JP5174739B2 - Plate heat exchanger and heat exchange unit equipped with the same - Google Patents

Description

  The present invention relates to a plate heat exchanger used as an evaporator of a refrigerator and a heat exchange unit including the plate heat exchanger.

  Conventionally, plate heat exchangers are frequently used as heat exchangers used in evaporators of refrigerators.

  As shown in FIG. 9, the plate heat exchanger includes a plurality of stacked heat transfer plates 100 ′. The plate-type heat exchanger 10 ′ is composed of a plurality of heat transfer plates 100 ′ between the heat transfer plates 100 ′, as shown in FIGS. 10 (a) and 10 (b). Refrigerant flow paths 101 ′ through which the refrigerant M such as ammonia flows and cooling target flow paths 102 ′ through which the cooled object W such as water or brine flows are alternately formed, and each heat transfer plate 100 is formed. Refrigerant inflow passage 103 'and refrigerant outflow passage through which refrigerant M flows into and out of each refrigerant flow passage 101' ... through holes H1 '..., H2' ..., H3 '..., H4' ... formed in '... 104 ′ is formed, and a cooled body inflow path 105 ′ and a cooled body outflow path 106 ′ through which the cooled body W flows in and out of each cooled body flow path 102 ′ are formed.

  As shown in FIGS. 11 (a) and 11 (b), the plate heat exchanger 10 ′ having the above-described configuration causes the refrigerant M to flow from the refrigerant inflow path 103 ′ to the refrigerant flow path 101 ′, so that the refrigerant outflow path. In addition to flowing out to 104 ′, the cooled object W flows from the cooled object inflow path 105 ′ to the cooled object flow path 102 ′, and flows out to the cooled object outflow path 106 ′. Heat is exchanged between the refrigerant M and the object to be cooled W via the heat plates 100 ′ (heat transfer surface).

  In this type of plate heat exchanger 10 ′, the number of refrigerant flow paths 101 ′ and cooling target flow paths 102 ′ is increased by increasing the number of stacked heat transfer plates 100 ′. In addition to increasing the heat transfer area, the heat exchange capacity is said to increase.

  By the way, the plate type heat exchanger 10 ′ having the above-described configuration forms the refrigerant inflow passage 103 ′ by connecting the through holes H1 ′ formed in the respective heat transfer plates 100 ′. When the number of the heat plates 100 ′ increases, the total length of the refrigerant inflow passage 103 ′ inevitably increases, and the flow resistance of the refrigerant M increases. Therefore, in this type of plate heat exchanger 10 ′, the refrigerant M is placed in the refrigerant flow path 101 ′ located on the back side of the refrigerant flow path 101 ′ on the inlet side (primary side) of the refrigerant flow path 103 ′. As a result, it becomes difficult to flow in. As a result, there is a problem that uneven distribution of the refrigerant M occurs in the stacking direction of the heat transfer plates 100 ′, and the heat exchange efficiency is lowered.

  Therefore, in order to efficiently flow the refrigerant M into each of the plurality of refrigerant inflow passages 103 ′, as shown in FIG. 12A, a shower pipe P in which a plurality of nozzles N are attached at intervals in the axial direction. Are inserted into the plurality of heat transfer plates 100 ′ as refrigerant inflow passages 103 ′, and the refrigerant M is sent from the nozzles N to the refrigerant flow paths 101 ′, as shown in FIG. 12B. The refrigerant inflow passages 103 ′ are divided to form a plurality of divided inflow passages 103 ″ extending in a direction orthogonal to the refrigerant flow passages 101 ′, and the refrigerants at different positions in the divided inflow passages 103 ″. The thing etc. which made the refrigerant | coolant M flow in into flow path 101 '... are proposed (for example, refer patent document 1).

JP 2002-303499 A

  However, in the plate heat exchanger 10 ′ provided with the shower pipe P, the flow resistance of the refrigerant M increases due to the presence of the nozzle N and restricts the flow of the refrigerant M. There is a problem that it cannot follow the load fluctuation.

  On the other hand, the plate type heat exchanger 10 ′ in which a single refrigerant inflow passage 103 ′ is divided to form a plurality of divided inflow passages 103 ″. Although it is possible to suppress an unnecessarily large size, each of the divided inflow passages 103 ″... Has a different arrangement of the refrigerant M supply target (the refrigerant flow channel 101 ′. As a result of the different lengths, the flow resistance of the refrigerant M in the divided inflow passages 103 '' ... for the refrigerant flow channels 101 '... in the stacking direction of the heat transfer plates 100' ... is reduced to the primary side (inlet side). ) Of the refrigerant flow path 101 ′, the flow resistance of the refrigerant M in the divided inflow paths 103 ″. Further, in the plate heat exchanger 10 ′, all the refrigerant flow paths 101 ′,... Are in communication with each other through the refrigerant inflow path 103 ′. However, it is influenced by the fluid pressure of the refrigerant M in the other refrigerant flow paths 101 ′.

  For this reason, the plate heat exchanger 10 ′ having the above-described configuration has a variation in the fluid pressure of the refrigerant M flowing in each of the divided inflow passages 103 ″. As a result, the refrigerant M becomes more difficult to flow into the refrigerant flow path 101 ′ at the back side in the stacking direction of 100 ′, and as a result, the heat exchange efficiency (cooling efficiency with respect to the object M to be cooled) depends on the arrangement of the flow paths 101 ′. ) Is different, and there is a problem that the heat exchange performance that should be originally achieved cannot be exhibited as a whole apparatus.

  Therefore, in view of such circumstances, the present invention includes a plate heat exchanger capable of exhibiting heat exchange performance that should be inherent in the entire apparatus when heat exchange is performed between the refrigerant and the object to be cooled, and the plate heat exchanger. It is an object to provide a heat exchange unit.

The plate heat exchanger according to the present invention includes a flow path for a coolant that circulates a refrigerant between each of the heat transfer plates and a flow for a cooled body that circulates the cooled body between the plurality of stacked heat transfer plates. Are formed alternately, and through holes formed in each heat transfer plate are connected to form a refrigerant inflow passage and a refrigerant outflow passage through which the refrigerant flows in and out of the refrigerant flow passage, and a flow path for the object to be cooled The plate-type heat exchanger has a cooled body inflow path and a cooled body outflow path through which the cooled body flows in and out, and a plurality of refrigerant flow paths formed in the stacking direction of the heat transfer plates are transmitted. The liquid plate is partitioned liquid-tight or air-tight by a predetermined number in the stacking direction of the heat plates and divided into two or more blocks, and two or more refrigerant inflow paths are formed corresponding to the number of the blocks. One or more of each of the refrigerant inflow channel, stacked plurality of heat Most through hole from the heat transfer plate on the outside is contiguous in a row in the plate, while being formed so as to communicate with the refrigerant passage of the different blocks, the refrigerant outlet channel, all of the refrigerant in the stacking direction of the heat transfer plate It is characterized by being formed so as to communicate with the use channel.

  According to the plate heat exchanger configured as described above, a plurality of refrigerant flow paths formed in the heat transfer plate stacking direction are partitioned in a liquid-tight or air-tight manner by a predetermined number in the heat transfer plate stacking direction. Two or more refrigerant inflow passages are formed corresponding to the number of the blocks, and each of the two or more refrigerant inflow passages communicates with the refrigerant flow passages of different blocks. On the other hand, the refrigerant outflow path is formed so as to communicate with all the refrigerant flow paths in the stacking direction of the heat transfer plate, so that it is not affected by the pressure state of other blocks, The refrigerant can be circulated through the refrigerant flow path of each block.

