Shell and plate type heat exchanger and refrigeration equipment

Abstract

To improve performance of a shell and plate type heat exchanger.SOLUTION: A refrigerant flow passage (41) and a heating medium flow passage (42) are formed in a plate laminate (40) of a heat exchanger (10). An upper side through hole (95) and a lower side through hole (96) are formed in each heat transfer plate (50) of the plate laminate (40). The upper side through hole (95) forms an upper side communication passage (43) in communication with the heating medium flow passage (42). The lower side through hole (96) forms a lower side communication passage (44) in communication with the heating medium flow passage (42). A guide structure (100) for guiding a refrigerant flowing in the refrigerant flow passage (41) to a space between the upper side through hole (95) and the lower side through hole (96) is formed in each heat transfer plate (50).SELECTED DRAWING: Figure 8

Description

[Technical Field]

[0001] The present disclosure relates to a shell-and-plate heat exchanger and a refrigeration system. [Background technology]

[0002] Shell-and-plate heat exchangers have been known for some time. In shell-and-plate heat exchangers, a plate stack is housed in the internal space of a cylindrical shell. Patent Document 1 discloses a shell-and-plate heat exchanger used as an evaporator.

[0003] In the plate stack, refrigerant channels and heat transfer medium channels are formed with the heat transfer plates sandwiched between them. In an evaporator constructed using a shell-and-plate heat exchanger, the refrigerant in the shell flows into the refrigerant channels of the plate stack and evaporates through heat exchange with the heat transfer medium, such as water, flowing through the heat transfer medium channels. As a result, the heat transfer medium flowing through the heat transfer medium channels is cooled.

[0004] Each heat transfer plate of the heat exchanger of Patent Document 1 has two through holes formed in the center in the left-right direction, one above the other. The lower through hole forms an inlet passage for introducing the heat medium into the heat medium flow path. The upper through hole forms an outlet passage for discharging the heat medium from the heat medium flow path. The inlet passage and outlet passage, through which the heat medium flows, are separated from the refrigerant flow path through which the refrigerant flows. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] Special Publication No. 2020-510181 Summary of the Invention [Problem to be solved by the invention]

[0006] In the refrigerant flow channels of the plate stack of a shell-and-plate heat exchanger, liquid refrigerant evaporates and turns into gas refrigerant. The gas refrigerant generated in the refrigerant flow channels flows upward due to buoyancy. Therefore, the refrigerant flows from bottom to top in the refrigerant flow channels.

[0007] As described above, the refrigerant flow path is separated from the inlet and outlet passages through which the heat transfer medium flows. Therefore, the refrigerant flowing upward in the refrigerant flow path avoids the inlet and outlet passages. As a result, the amount of liquid refrigerant that flows into the portion of the refrigerant flow path between the inlet and outlet passages is reduced.

[0008] If the amount of liquid refrigerant flowing into the portion of the refrigerant flow path between the inlet and outlet passages is small, the area of ​​the region between the vertically arranged through-holes in each heat transfer plate that comes into contact with the liquid refrigerant is reduced, which reduces the area of ​​the heat transfer surface of the heat transfer plate where heat exchange between the liquid refrigerant and the heat medium occurs, thereby reducing the amount of heat exchanged between the refrigerant and the heat medium in the shell-and-plate heat exchanger.

[0009] An object of the present disclosure is to improve the performance of a shell and plate heat exchanger. [Means for solving the problem]

[0010] A first aspect of the present disclosure is a shell-and-plate heat exchanger (10) including a shell (20) forming an internal space (21), and a plate stack (40) having a plurality of heat transfer plates (50) stacked laterally and joined to one another and accommodated in the internal space (21) of the shell (20), wherein the plate stack (40) is formed with a plurality of refrigerant flow paths (41) communicating with the internal space (21) of the shell (20) and through which a refrigerant flows, and a plurality of heat transfer medium flow paths (42) isolated from the internal space (21) of the shell (20) and through which a heat medium flows, the plurality of refrigerant flow paths being adjacent to each other across the heat transfer plates (50), and the refrigerant evaporates in the refrigerant flow paths (41) of the plate stack (40). Each of the plurality of heat transfer plates (50) is formed with an upper through-hole (95) and a lower through-hole (96) arranged vertically side by side at a distance from each other. In the plate stack (40), the upper through-holes (95) of the heat transfer plates (50) form upper communication passages (43) that communicate with the heat medium flow passages (42) and are isolated from the refrigerant flow passages (41), and the lower through-holes (96) of the heat transfer plates (50) form lower communication passages (44) that communicate with the heat medium flow passages (42) and are isolated from the refrigerant flow passages (41). Each of the heat transfer plates (50) is formed with a guide structure (100) that guides the refrigerant flowing through the refrigerant flow passages (41) between the upper through-hole (95) and the lower through-hole (96).

[0011] In the first embodiment of the shell-and-plate heat exchanger (10), the refrigerant flows into the refrigerant flow paths (41) of the plate stack (40) and evaporates through heat exchange with the heat medium flowing through the heat medium flow paths (42). The gas refrigerant generated in the refrigerant flow paths (41) flows upward due to buoyancy. Therefore, the refrigerant flows generally from bottom to top in the refrigerant flow paths (41). A portion of the refrigerant flowing upward in the refrigerant flow paths (41) is guided between the upper communicating passage (43) and the lower communicating passage (44) by the guide structure (100). Therefore, in the heat transfer plate (50), both the portion between the upper through-holes (95) and the lower through-holes (96) and the outside of this portion come into contact with the liquid refrigerant and exchange heat with the liquid refrigerant. As a result, the amount of heat exchanged between the refrigerant and the heat medium in the shell-and-plate heat exchanger (10) increases, improving the performance of the shell-and-plate heat exchanger (10).

[0012] A second aspect of the present disclosure is a shell-and-plate heat exchanger according to the first aspect, wherein the guide structure (100) is configured by a plurality of linear ridge portions (80a, 80b) parallel to each other, and each of the plurality of ridge portions (80a, 80b) is formed by raising the heat transfer plate (50).

[0013] In the second embodiment, a plurality of ridge portions (80a, 80b) constitute the guide structure (100). The ridge portions (80a, 80b) are formed by raising the heat transfer plate (50) and bulge toward the refrigerant flow path (41). Therefore, the flow direction of the refrigerant in the refrigerant flow path (41) is changed by the ridge portions (80a, 80b) constituting the guide structure (100).

[0014] A third aspect of the present disclosure is a shell-and-plate heat exchanger according to the second aspect, wherein the heat transfer plate (50) includes a first plate (50a) and a second plate (50b), the first plates (50a) and the second plates (50b) are alternately stacked in the plate stack (40), and guide regions (61a, 61b, 71a, 71b) including a plurality of ridge portions (80a, 80b) constituting the guide structure (100) are formed in each of the first plate (50a) and the second plate (50b), and the plate stack (40) is a shell-and-plate heat exchanger wherein the guide regions (61a, 71a) of the first plate (50a) and the guide regions (71b, 61b) of the second plate (50b) overlap in the stacking direction of the heat transfer plates (50).

[0015] In the plate stack (40) of the third aspect, the guide regions (61a, 61b, 71a, 71b) of the heat transfer plates (50) overlap in the stacking direction of the heat transfer plates (50). The refrigerant flowing through the refrigerant flow passages (41) of the plate stack (40) is guided between the upper communicating passage (43) and the lower communicating passage (44) by the ridge portions (80a, 80b) included in the overlapping guide regions (61a, 61b, 71a, 71b).

[0016] A fourth aspect of the present disclosure is a shell-and-plate heat exchanger according to the third aspect, wherein the guide regions (61a, 61b, 71a, 71b) of each of the first plate (50a) and the second plate (50b) extend from the portion between the upper through-hole (95) and the lower through-hole (96) to the outside of that portion.

[0017] In each heat transfer plate (50) of the fourth aspect, the guide regions (61a, 61b, 71a, 71b) are arranged from the portion between the upper through-hole (95) and the lower through-hole (96) to the outside of that portion. Therefore, in the refrigerant flow path (41) of the plate stack (40), part of the refrigerant flowing outside the portion between the upper communicating passage (43) and the lower communicating passage (44) is guided to that portion by the ridge portions (80a, 80b) included in the guide regions (61a, 61b, 71a, 71b).

[0018] A fifth aspect of the present disclosure is a shell-and-plate heat exchanger according to the fourth aspect, wherein the guide regions (61a, 61b, 71a, 71b) are formed on the right and left sides of the lower through-hole (96) in each of the first plate (50a) and the second plate (50b).

[0019] In the plate stack (40) of the fifth aspect, the refrigerant flowing through the refrigerant flow path (41) is guided to the area between the upper communicating passage (43) and the lower communicating passage (44) by the ridge portions (80a, 80b) of the guide regions (61a, 61b, 71a, 71b) provided on the right and left sides, respectively, of the lower communicating passage (44).

[0020] A sixth aspect of the present disclosure is a shell-and-plate heat exchanger according to the fifth aspect, wherein the upper ends of the guide regions (61a, 61b, 71a, 71b) are located in portions of the heat transfer plate (50) between the upper through-holes (95) and the lower through-holes (96), and the guide regions (61a, 61b, 71a, 71b) extend obliquely downward from the upper ends of the guide regions (61a, 61b, 71a, 71b).

[0021] In each heat transfer plate (50) of the sixth aspect, the guide regions (61a, 61b, 71a, 71b) extend obliquely downward from a portion between the upper through-hole (95) and the lower through-hole (96). Therefore, the refrigerant flowing upward in a portion of the refrigerant flow path (41) on the side of the lower communicating passage (44) is guided to a portion between the upper communicating passage (43) and the lower communicating passage (44) by the ridge portions (80a, 80b) included in the guide regions (61a, 61b, 71a, 71b).

[0022] A seventh aspect of the present disclosure is a shell-and-plate heat exchanger according to the fifth or sixth aspect, wherein the ridge portions included in the guide region (61a, 71a) of the first plate (50a) are first ridge portions (81a, 82a), and the ridge portions included in the guide region (71b, 61b) of the second plate (50b) are second ridge portions (82b, 81b), and the bisector (L1) of the obtuse angle formed by the first ridge portions (81a, 82a) and the second ridge portions (82b, 81b) and the bisector (L2) of the acute angle formed by the first ridge portions (81a, 82a) and the second ridge portions (82b, 81b) that has a smaller acute angle with the vertical direction is inclined so as to approach the center of the width direction of the heat transfer plate (50) as it goes upward.

[0023] In the seventh aspect, the refrigerant flowing through the portion of the refrigerant flow path (41) sandwiched between the guide regions (61a, 61b, 71a, 71b) of the heat transfer plates (50) tends to flow in the direction along the bisector (L1) of the obtuse angle formed by the first ridge portions (81a, 82a) and the second ridge portions (82b, 81b) and the bisector (L2) of the acute angle formed by the first ridge portions (81a, 82a) and the second ridge portion (812), whichever bisector forms the smaller acute angle with the vertical direction. This is because buoyancy acts vertically upward on the gas refrigerant flowing through the refrigerant flow path (41).

