Shell-and-plate heat exchanger and refrigeration device

Abstract

To disperse a refrigerant in the stacking direction of heat transfer plates.SOLUTION: The partition member (60) is disposed above the refrigerant inlet (21) and below the plate stack (30). The partition member (60) extends in a first direction that is the stacking direction of the heat transfer plates (40). The partition member (60) has a hole row (70) in which a plurality of holes (65) are formed at intervals in the first direction. An average pitch p of the plurality of holes (65) in the hole row (70) and a distance h from an upper surface of the partition member (60) to a lower surface of the plate stack (30) satisfy a condition of h / p> 0.1.SELECTED DRAWING: Figure 5

Description

[Technical Field]

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

[0002] Patent Document 1 discloses a shell-and-plate heat exchanger that includes a plate stack in which multiple heat transfer plates are stacked, and a partition member (dispersion plate) that is positioned below the plate stack and separates the dispersion chamber.

[0003] The partition member has a plurality of holes formed therein. The refrigerant that flows into the dispersion chamber from the refrigerant inlet spreads in the stacking direction of the heat transfer plates, flows out of the plurality of holes, and is supplied to the plate stack. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent Publication No. 2021-110515 Summary of the Invention [Problem to be solved by the invention]

[0005] However, if the distance between the plate stack and the partition member is small, the refrigerant flowing out from the holes in the partition member may not spread sufficiently in the stacking direction of the heat transfer plates, which may reduce the heat exchange efficiency of the heat exchanger as a whole.

[0006] An object of the present disclosure is to enable the refrigerant to be dispersed in the stacking direction of the heat transfer plates. [Means for solving the problem]

[0007] A first aspect of the present disclosure includes a shell (11) that forms an internal space (15), has a refrigerant inlet (21) at a lower part, and has a refrigerant outlet (22) at an upper part; a plate stack (30) that is accommodated in the internal space (15), has a plurality of heat transfer plates (40) that are stacked in the plate thickness direction and joined to each other, and has a refrigerant flow path (31) through which a refrigerant flows and a heat transfer medium flow path (32) through which a heat transfer medium flows; and a partition member (60) that is arranged above the refrigerant inlet (21) and below the plate stack (30) and extends in a first direction that is a stacking direction of the heat transfer plates (40), wherein the partition member (60) has a hole row (70) in which a plurality of holes (65) are formed at intervals in the first direction, and an average pitch p of the plurality of holes (65) in the hole row (70) and a distance h from the upper surface of the partition member (60) to the lower surface of the plate stack (30) satisfy the condition h / p>0.1.

[0008] In the first aspect, by appropriately setting the average pitch p of the holes (65) in the hole row (70) and the distance h from the upper surface of the partition member (60) to the lower surface of the plate stack (30), the refrigerant can be dispersed evenly in the stacking direction of the heat transfer plates, thereby preventing a decrease in heat exchange efficiency.

[0009] A second aspect of the present disclosure satisfies the condition h / p>0.4 in the shell and plate heat exchanger of the first aspect.

[0010] In the second aspect, the refrigerant can be more easily dispersed evenly in the stacking direction of the heat transfer plates (40), and a decrease in the heat exchange efficiency can be prevented.

[0011] A third aspect of the present disclosure is a shell-and-plate heat exchanger of the first or second aspect, wherein, when viewed from the top-bottom direction, a direction perpendicular to the first direction is defined as a second direction, and the hole row (70) includes a first hole row (71) and a second hole row (72) arranged at a distance from the first hole row (71) in the second direction, and the first hole row (71) or the second hole row (72) satisfies the condition h / p>0.1.

[0012] In the third aspect, by setting the first hole row (71) or the second hole row (72) to satisfy the above-mentioned conditions, the refrigerant can be uniformly dispersed in the stacking direction of the heat transfer plates (40), and a decrease in heat exchange efficiency can be suppressed.

[0013] A fourth aspect of the present disclosure is the plate-and-shell heat exchanger of any one of the first to third aspects, wherein the refrigerant is a single refrigerant that is an HFO refrigerant or a mixed refrigerant that contains an HFO refrigerant as a component.

[0014] In the fourth embodiment, a single refrigerant that is an HFO refrigerant or a mixed refrigerant that contains an HFO refrigerant as a component can be used as the refrigerant.

[0015] A fifth 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 fourth aspects, and a refrigerant circuit (1a) through which refrigerant that has undergone heat exchange in the shell-and-plate heat exchanger (10) flows.