  The plate-type heat exchanger having the above-described configuration can be attached to each refrigerant inflow passage with pressure reducing means for reducing the refrigerant fluid pressure, and the pressure reducing means reduces the refrigerant fluid pressure for each refrigerant inflow passage. By supplying the refrigerant, the refrigerant can be properly circulated in each block (each refrigerant flow path) partitioned in the stacking direction of the heat transfer plates.

  Specifically, the plate-type heat exchanger having the above-described configuration is provided with a refrigerant inflow path for each block, whereas the refrigerant outflow path communicates with all the refrigerant flow paths to form a common flow path. Therefore, the differential pressure between the fluid pressure of the refrigerant flowing in each refrigerant inflow passage and the fluid pressure of the refrigerant flowing in the refrigerant outflow passage is apparently corresponding to the length of the refrigerant inflow passage (circulation resistance), The refrigerant inflow path connected to the block (refrigerant flow path) on the back side in the stacking direction of the heat transfer plates increases.

  However, the plate heat exchanger having the above-described configuration attaches pressure reducing means to each refrigerant inflow passage and greatly reduces the fluid pressure of the refrigerant on the secondary side, so that the refrigerant fluid pressure (pressure reducing means on the primary side of the pressure reducing means is reduced. The pressure difference between the fluid pressure of the refrigerant before being reduced in pressure and the fluid pressure of the refrigerant on the secondary side of the refrigerant outflow path (fluid pressure of the refrigerant flowing out of the plate heat exchanger) The pressure is reduced, and the differential pressure between the refrigerant inflow path and the refrigerant outflow path in each block (differential pressure related to the length of the refrigerant inflow path (flow resistance)) is almost negligible. As a result, the influence of the differential pressure due to the difference in position in the stacking direction of the heat transfer plates in each block is almost eliminated, and the fluid pressure of refrigerant (circulation state of refrigerant) in each block becomes substantially equal.

  Therefore, according to the plate heat exchanger having the above-described configuration, there is no significant difference in the differential pressure between the refrigerant fluid pressures at different positions (refrigerant channels) in the stacking direction of the heat transfer plates. Thus, the refrigerant circulates in a well-balanced manner, and in exchanging heat between the refrigerant and the object to be cooled, it is possible to exhibit the heat exchange performance that should be inherent in the entire apparatus.

The heat exchange unit according to the present invention includes a refrigerant flow path for circulating a refrigerant between a plurality of stacked heat transfer plates, and a flow path for a cooled body for circulating a cooled body. Alternately formed through holes formed in each heat transfer plate are connected to form a refrigerant inflow passage and a refrigerant outflow passage through which the refrigerant flows in and out of the refrigerant flow passage, and the cooling target flow passage is cooled. A heat exchange unit including a plate heat exchanger in which a cooled body inflow passage and a cooled body outflow passage are formed to flow in and out of the body, and the refrigerant is reduced from the fluid pressure on the primary side to the secondary side. The plate-type heat exchanger further includes a plurality of refrigerant flow paths formed in the stacking direction of the heat transfer plates at a predetermined number in the stacking direction of the heat transfer plates. It is divided into two or more blocks by partitioning tightly or airtightly. Both are formed refrigerant inflow passage than twofold in accordance with the number of said blocks, each of said two or more refrigerant inflow channel, the heat transfer plates the outermost of the stacked plurality heat transfer plates The through holes are connected in a row and are formed to communicate with the refrigerant flow paths of different blocks, while the refrigerant outflow path is formed to communicate with all the refrigerant flow paths in the stacking direction of the heat transfer plates. The decompression means is provided for each refrigerant inflow passage and is directly or indirectly connected to each refrigerant inflow passage.

  According to the heat exchange unit having the above configuration, a plurality of refrigerant flow paths formed in the stacking direction of the heat transfer plates in the plate heat exchanger are liquid-tight or air-tight for each predetermined number in the stacking direction of the heat transfer plates. The refrigerant is divided into two or more blocks, and two or more refrigerant inflow passages are formed corresponding to the number of the blocks, and each of the two or more refrigerant inflow passages is a refrigerant flow of a different block. While the refrigerant outflow passage is formed to communicate with all the refrigerant flow paths in the stacking direction of the heat transfer plates, the refrigerant outflow passage is formed in other blocks (refrigerant inflow passages). The refrigerant can be properly circulated through the refrigerant flow path of each block without being affected by the fluid pressure of the refrigerant.

  The heat exchange unit having the above-described configuration further includes a decompression unit configured to depressurize the refrigerant from the primary side fluid pressure and supply the refrigerant to the secondary side, and the decompression unit is provided for each refrigerant inflow passage. Since each refrigerant inflow passage is directly or indirectly connected to each refrigerant inflow passage, each refrigerant inflow passage is divided in the stacking direction of the heat transfer plates by reducing the fluid pressure of the refrigerant with the decompression means and supplying the refrigerant. The refrigerant can be properly distributed in each of the blocks (each refrigerant flow path).

  Specifically, the plate heat exchanger having the above-described configuration is provided with a first inlet channel for each block, whereas the refrigerant outlet channel communicates with all the refrigerant channels to form a common channel. Therefore, the differential pressure between the fluid pressure of the refrigerant flowing through each refrigerant inflow passage and the fluid pressure of the refrigerant flowing through the refrigerant outflow passage apparently corresponds to the length of the refrigerant inflow passage (circulation resistance). The refrigerant inflow path connected to the block (coolant flow path) located on the back side in the stacking direction of the heat transfer plates becomes larger.

  However, the heat exchange unit having the above configuration greatly reduces the fluid pressure of the refrigerant on the secondary side by the decompression means connected directly or indirectly to each refrigerant inflow path, so that the refrigerant on the primary side of the decompression means is reduced. Most of the differential pressure between the fluid pressure (fluid pressure of the refrigerant before being decompressed by the decompression means) and the fluid pressure of the refrigerant on the secondary side of the refrigerant outflow path (fluid pressure of refrigerant flowing out of the plate heat exchanger) However, the pressure is reduced by the pressure reducing means, and the differential pressure between the refrigerant inflow path and the refrigerant outflow path in each block (the differential pressure related to the length of the refrigerant inflow path (flow resistance)) is almost negligible. . As a result, the influence of the differential pressure due to the difference in position in the stacking direction of the heat transfer plates in each block is almost eliminated, and the fluid pressure of refrigerant (circulation state of refrigerant) in each block becomes substantially equal.

  Therefore, according to the heat exchange unit (plate-type heat exchanger) having the above configuration, as a result of no significant difference in the differential pressure of the refrigerant fluid pressure for each position (refrigerant channel) in the stacking direction of the heat transfer plate, The refrigerant circulates in a well-balanced manner in each refrigerant flow path, and when the refrigerant and the cooled object are subjected to heat exchange, the entire apparatus can exhibit the heat exchange performance that should originally be provided.

  As one aspect of the present invention, it is preferable that the decompression means is composed of a flow rate adjustment valve capable of adjusting the flow rate of the refrigerant. In this way, the fluid pressure of the refrigerant can be adjusted for each block. That is, when the refrigerant flow rate is adjusted, the refrigerant fluid pressure also fluctuates in accordance with the change in the flow rate. Therefore, by attaching a flow rate adjustment valve to each refrigerant inflow passage, the refrigerant fluid pressure is adjusted appropriately for each block. Can be in a state.

