Shell-and-plate type heat exchanger and refrigeration device

Abstract

A partitioning member (60) is disposed above a refrigerant inlet (21) and below a plate stack (30). The partitioning member (60) extends in a first direction that is a stacking direction of heat transfer plates (40). The partitioning member (60) has a hole row (70) including a plurality of holes (65) spaced apart from one another in the first direction. An average pitch p [mm] of the plurality of holes (65) in the hole row (70) and a distance h [mm] from an upper surface of the partitioning member (60) to a lower surface of the plate stack (30) satisfies the condition h / p > 0.1.

Description

TECHNICAL FIELD

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

[0002] Patent Document 1 discloses a shell-and-plate heat exchanger that includes a plate stack including a plurality of heat transfer plates stacked together and a partitioning member (a distribution plate) located below the plate stack to define a distribution chamber.

[0003] The partitioning member has a plurality of holes. A refrigerant that has flowed into the distribution chamber from a refrigerant inlet spreads in a stacking direction of the heat transfer plates, and flows out of the plurality of holes and is supplied to the plate stack.CITATION LISTPATENT DOCUMENT

[0004] Patent Document 1: Japanese Unexamined Patent Publication No. 2021-110515SUMMARY OF THE INVENTIONTECHNICAL PROBLEM

[0005] If the distance between the plate stack and the partitioning member is short, the refrigerant that has flowed out from the holes of the partitioning member may fail to spread sufficiently in the stacking direction of the heat transfer plates, and the heat exchange efficiency of the heat exchanger as a whole may be lowered.

[0006] It is an object of the present disclosure to enable distribution of a refrigerant in a stacking direction of heat transfer plates.SOLUTION TO THE PROBLEM

[0007] A first aspect of the present disclosure includes: a shell (11) forming an internal space (15), the shell (11) having a refrigerant inlet (21) at a lower portion and a refrigerant outlet (22) at an upper portion; a plate stack (30) housed in the internal space (15), the plate stack (30) including a plurality of heat transfer plates (40) stacked in a plate thickness direction and joined together, the plate stack (30) having refrigerant channels (31) through which a refrigerant flows and heating medium channels (32) through which a heating medium flows; and a partitioning member (60) disposed above the refrigerant inlet (21) and below the plate stack (30), the partitioning member (60) extending in a first direction that is a stacking direction of the heat transfer plates (40), the partitioning member (60) having a hole row (70) including a plurality of holes (65) spaced apart from one another in the first direction, an average pitch p [mm] of the plurality of holes (65) in the hole row (70) and a distance h [mm] from an upper surface of the partitioning member (60) to a lower surface of the plate stack (30) satisfying a condition h / p > 0.1.

[0008] According to the first aspect, 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 partitioning member (60) to the lower surface of the plate stack (30) are appropriately determined, thereby making it possible to uniformly distribute the refrigerant in the stacking direction of the heat transfer plates and mitigate the decrease in heat exchange efficiency.

[0009] A second aspect of the present disclosure is an embodiment of the shell-and-plate heat exchanger of the first aspect. In the second aspect, a condition h / p > 0.4 is satisfied.

[0010] According to the second aspect, it is possible to distribute the refrigerant in the stacking direction of the heat transfer plates (40) more uniformly and mitigate the decrease in heat exchange efficiency.

[0011] A third aspect of the present disclosure is an embodiment of the shell-and-plate heat exchanger of the first or second aspect. In the third aspect, a direction orthogonal to the first direction when viewed in an up-and-down direction is a second direction, the hole row (70) includes a first hole row (71) and a second hole row (72) spaced apart from the first hole row (71) in the second direction, and in the first hole row (71) or the second hole row (72), a condition h / p > 0.1 is satisfied.

[0012] According to the third aspect, parameters of the first hole row (71) or the second hole row (72) are determined to satisfy the above condition, thereby making it possible to uniformly distribute the refrigerant in the stacking direction of the heat transfer plates (40) and mitigate the decrease in heat exchange efficiency.

[0013] A fourth aspect of the present disclosure is an embodiment of the shell-and-plate heat exchanger of any one of the first to third aspects. In the fourth aspect, the refrigerant is a single component refrigerant, which is an HFO refrigerant, or a refrigerant mixture containing the HFO refrigerant as a component.