[0024] In the seventh aspect, the bisector that forms a smaller acute angle with the vertical direction is inclined so that the higher it goes, the closer it is to the center in the width direction of the heat transfer plate (50). Therefore, the refrigerant flowing through the portion of the refrigerant flow path (41) sandwiched between the guide regions (61a, 61b, 71a, 71b) of each heat transfer plate (50) is guided between the upper communicating passage (43) and the lower communicating passage (44) by the first ridge portions (81a, 82a) and the second ridge portions (82b, 81b).

[0025] An eighth aspect of the present disclosure is a shell-and-plate heat exchanger according to the third aspect, wherein, in each of the plurality of heat transfer plates (50), the guide regions (53a, 53b) extend in the left-right direction and cross the portion between the upper through-hole (95) and the lower through-hole (96).

[0026] In the eighth aspect, the refrigerant flowing through the refrigerant flow path (41) is guided between the upper communicating passage (43) and the lower communicating passage (44) by the guide region (53a, 53b) that traverses the portion between the upper through-hole (95) and the lower through-hole (96).

[0027] A ninth aspect of the present disclosure is a shell-and-plate type heat exchanger according to the eighth aspect, wherein the ridge portion included in the guide region (53a, 53b) of the first plate (50a) is a first ridge portion (83a), and the ridge portion included in the guide region (53a, 53b) of the second plate (50b) is a second ridge portion (83b), and the first ridge portion (83a) and the second ridge portion (83b) have different extension directions, and the acute angle between each extension direction and the horizontal direction is 45° or less.

[0028] In the ninth aspect, the ridge portions (83a, 83b) included in the guide regions (53a, 53b) that cross the portion between the upper through-hole (95) and the lower through-hole (96) form an acute angle of 45° or less between their extension direction and the horizontal direction. Therefore, in the refrigerant flow path (41), the refrigerant that flows upward and reaches the guide regions (53a, 53b) is guided between the upper communicating passage (43) and the lower communicating passage (44) by the ridge portions (83a, 83b) included in the guide regions (53a, 53b).

[0029] A tenth aspect of the present disclosure is a refrigeration system including a shell-and-plate heat exchanger (10) according to any one of the first to ninth aspects, and a refrigerant circuit (205) in which the shell-and-plate heat exchanger (10) is provided and which circulates a refrigerant to perform a refrigeration cycle.

[0030] In a tenth aspect, a shell-and-plate heat exchanger (10) is provided in a refrigerant circuit (205) that performs a refrigeration cycle. [Brief explanation of the drawings]

[0031] [Figure 1] FIG. 1 is a piping diagram showing a refrigerant circuit of a refrigeration device according to a first embodiment. [Figure 2] FIG. 2 is a side view and a cross-sectional view taken along line II-II of the shell-and-plate heat exchanger of the first embodiment. [Figure 3] FIG. 3 is a cross-sectional view of the plate-and-shell heat exchanger taken along line III-III in FIG. [Figure 4] FIG. 4 is a cross-sectional view of the plate stack of the first embodiment. [Figure 5] FIG. 5 is a front view of the first plate (heat transfer plate) of the first embodiment. [Figure 6] FIG. 6 is a front view of the second plate (heat transfer plate) of the first embodiment. [Figure 7] FIG. 7 is an enlarged view of a main part of the plate stack of the first embodiment. [Figure 8] FIG. 8 is a schematic front view of the first plate of the first embodiment, illustrating the flow of the refrigerant in the refrigerant flow path. [Figure 9] FIG. 9 is a schematic front view of the second plate of the first embodiment, illustrating the flow of the heat medium in the heat medium flow path. [Figure 10] FIG. 10 is a front view of the first plate (heat transfer plate) of the second embodiment. [Figure 11] FIG. 11 is a front view of the second plate (heat transfer plate) of the second embodiment. [Figure 12] FIG. 12 is an enlarged view of a main part of the plate stack of the second embodiment. [Figure 13] FIG. 13 is a schematic front view of the first plate of the second embodiment, illustrating the flow of the coolant in the coolant flow path. [Figure 14] FIG. 14 is a front view of a first plate (heat transfer plate) of a modified example of the second embodiment. [Figure 15] FIG. 15 is a front view of a second plate (heat transfer plate) of a modified example of the second embodiment. [Figure 16] FIG. 16 is a front view of the first plate (heat transfer plate) of the third embodiment. [Figure 17] FIG. 17 is a front view of the second plate (heat transfer plate) of the third embodiment. [Figure 18] FIG. 18 is a front view of a first plate (heat transfer plate) of a modified example of the third embodiment. [Figure 19] FIG. 19 is a front view of a second plate (heat transfer plate) of a modified example of the third embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0032] First Embodiment A first embodiment will be described. This embodiment is a refrigeration system (200) including a shell-and-plate heat exchanger (10).

[0033] -Refrigeration equipment- As shown in Fig. 1, the refrigeration system (200) of this embodiment includes a refrigerant circuit (205). The refrigerant circuit (205) is a closed circuit formed by connecting a compressor (206), a condenser (207), an expansion valve (208), and an evaporator (209) in this order with piping. The refrigerant circuit (205) is filled with refrigerant. In this refrigeration system (200), the evaporator (209) is a shell-and-plate heat exchanger (10).

[0034] The refrigerant circuit (205) performs a refrigeration cycle by circulating a refrigerant. When the compressor (206) is operated, the refrigerant circulates in the refrigerant circuit (205). The refrigerant discharged from the compressor (206) is condensed in the condenser (207) by dissipating heat to a cooling medium such as water. The refrigerant flowing out from the condenser (207) is reduced in pressure while passing through the expansion valve (208) and then flows into the evaporator (209). In the evaporator (209), the refrigerant absorbs heat from a heat medium such as water and evaporates. The refrigerant flowing out from the evaporator (209) is drawn into the compressor (206) and compressed. The compressor (206) discharges the compressed refrigerant.

[0035] -Shell and plate heat exchanger- The shell-and-plate heat exchanger (10) (hereinafter referred to as "heat exchanger") of this embodiment is a flooded evaporator. The heat exchanger (10) of this embodiment performs cooling by exchanging heat between a heat medium and a refrigerant. Examples of the heat medium include water and brine.

[0036] 2, the heat exchanger (10) of this embodiment includes a shell (20) and a plate stack (40). The plate stack (40) is housed in the internal space (21) of the shell (20).

[0037] -shell- The shell 20 is formed in a cylindrical shape with both ends closed, and is installed in a position where its longitudinal direction is oriented horizontally.

[0038] A refrigerant inlet (22) is provided at the bottom of the shell (20) for introducing a refrigerant into the internal space (21) of the shell (20). The refrigerant inlet (22) is connected to an expansion valve (208) via a pipe. A refrigerant outlet (23) is provided at the top of the shell (20) for discharging the refrigerant from the internal space (21) of the shell (20). The refrigerant outlet (23) is connected to a compressor (206) via a pipe.

[0039] The shell (20) is provided with a heat transfer medium inlet (24) and a heat transfer medium outlet (25). The heat transfer medium inlet (24) and the heat transfer medium outlet (25) are each tubular members. The heat transfer medium inlet (24) and the heat transfer medium outlet (25) each pass through one end of the shell (20) and connect to the plate stack (40). The heat transfer medium inlet (24) connects to a lower communication passage (44) of the plate stack (40) and supplies the heat transfer medium to the plate stack (40). The heat transfer medium outlet (25) connects to an upper communication passage (43) of the plate stack (40) and discharges the heat transfer medium from the plate stack (40).

[0040] -Plate laminate- As shown in Fig. 2, the plate stack (40) is composed of a plurality of stacked heat transfer plates (50). The plate stack (40) is housed in the internal space (21) of the shell (20) with the stacking direction of the heat transfer plates (50) oriented horizontally. The plate stack (40) is disposed in the lower part of the internal space (21) of the shell (20).

[0041] As shown in Fig. 3, the heat transfer plates (50) constituting the plate stack (40) are generally trapezoidal plate-like members. In the heat transfer plates (50), an upper edge (91) corresponding to the upper base of the trapezoid is longer than a lower edge (92) corresponding to the lower base of the trapezoid. The left and right side edges (93) of the heat transfer plates (50) are downwardly arc-shaped along the inner surface of the shell (20). Each of the four corners of the heat transfer plates (50) is arc-shaped.

[0042] As shown in Fig. 4, the plate stack (40) includes a first plate (50a) and a second plate (50b) as heat transfer plates. The second plate (50b) is the first plate (50a) turned upside down. The detailed structures of the first plate (50a) and the second plate (50b) will be described later.

[0043] The plate stack 40 includes a plurality of first plates 50 a and a plurality of second plates 50 b. In the plate stack 40, the first plates 50 a and the second plates 50 b are stacked alternately. The plate stack 40 is installed in the shell 20 with the upper edges 91 and lower edges 92 of the heat transfer plates 50 substantially horizontal.

[0044] <Heat transfer plate> The first plate (50a) and the second plate (50b), which are heat transfer plates, will be described with reference to Figures 4 to 6. In the following description, for each of the first plate (50a) and the second plate (50b), the left side in Figure 4 will be referred to as the front side, and the right side in Figure 4 will be referred to as the back side.

[0045] As shown in FIG. 5, an upper through-hole (95) and a lower through-hole (96) are formed in the first plate (50a). The upper through-hole (95) and the lower through-hole (96) are each a relatively large circular through-hole. The diameter of the upper through-hole (95) and the diameter of the lower through-hole (96) are substantially equal. The upper through-hole (95) and the lower through-hole (96) are arranged side by side in the vertical direction in the center of the first plate (50a) in the horizontal direction. The center of the upper through-hole (95) and the center of the lower through-hole (96) are located on the center line of the first plate (50a) in the width direction.

[0046] The first plate (50a) is formed with an upper peripheral edge (95a) and a lower peripheral edge (96a). The upper peripheral edge (95a) is an annular portion that follows the periphery of the upper through-hole (95). The lower peripheral edge (96a) is an annular portion that follows the periphery of the lower through-hole (96). The upper peripheral edge (95a) and the lower peripheral edge (96a) each bulge out toward the front surface of the first plate (50a) (see FIG. 4).

[0047] A partition portion (97) is formed in the first plate (50a). The partition portion (97) is a linear, flat portion that is substantially parallel to the upper edge (91) and the lower edge (92) of the first plate (50a). The partition portion (97) is disposed so as to cross between the upper through-hole (95) and the lower through-hole (96). The length of the partition portion (97) is shorter than the upper edge (91) of the first plate (50a) and longer than the lower edge (92) of the first plate (50a).