  As described above, according to the plate heat exchanger according to the present invention, in exchanging heat between the refrigerant and the object to be cooled, the excellent effect that the heat exchange performance that should be originally provided in the entire apparatus can be exhibited. Can be played.

  In addition, the heat exchange unit according to the present invention can also exhibit an excellent effect that the heat exchange performance that should be originally provided in the entire apparatus can be exhibited in exchanging heat between the refrigerant and the object to be cooled.

The conceptual diagram of the heat exchange unit which concerns on one Embodiment of this invention is shown. It is a whole perspective view of the plate type heat exchanger used for the heat exchange unit concerning the embodiment, Comprising: A plurality of refrigerant inflow passages are lined up in the direction (longitudinal direction of a heat transfer plate) perpendicular to the lamination direction of a heat transfer plate. The whole perspective view of the plate type heat exchanger formed by is shown. The longitudinal cross-sectional view for demonstrating the distribution | circulation route of the refrigerant | coolant of the plate type heat exchanger which concerns on the same embodiment is shown. The longitudinal cross-sectional view for demonstrating the flow path of the to-be-cooled body of the plate type heat exchanger which concerns on the same embodiment is shown. It is a schematic sectional drawing for demonstrating the flow of the refrigerant | coolant in the plate type heat exchanger which concerns on the same embodiment, and a to-be-cooled body, Comprising: (a) is for demonstrating the flow of the refrigerant | coolant in a 1st block. A sectional view is shown, (b) shows a sectional view for explaining the flow of the refrigerant in the second block located behind the heat transfer plate in the stacking direction from the first block, and (c) shows the first block. Sectional drawing for demonstrating the flow of the refrigerant | coolant in the 3rd block in the back | inner side of the lamination direction of a heat exchanger plate rather than two blocks is shown, (d) is from a to-be-cooled body inflow path to a to-be-cooled body outflow path. Sectional drawing for demonstrating the flow of the to-be-cooled body toward is shown. It is the whole plate-type heat exchanger used for the heat exchange unit which concerns on other embodiment of this invention, Comprising: It is a direction (short side of a heat exchanger plate) in which a some refrigerant | coolant inflow path is orthogonal to the lamination direction of a heat exchanger plate. The perspective view of the plate type heat exchanger formed along with (direction) is shown. It is a schematic sectional drawing for demonstrating the flow of the refrigerant | coolant and to-be-cooled body in the plate type heat exchanger shown in FIG. 6, Comprising: (a) is a cross section for demonstrating the flow of the refrigerant | coolant in a 1st block. FIG. 4B is a cross-sectional view for explaining the flow of the refrigerant in the second block located on the back side in the stacking direction of the heat transfer plate with respect to the first block, and FIG. Sectional drawing for demonstrating the flow of the refrigerant | coolant in the 3rd block in the back | inner side of the lamination direction of a heat exchanger plate rather than a block is shown, (d) is toward a to-be-cooled body outflow path from a to-be-cooled body inflow path. Sectional drawing for demonstrating the flow of all the to-be-cooled bodies is shown. The longitudinal cross-sectional view for demonstrating the flow path of the refrigerant | coolant of the plate-type heat exchanger which concerns on another embodiment of this invention is shown. An overall perspective view of a conventional plate heat exchanger is shown. It is a longitudinal cross-sectional view of the plate type heat exchanger of FIG. 9, (a) shows the longitudinal cross-sectional view for demonstrating the distribution path of a refrigerant | coolant, (b) demonstrates the distribution path of a to-be-cooled body. The longitudinal cross-sectional view for this is shown. It is a schematic sectional drawing for demonstrating the flow of the refrigerant | coolant in the plate type heat exchanger of FIG. 9, and a to-be-cooled body, Comprising: (a) is a flow of the refrigerant | coolant toward a refrigerant | coolant outflow path from a refrigerant | coolant inflow path. Sectional drawing for demonstrating is shown, (b) shows sectional drawing for demonstrating the flow of the to-be-cooled body from a to-be-cooled body inflow path toward a to-be-cooled body outflow path. It is a fragmentary sectional view of the conventional plate-type heat exchanger, (a) shows the fragmentary longitudinal cross-sectional view of the plate-type heat exchanger provided with the shower pipe as a refrigerant | coolant inflow path, (b) is a refrigerant | coolant inflow path. Fig. 2 shows a partial longitudinal sectional view of a plate heat exchanger divided into a plurality of divided inflow passages.

  Hereinafter, a heat exchange unit according to an embodiment of the present invention will be described with reference to the accompanying drawings.

  As shown in FIG. 1, the heat exchange unit according to this embodiment includes a plate heat exchanger 10 that exchanges heat between the refrigerant M and the object W to be cooled, and a secondary by depressurizing the refrigerant M from the fluid pressure on the primary side. Pressure reducing means 20a, 20b, 20c configured to be supplied to the side.

  As shown in FIG. 2, the plate heat exchanger 10 includes a plurality of stacked heat transfer plates 100 and a pair of frames 110 and 120 provided so as to sandwich the plurality of heat transfer plates 100. I have.

  In the plate heat exchanger 10 according to the present embodiment, as shown in FIGS. 3 and 4, the refrigerant M is circulated between the plurality of stacked heat transfer plates 100 with the heat transfer plates 100 as boundaries. Refrigerant flow paths 101... And cooled object flow paths 102 for circulating the cooled object W are alternately formed, and through holes H1a, H1b, H1c, H2, H3 formed in the respective heat transfer plates 100. , H4 are connected to form the refrigerant inflow passages 103a, 103b, 103c and the refrigerant outflow passage 104 through which the refrigerant M flows in and out of the refrigerant flow passages 101. The body to be cooled inflow path 105 and the body to be cooled outflow path 106 are formed.

  In the plate heat exchanger 10 according to this embodiment, as shown in FIG. 3, a plurality of refrigerant flow paths 101 formed in the stacking direction of the heat transfer plates 100 are stacked in the stacking direction of the heat transfer plates 100. And is divided into two or more (three in this embodiment) blocks A, B, and C that are partitioned liquid-tight or air-tight by a predetermined number, and the refrigerant inflow passages 103a, 103b, and 103c are the blocks. Two or more (three in this embodiment) are formed corresponding to the number of A, B, and C. And each refrigerant | coolant inflow path 103a, 103b, 103c is formed so that it may connect with the flow paths 101 ... for refrigerant | coolants of a different block A, B, C, respectively.

  Here, the plate heat exchanger 10 according to this embodiment will be described in detail. The plurality of heat transfer plates 100 are formed in a rectangular shape (rectangular shape) when viewed from the front, as shown in FIG. . Each of the heat transfer plates 100 is press-formed, and a plurality of ridges (not shown) and ridges (not shown) are alternately formed on the front and back. In the present embodiment, by forming the ridges and ridges on the front and back of each heat transfer plate 100, the ridges and ridges of the adjacent heat transfer plates 100 are crossed when viewed from the front. On the other hand, the ridges are in point contact.