[0016] In a fifth aspect, a refrigeration system can be provided, which includes a shell-and-plate heat exchanger (10) and a refrigerant circuit (1a). [Brief explanation of the drawings]

[0017] [Figure 1] FIG. 1 is a refrigerant circuit diagram showing the configuration of the refrigeration device of the first embodiment. [Figure 2] FIG. 2 is a side cross-sectional view showing the configuration of a shell-and-plate heat exchanger. [Figure 3] FIG. 3 is a front cross-sectional view showing the configuration of a shell-and-plate heat exchanger. [Figure 4] FIG. 4 is a side cross-sectional view showing the configuration of the plate stack. [Figure 5] FIG. 5 is a plan view showing the configuration of the partition member. [Figure 6] FIG. 6 is a cross-sectional plan view showing the configuration of the partition member. [Figure 7]FIG. 7 is a plan view illustrating the arrangement of holes in the partition member. [Figure 8] FIG. 8 is a graph showing the relationship between h / p and the percentage of effective coverage of the heat exchanger. [Figure 9] FIG. 9 is a diagram showing the average pitch, h / p, and the judgment results for each hole row. [Figure 10] FIG. 10 is a plan view illustrating the arrangement of holes in the partition member according to the second embodiment. [Figure 11] FIG. 11 is a diagram showing the average pitch, h / p, and the judgment results for each hole row. [Figure 12] FIG. 12 is a plan view illustrating the arrangement of holes in the partition member according to the third embodiment. [Figure 13] FIG. 13 is a diagram showing the average pitch, h / p, and the judgment results for each hole row. [Figure 14] FIG. 14 is a plan view illustrating the arrangement of holes in the partition member according to the fourth embodiment. [Figure 15] FIG. 15 is a diagram showing the average pitch, h / p, and the judgment results for each hole row. [Figure 16] FIG. 16 is a plan view illustrating the arrangement of holes in the partition member according to the fifth embodiment. [Figure 17] FIG. 17 is a diagram showing the average pitch, h / p, and the judgment results for each hole row. DETAILED DESCRIPTION OF THE INVENTION

[0018] First Embodiment As shown in FIG. 1, a shell-and-plate heat exchanger (10) (hereinafter simply referred to as a "heat exchanger") is provided in a refrigeration system (1). The refrigeration system (1) has a refrigerant circuit (1a) filled with a refrigerant. The refrigerant circuit (1a) has a compressor (2), a radiator (3), a pressure reduction mechanism (4), and a heat exchanger (10) serving as an evaporator. The pressure reduction mechanism (4) is, for example, an expansion valve. The refrigerant circuit (1a) performs a vapor compression refrigeration cycle.

[0019] The refrigeration system (1) is, for example, an air conditioner. The air conditioner may be a dedicated cooling system, a dedicated heating system, or an air conditioner that switches between cooling and heating. In this case, the air conditioner has a switching mechanism (e.g., a four-way switching valve) that switches the refrigerant circulation direction. The refrigeration system (1) may be a water heater, a chiller unit, a cooling device that cools the air inside a storage unit, or the like. A cooling device cools the air inside a refrigerator, a freezer, a container, or the like.

[0020] <Heat exchanger> As shown in FIGS. 2 and 3, the heat exchanger (10) includes a shell (11) and a plate stack (30). The shell (11) has an internal space (15). A refrigerant flows into the internal space (15) of the shell (11). The plate stack (30) is accommodated in the internal space (15) of the shell (11). The refrigerant exchanges heat with a heat transfer medium circulating within the plate stack (30). In this way, the heat exchanger (10) functions as an evaporator by evaporating the refrigerant that flows into the internal space (15) of the shell (11).

[0021] The refrigerant used here is a single HFO refrigerant or a mixed refrigerant containing an HFO refrigerant as a component. Specific examples include R1233zd(E), R1234ze(E), and R513A. The heat transfer medium used may be, for example, water or brine.

[0022] <shell> The shell 11 has a cylindrical body 12, support legs 13, and a closing member 14. The cylindrical body 12 is formed of a cylindrical member that extends horizontally and is open at both axial ends.

[0023] The support legs 13 are disposed on both axial ends of the cylindrical body 12. The support legs 13 have holes formed therein that correspond to the openings of the cylindrical body 12. The support legs 13 are attached to the cylindrical body 12 by, for example, welding.

[0024] The closing members 14 close the openings at both ends of the cylindrical body 12. The closing members 14 are fastened to the support legs 13 by fastening bolts, for example.

[0025] The shell 11 defines an internal space 15 by means of a cylindrical body 12, support legs 13, and a closing member 14. The shell 11 is installed with its axial direction aligned horizontally. A liquid refrigerant is stored in the internal space 15. A plate stack 30 is housed in the internal space 15.

[0026] The shell 11 has a refrigerant inlet 21 and a refrigerant outlet 22. The refrigerant inlet 21 is provided in the lower part of the shell 11. The refrigerant inlet 21 is provided in the bottom part of the shell 11. The refrigerant is introduced into the internal space 15 through the refrigerant inlet 21. In the example shown in FIG. 2, the refrigerant inlet 21 is provided in the lower part of the shell 11 at a central position in the stacking direction of the plate stack 30.