[0048] A large number of ridges (80a) are formed on the heat transfer surface of the first plate (50a). The ridges (80a) are linear portions formed by raising a portion of the first plate (50a). The ridges (80a) of the first plate (50a) are raised on the front surface side of the first plate (50a) (see FIG. 4).

[0049] As described above, the second plate (50b) is the first plate (50a) turned upside down. As shown in FIG. 6, the second plate (50b) has upper through-holes (95), lower through-holes (96), upper peripheral edges (95a), lower peripheral edges (96a), and partitions (97) formed therein, similar to the first plate (50a). The shapes and arrangements of the upper through-holes (95), lower through-holes (96), upper peripheral edges (95a), lower peripheral edges (96a), and partitions (97) of the second plate (50b) are the same as those of the first plate (50a). However, the upper peripheral edges (95a) and lower peripheral edges (96a) of the second plate (50b) bulge outward from the rear surface of the second plate (50b) (see FIG. 4).

[0050] Similar to the first plate 50a, the heat transfer surface of the second plate 50b is formed with a large number of ridges 80b, which protrude from the rear surface of the second plate 50b (see FIG. 4).

[0051] <Refrigerant flow path, heat medium flow path> 4, in the plate stack (40), a plurality of refrigerant channels (41) and a plurality of heat medium channels (42) are formed with the heat transfer plates (50) interposed therebetween. The refrigerant channels (41) and the heat medium channels (42) are separated from each other by the heat transfer plates (50).

[0052] The refrigerant flow path (41) is a flow path sandwiched between the front surface of the first plate (50a) and the back surface of the second plate (50b). The refrigerant flow path (41) is in communication with the internal space (21) of the shell (20). The heat medium flow path (42) is a flow path sandwiched between the back surface of the first plate (50a) and the front surface of the second plate (50b). The heat medium flow path (42) is isolated from the internal space (21) of the shell (20) and is in communication with a heat medium inlet (24) and a heat medium outlet (25) attached to the shell (20).

[0053] <Upper communication path, lower communication path> In the plate stack 40, the peripheral edge of each first plate 50 a is joined around the entire periphery by welding or brazing to the peripheral edge of the second plate 50 b adjacent to the back surface of the first plate 50 a. In the plate stack 40, the upper through-hole 95 of each first plate 50 a overlaps with the upper through-hole 95 of the second plate 50 b adjacent to the front surface of the first plate 50 a, and the edges of the two overlapping upper through-holes 95 are joined around the entire periphery by welding or brazing. In addition, in the plate stack (40), the lower through-hole (96) of each first plate (50a) overlaps with the lower through-hole (96) of the second plate (50b) adjacent to the front surface side of the first plate (50a), and the edges of the two overlapping lower through-holes (96) are joined around the entire circumference by welding or brazing.

[0054] In the plate stack (40), the upper through-holes (95) and the upper peripheral edges (95a) of each heat transfer plate (50) form upper communication passages (43). In addition, in the plate stack (40), the lower through-holes (96) and the lower peripheral edges (96a) of each heat transfer plate (50) form lower communication passages (44).

[0055] The upper communication passage (43) and the lower communication passage (44) are passages extending in the stacking direction of the heat transfer plates (50) in the plate stack (40). The upper communication passage (43) is a passage isolated from the internal space (21) of the shell (20), communicates with all the heat transfer medium flow passages (42), and connects all the heat transfer medium flow passages (42) to the heat transfer medium outlets (25). The lower communication passage (44) is a passage isolated from the internal space (21) of the shell (20), communicates with all the heat transfer medium flow passages (42), and connects all the heat transfer medium flow passages (42) to the heat transfer medium inlets (24).

[0056] -Heat transfer surface of the first plate- 5, the heat transfer surface of the first plate (50a) is divided into an upper region (51a), a lower region (52a), a first guide region (61a), a first lower lateral region (62a), a first lateral region (63a), a first upper lateral region (64a), a second guide region (71a), a second lower lateral region (72a), a second lateral region (73a), and a second upper lateral region (74a). A plurality of ridges (80a) are formed in each of these regions (51a, 52a, 61a to 64a, 71a to 74a).

[0057] Note that the terms "right," "left," "upper," and "lower" used in the description of the heat transfer surface of the first plate (50a) refer to the "right," "left," "upper," and "lower" of the first plate (50a) shown in Fig. 5. The angle values ​​shown in this description are merely examples.

[0058] <Top area> The upper region (51a) is a rectangular region located above the partition (97). The upper region (51a) is formed from the partition (97) to the upper end of the heat transfer surface of the first plate (50a). The length of the long side of the upper region (51a) is approximately equal to the length of the partition (97). The upper through-hole (95) is formed in the center of the upper region (51a) in the left-right direction.

[0059] The ridges 80a formed in the upper region 51a are inclined upward to the right, and the angle formed between the extension direction of the ridges 80a in the upper region 51a and the horizontal direction is approximately 45°.

[0060] <Lower area> The lower region (52a) is an isosceles trapezoidal region located below the partition (97). The lower region (52a) is formed from the partition (97) to the lower end of the heat transfer surface of the first plate (50a). In the lower region (52a), the length of the side corresponding to the upper base of the trapezoid is shorter than the length of the side corresponding to the lower base of the trapezoid. In addition, in the lower region (52a), the length of the side corresponding to the upper base of the trapezoid is shorter than the diameters of the upper through-hole (95) and the lower through-hole (96). The lower through-hole (96) is formed in the center of the lower region (52a) in the left-right direction.

[0061] The ridges 80a formed in the lower region 52a are inclined upward to the right, and the angle formed between the extension direction of the ridges 80a in the lower region 52a and the horizontal direction is approximately 45°.

[0062] <First guide area> The first guide region (61a) is a region along the right oblique side of the lower region (52a). The first guide region (61a) is formed from the partition portion (97) to the lower end of the heat transfer surface of the first plate (50a). The width of the first guide region (61a) is approximately constant from the upper end to the lower end of the first guide region (61a).

[0063] The upper end of the first guide region (61a) is located in the portion of the first plate (50a) between the upper through-hole (95) and the lower through-hole (96) (the dotted region in FIG. 8). The first guide region (61a) extends diagonally downward to the right from its upper end. The first guide region (61a) is formed over both the portion of the first plate (50a) between the upper through-hole (95) and the lower through-hole (96) and the outside of that portion.

[0064] The ridge portion (81a) of the first guide region (61a) is inclined upward to the left, and the angle formed between the extension direction of the ridge portion (81a) of the first guide region (61a) and the horizontal direction is approximately 5°.

[0065] <First lateral lower area> The first lower side region (62a) is located to the right of the first guide region (61a). The first lower side region (62a) is formed from the partition (97) to the side edge of the heat transfer surface of the first plate (50a). The right side of the first lower side region (62a) extends diagonally downward to the right from the right edge of the partition (97).

[0066] The ridge portion (80a) of the first lower side region (62a) is inclined upward to the left, and the angle formed between the extension direction of the ridge portion (80a) of the first lower side region (62a) and the horizontal direction is approximately 85°.

[0067] <First lateral area> The first side region (63a) is located to the right of the first lower side region (62a). The first side region (63a) is formed from the right end of the partition (97) to the side edge of the heat transfer surface of the first plate (50a). The first side region (63a) has a triangular shape that widens from the right end of the partition (97) toward the side edge (93) of the first plate (50a).

[0068] The ridge portion (80a) of the first side region (63a) is inclined upward to the left, and the angle formed between the extension direction of the ridge portion (80a) of the first side region (63a) and the horizontal direction is approximately 45°.

[0069] <First lateral upper area> The first upper side region (64a) is a region sandwiched between the upper region (51a) and the first upper side region (63a). The first upper side region (64a) is formed from the right end of the partition (97) to the upper end of the heat transfer surface of the first plate (50a). The first upper side region (64a) has a triangular shape that widens from the right end of the partition (97) toward the upper edge (91) of the first plate (50a).

[0070] The ridge portion (80a) of the first upper side region (64a) is inclined upward to the right, and the angle formed by the extension direction of the ridge portion (80a) of the first upper side region (64a) and the horizontal direction is approximately 10°.

[0071] <Second guide area> The second guide region (71a) is a region along the left oblique side of the lower region (52a). The second guide region (71a) is formed from the partition portion (97) to the lower end of the heat transfer surface of the first plate (50a). The width of the second guide region (71a) is approximately constant from the upper end to the lower end of the second guide region (71a).

[0072] The upper end of the second guide region (71a) is located in the portion of the first plate (50a) sandwiched between the upper through-hole (95) and the lower through-hole (96) (the dotted region in FIG. 8). The second guide region (71a) extends diagonally downward and to the left from its upper end. The second guide region (71a) is formed over both the portion of the first plate (50a) sandwiched between the upper through-hole (95) and the lower through-hole (96) and the outside of that portion.

[0073] The ridge portion (82a) of the second guide region (71a) is inclined upward to the left, and the angle formed between the extension direction of the ridge portion (82a) of the second guide region (71a) and the horizontal direction is approximately 75°.

[0074] <Second lateral lower area> The second lower side region (72a) is located to the left of the second guide region (71a). The second lower side region (72a) is formed from the partition (97) to the side edge of the heat transfer surface of the first plate (50a). The left side of the second lower side region (72a) extends diagonally downward and left from the left edge of the partition (97).

[0075] The ridge portion (80a) of the second lower side region (72a) is inclined upward to the right, and the angle formed between the extension direction of the ridge portion (80a) of the second lower side region (72a) and the horizontal direction is approximately 5°.

[0076] <Second lateral area> The second side region (73a) is located to the left of the second lower side region (72a). The second side region (73a) is formed from the left end of the partition (97) to the side edge of the heat transfer surface of the first plate (50a). The second side region (73a) has a triangular shape that widens from the left end of the partition (97) toward the side edge (93) of the first plate (50a).

[0077] The ridge portion (80a) of the second side region (73a) is inclined upward to the left, and the angle formed between the extension direction of the ridge portion (80a) of the second side region (73a) and the horizontal direction is approximately 45°.

[0078] <Second lateral upper area> The second upper side region (74a) is a region sandwiched between the upper region (51a) and the second upper side region (73a). The second upper side region (74a) is formed from the left end of the partition (97) to the upper end of the heat transfer surface of the first plate (50a). The second upper side region (74a) has a triangular shape that widens from the left end of the partition (97) toward the upper edge (91) of the first plate (50a).

[0079] The ridge portion (80a) of the second upper side region (74a) is inclined upward to the left, and the angle formed by the extension direction of the ridge portion (80a) of the second upper side region (74a) and the horizontal direction is approximately 80°.

