Fig. 12B This is a schematic diagram of the flow path of the heat exchanger. Fig.13A This is a schematic diagram of a conventional first plate stack type heat exchanger in which an inlet 10 and an outlet 11 are separately arranged at the top and bottom of a core 9 . Fig. 13B It is a graph showing the flow channel distribution of each stage in the core 9 of the heat exchanger. Fig.14A This is a schematic diagram of a conventional second plate stack type heat exchanger in which an inlet 10 and an outlet 11 are arranged only on the upper end side of a core 9 . Fig. 14B It is a graph showing the flow channel distribution of each stage in the core 9 of the heat exchanger. DETAILED DESCRIPTION

[0017] Next, embodiments of the present invention will be described with reference to the drawings. The common structure of the plate stack type heat exchangers of the first to sixth embodiments is as follows. A plurality of stacked disc-shaped plates 1 and 2 with raised outer peripheral edges constitute a core 9. A first flow channel 4 for a first fluid 3 to flow through and a second flow channel 6 for a second fluid 5 to flow through are alternately formed on every other plate in the stacking direction of the plates 1 and 2. A first connecting hole 7 and a second connecting hole 8 are provided separately from each other on each plate 1 and 2. The first connecting hole 7 and the second connecting hole 8 are connected to each section of the first flow channel 4 of the core 9. The first fluid 3 is guided from the first communicating hole 7 to the second communicating hole 8 through the first flow path 4. The second fluid 5 flows through the second flow path 6. Then, heat exchange is performed between the first fluid 3 and the second fluid 5. The first flow channel 4 is hollow. When the flow channel is hollow like the first flow channel 4, its flow resistance is small, so it is generally easy to cause flow imbalance between stages. In the first flow channel 4, a protrusion can be formed to improve heat transfer, but in this case, the flow channel resistance is also relatively small, so there is generally a tendency for flow imbalance between stages. Furthermore, for example, the first fluid 3 is water, a refrigerant, or the like, and the second fluid 5 is oil or the like. In this example, the plan view shape of each plate 1, 2 is formed into a square (such as Figure 1C As shown, it includes a shape with rounded corners), but the top view shape is not limited to a square, and any shape can be used. [Example 1]

[0018] Figure 1A is a cross-sectional view of the plate stack type heat exchanger of the first embodiment, Figure 1B This is a schematic diagram of its flow path. Figure 1C yes Figure 1A Top view of the . The heat exchanger of the first embodiment is as follows Figure 1A , Figure 1B As described above, an inlet 10 of the first fluid 3 is formed at one end of the plates 1 and 2 in the stacking direction, and an outlet 11 of the first fluid 3 is formed at the other end (I-shaped inlet and outlet configuration). The inlet 10 is connected to the first connecting hole 7, and the outlet 11 is connected to the second connecting hole 8. The flow channel that directly connects the inlet 10 and the outlet 11 is the main flow channel of the first fluid 3.

[0019] A bypass composed of a communication path 13 and a first bypass path 12a is formed from the second communication hole 8 at one end in the stacking direction of the plates 1 and 2. The flow path that reaches the outlet 11 through the bypass is a secondary flow path.

[0020] In the first embodiment, the first fluid 3 flowing into the main channel from the inlet 10 flows down from one end to the other end in the stacking direction of the plates 1 and 2 in the first connecting hole 7 by inertia, and there is a tendency for flow imbalance in the section of the first flow channel 4 near the other end. On the other hand, in the secondary flow channel, the distance that the layer on one side passes through the second connecting hole 8 is shorter, and since the flow channel length inside the core 9 is shortened, the flow imbalance tendency caused by the flow channel length is opposite to the flow imbalance tendency in the main flow channel. According to this, the flow rate imbalance tendency due to inertia in the main flow channel and the flow rate imbalance tendency due to the flow channel length in the secondary flow channel are offset, and the flow rate imbalance between the stages is suppressed.

