Heat exchanger unit, air conditioning indoor machine, and refrigeration cycle device

Abstract

To improve flow dividing performance of a heat exchanger unit comprising a flow dividing passage.SOLUTION: A flow dividing passage (70) includes: an inflow passage (71) extending in a second direction along a vertical direction; a flow dividing space (80) to which an outflow port (O) of the inflow passage (71) is connected; and a plurality of outflow passages (91, 92, and 93) comprising inflow ports (I1, I2, and I3) connected to the flow dividing space (80) respectively, and extending in the second direction. A plurality of plates (P) include a plurality of flow dividing plates (FP2, FP3, and FP4) in which plate spaces (81, 82, and 83) are formed respectively, and which is adjacent to each other in a first direction. The flow dividing space (80) is formed in such a manner that the respective plate spaces (81, 82, and 83) of the plurality of flow dividing plates (FP2, FP3, and FP4) are continuous in the first direction.SELECTED DRAWING: Figure 8

Description

[Technical field]

[0001] The present disclosure relates to a heat exchanger unit, an air conditioning indoor unit, and a refrigeration cycle apparatus. [Background technology]

[0002] Patent Document 1 discloses a header provided in a heat exchanger. The header in Patent Document 1 is constructed by stacking multiple plates. As shown in FIG. 6 of Patent Document 1, a space (division space) for dividing the flow of refrigerant is formed inside the header. One inflow path and multiple outflow paths are connected to the division space. The refrigerant that flows from the inflow path into the division space is divided into multiple outflow paths. The refrigerant divided into each outflow path is supplied to each heat transfer tube of the heat exchanger. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent Publication No. 2021-179308 Summary of the Invention [Problem to be solved by the invention]

[0004] In a flow dividing structure as described in Patent Document 1, if the refrigerant is biased toward some of the outflow paths, the performance of the heat exchanger will be reduced.

[0005] An object of the present disclosure is to improve the flow splitting performance of a heat exchanger unit having a flow splitting passage. [Means for solving the problem]

[0006] The first aspect is directed to a heat exchanger unit, and includes a heat exchange section (40A) having fins (41) and heat transfer tubes (42), and a plate stack (50) having a plurality of plates (P) stacked in a first direction along the horizontal direction, and in which a refrigerant flow path (51) communicating with the heat transfer tubes (42) is formed. A diversion flow path (70) for diversion of the refrigerant is formed in the plate stack (50). The diversion flow path (70) includes an inlet path (71) extending in a second direction along the vertical direction, a diversion space (80) to which an outlet (O) of the inlet path (71) is connected, and a plurality of outlet paths (91, 92, 93) each having an inlet (I1, I2, I3) connected to the diversion space (80) and extending in the second direction. The plurality of plates (P) includes a plurality of flow dividing plates (FP2, FP3, FP4) each having a plate space (81, 82, 83) formed therein and adjacent to each other in the first direction. The flow dividing space (80) is formed by the plate spaces (81, 82, 83) of the plurality of flow dividing plates (FP2, FP3, FP4) being continuous in the first direction.

[0007] In the first aspect, the plurality of flow-dividing plates (FP2, FP3, FP4) are stacked in the first direction, so that the plate spaces (81, 82, 83) of the respective flow-dividing plates (FP2, FP3, FP4) are continuous in the first direction. As a result, in the heat exchanger unit, the plurality of plate spaces (81, 82, 83) form a flow-dividing space (80). The flow-dividing space (80) is not limited to one plate (P) but extends across the plurality of plates (P), so that the volume of the space expands in the first direction (stacking direction) of the plates (P). This makes it possible to prevent the distance between the outlet (O) of the inflow passage (71) and the inlets (I1, I2, I3) of the plurality of outflow passages (91, 92, 93) from differing greatly. As a result, it is possible to prevent the flow path resistance between the outlet (O) and each of the inlets (I1, I2, I3) from differing greatly, so that it is possible to prevent the refrigerant from flowing unevenly into some of the outflow passages (91, 92, 93).

[0008] In the second embodiment, the outlet (O) of the first embodiment is disposed on the opposite side of the flow dividing space (80) from the inlets (I1, I2, I3).

[0009] In the second aspect, the flow resistance of the refrigerant flowing through the flow division space (80) can be reduced.

[0010] In the third embodiment, in the second embodiment, the outlet (O) and the inlets (I1, I2, I3) are offset from each other when viewed from the second direction.

[0011] In the third aspect, the outlet (O) and a certain inlet (I1, I2, I3) do not overlap when viewed in the second direction, so that it is possible to prevent the refrigerant from being biased toward a certain inlet (I1, I2, I3).

[0012] A fourth aspect is any one of the first to third aspects, wherein at least two of the plurality of inlets (I1, I2, I3) are formed in different flow dividing plates (FP2, FP3, FP4).

[0013] In the fourth aspect, at least two of the multiple inlets (I1, I2, I3) are not formed in the same distribution plate (FP2, FP3, FP4), thereby preventing the distances between the outlet (O) and these inlets (I1, I2, I3) from differing significantly.

[0014] In the fifth aspect, in the fourth aspect, the number of inlets (I1, I2, I3) is three or more, and at least three of the number of inlets (I1, I2, I3) are formed in different flow distribution plates (FP2, FP3, FP4).