[0014] According to the fourth aspect, a single component refrigerant, which is an HFO refrigerant, or a refrigerant mixture containing the HFO refrigerant as a component can be used as the refrigerant.

[0015] A fifth aspect of the present disclosure is directed to a refrigeration apparatus including: the shell-and-plate heat exchanger (10) of any one of the first to fourth aspects; and a refrigerant circuit (1a) through which a refrigerant having exchanged heat in the shell-and-plate heat exchanger (10) flows.

[0016] According to the fifth aspect, it is possible to provide the refrigeration apparatus including the shell-and-plate heat exchanger (10) and the refrigerant circuit (1a).BRIEF DESCRIPTION OF THE DRAWINGS

[0017] [FIG. 1] FIG. 1 is a refrigerant circuit diagram illustrating a configuration of a refrigeration apparatus according to a first embodiment. [FIG. 2] FIG. 2 is a side cross-sectional view illustrating a configuration of a shell-and-plate heat exchanger. [FIG. 3] FIG. 3 is a front cross-sectional view illustrating the configuration of the shell-and-plate heat exchanger. [FIG. 4] FIG. 4 is a side cross-sectional view illustrating a configuration of a plate stack. [FIG. 5] FIG. 5 is a plan view illustrating a configuration of a partitioning member. [FIG. 6] FIG. 6 is a plan cross-sectional view illustrating the configuration of the partitioning member. [FIG. 7] FIG. 7 is a plan view for describing the arrangement of holes in the partitioning member. [FIG. 8] FIG. 8 is a graph showing the relationship between h / p and the proportion of the effective range of a heat exchanger. [FIG. 9] FIG. 9 is a table showing the average pitch in each hole row, h / p, and determination results. [FIG. 10] FIG. 10 is a plan view for describing the arrangement of holes in a partitioning member according to a second embodiment. [FIG. 11] FIG. 11 is a table showing the average pitch in each hole row, h / p, and determination results. [FIG. 12] FIG. 12 is a plan view for describing the arrangement of holes in a partitioning member according to a third embodiment. [FIG. 13] FIG. 13 is a table showing the average pitch in each hole row, h / p, and determination results. [FIG. 14] FIG. 14 is a plan view for describing the arrangement of holes in a partitioning member according to a fourth embodiment. [FIG. 15] FIG. 15 is a table showing the average pitch in each hole row, h / p, and determination results. [FIG. 16] FIG. 16 is a plan view for describing the arrangement of holes in a partitioning member according to a fifth embodiment. [FIG. 17] FIG. 17 is a table showing the average pitch in each hole row, h / p, and determination results. DESCRIPTION OF EMBODIMENTS«First Embodiment»

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

[0019] The refrigeration apparatus (1) is an air conditioner, for example. The air conditioner may be any of a cooling-only apparatus, a heating-only apparatus, or an air conditioner switchable between cooling and heating. In this case, the air conditioner has a switching mechanism (e.g., a four-way switching valve) configured to switch the direction of circulation of the refrigerant. The refrigeration apparatus (1) may be a water heater, a chiller unit, or a cooling apparatus configured to cool air in an internal space. The cooling apparatus cools air in a refrigerator, a freezer, a container, or the like.<Heat Exchanger>

[0020] As illustrated 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). The refrigerant flows into the internal space (15) of the shell (11). The plate stack (30) is housed in the internal space (15) of the shell (11). The refrigerant exchanges heat with a heating medium flowing in the plate stack (30). Accordingly, the heat exchanger (10) allows the refrigerant that has flowed into the internal space (15) of the shell (11) to evaporate, and thus, functions as an evaporator.

[0021] Here, the refrigerant used is a single component refrigerant, which is a hydrofluoroolefin (HFO) refrigerant, or a refrigerant mixture containing the HFO refrigerant as a component. Specifically, R1233zd(E), R1234ze(E), R513A, or any other suitable refrigerant is used. As the heating medium, water and brine are used, for example.<Shell>

[0022] The shell (11) includes a cylindrical body (12), support legs (13), and closing members (14). The cylindrical body (12) is a circular cylindrical member extending in a horizontal direction and having openings on both axial ends.

[0023] The support legs (13) are located on both axial end sides of the cylindrical body (12). Each of the support legs (13) has a hole corresponding to the opening of the cylindrical body (12). The support legs (13) are attached to the cylindrical body (12) by welding, for example.