[0021] Figure 2A is a cross-sectional view showing another example of the first embodiment, Figure 2BThis is a schematic diagram of its flow path. Figure 1A In the heat exchanger of FIG. 1 , the first bypass 12a is formed inside the core 9, but Figure 2A In the heat exchanger, the first bypass 12 a is formed outside the core 9 . The first bypass 12a functions as a bypass without changing whether it is located inside or outside the core 9, and therefore, the effect of the present invention does not differ. As an example, the first bypass 12a may be formed of a pipe as shown in the figure. [Example 2]

[0022] Figure 3A is a cross-sectional view of a plate stack type heat exchanger according to a second embodiment of the present invention, Figure 3B This is a schematic diagram of the flow path of the heat exchanger. This embodiment is also a plate stack type heat exchanger with an I-shaped inlet and outlet arrangement, similar to the first embodiment. The second embodiment differs from the first embodiment in the position where the bypass is formed. In the second embodiment, a bypass composed of the communication passage 13 and the second bypass 12b is formed from the inlet 10. The flow path that passes through the bypass and reaches the first communication hole 7 at the other end of the plates 1 and 2 in the stacking direction is a secondary flow path. The second bypass 12b of this example is formed outside the core 9, but Figure 4A , Figure 4B In that way, it can be formed inside the core 9. The tendency of flow rate imbalance due to the inertia of the first fluid 3 flowing through the main channel is the same as that of the first embodiment. On the other hand, the flow rate imbalance tendency due to the inertia of the first fluid 3 in the secondary flow channel is opposite to the flow rate imbalance tendency in the primary flow channel. According to this, the flow rate imbalance tendency due to inertia in the main flow channel and the flow rate imbalance tendency due to inertia in the secondary flow channel are offset, and the flow rate imbalance between the stages is suppressed. [Example 3]

[0023] Figure 5A is a cross-sectional view of a plate stack type heat exchanger according to a third embodiment of the present invention. Figure 5B This is a schematic diagram of the flow path of the heat exchanger. In the third embodiment, an inlet 10 and an outlet 11 (U-shaped inlet and outlet arrangement) of the first fluid 3 are formed at one end of the stacking direction of the plates 1 and 2. The inlet 10 is connected to the first connecting hole 7, and the outlet 11 is connected to the second connecting hole 8. The flow channel that directly connects the inlet 10 and the outlet 11 is the main flow channel of the first fluid 3. In this embodiment, if Figure 5AAs described, a bypass composed of the third bypass 12c and the communication passage 13 is formed from the second communication hole 8 at the other end in the stacking direction of the plates 1 and 2. The flow path that reaches the outlet 11 through the bypass is a secondary flow path. In this example, if Figure 5A As shown, the third bypass 12c is formed inside the core 9, but as shown in Fig. 6A , Figure 6B As shown, it can also be formed outside the core 9. In the main flow channel, when the influence of the flow channel length inside the core is dominant, there is a tendency for the flow rate of the first fluid 3 flowing in from the inlet 10 to be unbalanced in the section of the first flow channel 4 near the one end where the flow channel length inside the core is shorter. On the other hand, the flow rate imbalance tendency due to the inertia of the first fluid 3 in the secondary flow channel is opposite to the flow rate imbalance tendency in the primary flow channel. According to this, the flow rate imbalance tendency due to the flow channel length in the main flow channel and the flow rate imbalance tendency due to the inertia in the secondary flow channel are offset, and the flow rate imbalance between the stages is suppressed. [Example 4]