  Each of the heat transfer plates 100 is provided with a plurality of through holes H1a, H1b, H1c, H2, H3, and H4 at different appropriate positions as shown in FIGS. The heat transfer plate 100 in the plate heat exchanger 10 according to the present embodiment is provided with one through hole H2, H3, H4 in each of three corners of the four corners in a front view, and the rest. One or more through holes H1a, H1b, and H1c are provided at one corner.

  Each of the heat transfer plates 100 corresponds to the arrangement of the through holes H1a, H1b, H1c, H2, H3, and H4, and the through holes of the adjacent heat transfer plates 100 in a stacked state (superposed state). H1a, H1b, H1c, H2, H3, H4 are connected to form the refrigerant inflow passages 103a, 103b, 103c and the refrigerant outflow passage 104 through which the refrigerant M flows in and out, and the body to be cooled through which the body W to be cooled flows out and in An inflow path 105 and a cooled body outflow path 106 can be formed.

  In the plate heat exchanger 10 according to the present embodiment, a refrigerant outflow path 104, a cooled body inflow path 105, and a cooled body outflow path 106 are provided at three corners of the four corners of each heat transfer plate 100. One through hole H2, H3, H4 for forming is provided one by one. Each of the heat transfer plates 100... Flows out of the refrigerant into one of the two corners on one end side in the longitudinal direction (the corner portion on one end side in the direction orthogonal to the longitudinal direction (hereinafter referred to as the short direction)). A through hole H2 for forming the passage 104 is provided, and a through hole H3 for forming the cooled body inflow passage 105 is provided on the other side (corner on the other end side in the short side direction). Further, each of the heat transfer plates 100... Is provided at one of the two corners on the other end side in the longitudinal direction (the corner on the other end side in the short side direction) at the cooled body outflow path 106. A through-hole H4 is formed for forming the.

  Further, each of the heat transfer plates 100... Has a refrigerant inflow path 103a, 103b, and a refrigerant inflow passage 103a, 103b, Through holes H1a, H1b, and H1c for forming 103c are formed.

In the plate heat exchanger 10 according to the present embodiment, as described above, in the stacking direction of the heat transfer plates 100..., The plurality of refrigerant channels 101. Since a plurality of refrigerant inflow passages 103a, 103b, and 103c are formed corresponding to the number of blocks A, B, and C , the inlets of the refrigerant inflow passages 103a, 103b, and 103c are formed as shown in FIGS. The refrigerant inflow passages 103a, 103b, 103c are connected to the heat transfer plates 100 constituting the block A on the side (one frame 110 side provided with connecting portions J1a, J1b, J1c, J2, J3, J4 described later). Through holes H1a, H1b, and H1c are formed in a number corresponding to the number of blocks A, B, and C. On the other hand, the refrigerant inflow passages 103b, 103c are connected to the heat transfer plates 100 constituting the blocks B, C on the back side of the refrigerant inflow passages 103a, 103b, 103c (the other frame 120 side in the non-penetrating state). Through holes H1b and H1c are provided in a number smaller than the number of blocks A, B and C partitioned.

  That is, when the blocks A, B, and C divided into a plurality are ranked in order from the primary side (inlet side) to the back side of the refrigerant inflow passages 103a, 103b, and 103c, the refrigerant inflow passages 103a, 103b, and 103c In the heat transfer plates 100 constituting the block A of the lowest order (first order) on the inlet side, the number of blocks A, B, and C (the number of divided blocks A, B, and C) is increased. A corresponding number of through-holes H1a, H1b, H1c are formed, and as the order of the blocks B, C constituting the heat transfer plates 100 decreases one by one, the heat transfer plates 100,. The number of through holes H1b and H1c that form the refrigerant inflow passages 103b and 103c is reduced by one.

  Therefore, in this embodiment, since it is divided into three blocks A, B and C, three refrigerants are included in the heat transfer plates 100 constituting the first rank block (hereinafter referred to as the first block) A. Three through holes H1a, H1b, and H1c for forming the inflow passages 103a, 103b, and 103c are provided, and the heat transfer plates 100 that constitute a block (hereinafter referred to as a second block) B of the next order , Two through holes H1b, H1c for forming the two refrigerant flow paths 101 are provided, and the heat transfer that constitutes the block (hereinafter referred to as the third block) C of the next rank (maximum rank) The plate 100 is provided with one through hole H1c for forming one refrigerant inflow passage 103c.

  In the heat transfer plates 100 (the heat transfer plate 100 provided with a plurality of through holes H1a, H1b, H1c) constituting the first block A and the second block B, the plurality of through holes H1a, H1b, H1c are They are arranged in a row. In the present embodiment, the heat transfer plates 100 constituting the first block A and the second block B are provided such that a plurality of through holes H1a, H1b, H1c form a line in the longitudinal direction.

  Accordingly, the plate heat exchanger 10 according to the present embodiment forms a state in which a plurality of heat transfer plates 100 are stacked (a cooled body inflow path 105, a cooled body outflow path 106, and a refrigerant outflow path 104 are formed. Through-holes H2, H3, and H4 connected to each other), the through-holes H1c formed in the heat transfer plates 100 constituting the first block A, the second block B, and the third block C are connected to each other. A refrigerant inflow passage (hereinafter referred to as a third block refrigerant inflow passage) 103c communicating with the refrigerant flow paths 101 of the block C is formed, and the heat transfer plates 100 constituting the first block A and the second block B are formed. The formed through hole H1b is connected to form a refrigerant inflow passage (hereinafter referred to as a second block refrigerant inflow passage) 103b that communicates with the refrigerant flow passage 101 of the second block B, and further includes a first block. A through-hole H1a formed in the heat transfer plates 100 constituting the rack A is connected, and a refrigerant inflow path (hereinafter referred to as a first block refrigerant inflow path) 103a communicated with the refrigerant flow path 101 of the first block A. Is to be formed.

  As described above, the plate heat exchanger 10 according to the present embodiment has two corners on the other end side in the longitudinal direction with respect to the heat transfer plates 100 constituting the first block A and the second block B. Among them, since the plurality of through holes H1a, H1b, H1c in the other corner (corner on one end side in the short side direction) are formed in a line in the longitudinal direction, the first to third block refrigerant inflows The passages 103a, 103b, 103c are arranged at intervals in the longitudinal direction of the heat transfer plates 100.

  As described above, the plate heat exchanger 10 according to this embodiment forms the refrigerant inflow passages 103a, 103b, and 103c as the heat transfer plates 100 constituting the blocks A and B having higher ranks (smaller ranks). Since the number of through holes H1a, H1b, and H1c for the heat transfer plate 100 is increased, the heat transfer plates 100 at the boundaries of the blocks A, B, and C pass through the heat transfer plates 100 on the blocks B and C having lower ranks. The portions where the holes H1a and H1b are not formed (non-penetrating portions) are opposed to the through holes H1a and H1b of the heat transfer plates 100 of the blocks A and B which are adjacent to each other.

  The plate heat exchanger 10 according to the present embodiment includes adjacent heat transfer plates 100 around the through holes H1a, H1b, H1c, and H2 on one end side in the short direction of the adjacent heat transfer plates 100. Is sealed in a liquid-tight or air-tight manner, so that the refrigerant M flowing through the refrigerant inflow passages 103a, 103b, 103c and the refrigerant outflow passage 104 formed by the through holes H1a, H1b, H1c, H2 is transferred to the heat transfer plate 100 ... It is prevented from flowing into the channels 102 to be cooled formed between them. Further, the plate heat exchanger 10 is configured such that the adjacent heat transfer plates 100 around the through holes H3, 4 on the other end side in the short direction of the adjacent heat transfer plates 100 are sealed in a liquid-tight or air-tight manner. As a result, the coolant flow path is formed between the heat transfer plates 100 through which the cooled object inflow passages 105 and the cooled object outlet passages 106 formed by the through holes H3 and H4 pass. 101 is prevented from flowing.