[0027] The refrigerant outlet (22) is provided at the top of the shell (11). The refrigerant evaporated in the internal space (15) is discharged from the refrigerant outlet (22) to the outside of the shell (11). The refrigerant inlet (21) and the refrigerant outlet (22) are connected to the refrigerant circuit (1a).

[0028] The shell 11 has a heat transfer medium inlet 23 and a heat transfer medium outlet 24. The heat transfer medium inlet 23 and the heat transfer medium outlet 24 are tubular members.

[0029] The heat transfer medium inlet 23 penetrates one axial end of the shell 11. The heat transfer medium inlet 23 is connected to a heat transfer medium introduction passage 33 of the plate stack 30. The heat transfer medium inlet 23 supplies the heat transfer medium to the plate stack 30. Heat exchange occurs between the refrigerant that has flowed into the internal space 15 of the shell 11 and the heat transfer medium that has flowed into a heat transfer medium flow passage 32 (described later) of the plate stack 30.

[0030] The heat transfer medium outlet (24) penetrates one axial end of the shell (11) at a position higher than the heat transfer medium inlet (23). The heat transfer medium outlet (24) is connected to the heat transfer medium outlet path (34) of the plate stack (30). The heat transfer medium outlet (24) discharges the heat transfer medium from the plate stack (30). Note that the heat transfer medium inlet (23) may be configured to be located higher than the heat transfer medium outlet (24).

[0031] A partition member (60) is disposed below the plate stack (30). The refrigerant flowing in through the refrigerant inlet (21) flows along the partition plates (61) of the partition member (60) in the stacking direction of the heat transfer plates (40) and is discharged through the holes (65) toward the plate stack (30). The partition member (60) will be described in detail later.

[0032] A mesh member (50) is disposed above the plate stack (30) and below the refrigerant outlet (22). The mesh member (50) collects droplets contained in the refrigerant that passes through the refrigerant flow path (31) and flows out from the upper surface of the plate stack (30). The mesh member (50) is formed, for example, in the shape of a thick plate by stacking metal meshes. The refrigerant can pass through the mesh member (50) in the thickness direction. The mesh member (50) is supported by a support member (52) (see FIG. 3). The support member (52) is fixed to the inner surface of the shell (11).

[0033] <Plate stack> The plate stack 30 has a plurality of heat transfer plates 40 stacked in the thickness direction and joined together. The plate stack 30 is accommodated in the internal space 15 of the shell 11 with the stacking direction of the heat transfer plates 40 aligned horizontally. The length of the plate stack 30 in the width direction is, for example, 600 to 1500 mm.

[0034] 4, the heat transfer plate (40) includes a first plate (40a) and a second plate (40b). The first plates (40a) and the second plates (40b) are alternately stacked in the plate stack (30). The second plates (40b) are the first plates (40a) turned upside down.

[0035] In the following description, the left side of each of the first plate (40a) and the second plate (40b) in FIG. 4 is referred to as the front side, and the right side of each of the first plate (40a) and the second plate (40b) in FIG. 4 is referred to as the back side.

[0036] <Heat medium introduction path, heat medium outlet path> The first plate (40a) has an inlet protrusion (41a) and an outlet protrusion (43a). The inlet protrusion (41a) and the outlet protrusion (43a) are formed by bulging a part of the first plate (40a) toward the surface side.

[0037] The inlet protrusion (41a) is formed in the lower part of the first plate (40a). A first inlet hole (42a) is formed in the center of the inlet protrusion (41a). The first inlet hole (42a) is a circular hole that penetrates the first plate (40a) in the thickness direction.

[0038] The outlet protrusion (43a) is formed on the upper part of the first plate (40a). A first outlet hole (44a) is formed in the center of the outlet protrusion (43a). The first outlet hole (44a) is a circular hole that penetrates the first plate (40a) in the thickness direction.

[0039] The second plate (40b) has an inlet recess (41b) and an outlet recess (43b). The inlet recess (41b) and the outlet recess (43b) are formed by bulging a part of the second plate (40b) toward the rear surface side.

[0040] The inlet recess (41b) is formed in the lower part of the second plate (40b). A second inlet hole (42b) is formed in the center of the inlet recess (41b). The second inlet hole (42b) is a circular hole that penetrates the second plate (40b) in the thickness direction. The inlet recess (41b) is formed at a position corresponding to the inlet protrusion (41a) of the first plate (40a). The second inlet hole (42b) is formed at a position corresponding to the first inlet hole (42a) of the first plate (40a).

[0041] The outlet recess (43b) is formed in the upper part of the second plate (40b). A second outlet hole (44b) is formed in the center of the outlet recess (43b). The second outlet hole (44b) is a circular hole that penetrates the second plate (40b) in the thickness direction. The outlet recess (43b) is formed at a position corresponding to the outlet protrusion (43a) of the first plate (40a). The second outlet hole (44b) is formed at a position corresponding to the first outlet hole (44a) of the first plate (40a).