[0024] The closing members (14) close the respective openings on both ends of the cylindrical body (12). The closing members (14) are fastened to the associated support legs (13) through clamping bolts, for example.

[0025] The shell (11) has the internal space (15) defined by the cylindrical body (12), the support legs (13), and the closing members (14). The shell (11) is arranged so that its axial direction coincides with the horizontal direction. The internal space (15) stores the liquid refrigerant. The 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 formed at a lower portion of the shell (11). The refrigerant inlet (21) is formed at the bottom 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 formed in a lower portion of the shell (11) at a central position in the stacking direction of the plate stack (30).

[0027] The refrigerant outlet (22) is formed at an upper portion of the shell (11). The refrigerant evaporated in the internal space (15) is emitted to the outside of the shell (11) through the refrigerant outlet (22). The refrigerant inlet (21) and the refrigerant outlet (22) are connected to the refrigerant circuit (1a).

[0028] The shell (11) has a heating medium inlet (23) and a heating medium outlet (24). The heating medium inlet (23) and the heating medium outlet (24) are tubular members.

[0029] The heating medium inlet (23) penetrates one axial end of the shell (11). The heating medium inlet (23) is connected to a heating medium introduction path (33) of the plate stack (30). The heating medium inlet (23) supplies the heating medium to the plate stack (30). The refrigerant that has flowed into the internal space (15) of the shell (11) exchanges heat with the heating medium that has flowed into heating medium channels (32), which will be described later, of the plate stack (30).

[0030] The heating medium outlet (24) penetrates the one axial end of the shell (11) above the heating medium inlet (23). The heating medium outlet (24) is connected to a heating medium emission path (34) of the plate stack (30). The heating medium outlet (24) emits the heating medium from the plate stack (30). The heating medium inlet (23) may be located above the heating medium outlet (24).

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

[0032] A mesh member (50) is located 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 channels (31) and flowed out from the upper surface of the plate stack (30). The mesh member (50) is in a thick plate shape made of a stack of metal meshes, for example. The refrigerant can pass through the mesh member (50) in the thickness direction. The mesh member (50) is supported by supports (52) (see FIG. 3). The supports (52) are fixed to the inner surface of the shell (11).<Plate Stack>

[0033] The plate stack (30) includes a plurality of heat transfer plates (40) stacked and joined together in a plate thickness direction. The plate stack (30) is housed in the internal space (15) of the shell (11) so that the stacking direction of the heat transfer plates (40) coincides with the horizontal direction. The plate stack (30) has a length of, for example, 600 mm to 1500 mm in its width direction.

[0034] As illustrated in FIG. 4, the heat transfer plates (40) include first plates (40a) and second plates (40b). The first plates (40a) and the second plates (40b) are alternately stacked to form the plate stack (30). The second plates (40b) correspond to the first plates (40a) turned back to front.

[0035] In the following description, for each of the first plates (40a) and the second plates (40b), a surface on the left side in FIG. 4 will be referred to as a "front surface," and a surface on the right side in FIG. 4 will be referred to as a "back surface."<Heating Medium Introduction Path and Heating Medium Emission Path>

[0036] Each of the first plates (40a) has an inlet protrusion (41a) and an outlet protrusion (43a). The inlet protrusion (41a) and the outlet protrusion (43a) are portions of the first plate (40a) bulged toward the front surface.

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

[0038] The outlet protrusion (43a) is formed in an upper portion of the first plate (40a). A first outlet hole (44a) is formed in a center portion of the outlet protrusion (43a). The first outlet hole (44a) is a circular hole penetrating the first plate (40a) in the thickness direction.

[0039] Each of the second plates (40b) has an inlet recess (41b) and an outlet recess (43b). The inlet recess (41b) and the outlet recess (43b) are portions of the second plate (40b) bulged toward the back surface.

[0040] The inlet recess (41b) is formed in a lower portion of the second plate (40b). A second inlet hole (42b) is formed in a center portion of the inlet recess (41b). The second inlet hole (42b) is a circular hole penetrating 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 an upper portion of the second plate (40b). A second outlet hole (44b) is formed in a center portion of the outlet recess (43b). The second outlet hole (44b) is a circular hole penetrating 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), each first plate (40a) and an adjacent one of the second plates (40b) on the back surface side of the first plate (40a) are welded together at their peripheral portions along the entire perimeter. These plates may be brazed together.