  That is, in the plate heat exchanger 10 according to the present embodiment, a space between one surface forming the refrigerant flow paths 101 of the adjacent heat transfer plates 100 is defined and sealed with the refrigerant flow paths 101. Between the other surfaces of the adjacent heat transfer plates 100 that form the flow channel 102 for the cooled object, the flow channel 102 for the cooled object is defined and sealed.

  Sealing between the heat transfer plates 100 is performed by sandwiching a gasket made of rubber or the like between adjacent heat transfer plates 100 or welding the adjacent heat transfer plates 100. Since the plate-type heat exchanger 10 according to the present embodiment may seal between the heat transfer plates 100 by any method, description of the sealing structure here will be omitted.

  As described above, the plate heat exchanger 10 according to the present embodiment divides a plurality of refrigerant flow paths 101 into a predetermined number of blocks A, B, and C in the stacking direction of the heat transfer plates 100. Therefore, the plurality of heat transfer plates 100 constituting the first block A are composed of the refrigerant flow paths 101 of the first block A as shown in FIGS. 5 (a) and 5 (d). Including a through hole H1a serving as a first block refrigerant inflow passage 103a and a through hole H2 serving as a refrigerant outflow passage 104, and through holes H3 serving as a cooled body inflow passage 105 and a cooled body outflow passage 106. A seal S is provided between the opposing surfaces so as to define a region avoiding H4, and the through-hole H3 serving as the cooled body inflow path 105 communicating with the cooled body flow path 102 ... Including a through hole H4 to be a path 106, and Medium inflow passage 103a, 103b, 103c and the through-hole H1a comprising a refrigerant outflow passage 104, H1b, H1c, seal S is applied between the other surface facing to define a region except the H2.

  Further, the plurality of heat transfer plates 100 constituting the second block B are in communication with the refrigerant flow paths 101 of the second block B as shown in FIGS. 5B and 5D. A region including a through hole H1b serving as the block refrigerant inflow path 103b and a through hole H2 serving as the refrigerant outflow path 104, and avoiding the through holes H3 and H4 serving as the cooled body inflow path 105 and the cooled body outflow path 106 A seal S is provided between the opposing surfaces so as to define a through-hole H3 serving as a cooled body inflow passage 105 and a through hole serving as a cooled body outflow path 106 communicating with the cooled body flow paths 102. A seal S is provided between the opposite surfaces so as to define a region that includes the hole H4 and avoids the through holes H3 and H4 serving as the refrigerant inflow passages 103a, 103b, and 103c and the refrigerant outflow passage 104. .

  Further, the plurality of heat transfer plates 100 constituting the third block C are in communication with the refrigerant flow passages 101 of the third block C as shown in FIGS. 5 (c) and 5 (d). A region including a through hole H1c serving as the block refrigerant inflow path 103c and a through hole H2 serving as the refrigerant outflow path 104, and avoiding the through holes H3 and H4 serving as the cooled body inflow path 105 and the cooled body outflow path 106 A seal S is provided between the opposing surfaces so as to define a through-hole H3 serving as a cooled body inflow passage 105 and a through hole serving as a cooled body outflow path 106 communicating with the cooled body flow paths 102. A seal S is provided between the opposite surfaces so as to define a region that includes the hole H4 and avoids the through holes H1a, H1b, H1c, and H2 that serve as the refrigerant inflow passages 103a, 103b, and 103c and the refrigerant outflow passage 104. It has been subjected.

  In the first to third blocks A, B, and C, the plate heat exchanger 10 includes a refrigerant from the refrigerant inflow passages 103a, 103b, and 103c to the refrigerant outflow passage 104 in the refrigerant flow passage 101. M can be smoothly circulated, and in the cooled object flow path 102, the cooled object W can be smoothly circulated from the cooled object inflow path 105 side to the cooled object outlet path 106 side. A seal S is provided between the heat transfer plates 100 so that the refrigerant flow paths 101 adjacent to each other through the heat transfer plates 100 and the flow paths 102 to be cooled can be overlapped as much as possible. The flow paths 101... And the cooling target flow paths 102 are defined.

  In the plate heat exchanger 10 according to the present embodiment, as shown in FIGS. 5A to 5D, the refrigerant M flows into the refrigerant inflow paths 103a, 103b, 103c (first to third) in the refrigerant flow paths 101. When the refrigerant M flows from the block refrigerant inflow passages 103a, 103b, 103c) toward the refrigerant outflow passage 104, the refrigerant M spreads in the short direction toward the intermediate position in the longitudinal direction, and is then placed in one place of the refrigerant outflow passage 104. A so-called trapezoidal flow that flows in the direction toward the cooled body W flows from the cooled body inflow path 105 side to the cooled body outflow path 106 side in the cooled body flow path 102. So as to form a so-called trapezoidal flow in which the refrigerant flows toward one portion of the cooled object outlet passage 106 after spreading in the lateral direction toward the intermediate position in the longitudinal direction and the cooled object Flow path 102 ... It is adapted to define.

  As shown in FIGS. 2 to 4, each of the pair of frames 110 and 120 is formed of a thick plate. In the plate heat exchanger 10 according to the present embodiment, both the frames 110 and 120 are formed in a rectangular shape when viewed from the front, and have the same dimensions as the heat transfer plates 100 so as to face the entire surface of the heat transfer plates 100. Alternatively, it is set to a size larger than that. One frame 110 is formed with a through hole at a position corresponding to the arrangement of the through holes H1a, H1b, H1c, H2, H3, and H4 of the heat transfer plate 100. That is, in one frame 110, a plurality of refrigerant inflow passages 103a, 103b, 103c (first to third block refrigerant inflow passages 103a, 103b, 103c), a single refrigerant outflow passage 104, and an object to be cooled inflow passage 105 are provided. And a hole (not numbered) corresponding to the cooled body outflow path 106 is formed. And this one flame | frame 110 is liquid-tight or the cylindrical connection part J1a, J1b, J1c, J2, J3, J4 on the surface which becomes an outer side (surface on the opposite side to the surface which opposes the heat-transfer plate 100 ...) Airtight connection. The connecting portions J1a, J1b, J1c, J2, J3, J4 are provided corresponding to the through holes H1a, H1b, H1c, H2, H3, H4 of the heat transfer plates 100. That is, the connecting portions J1a, J1b, J1c, J2, J3, and J4 are fixed to the frame 110 so as to be concentric or substantially concentric with the holes formed in the frame 110, and are surfaces that are outside the frame 110. The aspect which protruded from has been comprised.

  In the present embodiment, the connecting portions J1a, J1b, J1c communicating with the refrigerant inflow passages 103a, 103b, 103c are connected directly or indirectly to the decompression means 20a, 20b, 20c. .