[0042] In the plate stack 30, the peripheral edge of the first plate 40a and the peripheral edge of the second plate 40b adjacent to the back surface of the first plate 40a are joined together along the entire periphery by welding, or may be joined by brazing.

[0043] In the plate stack (30), the first inlet hole (42a) of the first plate (40a) overlaps with the second inlet hole (42b) of the second plate (40b) adjacent to the front surface of the first plate (40a). The overlapping edges of the first inlet hole (42a) and the second inlet hole (42b) are joined by welding along the entire periphery. Alternatively, they may be joined by brazing. The first inlet hole (42a) and the second inlet hole (42b) communicate with the heat medium flow path (32) described below and introduce the heat medium into the heat medium flow path (32).

[0044] In the plate stack (30), the first outlet hole (44a) of the first plate (40a) overlaps with the second outlet hole (44b) of the second plate (40b) adjacent to the front surface of the first plate (40a). The overlapping edges of the first outlet hole (44a) and the second outlet hole (44b) are joined by welding along the entire periphery. Alternatively, they may be joined by brazing. The first outlet hole (44a) and the second outlet hole (44b) communicate with the heat medium flow path (32) described below and guide the heat medium from the heat medium flow path (32).

[0045] In the plate stack (30), the inlet protrusion (41a) and the first inlet hole (42a) of the first plate (40a) and the inlet recess (41b) and the second inlet hole (42b) of the second plate (40b) form a heat medium introduction passage (33).

[0046] In the plate stack (30), the outlet convex portion (43a) and the first outlet hole (44a) of the first plate (40a) and the outlet concave portion (43b) and the second outlet hole (44b) of the second plate (40b) form a heat medium discharge path (34).

[0047] The heat medium inlet passage 33 is a passage extending in the stacking direction of the heat transfer plates 40 in the plate stack 30. The heat medium inlet passage 33 is a passage isolated from the internal space 15 of the shell 11, and connects all the heat medium flow passages 32 to the heat medium inlet 23.

[0048] The heat medium outlet channel (34) is a passage extending in the stacking direction of the heat transfer plates (40) in the plate stack (30). The heat medium outlet channel (34) is a passage isolated from the internal space (15) of the shell (11) and connects all the heat medium flow channels (32) to the heat medium outlets (24).

[0049] <Refrigerant flow path, heat medium flow path> The plate stack (30) has refrigerant channels (31) and heat medium channels (32). A plurality of refrigerant channels (31) and a plurality of heat medium channels (32) are formed with a heat transfer plate (40) sandwiched therebetween. The refrigerant channels (31) and the heat medium channels (32) are separated from each other by the heat transfer plate (40). The first plate (40a) and the second plate (40b) each have repeated elongated ridge-like projections and depressions.

[0050] The first plate (40a) is provided with first front-side protrusions (45a) and first back-side protrusions (47a) that are alternately arranged. The first front-side protrusions (45a) bulge out toward the front side of the first plate (40a). The first back-side protrusions (47a) bulge out toward the back side of the first plate (40a).

[0051] The second plate (40b) is provided with second front-side protrusions (47b) and second rear-side protrusions (45b) alternately and repeatedly. The second front-side protrusions (47b) bulge out toward the front side of the second plate (40b). The second rear-side protrusions (45b) bulge out toward the rear side of the second plate (40b).

[0052] The refrigerant flow path (31) is a flow path sandwiched between the front surface of the first plate (40a) and the back surface of the second plate (40b). The refrigerant flow path (31) is a flow path through which the refrigerant flows, communicating with the internal space (15) of the shell (11). Specifically, the refrigerant flow path (31) includes a flow path formed between the front surface of the first back-side convex portion (47a) and the back surface of the second front-side convex portion (47b).

[0053] The heat medium flow path (32) is a flow path sandwiched between the back surface of the first plate (40a) and the front surface of the second plate (40b). The heat medium flow path (32) is a flow path through which the heat medium flows while being isolated from the internal space (15) of the shell (11). Specifically, the heat medium flow path (32) includes a flow path formed between the back surface of the first front-side convex portion (45a) and the front surface of the second back-side convex portion (45b).

[0054] <Flow of heat transfer medium and refrigerant> The flow of the heat medium and the refrigerant in the heat exchanger (10) will be described. As shown in Fig. 4, the heat medium flows from the heat medium inlet (23) into the heat medium introduction passage (33). The heat medium flowing through the heat medium introduction passage (33) flows through the heat medium flow passage (32) from the first inlet hole (42a) and the second inlet hole (42b) toward the first outlet hole (44a) and the second outlet hole (44b).