[0024] Fig. 7A is a cross-sectional view of a plate stack type heat exchanger according to a fourth embodiment of the present invention. Figure 7B This is a schematic diagram of the flow path of the heat exchanger. The fourth embodiment is similar to the third embodiment, and adopts a U-shaped inlet and outlet configuration. The inlet 10 is connected to the first communication hole 7 , and the outlet 11 is connected to the second communication hole 8 . In this example, if Fig. 7A As shown, a bypass composed of the communication passage 13 and the fourth bypass 12d is formed from the inlet 10. The flow path that passes through the bypass and reaches the first communication hole 7 at the other end of the plates 1 and 2 in the stacking direction is a secondary flow path. The fourth bypass 12d Fig. 7A , Figure 7B As shown, it is formed inside the core 9, but it can also be formed as shown in FIG. Fig. 8A , Figure 8B As shown, it is formed outside the core 9. In the main flow channel, when the influence of the inertia of the first fluid 3 is dominant, there is a tendency for the first fluid 3 flowing in from the inlet 10 to flow from one end to the other end in the stacking direction of the plates 1 and 2 in the first connecting hole 7, and the flow rate tends to be unbalanced in the section of the first flow channel 4 near the other end. On the other hand, the flow rate imbalance tendency due to the inertia of the first fluid 3 in the secondary flow channel is opposite to the flow rate imbalance tendency in the primary flow channel. According to this, the flow rate imbalance tendency due to inertia in the main flow channel and the flow rate imbalance tendency due to inertia in the secondary flow channel are offset, and the flow rate imbalance between the stages is suppressed. [Example 5]

[0025] Fig. 9A is a cross-sectional view of a plate stack type heat exchanger according to a fifth embodiment of the present invention. Fig. 9B This is a schematic diagram of the flow path of the heat exchanger. The fifth embodiment is similar to the first and second embodiments, and adopts an I-shaped inlet and outlet arrangement. The inlet 10 is connected to the first communication hole 7 , and the outlet 11 is connected to the second communication hole 8 . In this example, if Fig. 9A As shown, a bypass consisting of a communicating hole 13 and a first bypass 12a is formed from the second communicating hole 8 at one end of the plates 1 and 2 in the stacking direction, and a bypass consisting of a communicating channel 13 and a second bypass 12b is formed from the inlet 10. The first bypass 12a and the second bypass 12b are as follows Fig. 9A , Fig. 9B As shown, it is formed inside the core 9, but it can also be formed as Fig. 10A , Fig. 10B As shown, it is formed outside the core 9. Since both the bypass 12a of the first embodiment and the bypass 12b of the second embodiment are present, the flow imbalance tendency in the secondary flow channel, whether caused by the flow channel length or by inertia, is offset by the flow imbalance tendency in the main flow channel, thereby suppressing the flow imbalance between the sections. [Example 6]

[0026] Fig.11A is a cross-sectional view of a plate stack type heat exchanger according to a sixth embodiment of the present invention, Fig. 11B This is a schematic diagram of the flow path of the heat exchanger. The sixth embodiment is similar to the third and fourth embodiments, and adopts a U-shaped inlet and outlet arrangement. The inlet 10 is connected to the first communication hole 7 , and the outlet 11 is connected to the second communication hole 8 . like Fig.11A As shown, a bypass consisting of a third bypass 12c and a communication channel 13 is formed from the second communication hole 8 at the other end of the stacking direction of the plates 1 and 2, and a bypass consisting of the communication channel 13 and a fourth bypass 12d is formed from the inlet 10. The third bypass 12c and the fourth bypass 12d are as follows Fig.11A , Fig. 11B As shown, it is formed inside the core 9, but it can also be formed as Fig. 12A , Fig. 12B As shown, it is formed outside the core 9. Since the bypass 12c of the third embodiment and the bypass 12d of the fourth embodiment are combined, the flow imbalance tendency in the main channel, whether caused by the channel length or by inertia, is offset by the flow imbalance tendency in the secondary channel, thereby suppressing the flow imbalance between the sections. [Industrial Applicability]

[0027] The present invention can be widely applied to plate stacking type heat exchangers, and is particularly suitable for oil coolers for vehicles. In addition, it can also be applied to battery coolers for electric vehicles, evaporators for air conditioners, and the like. [Explanation of Reference Numerals]

[0028] 1.2 boards 3.1st Fluid 41st flow channel 5 Second Fluid 6 2nd flow channel 71st connecting hole 8Second connecting hole 9 cores 10 Entrance 11 Exit 12a Bypass channel 1 12b Second bypass channel 12c 3rd bypass channel 12d 4th bypass channel 13 Connecting Channels 14 Cover 15 Base Plate