  On the other hand, the other frame 120 is formed of a flat plate having no holes (non-penetrating). The pair of frames 110 and 120 are connected to each other directly or indirectly so as to sandwich the plurality of stacked heat transfer plates 100 from both sides. In addition, when this kind of plate-type heat exchanger 10 is a large-sized thing, while a pair of flame | frames 110 and 120 pinched | interposed the heat-transfer plate 100 ..., each other edge part is bolted, In the case of a small size, the pair of frames 110, 120 sandwich the heat transfer plates 100, and the ends of the frames are bolted to each other, or both frames are adjacent to the adjacent heat transfer plates 100 ... It may be fixed directly by welding.

  And by sandwiching the heat transfer plates 100 between the pair of frames 110, 120, the connecting portions J1a, J1b, J1c, J2, J3, J4 of one frame 110 are through holes H1a, H1b of the heat transfer plates 100 ... , H1c, H2, H3, H4 (a plurality of refrigerant inflow passages 103a, 103b, 103c, a single refrigerant outflow passage 104, a cooled body inflow path 105, and a cooled body outflow path 106). It is in a state. Note that an appropriate seal is also provided between the frames 110 and 120 and the heat transfer plates 100 to prevent the refrigerant M and the cooling target W from leaking.

  Returning to FIG. 1, the decompression means 20a, 20b, 20c are directly or indirectly connected to the connecting portions J1a, J1b, J1c connected to the refrigerant inflow passages 103a, 103b, 103c. That is, the decompression means 20a, 20b, and 20c are connected to pipes that are fluidly connected to the connection portions J1a, J1b, and J1c according to the environment such as the installation location of the plate heat exchanger 10, or the connection portions J1a, Or directly connected to J1b and J1c. And each decompression means 20a, 20b, 20c can reduce the fluid pressure of refrigerant M on the secondary side to 1/10 to 1/2 (10% to 50%) with respect to the fluid pressure of refrigerant M on the primary side. Things are adopted. For example, when the refrigerant M is Freon (R134a) and the fluid pressure of the refrigerant M is set to 0.8 MPa to 2.0 MPa on the primary side of the decompression means 20a, 20b, 20c, the decompression means 20a. , 20b, and 20c are employed so that the fluid pressure of the refrigerant M can be reduced to 0.2 MPa to 0.4 MPa and the refrigerant M can be introduced (supplied) into the refrigerant inflow passages 103a, 103b, and 103c.

  The decompression means 20a, 20b, and 20c employ a fixed type that reduces the fluid pressure of the refrigerant M to a constant pressure or a variable type that can reduce the fluid pressure of the refrigerant M to an arbitrary pressure. However, in this embodiment, a variable type in which the pressure reduction of the fluid pressure of the refrigerant M is variable is adopted. The heat exchange unit 1 according to the present embodiment includes a flow rate adjustment valve capable of adjusting the flow rate of the refrigerant M as the decompression means 20a, 20b, and 20c, and by adjusting the flow rate of the refrigerant M, the fluid of the refrigerant M The pressure is reduced. In addition, it is preferable to employ | adopt a needle valve, an orifice valve, etc. as the pressure reduction means 20a, 20b, 20c, for example.

  This type of heat exchange unit 1 is generally employed as one configuration of a circulation system that returns the refrigerant M flowing out of the refrigerant outflow passage 104 to the refrigerant inflow passages 103a, 103b, and 103c. In order to liquefy the refrigerant M, which is in a gaseous state, a compressor and another heat exchanger (condenser) are installed between the refrigerant outflow passage 104 and the refrigerant inflow passages 103a, 103b, 103c. The refrigerant inflow paths 103a, 103b, and 103c are connected to the other heat exchanger (condenser). Therefore, each refrigerant inflow path 103a, 103b, 103c can be connected to another heat exchanger (condenser) by an independent piping system via the decompression means 20a, 20b, 20c. In the embodiment, a single pipe connected to another heat exchanger (condenser) is branched into a plurality (three), and the branched pipe is then used as the primary pressure reducing means 20a, 20b, 20c. It is connected to the side.

  The heat exchange unit 1 according to the present embodiment has the above-described configuration. Next, the operation of the heat exchange unit 1 having the above configuration will be described.

  First, the pressure reducing means 20a, 20b, 20c (flow rate adjusting valve) is adjusted, and the refrigerant M is reduced in a state where the pressure is reduced to 1/10 to 1/2 (10% to 50%) of the fluid pressure of the refrigerant M on the primary side. It supplies to each of the 1st-3rd block refrigerant | coolant inflow passages 103a, 103b, 103c. At the same time, the cooled object W is supplied to the cooled object inflow path 105.

  Then, as shown in FIG. 5, in each of the refrigerant flow paths 101 of the first to third blocks A, B, C, the refrigerant inflow paths 103a, 103b, 103c (first to third block refrigerant inflow paths 103a, 103b, 103c) to the refrigerant outflow path 104, while the refrigerant M flows from the cooled body inflow path 105 to the cooled body outflow path 106 in the cooled body flow path 102. Circulate. In this state, the refrigerant M and the object to be cooled W circulate in a state of being opposed to each other with the heat transfer plates 100 interposed therebetween. Will be.

  In the heat exchange unit 1 according to the present embodiment, a plurality of refrigerant flow paths 101 formed in the stacking direction of the heat transfer plates 100 in the plate heat exchanger 10 are predetermined in the stacking direction of the heat transfer plates 100. Since each of the blocks is divided into two or more blocks A, B, and C in a liquid-tight or air-tight manner, as described above, each of the refrigerant inflow passages 103a of the first to third blocks A, B, and C. , 103b, 103c, each block A is not affected by the fluid pressure of the refrigerant M in the refrigerant flow paths 101 and the refrigerant inflow paths 103a, 103b, 103c of the other blocks A, B, C. , B, C refrigerant channels 101...

  The heat exchanging unit 1 configured as described above is configured so that the pressure reducing means 20a, 20b, 20c configured to depressurize the refrigerant M from the fluid pressure on the primary side and supply the secondary side to the refrigerant inflow passages 103a, 103b, 103c. Since the refrigerant M is supplied to the refrigerant inflow passages 103a, 103b, and 103c by reducing the fluid pressure of the refrigerant M using the decompression means 20a, 20b, and 20c for each refrigerant inflow passage 103a, 103b, and 103c. Thus, the refrigerant M appropriately flows through the blocks A, B, and C (each refrigerant flow path 101...) Partitioned in the stacking direction.

  Specifically, as shown in FIG. 1, the plate heat exchanger 10 having the above-described configuration is provided with the refrigerant inflow paths 103 a, 103 b, and 103 c for each of the blocks A, B, and C, whereas the refrigerant outflow path 104. Communicate with all the refrigerant flow paths 101 and constitute a common flow path, so that the fluid pressure P1a′P1b′P1c ′ of the refrigerant M flowing through the refrigerant inflow paths 103a, 103b, and 103c and the refrigerant outflow The differential pressures ΔPa ′, ΔPb ′, ΔPc ′ from the fluid pressure P2 of the refrigerant M flowing through the path 104 (and the pipe connected to the refrigerant outflow path 104) are the lengths (flow resistance) of the refrigerant inflow paths 103a, 103b, 103c. Correspondingly, the rear side of the heat transfer plates 100 in the stacking direction (the other frame 120 side) becomes larger (ΔPa ″ <ΔPb ″ <ΔPc ″).