[0043] In the plate stack (30), the first inlet hole (42a) of each first plate (40a) overlaps the second inlet hole (42b) of an adjacent one of the second plates (40b) on the front surface side of the first plate (40a). The rims of the overlapping first inlet hole (42a) and second inlet hole (42b) are welded together along the entire perimeter. These rims may be brazed together. The first inlet hole (42a) and the second inlet hole (42b) communicate with the heating medium channels (32), which will be described later, to introduce the heating medium into the heating medium channels (32).

[0044] In the plate stack (30), the first outlet hole (44a) of each first plate (40a) overlaps the second outlet hole (44b) of an adjacent one of the second plates (40b) on the front surface side of the first plate (40a). The rims of the overlapping first outlet hole (44a) and second outlet hole (44b) are welded together along the entire perimeter. These rims may be brazed together. The first outlet hole (44a) and the second outlet hole (44b) communicate with the heating medium channels (32), which will be described later, to emit the heating medium from the heating medium channels (32).

[0045] In the plate stack (30), the inlet protrusions (41a) and first inlet holes (42a) of the first plates (40a) and the inlet recesses (41b) and second inlet holes (42b) of the second plates (40b) form the heating medium introduction path (33).

[0046] In the plate stack (30), the outlet protrusions (43a) and first outlet holes (44a) of the first plates (40a) and the outlet recesses (43b) and second outlet holes (44b) of the second plates (40b) form the heating medium emission path (34).

[0047] The heating medium introduction path (33) is a passage extending in the stacking direction of the heat transfer plates (40) in the plate stack (30). The heating medium introduction path (33) is a passage isolated from the internal space (15) of the shell (11), and allows all the heating medium channels (32) to communicate with the heating medium inlet (23).

[0048] The heating medium emission path (34) is a passage extending in the stacking direction of the heat transfer plates (40) in the plate stack (30). The heating medium emission path (34) is a passage isolated from the internal space (15) of the shell (11), and allows all the heating medium channels (32) to communicate with the heating medium outlet (24).<Refrigerant Channel and Heating Medium Channel>

[0049] The plate stack (30) includes a refrigerant channel (31) and a heating medium channel (32). Multiple refrigerant channels (31) and multiple heating medium channels (32) are formed with the heat transfer plate (40) interposed therebetween. The heat transfer plate (40) separates the refrigerant channel (31) and the heating medium channel (32) from each other. Each of the first plate (40a) and the second plate (40b) includes repetition of long and narrow ridges and grooves.

[0050] Each first plate (40a) includes first front-side protrusions (45a) and first back-side protrusions (47a) alternately arranged. The first front-side protrusions (45a) bulge toward the front side of the first plate (40a). The first back-side protrusions (47a) bulge toward the back side of the first plate (40a).

[0051] Each second plate (40b) includes second front-side protrusions (47b) and second back-side protrusions (45b) alternately arranged. The second front-side protrusions (47b) bulge toward the front side of the second plate (40b). The second back-side protrusions (45b) bulge toward the back side of the second plate (40b).

[0052] Each of the refrigerant channels (31) is a channel sandwiched between the front surface of the first plate (40a) and the back surface of the second plate (40b). The refrigerant channel (31) is a channel that communicates with the internal space (15) of the shell (11) and allows the refrigerant to flow therethrough. Specifically, the refrigerant channels (31) include channels each formed between the front surface of the first back-side protrusion (47a) and the back surface of the second front-side protrusion (47b).

[0053] Each of the heating medium channels (32) is a channel sandwiched between the back surface of the first plate (40a) and the front surface of the second plate (40b). The heating medium channel (32) is a channel isolated from the internal space (15) of the shell (11) and allows the heating medium to flow therethrough. Specifically, the heating medium channels (32) include channels each formed between the back surface of the first front-side protrusion (45a) and the front surface of the second back-side protrusion (45b).<Flows of Heating Medium and Refrigerant>

[0054] Flows of the heating medium and the refrigerant in the heat exchanger (10) will be described. As illustrated in FIG. 4, the heating medium flows from the heating medium inlet (23) into the heating medium introduction path (33). The heating medium flowing through the heating medium introduction path (33) flows through the heating medium channels (32) from the first inlet holes (42a) and the second inlet holes (42b) toward the first outlet holes (44a) and the second outlet holes (44b).