[0080] -Heat transfer surface of the second plate- As shown in FIG. 6, the heat transfer surface of the second plate (50b), like the first plate (50a), is divided into an upper region (51b), a lower region (52b), a first guide region (61b), a first lower lateral region (62b), a first lateral region (63b), a first upper lateral region (64b), a second guide region (71b), a second lower lateral region (72b), a second lateral region (73b), and a second upper lateral region (74b).

[0081] The terms "right," "left," "upper," and "lower" used in the description of the heat transfer surface of the second plate (50b) refer to the "right," "left," "upper," and "lower" of the second plate (50b) shown in FIG.

[0082] As described above, the second plate (50b) is the first plate (50a) turned upside down. Therefore, the second plate (50b) has the second guide region (71b), the second lower lateral region (72b), the second lateral region (73b), and the second upper lateral region (74b) formed on the right side of the upper through-hole (95) and the lower through-hole (96). Furthermore, the second plate (50b) has the first guide region (61b), the first lower lateral region (62b), the first lateral region (63b), and the first upper lateral region (64b) formed on the left side of the upper through-hole (95) and the lower through-hole (96).

[0083] - Correspondence between each region of the first plate and each region of the second plate - As described above, the first plates 50a and the second plates 50b are alternately stacked in the plate stack 40. Therefore, in the plate stack 40, the upper region 51a of the first plate 50a overlaps with the upper region 51b of the second plate 50b, and the lower region 52a of the first plate 50a overlaps with the lower region 52b of the second plate 50b.

[0084] As described above, the second plate (50b) is the first plate (50a) turned upside down. Therefore, in the plate stack (40), the first guide region (61a) of the first plate (50a) overlaps with the second guide region (71b) of the second plate (50b), the first side lower region (62a) of the first plate (50a) overlaps with the second side lower region (72b) of the second plate (50b), the first side region (63a) of the first plate (50a) overlaps with the second side region (73b) of the second plate (50b), and the first side upper region (64a) of the first plate (50a) overlaps with the second side upper region (74b) of the second plate (50b). In addition, in the plate stack (40), the second guide region (71a) of the first plate (50a) overlaps with the first guide region (61b) of the second plate (50b), the second lateral lower region (72a) of the first plate (50a) overlaps with the first lateral lower region (62b) of the second plate (50b), the second lateral region (73a) of the first plate (50a) overlaps with the first lateral region (63b) of the second plate (50b), and the second lateral upper region (74a) of the first plate (50a) overlaps with the first lateral upper region (64b) of the second plate (50b).

[0085] In the plate stack 40, the partitions 97 of the first plate 50a and the partitions 97 of the second plate 50b overlap each other. The partitions 97 of the first plate 50a and the partitions 97 of the second plate 50b are joined to each other by brazing or the like over their entire lengths. However, the partitions 97 of the first plate 50a and the partitions 97 of the second plate 50b do not have to be joined to each other.

[0086] -Guide structure- The ridge portion (81a) in the first guide region (61a) of the first plate (50a) and the ridge portion (82a) in the second guide region (71a) are a first ridge portion provided on the first plate (50a) and form a guide structure (100). The ridge portion (81b) in the first guide region (61b) of the second plate (50b) and the ridge portion (82b) in the second guide region (71b) are a second ridge portion provided on the second plate (50b) and form a guide structure (100). The guide structure (100) is a structure for guiding the refrigerant flowing through the refrigerant flow path (41) between the upper through-holes (95) and the lower through-holes (96).

[0087] As shown in Fig. 7, in the plate stack 40, the first guide region 61a of the first plate 50a overlaps with the second guide region 71b of the second plate 50b. The ridge portion 81a of the first guide region 61a of the first plate 50a and the ridge portion 82b of the second guide region 71b of the second plate 50b intersect with each other. In Fig. 7, the ridge portion 81a of the first guide region 61a of the first plate 50a is indicated by a solid line, and the ridge portion 82b of the second guide region 71b of the second plate 50b is indicated by a dashed line.

[0088] The bisector of the obtuse angle formed by the ridge portion (81a) of the first guide region (61a) of the first plate (50a) and the ridge portion (82b) of the second guide region (71b) of the second plate (50b) is defined as the first bisector (L1). The angle between the first bisector (L1) and a vertical line is θ1.

[0089] The bisector of the acute angle formed by the ridge portion (81a) of the first guide region (61a) of the first plate (50a) and the ridge portion (82b) of the second guide region (71b) of the second plate (50b) is defined as the second bisector (L2). The angle between the second bisector (L2) and a vertical line is θ2.

[0090] In the plate stack (40) of this embodiment, the angle θ1 is smaller than the angle θ2 (θ1<θ2). In this plate stack (40), the first bisector (L1) is inclined to the left in Fig. 7. In other words, the first bisector (L1) is inclined so that the higher it goes, the closer it is to the center of the heat transfer plate (50) in the width direction.

[0091] In the plate stack 40, the second guide region 71a of the first plate 50a overlaps with the first guide region 61b of the second plate 50b. The ridge portion 82a of the second guide region 71a of the first plate 50a and the ridge portion 81b of the first guide region 61b of the second plate 50b intersect with each other.

[0092] The angle formed by the bisector of the obtuse angle between the "ridge portion (82a) of the second guide region (71a) of the first plate (50a)" and the "ridge portion (81b) of the first guide region (61b) of the second plate (50b)" and the vertical line is θ1. The angle formed by the bisector of the acute angle between the "ridge portion (82a) of the second guide region (71a) of the first plate (50a)" and the "ridge portion (81b) of the first guide region (61b) of the second plate (50b)" and the vertical line is θ2.

[0093] As described above, the angle θ1 is smaller than the angle θ2 (θ1<θ2). In the plate stack (40) of this embodiment, the bisector of the obtuse angle formed by the "ridge portion (82a) of the second guide region (71a) of the first plate (50a)" and the "ridge portion (81b) of the first guide region (61b) of the second plate (50b)" is inclined so as to approach the center of the heat transfer plate in the width direction as it goes upward.

[0094] -Flow of refrigerant and heat transfer medium in heat exchangers- The flow of the refrigerant and the heat medium in the heat exchanger (10) of this embodiment will be described below. In the heat exchanger (10), the refrigerant and the heat medium exchange heat in the plate stack (40).

[0095] <Refrigerant flow> The refrigerant in a gas-liquid two-phase state that has passed through the expansion valve 208 flows into the heat exchanger 10. The refrigerant flows through the refrigerant inlet 22 into the internal space 21 of the shell 20.

[0096] In the internal space (21) of the shell (20), most of the plate stack (40) is immersed in liquid refrigerant, and the refrigerant flows into the refrigerant flow paths (41) of the plate stack (40). The liquid refrigerant that flows into the refrigerant flow paths (41) comes into contact with the heat transfer plates (50) and absorbs heat from the heat medium flowing through the heat medium flow paths (42), thereby evaporating. The gas refrigerant generated in the refrigerant flow paths (41) flows upward, exits the refrigerant flow paths (41), and passes through the refrigerant outlet (23) to the outside of the shell (20).

[0097] The flow of refrigerant in the refrigerant channel (41) will be described with reference to FIG.

[0098] In the refrigerant flow path (41), the liquid refrigerant evaporates and becomes gaseous refrigerant. The gaseous refrigerant generated in the refrigerant flow path (41) rises due to buoyancy. As a result, an upward flow of refrigerant occurs in the refrigerant flow path (41).

[0099] The refrigerant flow path (41) is separated from the lower communication passage (44) and the upper communication passage (43), through which the heat transfer medium flows. The refrigerant flowing upward through the refrigerant flow path (41) avoids the lower communication passage (44) and the upper communication passage (43). Therefore, unless measures are taken, the refrigerant flows upward through the refrigerant flow path (41) mainly in portions to the sides of the lower communication passage (44) and the upper communication passage (43), and the refrigerant is less likely to flow into the portion between the lower communication passage (44) and the upper communication passage (43).

[0100] In contrast, in the heat-transfer plate (50) of the present embodiment, one guide region (61a, 61b, 71a, 71b) is formed on each side of the lower through-hole (96). In the plate stack (40) of the present embodiment, the first guide region (61a) of the first plate (50a) overlaps with the second guide region (71b) of the second plate (50b), and the second guide region (71a) of the first plate (50a) overlaps with the first guide region (61b) of the second plate (50b).

[0101] In the refrigerant flow path (41), a portion of the refrigerant flowing upward on the right side of the lower communicating passage (44) is guided by the ridge portion (81a) of the first guide region (61a) and the ridge portion (82b) of the second guide region (71b) and flows into the lower communicating passage (44) and the upper communicating passage (43). In the refrigerant flow path (41), a portion of the refrigerant flowing upward on the left side of the lower communicating passage (44) is guided by the ridge portion (82a) of the second guide region (71a) and the ridge portion (81b) of the first guide region (61b) and flows into the lower communicating passage (44) and the upper communicating passage (43). The liquid refrigerant that has flowed into the lower communicating passage (44) and the upper communicating passage (43) of the refrigerant flow path (41) comes into contact with the heat transfer plate (50) and exchanges heat with the heat medium.

[0102] <Flow of heat transfer medium> The heat transfer medium supplied to the heat exchanger (10) flows through the heat transfer medium inlet (24) into the lower communication passages (44) of the plate stack (40) and is distributed to each heat transfer medium flow passage (42).

[0103] 9, the heat medium that has flowed into the heat medium flow path (42) flows from the lower through-hole (96) toward the upper through-hole (95), bypassing the partitions (97) of the heat transfer plate (50). Specifically, the heat medium that has flowed into the heat medium flow path (42) splits into left and right flows toward the side edges (93) of the heat transfer plate (50). Thereafter, the heat medium flows along the side edges (93) of the heat transfer plate (50), around the upper side of the partitions (97), and flows toward the upper through-hole (95).

[0104] While flowing through the heat medium flow paths (42), the heat medium dissipates heat to the refrigerant flowing through the refrigerant flow paths (41). As a result, the temperature of the heat medium decreases. The heat medium cooled in the heat medium flow paths (42) flows from each heat medium flow path (42) into the upper communication path (43), where they join together, and then flows out of the shell (20) through the heat medium outlet (25).

[0105] -Feature (1) of the first embodiment- In the plate-and-shell heat exchanger (10) of this embodiment, a plate stack (40) including a plurality of heat transfer plates (50) is installed in the internal space (21) of the shell (20). The plate stack (40) is formed with a plurality of refrigerant flow paths (41) and a plurality of heat transfer medium flow paths (42). Each heat transfer plate (50) is formed with an upper through-hole (95) and a lower through-hole (96). In the plate stack (40), the upper through-hole (95) of each heat transfer plate (50) forms an upper communication passage (43) that communicates with the heat transfer medium flow path (42). In addition, in the plate stack (40), the lower through-hole (96) of each heat transfer plate (50) forms a lower communication passage (44) that communicates with the heat transfer medium flow path (42). Each heat transfer plate (50) is formed with a guide structure (100) for guiding the refrigerant flowing through the refrigerant flow path (41) between the upper through-hole (95) and the lower through-hole (96).