[0055] Specifically, the heat medium flowing through the heat medium inlet passage (33) flows into the heat medium flow path (32). The heat medium flows along the heat medium flow path (32) and then flows into the heat medium flow path (32) adjacent to the heat medium flow path (32) on the upper side of the heat medium flow path (32). In this manner, the heat medium flows upward while reaching both side ends of the heat transfer plate (40).

[0056] Next, the flow of the refrigerant will be described. The refrigerant that has passed through the pressure reducing mechanism (4) in the refrigerant circuit (1a) flows into the heat exchanger (10). The refrigerant flows through the refrigerant inlet (21) into the inner space (15) of the shell (11).

[0057] In the internal space 15 of the shell 11, most of the plate stack 30 is immersed in liquid refrigerant, and the liquid refrigerant flows into the refrigerant flow paths 31 of the plate stack 30. The liquid refrigerant that has flowed into the refrigerant flow paths 31 comes into contact with the heat transfer plates 40 and absorbs heat from the heat medium flowing through the heat medium flow paths 32, thereby evaporating. The gas refrigerant generated in the refrigerant flow paths 31 flows upward, exits the refrigerant flow paths 31, and is blown upward from the top surface of the plate stack 30.

[0058] The gas refrigerant that has passed through the plate stack (30) passes through the mesh member (50). The mesh member (50) collects liquid refrigerant contained in the gas refrigerant. The gas refrigerant that has passed through the mesh member (50) flows out of the shell (11) through the refrigerant outlet (22).

[0059] <Partition member> The partition plate (61) separates the plate stack (30) from the refrigerant inlet (21) (see FIG. 2). As shown in FIGS. 5 and 6, the partition member (60) includes the partition plate (61), a bottom plate (62), a peripheral wall portion (63), and a pair of guide plates (64).

[0060] The partition plate (61) extends in the stacking direction of the heat transfer plates (40). Hereinafter, the stacking direction of the heat transfer plates (40) is referred to as a first direction, and the width direction of the partition plate (61) perpendicular to the first direction when viewed from the top-bottom direction is referred to as a second direction.

[0061] The bottom plate (62) is disposed below the partition plate (61). The refrigerant inlet (21) is connected to the bottom plate (62). The peripheral wall (63) extends along the peripheral edges of the partition plate (61) and the bottom plate (62). The peripheral wall (63) connects the partition plate (61) and the bottom plate (62).

[0062] The partition member (60) has an internal flow path (66). The refrigerant flowing in through the refrigerant inlet (21) flows through the internal flow path (66). The internal flow path (66) is provided in a space surrounded by the partition plate (61), the bottom plate (62), and the peripheral wall portion (63).

[0063] The pair of guide plates (64) are erected between the partition plate (61) and the bottom plate (62). The pair of guide plates (64) extend in the first direction with a gap between them in the second direction. Both end portions of the pair of guide plates (64) in the first direction are located inside the peripheral wall portion (63). As a result, gaps are provided between the left end portions of the guide plates (64) and the left end portions of the peripheral wall portion (63) and between the right end portion of the guide plate (64) and the right end portion of the peripheral wall portion (63).

[0064] The internal flow path (66) includes a first flow path (67) and a second flow path (68). The first flow path (67) is formed in a space between the pair of guide plates (64). The first flow path (67) guides the refrigerant that has flowed in through the refrigerant inlet (21) in a first direction.

[0065] The second flow path (68) is formed by a space provided between the upper guide plate (64) and the upper end of the peripheral wall portion (63) in FIG. 6, and a space provided between the lower guide plate (64) and the lower end of the peripheral wall portion (63) in FIG. 6.

[0066] The second flow path (68) is bent back at the end of the first flow path (67) in the first direction, and guides the refrigerant that has passed through the first flow path (67) to a central position in the first direction.

[0067] The partition member (60) has a row of holes (70) in which a plurality of holes (65) are formed at intervals in the first direction. The plurality of holes (65) are formed in the partition plate (61).

[0068] The hole row 70 includes a first hole row 71, a second hole row 72, a third hole row 73, and a fourth hole row 74. The first hole row 71, the second hole row 72, the third hole row 73, and the fourth hole row 74 are arranged in order from the top in Figure 5 at intervals in the second direction.

[0069] The holes (65) of the first hole row (71) communicate with the second flow path (68) on the upper side in Figure 5. The holes (65) of the second hole row (72) communicate with the first flow path (67). The holes (65) of the third hole row (73) communicate with the first flow path (67). The holes (65) of the fourth hole row (74) communicate with the second flow path (68) on the lower side in Figure 5.

[0070] In this manner, the refrigerant that has flowed from the refrigerant inlet (21) into the internal space (15) of the shell (11) flows in the first direction through the first flow path (67) of the partition member (60). The refrigerant that has been turned back at the end of the first flow path (67) in the first direction flows in the second flow path (68).