[0055] Specifically, the heating medium flowing through the heating medium introduction path (33) enters the heating medium channel (32). The heating medium flows along the heating medium channel (32), and enters an adjacent heating medium channel (32) above the heating medium channel (32). In this manner, the heating medium flows upward while flowing from one end to the other of the heat transfer plate (40).

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

[0057] In the internal space (15) of the shell (11), a large portion of the plate stack (30) is immersed in the liquid refrigerant, and the liquid refrigerant flows into the refrigerant channels (31) of the plate stack (30). The liquid refrigerant that has flowed into the refrigerant channels (31) is in contact with the heat transfer plates (40), and absorbs heat from the heating medium flowing through the heating medium channels (32) and evaporates. The gas refrigerant generated in the refrigerant channels (31) flows upward to flow out of the refrigerant channels (31) and is blown upward from the upper 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 the 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).<Partitioning Member>

[0059] The partition plate (61) serves as a partition between the plate stack (30) and the refrigerant inlet (21) (see FIG. 2). As illustrated in FIGS. 5 and 6, the partitioning member (60) includes the partition plate (61), a bottom plate (62), a peripheral wall (63), and a pair of guide plates (64).

[0060] The partition plate (61) extends along the stacking direction of the heat transfer plates (40). Hereinafter, the stacking direction of the heat transfer plates (40) will be referred to as a "first direction," and the width direction of the partition plate (61) orthogonal to the first direction when viewed in the up-and-down direction will be referred to as a "second direction."

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

[0062] The partitioning member (60) has an internal channel (66). The refrigerant that has flowed into the internal channel (66) from the refrigerant inlet (21) flows through the internal channel (66). The internal channel (66) is formed in a space surrounded by the partition plate (61), the bottom plate (62), and the peripheral wall (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) are spaced apart from each other in the second direction and extend along the first direction. Both ends of each of the pair of guide plates (64) in the first direction are located inward of the peripheral wall (63). Thus, a gap is formed between the left end portions of the guide plates (64) and the peripheral wall (63), and between the right end portions of the guide plates (64) and the peripheral wall (63).

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

[0065] The second channels (68) are spaces formed between the upper guide plate (64) in FIG. 6 and the upper end portion of the peripheral wall (63) and between the lower guide plate (64) in FIG. 6 and the lower end portion of the peripheral wall (63).

[0066] The second channels (68) guide the refrigerant that has turned back at ends of the first channel (67) in the first direction and which has passed through the first channel (67), to central portions in the first direction.

[0067] The partitioning member (60) has hole rows (70) each including a plurality of holes (65) spaced apart from one another in the first direction. The plurality of holes (65) are formed in the partition plate (61).

[0068] The hole rows (70) include 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 sequentially from the top in FIG. 5, and are spaced apart from one another in the second direction.

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

[0070] As described, the refrigerant that has flowed into the internal space (15) of the shell (11) through the refrigerant inlet (21) passes through the first channel (67) of the partitioning member (60) and flows along the first direction. The refrigerant that has turned back at the ends of the first channel (67) in the first direction flows through the second channels (68).

[0071] The refrigerant flows out from the plurality of holes (65) of the partition plate (61) toward the plate stack (30). In this manner, the partitioning member (60) allows the refrigerant to flow so as to spread from the refrigerant inlet (21) toward its both ends in the first direction; therefore, the refrigerant can be distributed in the stacking direction of the heat transfer plates (40).

[0072] If the distance between the plate stack (30) and the partitioning member (60) is short, the refrigerant that has flowed out from the holes (65) of the partitioning member (60) may fail to spread sufficiently in the stacking direction of the heat transfer plates (40), and the heat exchange efficiency of the heat exchanger (10) as a whole may be lowered.

[0073] To address this, in this embodiment, the pitch of the plurality of holes (65) and the distance between the partitioning member (60) and the plate stack (30) are appropriately determined so that the refrigerant can be distributed appropriately in the first direction.

[0074] Specifically, the average pitch of the plurality of holes (65) in each hole row (70) is referred to as p, and the distance from an upper surface of the partitioning member (60) to a lower surface of the plate stack (30) is referred to as h. The average pitch p is an arithmetic mean of the pitches of the plurality of holes (65), and is obtained by dividing the sum of the pitches of the plurality of holes (65) by the number of pitches.