[0106] In the plate-and-shell heat exchanger (10) of this embodiment, the refrigerant flows into the refrigerant flow paths (41) of the plate stack (40) and evaporates through heat exchange with the heat medium flowing through the heat medium flow paths (42). The gas refrigerant generated in the refrigerant flow paths (41) flows upward due to buoyancy. Therefore, the refrigerant flows generally from bottom to top in the refrigerant flow paths (41).

[0107] In the refrigerant flow path (41), a portion of the refrigerant flowing upward is guided between the upper communicating passage (43) and the lower communicating passage (44) by the guide structure (100). Therefore, the heat transfer plate (50) is in contact with the liquid refrigerant at both the portion between the upper through-holes (95) and the lower through-holes (96) and the outside of this portion, and exchanges heat with the liquid refrigerant. As a result, the amount of heat exchanged between the refrigerant and the heat medium in the shell-and-plate heat exchanger (10) is increased, and the performance of the shell-and-plate heat exchanger (10) is improved.

[0108] -Feature (2) of the first embodiment- The guide structure (100) of the heat transfer plate (50) is composed of a plurality of linear ridges (80a, 80b) that are parallel to one another. The ridges (80a, 80b) are formed by raising the heat transfer plate (50) and bulge toward the refrigerant flow path (41). Therefore, the direction of the refrigerant flow in the refrigerant flow path (41) is changed by the ridges (80a, 80b) that constitute the guide structure (100).

[0109] -Feature (3) of the first embodiment- In the plate stack (40) of this embodiment, the guide regions (61a, 61b, 71a, 71b) of the heat transfer plates (50) overlap in the stacking direction of the heat transfer plates (50). The refrigerant flowing through the refrigerant flow paths (41) of the plate stack (40) is guided between the upper communicating passage (43) and the lower communicating passage (44) by the ridge portions (80a, 80b) included in the overlapping guide regions (61a, 61b, 71a, 71b).

[0110] -Feature (4) of the first embodiment- In each heat transfer plate (50) of this embodiment, the guide regions (61a, 61b, 71a, 71b) are arranged from the portion between the upper through-hole (95) and the lower through-hole (96) to the outside of this portion. Therefore, in the refrigerant flow path (41) of the plate stack (40), part of the refrigerant flowing outside the portion between the upper communicating passage (43) and the lower communicating passage (44) is guided to the portion by the ridge portions (80a, 80b) included in the guide regions (61a, 61b, 71a, 71b).

[0111] -Feature (5) of the first embodiment- In the plate stack (40) of this embodiment, the refrigerant flowing through the refrigerant flow path (41) is guided to the area between the upper communicating passage (43) and the lower communicating passage (44) by the ridge portions (80a, 80b) of the guide regions (61a, 61b, 71a, 71b) provided on the right and left sides, respectively, of the lower communicating passage (44).

[0112] -Feature (6) of the first embodiment- In each heat transfer plate (50) of this embodiment, the guide regions (61a, 61b, 71a, 71b) extend obliquely downward from a portion between the upper through-hole (95) and the lower through-hole (96). Therefore, the refrigerant flowing upward in a portion of the refrigerant flow path (41) on the side of the lower communicating passage (44) is guided to a portion between the upper communicating passage (43) and the lower communicating passage (44) by the ridge portions (80a, 80b) included in the guide regions (61a, 61b, 71a, 71b).

[0113] -Feature (7) of the first embodiment- In the heat exchanger (10) of this embodiment, the refrigerant flowing through the portion of the refrigerant flow path (41) sandwiched between the guide regions (61a, 61b, 71a, 71b) of the heat transfer plates (50) tends to flow in the direction along the bisector (L1) of the obtuse angle formed by the first ridge portions (81a, 82a) and the second ridge portions (82b, 81b) and the bisector (L2) of the acute angle formed by the first ridge portions (81a, 82a) and the second ridge portion (812), whichever bisector forms the smaller acute angle with the vertical direction. This is because buoyancy acts vertically upward on the gas refrigerant flowing through the refrigerant flow path (41).

[0114] In the heat exchanger (10) of this embodiment, the first bisector (L1), which is the bisector that forms a smaller acute angle with the vertical direction, is inclined so that the higher it goes, the closer it is to the center in the width direction of the heat transfer plate (50). Therefore, the refrigerant flowing through the portion of the refrigerant flow path (41) sandwiched between the guide regions (61a, 61b, 71a, 71b) of each heat transfer plate (50) is guided between the upper communicating passage (43) and the lower communicating passage (44) by the ridge portions (81a, 82a, 81b, 82b) of the guide regions (61a, 61b, 71a, 71b).

[0115] Second Embodiment A second embodiment will be described. The refrigeration system (200) of this embodiment differs from the first embodiment in the configuration of the shell-and-plate heat exchanger (10). Here, differences between the shell-and-plate heat exchanger (10) of this embodiment and the first embodiment will be described.

[0116] The plate-and-shell heat exchanger (10) of this embodiment differs from that of the first embodiment in the heat transfer plates (50) constituting the plate stack (40). The heat transfer plates (50) of this embodiment differ from those of the first embodiment in the configuration of the heat transfer surface. The outer shape of the heat transfer plates (50) of this embodiment is the same as that of the first embodiment. Furthermore, in the heat transfer plates (50) of this embodiment, the shapes and positions of the upper through-holes (95), lower through-holes (96), upper peripheral edge portion (95a), and lower peripheral edge portion (96a) are the same as those of the first embodiment.

[0117] -Heat transfer surface of the first plate- 10, the heat transfer surface of the first plate (50a) is divided into an upper region (51a), a lower region (52a), a middle guide region (53a), a first lower lateral region (62a), a first lateral region (63a), a first connecting region (65a), a first upper lateral region (64a), a second lower lateral region (72a), a second lateral region (73a), a second connecting region (75a), and a second upper lateral region (74a). A plurality of ridge portions (80a) are formed in each of these regions (51a-53a, 62a-65a, 72a-75a). No partition portions (97) are formed on the first plate (50a).

[0118] As such, the first plate (50a) of this embodiment differs from the first plate (50a) of embodiment 1 in that the first guide region (61a), the second guide region (71a), and the partition portion (97) are omitted, and an intermediate guide region (53a), a first connection region (65a), and a second connection region (75a) are provided.

[0119] Note that the terms "right," "left," "upper," and "lower" used in the description of the heat transfer surface of the first plate (50a) refer to the "right," "left," "upper," and "lower" of the first plate (50a) shown in Fig. 10. The angle values ​​shown in this description are merely examples.

[0120] <Intermediate guide area> The intermediate guide region (53a) is provided in place of the partition portion (97) of the first embodiment. The intermediate guide region (53a) is a horizontally long rectangular region. The intermediate guide region (53a) is located near the center of the first plate (50a) in the up-down direction. The intermediate guide region (53a) crosses the portion of the first plate (50a) sandwiched between the upper through-hole (95) and the lower through-hole (96) (the dotted region in FIG. 13). The length (length in the left-right direction) of the intermediate guide region (53a) is approximately equal to the length of the partition portion (97) of the first embodiment. The width (length in the up-down direction) of the intermediate guide region (53a) is wider than the width of the partition portion (97) of the first embodiment.

[0121] The ridge portion (83a) formed in the intermediate guide region (53a) is inclined upward to the left, and the angle formed between the extension direction of the ridge portion (83a) of the intermediate guide region (53a) and the horizontal direction is approximately 30°.

[0122] <Top area> The upper region (51a) is a rectangular region located above the intermediate guide region (53a). The upper region (51a) is formed from the intermediate guide region (53a) to the upper end of the heat transfer surface of the first plate (50a). The length of the long side of the upper region (51a) is approximately equal to the length of the intermediate guide region (53a). The upper through-hole (95) is formed in the center of the upper region (51a) in the left-right direction.

[0123] The ridge portion 80a formed in the upper region 51a is inclined upward to the left, and the angle formed by the extension direction of the ridge portion 80a in the upper region 51a and the horizontal direction is approximately 45°.

[0124] <Lower area> The lower region (52a) is a rectangular region located below the intermediate guide region (53a). The lower region (52a) is formed from the intermediate guide region (53a) to the lower end of the heat transfer surface of the first plate (50a). The length of the long side of the lower region (52a) is approximately equal to the length of the intermediate guide region (53a). The lower through-hole (96) is formed in the center of the lower region (52a) in the left-right direction.

[0125] The ridge portion 80a formed in the lower region 52a is inclined upward to the left, and the angle formed by the extension direction of the ridge portion 80a in the lower region 52a and the horizontal direction is approximately 45°.

[0126] <First lateral lower area> The first lower side region (62a) is located to the right of the lower region (52a). The first lower side region (62a) is formed from the right end of the lower region (52a) to the side end of the heat transfer surface of the first plate (50a). The first lower side region (62a) has a triangular shape that widens from the right end of the intermediate guide region (53a) toward the side edge (93) of the first plate (50a).

[0127] The ridge portion (80a) of the first lower side region (62a) is inclined upward to the left, and the angle formed between the extension direction of the ridge portion (80a) of the first lower side region (62a) and the horizontal direction is approximately 85°.

[0128] <First lateral area> The first side region (63a) is a region located above the first lower side region (62a). The first side region (63a) is formed from the right end of the intermediate guide region (53a) to the side end of the heat transfer surface of the first plate (50a). The first side region (63a) has a triangular shape that widens from the right end of the intermediate guide region (53a) toward the side edge (93) of the first plate (50a).

[0129] The ridge portion (80a) of the first side region (63a) is inclined upward to the right, and the angle formed between the extension direction of the ridge portion (80a) of the first side region (63a) and the horizontal direction is approximately 10°.

[0130] <First connection area> The first connection region (65a) is a region located above the first side region (63a). The first connection region (65a) is formed from the right end of the intermediate guide region (53a) to the upper right corner of the heat transfer surface of the first plate (50a). The first connection region (65a) has a triangular shape that widens from the right end of the intermediate guide region (53a) toward the upper edge (91) of the first plate (50a).

[0131] The ridge portion (80a) of the first connection region (65a) is inclined upward to the left, and the angle formed between the extension direction of the ridge portion (80a) of the first connection region (65a) and the horizontal direction is approximately 10°.

[0132] <First lateral upper area> The first upper side region (64a) is located to the right of the upper region (51a) and is a region sandwiched between the upper region (51a) and the first connection region (65a). The first upper side region (64a) is formed from the right end of the intermediate guide region (53a) to the upper end of the heat transfer surface of the first plate (50a). The first upper side region (64a) has a triangular shape that widens from the right end of the intermediate guide region (53a) toward the upper edge (91) of the first plate (50a).