[0071] The refrigerant flows out through the holes (65) of the partition plate (61) and flows toward the plate stack (30). In this way, the partition member (60) causes the refrigerant to flow from the refrigerant inlet (21) toward both ends in the first direction so as to spread, thereby dispersing the refrigerant in the stacking direction of the heat transfer plates (40).

[0072] However, if the distance between the plate stack (30) and the partition member (60) is small, the refrigerant flowing out from the holes (65) of the partition member (60) may not spread sufficiently in the stacking direction of the heat transfer plates (40), which may result in a decrease in the heat exchange efficiency of the heat exchanger (10) as a whole.

[0073] Therefore, in this embodiment, the pitch of the holes (65) and the distance between the partition member (60) and the plate stack (30) are appropriately set, so that the refrigerant can be appropriately dispersed in the first direction.

[0074] Specifically, the average pitch of the holes 65 in the hole row 70 is defined as p, and the distance from the upper surface of the partition member 60 to the lower surface of the plate stack 30 is defined as h. The average pitch p is the arithmetic mean of the pitches of the holes 65, and is calculated by dividing the sum of the pitches of the holes 65 by the number of pitches.

[0075] As shown in FIG. 7, the pitch of the holes 65 in the hole row 70 is p1, and the inner diameter of the holes 65 is d1. In the example shown in FIG. 7, the first hole row 71 has 17 holes 65. The pitch p1 of the holes 65 in the first hole row 71 is the same for all of them. In addition, the inner diameter d1 of the holes 65 in the first hole row 71 is also the same for all of them. Therefore, in the example shown in FIG. 7, the average pitch p of the holes 65 in the first hole row 71 is p=p1.

[0076] Similarly, the second hole row 72, the third hole row 73, and the fourth hole row 74 each have 17 holes 65. The pitch p1 of the holes 65 in the second hole row 72, the third hole row 73, and the fourth hole row 74 and the inner diameter d1 of the holes 65 are all the same. The average pitch p of the holes 65 in the second hole row 72, the third hole row 73, and the fourth hole row 74 is p = p1.

[0077] The pitch of the holes 65 in the first hole row 71 is equal to the pitch of the holes 65 in the second hole row 72. The pitch of the holes 65 in the first hole row 71, the pitch of the holes 65 in the second hole row 72, the pitch of the holes 65 in the third hole row 73, and the pitch of the holes 65 in the fourth hole row 74 are all equal.

[0078] FIG. 8 is a graph showing the relationship between the parameter h / p and the percentage of effective range of the heat exchanger (10). In FIG. 8, the percentage of effective range of the heat exchanger (10) is defined by assigning 100% performance of the heat exchanger (10) to "1.0" on the graph. In FIG. 8, dots indicate the percentage of effective range of the heat exchanger at a given h / p. In FIG. 8, dotted lines indicate an approximation curve for h / p values ​​greater than 0.1.

[0079] As shown in Fig. 8, it can be seen that the ratio of the effective range of the heat exchanger (10) drops sharply in the range where h / p is 0.1 or less. It can also be seen that the ratio significantly deviates from the approximate curve for values ​​where h / p is greater than 0.1, and the range in which the heat exchanger (10) can be effectively used drops sharply.

[0080] As shown in FIG. 8, when h / p is greater than 0.1, the ratio of the effective area of ​​the heat exchanger (10) is 0.5 or more. This allows the heat exchanger (10) to be used effectively. When h / p is greater than 0.4, the ratio of the effective area of ​​the heat exchanger (10) increases further. This allows the heat exchanger (10) to be used more effectively.

[0081] Therefore, in this embodiment, the average pitch p and the distance h are set so that the first hole row (71), the second hole row (72), the third hole row (73), or the fourth hole row (74) satisfies the condition h / p>0.1. More preferably, the condition h / p>0.4 is satisfied.

[0082] The parameter h / p will be discussed below using specific values. In the example shown in Fig. 7, the pitch of the holes 65 is p1 = 60 [mm], and the inner diameters of the holes 65 are d1 = 6 [mm] and h = 30 [mm].

[0083] 9, in the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74), h / p=0.5, which satisfies the condition h / p>0.1. When the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) are averaged together, h / p=0.5, which satisfies the condition h / p>0.1.

[0084] -Effects of the first embodiment- According to this embodiment, by appropriately setting the average pitch p of the multiple holes (65) in the hole row (70) and the distance h from the upper surface of the partition member (60) to the lower surface of the plate stack (30), the refrigerant can be evenly distributed in the stacking direction of the heat transfer plates, and a decrease in heat exchange efficiency can be suppressed.

[0085] According to this embodiment, by satisfying the condition h / p>0.4, the refrigerant can be more easily dispersed evenly in the stacking direction of the heat transfer plates (40), and a decrease in the heat exchange efficiency can be suppressed.

