Shell-and-plate type heat exchanger and refrigeration device

Abstract

A partition member (60) is disposed above a refrigerant inlet (21) and below a plate laminate (30). The partition member (60) extends in a first direction, which is the stacking direction of 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. The average pitch p [mm] of the plurality of holes (65) in the hole row (70) and the distance h [mm] from the upper surface of the partition member (60) to the lower surface of the plate laminate (30) satisfy a condition of h / p > 0.1.

Description

Shell and plate type heat exchanger and refrigeration equipment

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

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

[0004] Japanese Patent Application Laid-Open No. 2021-110515

[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.

[0007] A first aspect of the present disclosure provides a heat transfer system including: 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 formed therein 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 heat transfer device (10) that is located above the refrigerant inlet (21) and that is connected to the plate stack (30). and a partition member (60) arranged below the upper surface of the heat transfer plate (40) and extending in a first direction which is the stacking direction of the heat transfer plates (40), wherein 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, and an average pitch p [mm] of the plurality of holes (65) in the row of holes (70) and a distance h [mm] 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 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, 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 suppressed.

[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 configuring 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 plate (40), thereby preventing a decrease in heat exchange efficiency.

[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 the fifth aspect, a refrigeration system can be provided, which includes a shell-and-plate heat exchanger (10) and a refrigerant circuit (1a).

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

[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 cooling-only unit, a heating-only unit, 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. The cooling device cools the air inside a refrigerator, a freezer, a container, or the like.

[0020] <Heat Exchanger> As shown in Figures 2 and 3, the heat exchanger (10) has 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 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 tubular body (12), support legs (13), and a closing member (14). The tubular 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) and are fastened to the support legs (13) by, for example, fastening bolts.

[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 an upper portion 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 medium inlet (23) penetrates one axial end of the shell (11). The heat medium inlet (23) is connected to a heat medium introduction passage (33) of the plate stack (30). The heat medium inlet (23) supplies the heat 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 medium that has flowed into a heat medium flow passage (32) of the plate stack (30) described below.

[0030] The heat medium outlet (24) penetrates one axial end of the shell (11) at a position higher than the heat medium inlet (23). The heat medium outlet (24) is connected to a heat medium discharge path (34) of the plate stack (30). The heat medium outlet (24) discharges the heat medium from the plate stack (30). Note that the heat medium inlet (23) may be configured to be located higher than the heat 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 plurality of 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 has passed through the refrigerant flow path (31) and flowed 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 to one another. 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) horizontal. The length of the plate stack (30) in the width direction is, for example, 600 to 1500 mm.

[0034] As shown in Fig. 4, the heat transfer plate (40) includes a first plate (40a) and a second plate (40b). In the plate stack (30), the first plates (40a) and the second plates (40b) are stacked alternately. 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 Inlet 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 (41 a) is formed in the lower part of the first plate (40 a). A first inlet hole (42 a) is formed in the center of the inlet protrusion (41 a). The first inlet hole (42 a) is a circular hole that penetrates the first plate (40 a) 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. Alternatively, they 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 a heat medium flow path (32) described below and introduce a 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 a heat medium flow path (32) described below, and allow the heat medium to flow out of 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 transfer medium introduction passage (33).

[0046] In the plate stack (30), the heat medium discharge passage (34) is formed by the outlet protrusion (43a) and the first outlet hole (44a) of the first plate (40a) and the outlet recess (43b) and the second outlet hole (44b) of the second plate (40b).

[0047] The heat medium introduction channel (33) is a passage extending in the stacking direction of the heat transfer plates (40) in the plate stack (30). The heat medium introduction channel (33) 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 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 Channels, Heat Medium Channels> The plate stack (30) has refrigerant channels (31) and heat medium channels (32). A plurality of the refrigerant channels (31) and a plurality of the heat medium channels (32) are formed with the heat transfer plates (40) interposed therebetween. The refrigerant channels (31) and the heat medium channels (32) are separated from each other by the heat transfer plates (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 convex portions (45a) and first back-side convex portions (47a) alternately and repeatedly. The first front-side convex portions (45a) bulge out toward the front side of the first plate (40a). The first back-side convex portions (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 Medium and Refrigerant> The flow of the heat medium and 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 introduction 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 passes through the refrigerant inlet (21) and flows into the internal 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 in 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) captures 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 a partition plate (61), a bottom plate (62), a peripheral wall (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 from 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 portions of the guide plates (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 by a space provided 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 Figure 6, and a space provided between the lower guide plate (64) and the lower end of the peripheral wall portion (63) in Figure 6.

[0066] The second flow path (68) is turned 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 row of holes (70) includes a first row of holes (71), a second row of holes (72), a third row of holes (73), and a fourth row of holes (74). The first row of holes (71), the second row of holes (72), the third row of holes (73), and the fourth row of holes (74) are arranged in this 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 flowing from the refrigerant inlet (21) into the internal space (15) of the shell (11) passes through the first flow path (67) of the partition member (60) and flows in the first direction. The refrigerant 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 manner, 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 multiple 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 all the same. In addition, the inner diameter d1 of the holes (65) in the first hole row (71) is all the same. 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 the effective range of the heat exchanger (10). In Fig. 8, the percentage of the 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 the 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] 8, it can be seen that in the range where h / p is 0.1 or less, the ratio of the effective range of the heat exchanger (10) drops sharply. It can also be seen that the ratio significantly deviates downward from the approximation 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 range of the heat exchanger (10) is 0.5 or more. This allows the heat exchanger (10) to be used effectively. Furthermore, when h / p is greater than 0.4, the ratio of the effective range 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, and more preferably satisfies the condition h / p>0.4.