[0133] The ridge portion (80a) of the first upper side region (64a) is inclined upward to the right, and the angle formed by the extension direction of the ridge portion (80a) of the first upper side region (64a) and the horizontal direction is approximately 45°.

[0134] <Second lateral lower area> The second lower side region (72a) is located to the left of the lower region (52a). The second lower side region (72a) is formed from the left end of the lower region (52a) to the side end of the heat transfer surface of the first plate (50a). The second lower side region (72a) has a triangular shape that widens from the left end of the intermediate guide region (53a) toward the side edge (93) of the first plate (50a).

[0135] The ridge portion (80a) of the second lower side region (72a) is inclined upward to the right, and the angle formed between the extension direction of the ridge portion (80a) of the second lower side region (72a) and the horizontal direction is approximately 5°.

[0136] <Second lateral area> The second side region (73a) is a region located above the second lower side region (72a). The second side region (73a) is formed from the left end of the intermediate guide region (53a) to the side end of the heat transfer surface of the first plate (50a). The second side region (73a) has a triangular shape that widens from the left end of the intermediate guide region (53a) toward the side edge (93) of the first plate (50a).

[0137] The ridge portion (80a) of the second side region (73a) is inclined upward to the right, and the angle formed between the extension direction of the ridge portion (80a) of the second side region (73a) and the horizontal direction is approximately 80°.

[0138] <Second connection area> The second connection region (75a) is a region located above the second side region (73a). The second connection region (75a) is formed from the left end of the intermediate guide region (53a) to the upper left corner of the heat transfer surface of the first plate (50a). The second connection region (75a) has a triangular shape that widens from the left end of the intermediate guide region (53a) toward the upper edge (91) of the first plate (50a).

[0139] The ridge portion (80a) of the second connection region (75a) is inclined upward to the left, and the angle formed between the extension direction of the ridge portion (80a) of the first connection region (65a) and the horizontal direction is approximately 70°.

[0140] <Second lateral upper area> The second upper side region (74a) is located to the left of the upper region (51a) and is a region sandwiched between the upper region (51a) and the second connection region (75a). The second upper side region (74a) is formed from the left end of the intermediate guide region (53a) to the upper end of the heat transfer surface of the first plate (50a). The second upper side region (74a) has a triangular shape that widens from the left end of the intermediate guide region (53a) toward the upper edge (91) of the first plate (50a).

[0141] The ridge portion (80a) of the second upper side region (74a) is inclined upward to the right, and the angle formed by the extension direction of the ridge portion (80a) of the second upper side region (74a) and the horizontal direction is approximately 70°.

[0142] -Heat transfer surface of the second plate- As shown in FIG. 11, the heat transfer surface of the second plate (50b), like the first plate (50a), is divided into an upper region (51b), a lower region (52b), an intermediate guide region (53b), a first lateral lower region (62b), a first lateral region (63b), a first connection region (65b), a first lateral upper region (64b), a second lateral lower region (72b), a second lateral region (73b), a second connection region (75b), and a second lateral upper region (74b).

[0143] The terms "right," "left," "upper," and "lower" used in the description of the heat transfer surface of the second plate (50b) refer to the "right," "left," "upper," and "lower" of the second plate (50b) shown in FIG.

[0144] As in the first embodiment, the second plate (50b) is formed by inverting the first plate (50a). Therefore, the second plate (50b) has a second lower lateral region (72b), a second lower lateral region (73b), a second connecting region (75b), and a second upper lateral region (74b) on the right side of the upper region (51b), the lower region (52b), and the intermediate guide region (53b). The second plate (50b) also has a first lower lateral region (62b), a first lower lateral region (63b), a first connecting region (65b), and a first upper lateral region (64b) on the left side of the upper region (51b), the lower region (52b), and the intermediate guide region (53b).

[0145] - Correspondence between each region of the first plate and each region of the second plate - As described above, the first plates 50a and the second plates 50b are alternately stacked in the plate stack 40. Therefore, in the plate stack 40, the upper region 51a of the first plate 50a overlaps with the upper region 51b of the second plate 50b, the lower region 52a of the first plate 50a overlaps with the lower region 52b of the second plate 50b, and the intermediate guide region 53a of the first plate 50a overlaps with the intermediate guide region 53b of the second plate 50b.

[0146] As described above, the second plate (50b) is the first plate (50a) turned upside down. Therefore, in the plate stack (40), the first lower side region (62a) of the first plate (50a) overlaps with the second lower side region (72b) of the second plate (50b), the first side region (63a) of the first plate (50a) overlaps with the second side region (73b) of the second plate (50b), the first connection region (65a) of the first plate (50a) overlaps with the second connection region (75b) of the second plate (50b), and the first upper side region (64a) of the first plate (50a) overlaps with the second upper side region (74b) of the second plate (50b). In addition, in the plate stack (40), the second lateral lower region (72a) of the first plate (50a) overlaps with the first lateral lower region (62b) of the second plate (50b), the second lateral region (73a) of the first plate (50a) overlaps with the first lateral region (63b) of the second plate (50b), the second connection region (75a) of the first plate (50a) overlaps with the first connection region (65b) of the second plate (50b), and the second lateral upper region (74a) of the first plate (50a) overlaps with the first lateral upper region (64b) of the second plate (50b).

[0147] -Guide structure- The ridge portion (83a) of the intermediate guide region (53a) of the first plate (50a) is a first ridge portion provided on the first plate (50a) and constitutes a guide structure (100). The ridge portion (83b) of the intermediate guide region (53b) of the second plate (50b) is a second ridge portion provided on the second plate (50b) and constitutes a guide structure (100). The guide structure (100) is a structure for guiding the refrigerant flowing through the refrigerant flow path (41) between the upper through-holes (95) and the lower through-holes (96).

[0148] As shown in Figure 12, in the plate stack 40, the intermediate guide region 53a of the first plate 50a overlaps with the intermediate guide region 53b of the second plate 50b. The ridge portion 83a of the intermediate guide region 53a of the first plate 50a and the ridge portion 83b of the intermediate guide region 53b of the second plate 50b intersect with each other. In Figure 12, the ridge portion 83a of the intermediate guide region 53a of the first plate 50a is shown by a solid line, and the ridge portion 83b of the intermediate guide region 53b of the second plate 50b is shown by a dashed line.

[0149] As described above, in the intermediate guide region 53a of the first plate 50a, the angle between the extension direction of the ridge portion 83a and the horizontal direction is approximately 30°. Therefore, the acute angle between the extension direction of the ridge portion 83a and the horizontal direction is 45° or less. Furthermore, the acute angle between the extension direction of the ridge portion 83a and the horizontal direction is smaller than the acute angle between the extension direction of the ridge portion 80a of the lower region 52a and the horizontal direction.

[0150] As described above, the second plate (50b) is the first plate (50a) turned upside down. Therefore, in the second plate (50b), the acute angle formed between the extension direction of the ridge portion (83b) of the intermediate guide region (53b) and the horizontal direction is 45° or less, which is smaller than the acute angle formed between the extension direction of the ridge portion (80b) of the lower region (52b) and the horizontal direction.

[0151] -Flow of refrigerant and heat transfer medium in heat exchangers- The flow of the refrigerant and the heat medium in the heat exchanger (10) of this embodiment will be described below. In the heat exchanger (10), the refrigerant and the heat medium exchange heat in the plate stack (40).

[0152] <Refrigerant flow> As in the first embodiment, the refrigerant that has flowed into the internal space (21) of the shell (20) through the refrigerant inlet (22) flows into the refrigerant flow paths (41) of the plate stack (40) and evaporates by absorbing heat from the heat medium flowing through the heat medium flow paths (42). The gas refrigerant generated in the refrigerant flow paths (41) flows upward, exits the refrigerant flow paths (41), and passes through the refrigerant outlet (23) to the outside of the shell (20).

[0153] The flow of refrigerant in the refrigerant flow path (41) will be described with reference to FIG.

[0154] In the refrigerant flow path (41), the liquid refrigerant evaporates and becomes gaseous refrigerant. The gaseous refrigerant generated in the refrigerant flow path (41) rises due to buoyancy. As a result, an upward flow of refrigerant occurs in the refrigerant flow path (41).

[0155] The refrigerant flowing upward along the side of the lower communicating passage (44) hits the ridge portions (83a, 83b) of the intermediate guide regions (53a, 53b) of the heat transfer plate (50) and diffuses to the left and right. Therefore, in the refrigerant flow path (41), part of the refrigerant flowing upward along the side of the lower communicating passage (44) is guided by the ridge portions (83a, 83b) of the intermediate guide regions (53a, 53b) and flows into the lower communicating passage (44) and the upper communicating passage (43). The liquid refrigerant that has flowed into the lower communicating passage (44) and the upper communicating passage (43) of the refrigerant flow path (41) comes into contact with the heat transfer plate (50) and exchanges heat with the heat medium.

[0156] <Flow of heat transfer medium> The heat medium supplied to the heat exchanger 10 flows through the heat medium inlet 24 into the lower communication passages 44 of the plate stack 40 and is distributed to each heat medium flow path 42. The heat medium that flows into the heat medium flow path 42 flows from the lower through-holes 96 toward the upper through-holes 95. The flow of the heat medium hits the ridge portions 83a, 83b of the intermediate guide regions 53a, 53b of the heat transfer plate 50 and diffuses to the left and right. The heat medium then flows along the side edges 93 of the heat transfer plate 50, wraps around to the upper sides of the intermediate guide regions 53a, 53b, and flows toward the upper through-holes 95.

[0157] As in the first embodiment, the heat medium is cooled while flowing through the heat medium flow paths (42). The heat medium that has flowed from each heat medium flow path (42) into the upper communication passage (43) flows out of the shell (20) through the heat medium outlet (25).

[0158] -Feature (1) of the second embodiment- In the heat exchanger (10) of this embodiment, the guide areas (53a, 53b) provided in each heat transfer plate (50) extend straight in the left-right direction and cross the portion between the upper through-hole (95) and the lower through-hole (96). The refrigerant flowing through the refrigerant flow path (41) is guided between the upper communicating passage (43) and the lower communicating passage (44) by the guide areas (53a, 53b).

[0159] -Feature (2) of the second embodiment- In the heat exchanger (10) of this embodiment, the ridge portions (83a, 83b) included in the guide regions (53a, 53b) that cross between the upper through-hole (95) and the lower through-hole (96) form an acute angle of 45° or less between the extension direction of the ridge portions (83a, 83b) and the horizontal direction. Therefore, in the refrigerant flow path (41), the refrigerant that flows upward and reaches the guide regions (53a, 53b) is guided between the upper communicating passage (43) and the lower communicating passage (44) by the ridge portions (83a, 83b) included in the guide regions (53a, 53b).