[0075] As illustrated in FIG. 7, the pitches of the plurality of holes (65) in the hole row (70) are referred to as p1, and the inside diameter of the hole (65) is referred to as d1. In the example illustrated in FIG. 7, the first hole row (71) includes seventeen holes (65). The pitches p1 of the plurality of holes (65) in the first hole row (71) are all the same. The inside diameters d1 of the holes (65) in the first hole row (71) are all the same. Thus, in the example illustrated in FIG. 7, the average pitch p of the plurality of holes (65) in the first hole row (71) is p = p1.

[0076] As for the second hole row (72), the third hole row (73), and the fourth hole row (74), as well, the second hole row (72), the third hole row (73), and the fourth hole row (74) each have seventeen holes (65). As for the plurality of holes (65) in the second hole row (72), the third hole row (73), and the fourth hole row (74), the pitches p1 are all the same, and the inside diameters d1 of the holes (65) are all the same. The average pitch p of the plurality of 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 plurality of holes (65) in the first hole row (71) is equal to the pitch of the plurality of holes (65) in the second hole row (72). The pitch of the plurality of holes (65) in the first hole row (71), the pitch of the plurality of holes (65) in the second hole row (72), the pitch of the plurality of holes (65) in the third hole row (73), and the pitch of the plurality of holes (65) in the fourth hole row (74) are equal.

[0078] FIG. 8 is a graph showing the relationship between the parameter h / p and the proportion of the effective range of the heat exchanger (10). In FIG. 8, a case where the performance of the heat exchanger (10) is 100% is associated with "1.0" on the graph, thereby defining the proportion of the effective range of the heat exchanger (10). In FIG. 8, the dots indicate the proportions of the effective range of the heat exchanger at predetermined h / p. In FIG. 8, the dotted line indicates an approximation curve of h / p values greater than 0.1.

[0079] FIG. 8 shows that the proportion of the effective range of the heat exchanger (10) drops sharply in the range in which h / p is 0.1 or less. It is found that the proportion deviates downward significantly from the approximation curve at h / p values greater than 0.1 and that the range where 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 proportion of the effective range of the heat exchanger (10) is 0.5 or more. Accordingly, the heat exchanger (10) can be used effectively. When h / p is greater than 0.4, the proportion of the effective range of the heat exchanger (10) further increases. Accordingly, the heat exchanger (10) can be used more effectively.

[0081] In this embodiment, the average pitch p of the first hole row (71), the second hole row (72), the third hole row (73), or the fourth hole row (74) and the distance h are determined to satisfy the condition h / p > 0.1. More preferably, it is desirable that the condition h / p > 0.4 be satisfied.

[0082] The parameter h / p will now be considered using specific numerical values. In the example shown in FIG. 7, the pitch of the plurality of holes (65) is set to p1 = 60 [mm], the inside diameter of the holes (65) to d1 = 6 [mm], and the distance to h = 30 [mm].

[0083] As shown in FIG. 9, in each of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74), h / p = 0.5, and the condition h / p > 0.1 is satisfied. Since the entirety of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) averages h / p = 0.5, the condition h / p > 0.1 is satisfied.-Advantages of First Embodiment-

[0084] According to this embodiment, the average pitch p of the plurality of holes (65) in each hole row (70) and the distance h from the upper surface of the partitioning member (60) to the lower surface of the plate stack (30) are appropriately determined, thereby making it possible to uniformly distribute the refrigerant in the stacking direction of the heat transfer plates and mitigate the decrease in heat exchange efficiency.

[0085] According to this embodiment, the condition h / p > 0.4 is satisfied, thereby making it possible to distribute the refrigerant in the stacking direction of the heat transfer plates (40) more uniformly and mitigate the decrease in heat exchange efficiency.

[0086] According to this embodiment, parameters of the first hole row (71) or the second hole row (72) are determined to satisfy the above condition, thereby making it possible to uniformly distribute the refrigerant in the stacking direction of the heat transfer plates (40) and mitigate the decrease in heat exchange efficiency.

[0087] According to this embodiment, a single component refrigerant, which is an HFO refrigerant, or a refrigerant mixture containing the HFO refrigerant as a component can be used as the refrigerant.

[0088] According to this embodiment, it is possible to provide the refrigeration apparatus including the shell-and-plate heat exchanger (10) and the refrigerant circuit (1a).