Claims

1. A plate stack type heat exchanger comprising a core (9) having a plurality of disk-shaped plates (1, 2) stacked thereon, In the stacking direction of the plates (1, 2), first flow channels (4) for a first fluid (3) to flow through and second flow channels (6) for a second fluid (5) to flow through are alternately formed on every other plate. A first communicating hole (7) and a second communicating hole (8) are provided separately from each other on each plate (1, 2). The core (9) is used to guide the first fluid (3) from the first communicating hole (7) through the first flow channel (4) to the second communicating hole (8). It is characterized in that An inlet (10) for a first fluid (3) is formed at one end of the plates (1, 2) in the stacking direction, and an outlet (11) for the first fluid (3) is formed at the other end. The inlet (10) is connected to the first communicating hole (7), and the outlet (11) is connected to the second communicating hole (8). A bypass from the second communication hole (8) at the one end portion to the outlet (11) is formed through the inside or outside of the core (9).

2. A plate stack type heat exchanger comprising a core (9) in which a plurality of disk-shaped plates (1, 2) are stacked, In the stacking direction of the plates (1, 2), first flow channels (4) for a first fluid (3) to flow through and second flow channels (6) for a second fluid (5) to flow through are alternately formed on every other plate. A first communicating hole (7) and a second communicating hole (8) are provided separately from each other on each plate (1, 2). The core (9) is used to guide the first fluid (3) from the first communicating hole (7) through the first flow channel (4) to the second communicating hole (8). It is characterized in that An inlet (10) for a first fluid (3) is formed at one end of the plates (1, 2) in the stacking direction, and an outlet (11) for the first fluid (3) is formed at the other end. The inlet (10) is connected to the first communicating hole (7), and the outlet (11) is connected to the second communicating hole (8). A bypass from the inlet (10) to the first communication hole (7) at the other end is formed through the inside or outside of the core (9).

3. A plate stack type heat exchanger comprising a core (9) in which a plurality of disk-shaped plates (1, 2) are stacked, In the stacking direction of the plates (1, 2), first flow channels (4) for a first fluid (3) to flow through and second flow channels (6) for a second fluid (5) to flow through are alternately formed on every other plate. A first communicating hole (7) and a second communicating hole (8) are provided separately from each other on each plate (1, 2). The core (9) is used to guide the first fluid (3) from the first communicating hole (7) through the first flow channel (4) to the second communicating hole (8). It is characterized in that An inlet (10) and an outlet (11) for a first fluid (3) are formed at one end of the plates (1, 2) in the stacking direction. The inlet (10) is connected to the first communicating hole (7), and the outlet (11) is connected to the second communicating hole (8). A bypass from the second communication hole (8) at the other end of the plates (1, 2) in the stacking direction to the outlet (11) is formed inside or outside the core (9).

4. A plate stack type heat exchanger comprising a core (9) in which a plurality of disk-shaped plates (1, 2) are stacked, In the stacking direction of the plates (1, 2), first flow channels (4) for a first fluid (3) to flow through and second flow channels (6) for a second fluid (5) to flow through are alternately formed on every other plate. A first communicating hole (7) and a second communicating hole (8) are provided separately from each other on each plate (1, 2). The core (9) is used to guide the first fluid (3) from the first communicating hole (7) through the first flow channel (4) to the second communicating hole (8). It is characterized in that An inlet (10) and an outlet (11) for a first fluid (3) are formed at one end of the plates (1, 2) in the stacking direction. The inlet (10) is connected to the first communicating hole (7), and the outlet (11) is connected to the second communicating hole (8). A bypass passage from the inlet (10) to the first communication hole (7) at the other end of the plates (1, 2) in the stacking direction is formed inside or outside the core (9).

5. A plate stack type heat exchanger, characterized in that: It is the plate stack type heat exchanger according to claim 1, and it is also the plate stack type heat exchanger according to claim 2.

6. A plate stack type heat exchanger, characterized in that: It is the plate stack type heat exchanger according to claim 3, and it is also the plate stack type heat exchanger according to claim 4.

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