[0160] -Modification of the second embodiment- In the heat exchanger (10) of this embodiment, a partition (97) may be formed on each of the first plate (50a) and the second plate (50b).

[0161] As shown in FIGS. 14 and 15 , in each of the first plate 50a and the second plate 50b, the partition portion 97 is a linear region located near the center of the intermediate guide region 53a, 53b in the up-down direction. The partition portion 97 is formed from the left end to the right end of the intermediate guide region 53a, 53b and traverses the intermediate guide region 53a, 53b. As in the first embodiment, the partition portion 97 of the first plate 50a bulges out toward the front surface of the first plate 50a, and the partition portion 97 of the second plate 50b bulges out toward the back surface of the second plate 50b. As in the first embodiment, the partition portion 97 of the first plate 50a and the partition portion 97 of the second plate 50b that are adjacent to each other are joined by brazing or the like.

[0162] In the heat exchanger (10) of this modified example, the heat medium that has flowed into the heat medium flow path (42) flows from the lower through-holes (96) toward the upper through-holes (95), bypassing the partitions (97) of the heat transfer plate (50). Specifically, the heat medium that has flowed into the heat medium flow path (42) splits into left and right flows toward the side edges (93) of the heat transfer plate (50). Thereafter, the heat medium flows along the side edges (93) of the heat transfer plate (50), around the upper side of the partitions (97), and flows toward the upper through-holes (95).

[0163] Third Embodiment A third embodiment will be described. The refrigeration system (200) of this embodiment differs from the first embodiment in the configuration of the shell-and-plate heat exchanger (10). Here, differences between the shell-and-plate heat exchanger (10) of this embodiment and the first embodiment will be described.

[0164] The shell-and-plate heat exchanger (10) of this embodiment differs from that of the first embodiment in the heat transfer plates (50) constituting the plate stack (40). The heat transfer plates (50) of this embodiment differ from those of the first embodiment in the configuration of the heat transfer surface. The outer shape of the heat transfer plates (50) of this embodiment is the same as that of the first embodiment. Furthermore, in the heat transfer plates (50) of this embodiment, the shapes and positions of the upper through-holes (95), lower through-holes (96), upper peripheral edge portion (95a), and lower peripheral edge portion (96a) are the same as those of the first embodiment.

[0165] -Heat transfer surface of the first plate- 16, the heat transfer surface of the first plate (50a) is divided into an upper region (51a), a lower region (52a), a middle guide region (53a), a first guide region (61a), a first lower lateral region (62a), a first lateral region (63a), a first upper lateral region (64a), a second guide region (71a), a second lower lateral region (72a), a second lateral region (73a), and a second upper lateral region (74a). A plurality of ridges (80a) are formed in each of these regions (51a to 53a, 61a to 64a, 71a to 74a).

[0166] Note that the terms "right," "left," "upper," and "lower" used in the description of the heat transfer surface of the first plate (50a) refer to the "right," "left," "upper," and "lower" of the first plate (50a) shown in FIG. 16. The angle values ​​used in this description are merely examples. The first plate (50a) does not have a partition (97).

[0167] <Intermediate guide area> The intermediate guide region (53a) is provided in place of the partition portion (97) of the first embodiment. The intermediate guide region (53a) is a horizontally long rectangular region. The intermediate guide region (53a) is located near the center of the first plate (50a) in the vertical direction. The length (length in the left-right direction) of the intermediate guide region (53a) is approximately equal to the length of the partition portion (97) of the first embodiment. The width (length in the up-down direction) of the intermediate guide region (53a) is wider than the width of the partition portion (97) of the first embodiment.

[0168] The ridges (83a) formed in the intermediate guide region (53a) are inclined upward to the right, and the angle between the extension direction of the ridges (83a) in the intermediate guide region (53a) and the horizontal direction is approximately 5°.

[0169] <Top area> The upper region (51a) is a rectangular region located above the intermediate guide region (53a). The upper region (51a) is formed from the intermediate guide region (53a) to the upper end of the heat transfer surface of the first plate (50a). The length of the long side of the upper region (51a) is approximately equal to the length of the intermediate guide region (53a). The upper through-hole (95) is formed in the center of the upper region (51a) in the left-right direction.

[0170] The ridge portion 80a formed in the upper region 51a is inclined upward to the left, and the angle formed by the extension direction of the ridge portion 80a in the upper region 51a and the horizontal direction is approximately 45°.

[0171] <First and second guide areas> The first guide region (61a) and the second guide region (71a) are located below the intermediate guide region (53a). The shapes and positions of the first guide region (61a) and the second guide region (71b) are the same as those in the first embodiment. The shapes of the ridge portion (81a) of the first guide region (61a) and the ridge portion (82a) of the second guide region (71a) are the same as those in the first embodiment.

[0172] <1st and 2nd lateral lower area> The first lateral lower region (62a) and the second lateral lower region (72a) are located below the intermediate guide region (53a). The shapes and positions of the first lateral lower region (62a) and the second lateral lower region (72a) are the same as those in the first embodiment. The shapes of the ridge portions (80a) of the first lateral lower region (62a) and the second lateral lower region (72a) are the same as those in the first embodiment.

[0173] <1st and 2nd lateral areas> The first side region (63a) is located to the right of the intermediate guide region (53a). The second side region (73a) is located to the left of the intermediate guide region (53a). The shapes and positions of the first side region (63a) and the second side region (73a) are the same as those in the first embodiment. The shapes of the ridge portions (80a) of the first side region (63a) and the second side region (73a) are the same as those in the first embodiment.

[0174] <1st and 2nd lateral upper areas> The first upper lateral region (64a) is located to the right of the upper region (51a) and the intermediate guide region (53a). The second upper lateral region (74a) is located to the left of the upper region (51a) and the intermediate guide region (53a). The shapes and positions of the first upper lateral region (64a) and the second upper lateral region (74a) are the same as those in the first embodiment. The shapes of the ridge portion (80a) of the first upper lateral region (64a) and the ridge portion (80a) of the second upper lateral region (74a) are the same as those in the first embodiment.

[0175] -Heat transfer surface of the second plate- As shown in Figure 17, the heat transfer surface of the second plate (50b), like the first plate (50a), is divided into an upper region (51b), a lower region (52b), an intermediate guide region (53b), a first guide region (61b), a first lower lateral region (62b), a first lateral region (63b), a first upper lateral region (64b), a second guide region (71b), a second lower lateral region (72b), a second lateral region (73b), and a second upper lateral region (74b).

[0176] The terms "right," "left," "top," and "bottom" used in the description of the heat transfer surface of the second plate (50b) refer to the "right," "left," "top," and "bottom" of the second plate (50b) shown in FIG.

[0177] As in the first embodiment, the second plate (50b) is formed by inverting the first plate (50a). Therefore, the second plate (50b) has a second guide region (71b), a second lower lateral region (72b), a second lateral region (73b), and a second upper lateral region (74b) formed on the right side of the upper through-hole (95) and the lower through-hole (96). Furthermore, the second plate (50b) has a first guide region (61b), a first lower lateral region (62b), a first lateral region (63b), and a first upper lateral region (64b) formed on the left side of the upper through-hole (95) and the lower through-hole (96).

[0178] - Correspondence between each region of the first plate and each region of the second plate - In the plate stack 40, the intermediate guide region 53a of the first plate 50a overlaps the intermediate guide region 53b of the second plate 50b. The correspondence between the other regions 51a, 52a, 61a to 64a, 71a to 74a of the first plate 50a and the other regions 51b, 52b, 61b to 64b, 71b to 74b of the second plate 50b is the same as in the first embodiment.

[0179] -Guide structure- In the first plate (50a) of this embodiment, the ridge portion (81a) in the first guide region (61a), the ridge portion (82a) in the second guide region (71a), and the ridge portion (83a) in the intermediate guide region (53a) form a guide structure (100). In the second plate (50b), the ridge portion (81b) in the first guide region (61b), the ridge portion (82b) in the second guide region (71b), and the ridge portion (83b) in the intermediate guide region (53b) form a guide structure (100).

[0180] In the plate stack (40) of this embodiment, as in the first embodiment, the first bisector (L1), which is the bisector of the obtuse angle formed by the "ridge portion (81a) of the first guide region (61a) of the first plate (50a)" and the "ridge portion (82b) of the second guide region (71b) of the second plate (50b)," is inclined so as to approach the center in the width direction of the heat transfer plate (50) the higher it goes. Furthermore, in the plate stack (40) of this embodiment, as in the first embodiment, the first bisector (L1), which is the bisector of the obtuse angle formed by the "ridge portion (82a) of the second guide region (71b) of the first plate (50a)" and the "ridge portion (81b) of the first guide region (61b) of the second plate (50b)," is inclined so as to approach the center in the width direction of the heat transfer plate (50) the higher it goes.

[0181] As described above, in the intermediate guide region 53a of the first plate 50a, the angle between the extension direction of the ridge portion 83a and the horizontal direction is approximately 5°. Therefore, the acute angle between the extension direction of the ridge portion 83a and the horizontal direction is 45° or less.

[0182] As in the first embodiment, the second plate (50b) is the first plate (50a) turned upside down. Therefore, in the second plate (50b), the acute angle between the extension direction of the ridge portion (83b) of the intermediate guide region (53b) and the horizontal direction is 45° or less.

[0183] -Flow of refrigerant and heat transfer medium in heat exchangers- The flow of the refrigerant and the heat medium in the heat exchanger (10) of this embodiment will be described below. In the heat exchanger (10), the refrigerant and the heat medium exchange heat in the plate stack (40).

[0184] <Refrigerant flow> As in the first embodiment, the refrigerant that has flowed into the internal space (21) of the shell (20) through the refrigerant inlet (22) flows into the refrigerant flow paths (41) of the plate stack (40) and evaporates by absorbing heat from the heat medium flowing through the heat medium flow paths (42). The gas refrigerant generated in the refrigerant flow paths (41) flows upward, exits the refrigerant flow paths (41), and passes through the refrigerant outlet (23) to the outside of the shell (20).

[0185] The flow of refrigerant in the refrigerant flow path (41) will be described. In the refrigerant flow path (41), liquid refrigerant evaporates to become gas refrigerant. The gas refrigerant generated in the refrigerant flow path (41) rises due to buoyancy. Therefore, a flow of refrigerant from bottom to top occurs in the refrigerant flow path (41).

[0186] In the refrigerant flow path (41), part of the refrigerant flowing upward on the right side of the lower communicating passage (44) is guided by the ridge portion (81a) of the first guide region (61a) of the first plate (50a) and the ridge portion (82b) of the second guide region (71b) of the second plate (50b), and flows into the lower communicating passage (44) and the upper communicating passage (43). In addition, in the refrigerant flow path (41), part of the refrigerant flowing upward on the left side of the lower communicating passage (44) is guided by the ridge portion (82a) of the second guide region (71a) of the first plate (50a) and the ridge portion (81b) of the first guide region (61b) of the second plate (50b), and flows into the lower communicating passage (44) and the upper communicating passage (43).