  However, the fluid pressure P1a, P1b, P1c of the refrigerant M in the primary side pipe (not numbered) connected to the decompression means 20a, 20b, 20c, and the pipe (not shown) connected to the refrigerant outflow path 104 The differential pressures ΔPa, ΔPb, ΔPc of the refrigerant M with respect to the fluid pressure P2 are the above-described differential pressures ΔPa ′, ΔPb ′, ΔPc ′ corresponding to the lengths (flow resistances) of the refrigerant inflow passages 103a, 103b, 103c, respectively. , And the differential pressures ΔPa ″, ΔPb ″, ΔPc ″ due to the decompression by the decompression means 20a, 20b, 20c.

  Therefore, the pressure of the refrigerant M is greatly reduced by the pressure reducing means 20a, 20b, and 20c separately connected to the refrigerant inflow paths 103a, 103b, and 103c, and then the refrigerant M is supplied to the refrigerant inflow paths 103a, 103b, and 103c. , The fluid pressure of the refrigerant M on the primary side of the decompression means 20a, 20b, 20c (fluid pressure of the refrigerant M before being decompressed by the decompression means 20a, 20b, 20c) P1a, P1b, P1c and the refrigerant outflow Most of the differential pressures ΔPa, ΔPb, ΔPc from the fluid pressure of the refrigerant M (fluid pressure of the refrigerant M flowing out from the plate heat exchanger 10) P2 on the secondary side of the passage 104 are reduced by the decompression means 20a, 20b, 20c. Differential pressure components ΔPa ″, ΔPb ″, ΔPc ″ due to pressure reduction due to (ΔPa ′ << ΔPa ″, ΔPb ′ << ΔPb ″, ΔPc ′ << ΔPc ′ ), Differential pressure between the refrigerant inflow passages 103a, 103b, 103c and the refrigerant outflow passage 104 in each block A, B, C (differential pressure related to the length of the refrigerant inflow passage (flow resistance)) ΔPa ′, ΔPb ', ΔPc' is almost negligible.

  As a result, the influence of the differential pressure due to the difference in position in the stacking direction of the heat transfer plates 100 in each of the blocks A, B, and C is almost eliminated, and the fluid pressure of the refrigerant M in each of the blocks A, B, and C (of the refrigerant M). Distribution state) becomes substantially equal.

  Therefore, according to the heat exchange unit 1 (plate type heat exchanger 10) having the above-described configuration, the fluid pressure of the refrigerant M at each position (refrigerant channels 103a, 103b, 103c) in the stacking direction of the heat transfer plates 100. As a result, there is no significant difference in the differential pressures ΔPa, ΔPb, ΔPc of the refrigerant, and the refrigerant M flows in a balanced manner in the refrigerant flow paths 103a, 103b, 103c, and heat exchange between the refrigerant M and the cooled object W is performed. As a result, the heat exchange performance that should be inherent in the entire apparatus can be exhibited.

  As described above, the heat exchange unit 1 (plate heat exchanger 10) according to the present embodiment is not affected by the pressure states of the other blocks A, B, and C, and the blocks A, B, and C are not affected. The refrigerant M can be circulated through the refrigerant flow paths 101. In the plate heat exchanger 10 having the above-described configuration, the decompression means 20a, 20b, and 20c are attached (connected) to the refrigerant inflow passages 103a, 103b, and 103c. , 103c, by reducing the fluid pressure of the refrigerant M and supplying the refrigerant M, the blocks A, B, C (each refrigerant flow path 101 ...) partitioned in the stacking direction of the heat transfer plates 100 ... The refrigerant M can be properly circulated, and when the refrigerant M and the object to be cooled W exchange heat, the heat exchange performance that should be inherent in the entire apparatus can be exhibited.

  Moreover, since the heat exchange unit 1 according to the present embodiment employs a flow rate adjustment valve capable of adjusting the flow rate of the refrigerant M as the decompression means 20a, 20b, 20c, the refrigerant M is supplied to each block A, B, C. The fluid pressure can be adjusted.

  The plate heat exchanger and the heat exchange unit including the plate heat exchanger according to the present invention are not limited to the above embodiment, and various modifications can be made without departing from the scope of the present invention. Of course.

  For example, in the above embodiment, the first to third block refrigerant inflow passages 103a, 103b, and 103c are arranged in a line in the longitudinal direction of the heat transfer plates 100, but the present invention is not limited to this. As shown in FIG. 6, the first to third block refrigerant inflow passages 103a, 103b, 103c may be arranged in a line in the short direction perpendicular to the longitudinal direction of the heat transfer plates 100. Also in this case, as shown in FIG. 7, the plate heat exchanger 10 has a plurality of refrigerant channels 101... In a predetermined number of blocks A in the stacking direction of the heat transfer plates 100. , B, and C, the plurality of heat transfer plates 100 constituting the first block A are communicated with the refrigerant flow passages 101 of the first block A. A region including a through hole H1a serving as 103a and a through hole H2 serving as the refrigerant outflow path 104, and a region avoiding the through holes H3 and H4 serving as the cooled body inflow path 105 and the cooled body outflow path 106 is defined. A seal S is provided between the surfaces facing each other, and a through hole H3 serving as a cooled body inflow passage 105 and a through hole H4 serving as a cooled body outflow path 106 communicated with the flow path 102 for the cooled body. Including the refrigerant inflow path 103 And the through hole H1a comprising a refrigerant outflow passage 104, the seal S is applied between the other surface facing to define a region except the H2.

  Further, the plurality of heat transfer plates 100 constituting the second block B include a through hole H1b serving as a second block refrigerant inflow passage 103b communicating with the refrigerant flow passage 101 of the second block B, and a refrigerant outflow passage. A seal S is provided between the opposing faces so as to define a region that includes a through hole H2 that becomes 104 and avoids the through holes H3 and H4 that become the cooled body inflow path 105 and the cooled body outflow path 106. A through hole H3 serving as a cooled body inflow path 105 and a through hole H4 serving as a cooled body outflow path 106, and a refrigerant inflow path 103b and a refrigerant outflow path. A seal S is applied between the other surfaces facing each other so as to define a region avoiding the through-holes H1b and H2 to be 104.

  Further, the plurality of heat transfer plates 100 constituting the third block C include a through hole H1c serving as a third block refrigerant inflow passage 103c communicating with the refrigerant flow passage 101 of the third block C, and a refrigerant outflow passage. A seal S is provided between the opposing faces so as to define a region that includes a through hole H2 that becomes 104 and avoids the through holes H3 and H4 that become the cooled body inflow path 105 and the cooled body outflow path 106. A through-hole H3 serving as a cooled body inflow path 105 and a through-hole H4 serving as a cooled body outflow path 106, and a refrigerant inflow path 103c and a refrigerant outflow path. A seal S is applied between the other surfaces facing each other so as to define a region avoiding the through holes H1c and H2 to be 104. By doing in this way, similarly to the said embodiment, to-be-cooled body W with each to-be-cooled body flow path 102 ..., distribute | circulating the refrigerant | coolant M with the flow-path 101 for refrigerant | coolant of each block A, B, C. Can be distributed.

  In the above embodiment, the plurality of refrigerant inflow passages 103a, 103b, 103c formed in the stacking direction of the heat transfer plates 100 ... are partitioned into three blocks A, B, C in the stacking direction. It is not limited to this, For example, you may divide into two blocks or may divide into four or more blocks. That is, the plurality of refrigerant channels 101 may be divided into a plurality of blocks according to the number of stacked heat transfer plates 100 (the number of refrigerant channels 101).