[0086] According to this embodiment, by setting the first hole row (71) or the second hole row (72) to satisfy the above-mentioned conditions, the refrigerant can be evenly distributed in the stacking direction of the heat transfer plates (40), and a decrease in heat exchange efficiency can be suppressed.

[0087] According to this embodiment, a single refrigerant that is an HFO refrigerant or a mixed refrigerant that contains an HFO refrigerant as a component can be used as the refrigerant.

[0088] According to this embodiment, a refrigeration system including a shell-and-plate heat exchanger (10) and a refrigerant circuit (1a) can be provided.

[0089] Second Embodiment In the following, the same parts as those in the first embodiment are denoted by the same reference numerals, and only the differences will be described.

[0090] In the example shown in FIG. 10, the pitches of the plurality of holes (65) in the hole row (70) include p1 and p2. p1 and p2 are of different lengths. The hole row (70) includes a first hole row (71) and a second hole row (72). Further, the hole row (70) includes a third hole row (73) and a fourth hole row (74).

[0091] The first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) each have 14 holes (65). The pitches of the plurality of holes (65) in the first hole row (71) include p1 and p2. The pitches of the plurality of holes (65) in the second hole row (72) include p1 and p2. The pitches of the plurality of holes (65) in the third hole row (73) include p1 and p2. The pitches of the plurality of holes (65) in the fourth hole row (74) include p1 and p2.

[0092] In the hole row (70), the pitch of the plurality of holes (65) arranged at the central portion in the first direction is p2. In the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74), the pitch of the four holes (65) arranged at the central portion in the first direction is p2. The pitch of the remaining holes (65) is p1. Here, p1 < p2. Also, the inner diameters d1 of the holes (65) in the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) are all the same.

[0093] In the example shown in FIG. 10, the pitch of the plurality of holes (65) is set to p1 = 60 [mm], p2 = 120 [mm], the inner diameter of the hole (65) is d1 = 6 [mm], and h = 30 [mm].

[0094] As shown in Fig. 11, in the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74), the average pitch is p = 74 respectively. Also, in the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74), h / p = 0.41, satisfying the condition h / p > 0.1. When averaging the entirety of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74), h / p = 0.41, thus satisfying the condition h / p > 0.1.

[0095] 《Embodiment 3》 As shown in Fig. 12, the first hole row (71) and the fourth hole row (74) each have 17 holes (65). The pitches of the plurality of holes (65) in the first hole row (71) and the fourth hole row (74) are all the same. Also, the inner diameters d1 of the holes (65) in the first hole row (71) and the fourth hole row (74) are all the same. Therefore, in the example shown in Fig. 12, the average pitch p of the plurality of holes (65) in the first hole row (71) and the fourth hole row (74) is p = p1.

[0096] The second hole row (72) and the third hole row (73) each have 14 holes (65). The pitches of the plurality of holes (65) in the second hole row (72) and the third hole row (73) include p1 and p2. The pitch of the 4 holes (65) arranged in the central part in the first direction is p2. The pitches of the remaining holes (65) are p1. Here, p1 < p2. Also, the inner diameters d1 of the holes (65) in the second hole row (72) and the third hole row (73) are all the same.

[0097] In the example shown in Fig. 12, the pitch of the plurality of holes (65) is set as p1 = 60 [mm], p2 = 120 [mm], the inner diameter of the hole (65) is d1 = 6 [mm], and h = 30 [mm].

[0098] As shown in Fig. 13, in the first hole row (71) and the fourth hole row (74), the average pitch is p = 60. Also, in the first hole row (71) and the fourth hole row (74), h / p = 0.5, satisfying the condition h / p > 0.1.

[0099] In the second hole row (72) and the third hole row (73), the average pitch is p = 74. Also, in the second hole row (72) and the third hole row (73), h / p = 0.41, satisfying the condition h / p > 0.1.

[0100] When averaging the entire first hole row (71), second hole row (72), third hole row (c73), and fourth hole row (74), h / p = 0.45, thus satisfying the condition h / p > 0.1.

[0101] <<Embodiment 4>> As shown in FIG. 14, the first hole row (71) and the fourth hole row (74) each have 17 holes (65). The pitches of the plurality of holes (65) in the first hole row (71) and the fourth hole row (74) are all the same. Also, the inner diameters d1 of the holes (65) in the first hole row (71) and the fourth hole row (74) are all the same. Therefore, in the example shown in FIG. 14, the average pitch p of the plurality of holes (65) in the first hole row (71) and the fourth hole row (74) is p = p1.

[0102] The second hole row (72) and the third hole row (73) each have 4 holes (65). The pitches of the plurality of holes (65) in the second hole row (72) and the third hole row (73) include p1, p2, and p3. The pitch of the two holes (65) arranged in the central part in the first direction is p2. The pitches of the remaining holes (65) are p3. Here, p1 < p2 < p3. Also, the inner diameters d1 of the holes (65) in the second hole row (72) and the third hole row (73) are all the same.