[0187] Furthermore, the refrigerant flowing upward along the side of the lower communicating passage (44) hits the ridge portions (83a, 83b) of the intermediate guide regions (53a, 53b) and diffuses to the left and right. Therefore, in the refrigerant flow path (41), part of the refrigerant flowing upward along the side of the lower communicating passage (44) is guided by the ridge portions (83a, 83b) of the intermediate guide regions (53a, 53b) and flows into the lower communicating passage (44) and the upper communicating passage (43).

[0188] <Flow of heat transfer medium> The heat medium supplied to the heat exchanger 10 flows through the heat medium inlet 24 into the lower communication passages 44 of the plate stack 40 and is distributed to each heat medium flow path 42. The heat medium that flows into the heat medium flow path 42 flows from the lower through-holes 96 toward the upper through-holes 95. The flow of the heat medium hits the ridge portions 83a, 83b of the intermediate guide regions 53a, 53b of the heat transfer plate 50 and diffuses to the left and right. The heat medium then flows along the side edges 93 of the heat transfer plate 50, wraps around to the upper sides of the intermediate guide regions 53a, 53b, and flows toward the upper through-holes 95.

[0189] As in the first embodiment, the heat medium is cooled while flowing through the heat medium flow paths (42). The heat medium that has flowed from each heat medium flow path (42) into the upper communication passage (43) flows out of the shell (20) through the heat medium outlet (25).

[0190] -Modification of the third embodiment- In the heat exchanger of this embodiment, a partition (97) may be formed on each of the first plate (50a) and the second plate (50b).

[0191] As shown in FIGS. 18 and 19 , in each of the first plate (50a) and the second plate (50b), the partition portion (97) is a linear region located near the center in the up-down direction of the intermediate guide region (53a, 53b). The partition portion (97) is formed from the left end to the right end of the intermediate guide region (53a, 53b) and traverses the intermediate guide region (53a, 53b). As in the first embodiment, the partition portion (97) in the first plate (50a) bulges out toward the front surface of the first plate (50a), and the partition portion (97) in the second plate (50b) bulges out toward the back surface of the second plate (50b). As in the first embodiment, the partition portion (97) of the adjacent first plate (50a) and the partition portion (97) of the adjacent second plate (50b) are joined by brazing or the like.

[0192] In the heat exchanger (10) of this modified example, the heat medium that has flowed into the heat medium flow path (42) flows from the lower through-holes (96) toward the upper through-holes (95), bypassing the partitions (97) of the heat transfer plate (50). Specifically, the heat medium that has flowed into the heat medium flow path (42) splits into left and right flows toward the side edges (93) of the heat transfer plate (50). Thereafter, the heat medium flows along the side edges (93) of the heat transfer plate (50), around the upper side of the partitions (97), and flows toward the upper through-holes (95).

[0193] Other Embodiments -First Modification- In the heat exchanger (10) of embodiment 1, embodiment 3, or the modified example of embodiment 3, a plurality of guide regions (61a, 61b, 71a, 71b) may be formed on the right and left sides of the lower through-hole (96) in each heat transfer plate (50).

[0194] -Second modified example- In the heat exchanger (10) of the second embodiment, the modified example of the second embodiment, the third embodiment, or the modified example of the third embodiment, the shape of the intermediate guide regions (53a, 53b) formed on each heat transfer plate (50) is not limited to a shape extending straight in the left-right direction. The shape of the intermediate guide regions (53a, 53b) may be, for example, a broken line shape or a curved line shape.

[0195] -Third Modification- In the heat exchanger (10) of the first embodiment, the modified example of the second embodiment, or the modified example of the third embodiment, the shape of the partitions (97) formed on each heat transfer plate (50) is not limited to a shape extending straight in the left-right direction. The shape of the partitions (97) may be, for example, a broken line or a curved line.

[0196] -Fourth Modification- In the heat exchanger (10) of each of the above embodiments, the upper communication passages (43) of the plate stack (40) may be connected to the heat medium inlet (24), and the lower communication passages (44) of the plate stack (40) may be connected to the heat medium outlet (25). In this case, in the heat medium flow passages (42) of the plate stack (40), the heat medium flows in through the upper through-holes (95) of the heat transfer plates (50) and flows out through the lower through-holes (96) of the heat transfer plates (50).

[0197] Although the embodiments and modifications have been described above, it will be understood that various modifications in form and detail are possible without departing from the spirit and scope of the claims. Furthermore, elements of the above embodiments, modifications, and other embodiments may be combined or substituted as appropriate. Furthermore, the terms "first," "second," "third," etc. in the specification and claims are used to distinguish the terms to which these terms are attached, and do not limit the number or order of the terms. [Industrial Applicability]

[0198] As described above, the present disclosure is useful for a shell-and-plate heat exchanger and a refrigeration device. [Explanation of symbols]

[0199] 10. Shell and plate heat exchanger 20 shells 21 Interior Space 40 Plate stack 41 refrigerant flow path 42 Heat transfer medium flow path 43 Upper communication path 44 Lower communication path 50 Heat Transfer Plate 50a 1st Plate 50b Second Plate 53a, 53b Intermediate guide area (guide area) 61a, 61b First guide area (guide area) 71a, 71b Second guide area (guide area) 80a Ridge part (of the first plate) 80b Ridge part (of the second plate) 81a: Ridge portion (first ridge portion) (of the first guide region of the first plate) 82a: Ridge portion (first ridge portion) (of the second guide region of the first plate) 81b Ridge portion (second ridge portion) (of the first guide region of the second plate) 82b (second ridge portion) (second guide region of second plate) 83a: Ridge portion (first ridge portion) (in the intermediate guide region of the first plate) 83b Ridge portion (second ridge portion) (second plate intermediate guide region) 95 Upper through hole 96 Lower through hole 100 Guide structure 200 Refrigeration equipment 205 Refrigerant circuit

Claims

1. a shell (20) forming an interior space (21); a plate stack (40) having a plurality of heat transfer plates (50) stacked in a transverse direction and joined to one another, the plate stack (40) being accommodated in the internal space (21) of the shell (20); The plate stack (40) is formed with a plurality of refrigerant flow paths (41) communicating with the internal space (21) of the shell (20) and through which a refrigerant flows, and a plurality of heat medium flow paths (42) isolated from the internal space (21) of the shell (20) and through which a heat medium flows, the plurality of refrigerant flow paths being adjacent to each other with the heat transfer plate (50) interposed therebetween, a shell-and-plate heat exchanger (10) that evaporates a refrigerant in the refrigerant flow path (41) of the plate stack (40), Each of the plurality of heat transfer plates (50) is formed with an upper through-hole (95) and a lower through-hole (96) that are arranged vertically and spaced apart from each other, In the plate stack (40), The upper through-holes (95) of the plurality of heat transfer plates (50) form upper communication passages (43) that communicate with the heat medium passage (42) and are isolated from the refrigerant passage (41), and a lower communication passage (44) communicating with the heat medium flow passage (42) and isolated from the refrigerant flow passage (41) is formed by the lower through-holes (96) of the plurality of heat transfer plates (50); Each of the plurality of heat transfer plates (50) is formed with a guide structure (100) for guiding the refrigerant flowing through the refrigerant flow path (41) between the upper through-hole (95) and the lower through-hole (96). Shell and plate heat exchanger.

2. The guide structure (100) is formed of a plurality of linear ridges (80a, 80b) that are parallel to each other, Each of the plurality of ridges (80a, 80b) is formed by raising the heat transfer plate (50).

2. The plate-and-shell heat exchanger according to claim 1.

3. The heat transfer plate (50) includes a first plate (50a) and a second plate (50b), In the plate stack (40), the first plates (50a) and the second plates (50b) are stacked alternately, guide regions (61a, 61b, 71a, 71b) including a plurality of ridge portions (80a, 80b) constituting the guide structure (100) are formed on each of the first plate (50a) and the second plate (50b); In the plate stack (40), the guide regions (61a, 71a) of the first plate (50a) and the guide regions (71b, 61b) of the second plate (50b) overlap with each other in the stacking direction of the heat transfer plates (50).

3. The shell and plate heat exchanger according to claim 2.

4. In each of the first plate (50a) and the second plate (50b), the guide regions (61a, 61b, 71a, 71b) extend from a portion between the upper through-hole (95) and the lower through-hole (96) to the outside of that portion.

4. The plate-and-shell heat exchanger according to claim 3.

5. In each of the first plate (50a) and the second plate (50b), at least one guide region (61a, 61b, 71a, 71b) is formed on the right and left sides of the lower through-hole (96).

5. The plate-and-shell heat exchanger according to claim 4.

6. the upper ends of the guide regions (61a, 61b, 71a, 71b) are located in the heat transfer plate (50) between the upper through-hole (95) and the lower through-hole (96); The guide regions (61a, 61b, 71a, 71b) extend obliquely downward from the upper ends of the guide regions (61a, 61b, 71a, 71b).

6. The plate-and-shell heat exchanger according to claim 5.

7. the ridge portion included in the guide region (61a, 71a) of the first plate (50a) is a first ridge portion (81a, 82a); the ridge portion included in the guide region (71b, 61b) of the second plate (50b) is a second ridge portion (82b, 81b); Of the bisector (L1) of the obtuse angle formed by the first ridge portions (81a, 82a) and the second ridge portions (82b, 81b) and the bisector (L2) of the acute angle formed by the first ridge portions (81a, 82a) and the second ridge portions (82b, 81b), the one forming a smaller acute angle with the vertical direction is inclined so as to approach the center of the heat transfer plate (50) in the width direction as it goes upward.

7. The shell-and-plate heat exchanger according to claim 5 or 6.

8. In each of the plurality of heat transfer plates (50), the guide regions (53a, 53b) extend in the left-right direction and cross the portion between the upper through-hole (95) and the lower through-hole (96).

4. The plate-and-shell heat exchanger according to claim 3.

9. the ridge portion included in the guide region (53a, 53b) of the first plate (50a) is a first ridge portion (83a), the ridge portion included in the guide region (53a, 53b) of the second plate (50b) is a second ridge portion (83b), The first ridge portion (83a) and the second ridge portion (83b) extend in different directions, and the acute angle formed between each extension direction and the horizontal direction is 45° or less.

9. The plate-and-shell heat exchanger according to claim 8.

10. A shell-and-plate heat exchanger (10) according to claim 1, 2, 3, 4, 5, 6, 8 or 9; a refrigerant circuit (205) in which the shell-and-plate heat exchanger (10) is provided and a refrigerant is circulated to perform a refrigeration cycle; Refrigeration equipment.

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