  In the above-described embodiment, one refrigerant outflow passage 104 is provided. However, the present invention is not limited to this, and two or more refrigerant outflow passages may be provided. However, it is assumed that the refrigerant outflow passage 104 communicates with all the refrigerant passages 101... Regardless of the blocks A, B, and C.

  Although the plate heat exchanger 10 has been described as one configuration of the heat exchange unit 1 in the above embodiment, the present invention is not limited to this. For example, the plate heat exchanger 10 may have a single configuration. However, it goes without saying that the decompression means 20a, 20b, 20c can be attached to the respective refrigerant inflow passages 103a, 103b, 103c.

  In the above embodiment, the refrigerant inflow passages 103a, 103b, 103c, the refrigerant outflow passage 104, the cooled body inflow passage 105, and the flow path are formed so as to form a trapezoidal flow in the refrigerant flow path 101 and the cooled object flow path 102. Although the cooling body outflow path 106 is arranged, the present invention is not limited to this. For example, the refrigerant inflow paths 103a, 103b, 103c, and the refrigerant outflow path 104 are diagonally arranged at the four corners of the heat transfer plate 100. Are provided at the two corners at the position, and the cooled body inflow path 105 and the cooled body outflow path 106 are provided at the remaining two corners of the four corners of the heat transfer plate 100, and the refrigerant flow path 101 and You may make it form what is called an oblique flow which distribute | circulates the refrigerant | coolant M and the to-be-cooled body W in the diagonal direction in the flow path 102 for to-be-cooled bodies. In the above embodiment, the cooling target W is introduced from one end side in the longitudinal direction of the heat transfer plate 100, while the refrigerant M is introduced from the other end side in the longitudinal direction of the heat transfer plate 100. For example, the object to be cooled W and the refrigerant M may be allowed to flow from one end side or the other end side of the heat transfer plate 100 in the longitudinal direction. Needless to say, even if the position where the refrigerant M is introduced is changed, the plurality of refrigerant flow paths 101 are divided into two or more blocks A, B, and C in the stacking direction of the heat transfer plates 100. Refrigerant inflow passages 103a, 103b, 103c corresponding to the number of blocks A, B, C are formed, and the decompression means 20a, 20b, 20c are directly or indirectly connected to the respective refrigerant inflow passages 103a, 103b, 103c. Of course, they are connected.

  In the above embodiment, the connecting portions J1a, J1b, J1c are attached to one frame 110, and the refrigerant M is allowed to flow from the one frame 110 side. However, the present invention is not limited to this. As shown in FIG. 8, the refrigerant M may be caused to flow from both the frames 110 and 120 side.

  Specifically, two or more of the plurality of refrigerant flow paths 101 formed in the stacking direction of the heat transfer plates 100 are partitioned liquid-tight or air-tight by a predetermined number in the stacking direction of the heat transfer plates 100. The block is divided into four blocks A, B, C and D (four in the figure), and the refrigerant inflow passages 103a, 103b, 103c and 103d are divided into two or more corresponding to the number of blocks A, B, C and D ( In the figure, four are formed, and a predetermined number of the refrigerant inflow passages 103a, 103b out of the two or more refrigerant inflow passages 103a, 103b, 103c, 103d are introduced from the one frame 110 side. The remaining refrigerant inflow paths 103c and 103d may be formed so that the refrigerant M flows in from the other frame 120 side. Also in this case, the refrigerant inflow passages 103a, 103b, and 103c are formed so as to communicate with the refrigerant passages 101 of the different blocks A, B, C, and D, and the refrigerant inflow passages 103a, 103b, and 103c. Of course, the decompression means is connected directly or indirectly to the connecting portions J1a, J1b, J1c, J1d attached to the frames 110, 120 so as to communicate with the frames 103d. Of course, the refrigerant outflow path 104 is formed so as to penetrate different blocks A, B, C, and D.

  DESCRIPTION OF SYMBOLS 1 ... Heat exchange unit, 10 ... Plate type heat exchanger, 20a, 20b, 20c ... Pressure reducing means, 100 ... Heat transfer plate, 101 ... Refrigerant flow path, 102 ... Coolant flow path, 103a ... First block Refrigerant inflow path (refrigerant inflow path), 103b ... second block refrigerant inflow path (refrigerant inflow path), 103c ... third block refrigerant inflow path (refrigerant inflow path), 104 ... refrigerant outflow path, 105 ... cooled body inflow path 106 ... cooled body outflow path, 110,120 ... frame, A ... first block (block), B ... second block (block), C ... third block (block), H1a, H1b, H1c, H2, H3, H4 ... through hole, J1a, J1b, J1c, J2, J3, J4 ... connection part, M ... refrigerant, W ... body to be cooled

Claims (3)

Between the heat transfer plates that are stacked, a refrigerant flow path for circulating the refrigerant with each heat transfer plate as a boundary and a flow path for the cooled body for circulating the cooled object are alternately formed, and each heat transfer A cooling target body in which a through-hole formed in the plate is connected to form a refrigerant inflow path and a refrigerant outflow path through which the refrigerant flows into and out of the cooling medium flow path, and the cooling target body flows into and out of the cooling target flow path A plate type heat exchanger in which an inflow path and a cooled body outflow path are formed, and a plurality of refrigerant flow paths formed in the stacking direction of the heat transfer plates are provided for each predetermined number in the stacking direction of the heat transfer plates. It is partitioned liquid-tight or air-tight and is divided into two or more blocks, and two or more refrigerant inflow paths are formed corresponding to the number of the blocks, and each of the two or more refrigerant inflow paths is laminated. The outermost heat transfer plate Plate through hole is contiguous in a line from a different one that is formed so as to communicate with the refrigerant passage of the block, said coolant outlet channel, so as to communicate with all of the refrigerant flow path in the stacking direction of the heat transfer plate A plate heat exchanger characterized by being formed. Between the heat transfer plates that are stacked, a refrigerant flow path for circulating the refrigerant with each heat transfer plate as a boundary and a flow path for the cooled body for circulating the cooled object are alternately formed, and each heat transfer A cooling target body in which a through-hole formed in the plate is connected to form a refrigerant inflow path and a refrigerant outflow path through which the refrigerant flows into and out of the cooling medium flow path, and the cooling target body flows into and out of the cooling target flow path A heat exchanging unit including a plate heat exchanger in which an inflow path and a cooled body outflow path are formed, and decompression means configured to depressurize refrigerant from a primary side fluid pressure and supply the refrigerant to a secondary side The plate-type heat exchanger further includes a plurality of refrigerant flow paths formed in the heat transfer plate stacking direction and partitioned in a liquid-tight or air-tight manner by a predetermined number in the heat transfer plate stacking direction. And the refrigerant inflow passage is divided into two or more blocks. Are formed corresponding to the number of locking more than one, each of said two or more refrigerant inflow channel, most through-holes from the heat transfer plate on the outside is contiguous in a row in the stacked plurality heat transfer plates, The refrigerant outflow path is formed to communicate with all the refrigerant flow paths in the stacking direction of the heat transfer plate, and the decompression unit is configured to communicate with the refrigerant flow paths of different blocks. A heat exchange unit provided for each inflow path and connected directly or indirectly to each refrigerant inflow path.   The heat exchange unit according to claim 2, wherein the decompression unit is configured by a flow rate adjustment valve capable of adjusting a flow rate of the refrigerant.

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