[0103] In the example shown in FIG. 14, the pitch of the plurality of holes (65) is set as p1 = 60 [mm], p2 = 120 [mm], p3 = 420 [mm], the inner diameter of the holes (65) is d1 = 6 [mm], and h = 30 [mm].

[0104] As shown in FIG. 15, in the first hole row (71) and the fourth hole row (74), the average pitch is p = 60. Also, in the first hole row (71) and the fourth hole row (74), h / p = 0.5, satisfying the condition h / p > 0.1.

[0105] In the second hole row (72) and the third hole row (73), the average pitch is p = 320. Also, in the second hole row (72) and the third hole row (73), h / p = 0.09, and the condition h / p > 0.1 is not satisfied.

[0106] However, when averaging the entirety of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74), h / p = 0.3, so the condition h / p > 0.1 is satisfied.

[0107] 《Embodiment 5》 In the example shown in FIG. 16, the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) each have 14 holes (65). The pitches of the plurality of holes (65) in the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) include p1 and p2. The pitch of the 4 holes (65) arranged at the center in the first direction is p2. The pitch of the remaining holes (65) is p1. Here, p1 < p2.

[0108] Also, the inner diameters of the holes (65) in the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) include d1 and d2. Here, d1 < d2. The inner diameters of the first and second holes (65) from the left and the first and second holes (65) from the right in FIG. 16 are d2. The inner diameter of the remaining holes (65) is d1.

[0109] In the example shown in FIG. 16, the pitch of the plurality of holes (65) is set as p1 = 60 [mm], p2 = 120 [mm], the inner diameter of the holes (65) is set as d1 = 6 [mm], d2 = 8 [mm], and h = 30 [mm].

[0110] As shown in Figure 17, the average pitch of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) is p = 74. Furthermore, the ratio h / p of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) is h / p = 0.41, which satisfies the condition h / p > 0.1. When the ratio h / p of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) is averaged as a whole, the ratio h / p = 0.41, which satisfies the condition h / p > 0.1.

[0111] In the example shown in FIG. 17, if the difference in inner diameter between the different holes (65) becomes too large, it may affect performance, so it is preferable to set the inner diameter of the holes (65) to satisfy the condition, for example, d2≦2×d1.

[0112] Other Embodiments 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 between terms to which these terms are attached, and do not limit the number or order of those terms. [Industrial Applicability]

[0113] As described above, the present disclosure is useful for a shell-and-plate heat exchanger and a refrigeration device. [Explanation of symbols]

[0114] 1 Refrigeration equipment 1a Refrigerant circuit 10. Shell and plate heat exchanger 11 Shell 15 Interior Space 21 Refrigerant inlet 22 Refrigerant outlet 30 Plate stack 31 Refrigerant flow path 32 Heat transfer medium flow path 40 Heat Transfer Plate 60 Partition member 65 holes 70 hole rows 71 1st hole row 72 2nd hole row

Claims

1. a shell (11) that defines an internal space (15), has a refrigerant inlet (21) at a lower portion, and has a refrigerant outlet (22) at an upper portion; a plate stack (30) accommodated in the internal space (15), which has a plurality of heat transfer plates (40) stacked in a thickness direction and joined to each other, and which has formed therein a refrigerant flow path (31) through which a refrigerant flows and a heat medium flow path (32) through which a heat medium flows; a partition member (60) disposed above the refrigerant inlet (21) and below the plate stack (30), and extending in a first direction which is the stacking direction of the heat transfer plates (40), the partition member (60) has a row of holes (70) in which a plurality of holes (65) are formed at intervals in the first direction, The average pitch p of the plurality of holes (65) in the hole row (70) and the distance h from the upper surface of the partition member (60) to the lower surface of the plate stack (30) satisfy the condition h / p>0.

1. Shell and plate heat exchanger.

2. 2. The shell and plate heat exchanger of claim 1, Satisfy the condition h / p>0.4 Shell and plate heat exchanger.

3. The shell and plate heat exchanger according to claim 1 or 2, A direction perpendicular to the first direction when viewed from the top-bottom direction is defined as a second direction, the row of holes (70) includes a first row of holes (71) and a second row of holes (72) arranged at an interval in the second direction from the first row of holes (71); In the first row of holes (71) or the second row of holes (72), the condition h / p>0.1 is satisfied. Shell and plate heat exchanger.

4. The shell and plate heat exchanger according to claim 1 or 2, The refrigerant is a single refrigerant that is an HFO refrigerant or a mixed refrigerant that contains an HFO refrigerant as a component. Shell and plate heat exchanger.

5. A shell-and-plate heat exchanger (10) according to claim 1 or 2; a refrigerant circuit (1a) through which the refrigerant that has undergone heat exchange in the shell-and-plate heat exchanger (10) flows. Refrigeration equipment.

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