[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, the inner diameter of the holes 65 is 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 embodiment 1- 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 configuring 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 plate (40), thereby preventing a decrease in heat exchange efficiency.

[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 the present embodiment, a refrigeration system including a shell-and-plate heat exchanger (10) and a refrigerant circuit (1a) can be provided.

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

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

[0092] In the hole row (70), the pitch of the multiple holes (65) arranged in the center 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 in the center in the first direction is p2. The pitch of the remaining holes (65) is p1, where p1<p2. Furthermore, 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 p1=60 [mm], p2=120 [mm], and the inner diameter of the holes (65) is d1=6 [mm], h=30 [mm].

[0094] As shown in Figure 11, 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.

[0095] Third Embodiment As shown in Fig. 12 , the first row of holes (71) and the fourth row of holes (74) each have 17 holes (65). The pitches of the holes (65) in the first row of holes (71) and the fourth row of holes (74) are all the same. Furthermore, the inner diameters d1 of the holes (65) in the first row of holes (71) and the fourth row of holes (74) are all the same. Therefore, in the example shown in Fig. 12 , the average pitch p of the holes (65) in the first row of holes (71) and the fourth row of holes (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 holes (65) in the second hole row (72) and the third hole row (73) include p1 and p2. The pitch of the four holes (65) arranged in the center in the first direction is p2. The pitch of the remaining holes (65) is p1, where p1<p2. Furthermore, 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 p1=60 [mm], p2=120 [mm], and the inner diameter of the holes (65) is d1=6 [mm], h=30 [mm].

[0098] As shown in Fig. 13, in the first hole row (71) and the fourth hole row (74), the average pitch p is 60. Furthermore, in the first hole row (71) and the fourth hole row (74), h / p is 0.5, which satisfies 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. In the second hole row (72) and the third hole row (73), h / p = 0.41, which satisfies the condition h / p > 0.1.

[0100] When the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) are all averaged, h / p=0.45, which satisfies the condition h / p>0.1.

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

[0102] The second hole row (72) and the third hole row (73) each have four holes (65). The pitches of the multiple holes (65) in the second hole row (72) and the third hole row (73) include p1, p2, and p3. The pitch of two holes (65) arranged in the center in the first direction is p2. The pitch of the remaining holes (65) is p3, where p1<p2<p3. Furthermore, 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 Figure 14, the pitch of the multiple holes (65) is p1 = 60 [mm], p2 = 120 [mm], p3 = 420 [mm], and the inner diameter of the holes (65) is d1 = 6 [mm], h = 30 [mm].

[0104] As shown in Fig. 15, in the first hole row (71) and the fourth hole row (74), the average pitch p is 60. Furthermore, in the first hole row (71) and the fourth hole row (74), h / p is 0.5, which satisfies 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. Furthermore, in the second hole row (72) and the third hole row (73), h / p = 0.09, which does not satisfy the condition h / p > 0.1.

[0106] However, 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=0.3, which satisfies the condition h / p>0.1.

[0107] Fifth Embodiment 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 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 four holes (65) arranged in the center in the first direction is p2. The pitch of the remaining holes (65) is p1, where p1 < p2.

[0108] 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, where d1<d2. In Figure 16, the inner diameters of the first and second holes (65) from the left and the first and second holes (65) from the right are d2. The inner diameters of the remaining holes (65) are d1.

[0109] In the example shown in Figure 16, the pitch of the multiple holes (65) is p1 = 60 [mm], p2 = 120 [mm], and the inner diameters of the holes (65) are 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, and therefore it is preferable to set the inner diameter of the hole (65) so as 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.

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

[0114] REFRIGERATION SYSTEM 1a REFRIGERATOR CIRCUIT 10 PLATE-AND-SHELL HEAT EXCHANGER 11 SHELL 15 INTERNAL SPACE 21 REFRIGERATOR INLETS 22 REFRIGERATOR OUTLETS 30 PLATE LAYERS 31 REFRIGERATOR FLOW PATH 32 HEAT TRANSFER FLOW PATH 40 HEAT TRANSFER PLATES 60 PARTITIONING MEMBER 65 HOLES 70 HOLE ROW 71 FIRST HOLE ROW 72 SECOND HOLE ROW

Claims

1. A heat transfer device comprising: 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 the 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, A shell-and-plate heat exchanger in which the average pitch p [mm] of the plurality of holes (65) in the hole row (70) and the distance h [mm] 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.

2. A shell and plate heat exchanger according to claim 1, which satisfies the condition h / p>0.

4.

3. A shell-and-plate heat exchanger according to claim 1 or 2, wherein a direction perpendicular to the first direction when viewed from above is defined as a second direction, the hole rows (70) include a first hole row (71) and a second hole row (72) arranged at an interval in the second direction relative to the first hole row (71), and wherein the first hole row (71) or the second hole row (72) satisfies the condition h / p>0.

1.

4. A shell and plate type heat exchanger according to any one of claims 1 to 3, wherein the refrigerant is a single refrigerant that is an HFO refrigerant or a mixed refrigerant that contains an HFO refrigerant as a component.

5. A refrigeration system comprising: a shell-and-plate heat exchanger (10) according to any one of claims 1 to 4; and a refrigerant circuit (1a) through which refrigerant that has undergone heat exchange in the shell-and-plate heat exchanger (10) flows.

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