[0089] «Second Embodiment»

[0090] In the following description, the same reference characters designate the same components as those of the first embodiment, and the description is focused only on the differences.

[0091] In the example illustrated in FIG. 10, the pitches of a plurality of holes (65) in each of hole rows (70) include p1 and p2. The p1 and p2 are different lengths. The hole rows (70) include a first hole row (71) and a second hole row (72). The hole rows (70) further include a third hole row (73) and a fourth hole row (74).

[0092] Each of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) has fourteen holes (65). The pitch of the plurality of holes (65) in the first hole row (71) includes p1 and p2. The pitch of the plurality of holes (65) in the second hole row (72) includes p1 and p2. The pitch of the plurality of holes (65) in the third hole row (73) includes p1 and p2. The pitch of the plurality of holes (65) in the fourth hole row (74) includes p1 and p2.

[0093] The pitch of the plurality of holes (65) located in the middle portion of each hole row (70) in the first direction is p2. The pitch of the four holes (65) located in the middle portion of each of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) in the first direction is p2. The pitch of the remaining holes (65) is p1. Here, p1 < p2. The inside 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.

[0094] In the example illustrated in FIG. 10, the pitches of the plurality of holes (65) are set to p1 = 60 [mm] and p2 = 120 [mm], the inside diameter of the holes (65) to d1 = 6 [mm], and the distance to h = 30 [mm].

[0095] As shown in FIG. 11, in each of 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. In each 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, and the condition h / p > 0.1 is satisfied. Since the entirety of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) averages h / p = 0.41, the condition h / p > 0.1 is satisfied.«Third Embodiment»

[0096] As illustrated in FIG. 12, each of the first hole row (71) and the fourth hole row (74) has seventeen 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. The inside diameters d1 of the holes (65) in the first hole row (71) and the fourth hole row (74) are all the same. Thus, in the example illustrated 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.

[0097] Each of the second hole row (72) and the third hole row (73) has fourteen holes (65). The pitch of the plurality of holes (65) in the second hole row (72) and the third hole row (73) includes p1 and p2. The pitch of the four holes (65) located in the middle portion in the first direction is p2. The pitch of the remaining holes (65) is p1. Here, p1 < p2. The inside diameters d1 of the holes (65) in the second hole row (72) and the third hole row (73) are all the same.

[0098] In the example illustrated in FIG. 12, the pitches of the plurality of holes (65) are set to p1 = 60 [mm] and p2 = 120 [mm], the inside diameter of the holes (65) to d1 = 6 [mm], and the distance to h = 30 [mm].

[0099] As shown in FIG. 13, in the first hole row (71) and the fourth hole row (74), the average pitch is p = 60. In the first hole row (71) and the fourth hole row (74), h / p = 0.5, and the condition h / p > 0.1 is satisfied.

[0100] 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, and the condition h / p > 0.1 is satisfied.

[0101] Since the entirety of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) averages h / p = 0.45, the condition h / p > 0.1 is satisfied.«Fourth Embodiment»

[0102] As illustrated in FIG. 14, each of the first hole row (71) and the fourth hole row (74) has seventeen 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. The inside diameters d1 of the holes (65) in the first hole row (71) and the fourth hole row (74) are all the same. Thus, in the example illustrated 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.

[0103] Each of the second hole row (72) and the third hole row (73) has four holes (65). The pitch of the plurality of holes (65) in the second hole row (72) and the third hole row (73) includes p1, p2, and p3. The pitch of the two holes (65) located in the middle portion in the first direction is p2. The pitch of the remaining holes (65) is p3. Here, p1 < p2 < p3. The inside diameters d1 of the holes (65) in the second hole row (72) and the third hole row (73) are all the same.

[0104] In the example illustrated in FIG. 14, the pitches of the plurality of holes (65) are set to p1 = 60 [mm], p2 = 120 [mm], and p3 = 420 [mm], the inside diameter of the holes (65) to d1 = 6 [mm], and the distance to h = 30 [mm].

[0105] As shown in FIG. 15, in the first hole row (71) and the fourth hole row (74), the average pitch is p = 60. In the first hole row (71) and the fourth hole row (74), h / p = 0.5, and the condition h / p > 0.1 is satisfied.

[0106] In the second hole row (72) and the third hole row (73), the average pitch is p = 320. 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.

[0107] However, since the entirety of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) averages h / p = 0.3, the condition h / p > 0.1 is satisfied.«Fifth Embodiment»

[0108] In the example illustrated in FIG. 16, each of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) has fourteen holes (65). The pitch 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) includes p1 and p2. The pitch of the four holes (65) located in the middle portion in the first direction is p2. The pitch of the remaining holes (65) is p1. Here, p1 < p2.

[0109] The inside 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. In FIG. 16, the inside diameters of the first and second holes (65) from the left and the first and second holes (65) from the right are d2. The inside diameters of the remaining holes (65) are d1.

[0110] In the example illustrated in FIG. 16, the pitches of the plurality of holes (65) are set to p1 = 60 [mm] and p2 = 120 [mm], the inside diameters of the holes (65) to d1 = 6 [mm] and d2 = 8 [mm], and the distance to h = 30 [mm].

[0111] As shown in FIG. 17, in each of 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. In each 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, and the condition h / p > 0.1 is satisfied. Since the entirety of the first hole row (71), the second hole row (72), the third hole row (73), and the fourth hole row (74) averages h / p = 0.41, the condition h / p > 0.1 is satisfied.

[0112] Here, in the example shown in FIG. 17, an excessively large difference between the inside diameters of the different holes (65) may affect performance; thus, it is preferable to set the inside diameters of the holes (65) so as to satisfy the condition d2 ≤ 2 × d1, for example.«Other Embodiments»

[0113] It will be understood that the embodiments and variations described above can be modified with various changes in form and details without departing from the spirit and scope of the claims. The elements according to the embodiments, the variations thereof, and the other embodiments may be combined and replaced with each other. In addition, the expressions of "first," "second," "third," . . . , in the specification and claims are used to distinguish the terms to which these expressions are given, and do not limit the number and order of the terms.INDUSTRIAL APPLICABILITY

[0114] As can be seen from the foregoing description, the present disclosure is useful for a shell-and-plate heat exchanger and a refrigeration apparatus.DESCRIPTION OF REFERENCE CHARACTERS

[0115] 1Refrigeration Apparatus 1aRefrigerant Circuit 10Shell-and-Plate Heat Exchanger 11Shell 15Internal Space 21Refrigerant Inlet 22Refrigerant Outlet 30Plate Stack 31Refrigerant Channel 32Heating Medium Channel 40Heat Transfer Plate 60Partitioning Member 65Hole 70Hole Row 71First Hole Row 72Second Hole Row

Claims

1. A shell-and-plate heat exchanger comprising: a shell (11) forming an internal space (15), the shell (11) having a refrigerant inlet (21) at a lower portion and a refrigerant outlet (22) at an upper portion; a plate stack (30) housed in the internal space (15), the plate stack (30) including a plurality of heat transfer plates (40) stacked in a plate thickness direction and joined together, the plate stack (30) having refrigerant channels (31) through which a refrigerant flows and heating medium channels (32) through which a heating medium flows; and a partitioning member (60) disposed above the refrigerant inlet (21) and below the plate stack (30), the partitioning member (60) extending in a first direction that is a stacking direction of the heat transfer plates (40), the partitioning member (60) having a hole row (70) including a plurality of holes (65) spaced apart from one another in the first direction, an average pitch p [mm] of the plurality of holes (65) in the hole row (70) and a distance h [mm] from an upper surface of the partitioning member (60) to a lower surface of the plate stack (30) satisfying a condition h / p > 0.1.

2. The shell-and-plate heat exchanger of claim 1, wherein a condition h / p > 0.4 is satisfied.

3. The shell-and-plate heat exchanger of claim 1 or 2, wherein a direction orthogonal to the first direction when viewed in an up-and-down direction is a second direction, the hole row (70) includes a first hole row (71) and a second hole row (72) spaced apart from the first hole row (71) in the second direction, and in the first hole row (71) or the second hole row (72), a condition h / p > 0.1 is satisfied.

4. The shell-and-plate heat exchanger of any one of claims 1 to 3, wherein the refrigerant is a single component refrigerant, which is an HFO refrigerant, or a refrigerant mixture containing the HFO refrigerant as a component.

5. A refrigeration apparatus, comprising: the shell-and-plate heat exchanger (10) of any one of claims 1 to 4; and a refrigerant circuit (1a) through which a refrigerant having exchanged heat in the shell-and-plate heat exchanger (10) flows.

Images