[0015] In the fifth aspect, at least three of the three or more inlets (I1, I2, I3) are not formed in the same distribution plate (FP2, FP3, FP4), thereby preventing the distances between the outlet (O) and these inlets (I1, I2, I3) from differing significantly.

[0016] The sixth aspect is any one of the first to fifth aspects, wherein the multiple distribution plates (FP2, FP3, FP4) include a first plate (FP3) in which an outlet (O) is formed, a second plate (FP2) arranged at one end side in the thickness direction of the first plate (FP3) and in which an inlet (I1, I2, I3) is formed, and a third plate (FP4) arranged at the other end side in the thickness direction of the first plate (FP3) and in which an inlet (I1, I2, I3) is formed.

[0017] In the sixth aspect, the refrigerant flowing out from the outlet (O) of the first plate (FP3) is divided into one end side and the other end side in the thickness direction of the first plate (FP3). The refrigerant flowing into the one end side flows into the inlets (I1, I2, I3) of the second plate (FP2), and the refrigerant flowing into the other end side is divided into the inlets (I1, I2, I3) of the third plate (FP4). In this way, the inlets (I1, I2, I3) of the second plate (FP2) and the inlets (I1, I2, I3) of the third plate (FP4) are located on opposite sides of the first plate (FP3). This prevents the distance between the outlet (O) of the first plate (FP3) and the inlets (I1, I2, I3) of the second plate (FP2) and the distance between the outlet (O) of the first plate (FP3) and the inlets (I1, I2, I3) of the third plate (FP4) from differing significantly.

[0018] In a seventh aspect, in any one of the first to sixth aspects, the plate spaces (81, 82, 83) have a horizontally elongated shape extending in a third direction perpendicular to the first direction and aligned horizontally when viewed in the second direction.

[0019] In the seventh aspect, the plate spaces (81, 82, 83) of the plurality of flow dividing plates (FP2, FP3, FP4) are formed horizontally extending in the third direction, so that the volume of the flow dividing space (80) formed by connecting these flow dividing plates (FP2, FP3, FP4) can be increased.

[0020] In an eighth aspect, in any one of the first to seventh aspects, the plate spaces (81, 82, 83) are holes penetrating the flow dividing plates (FP2, FP3, FP4) in the thickness direction.

[0021] In the eighth aspect, the plate spaces (81, 82, 83) are defined by holes in the flow dividing plates (FP2, FP3, FP4). Therefore, the plate spaces (81, 82, 83) can be extended in the thickness direction of the flow dividing plates (FP2, FP3, FP4).

[0022] In a ninth aspect, in the eighth aspect, the plate spaces (81, 82, 83) have the same shape.

[0023] In the ninth aspect, the flow distribution space (80) can be easily processed.

[0024] In the tenth aspect, in the seventh aspect, the flow outlet (O) is positioned in the middle of the flow distribution space (80) in the third direction, and the flow inlets (I1, I2, I3) are positioned toward the ends of the flow distribution space (80) in the third direction.

[0025] In the tenth aspect, the distance between the outlet (O) and the inlets (I1, I2, I3) can be prevented from becoming short, and the refrigerant can be prevented from drifting toward the inlets (I1, I2, I3).

[0026] An eleventh aspect is any one of the first to tenth aspects, wherein the inflow channel (71) is formed with a narrowing section (75a) that narrows the cross section of the channel toward the downstream side.

[0027] In the eleventh aspect, the flow velocity of the refrigerant increases as the refrigerant flows through the narrowed portion (75a) of the inflow channel (71). By increasing the flow velocity of the refrigerant, it is possible to prevent the refrigerant from flowing unevenly into some of the outflow channels (91, 92, 93).

[0028] In a twelfth aspect, in any one of the first to eleventh aspects, the number of the outflow channels (91, 92, 93) is three or more and five or less.

[0029] In the twelfth aspect, even if the number of outflow channels (91, 92, 93) is three or more, the flow division performance can be improved by the flow division space (80). By limiting the number of outflow channels (91, 92, 93) to five or less, it is possible to prevent deterioration of the flow division performance caused by increasing the number of outflow channels (91, 92, 93).

[0030] A thirteenth aspect is any one of the first to twelfth aspects, wherein the length of the flow distribution space (80) in the second direction is not less than 1 mm and not more than 6 mm.

[0031] In the thirteenth aspect, since the length of the flow division space (80) in the second direction is 1 mm or more, it is possible to reduce the flow path resistance of the flow division space (80). Since the length of the flow division space (80) in the second direction is 6 mm or less, it is possible to prevent the refrigerant from being biased toward some of the outflow channels (91, 92, 93).

[0032] A fourteenth aspect is any one of the first to thirteenth aspects, wherein the plate stack (50) is formed with a first region (A1) that does not overlap with the heat exchange section (40A) in the first direction, and the branch flow path (70) is formed in the first region (A1).

[0033] In the fourteenth aspect, interference between the heat transfer tube (42) of the heat exchanger section (40A) and the branch flow path (70) in the first direction can be suppressed.

[0034] A fifteenth aspect is an air conditioning indoor unit equipped with a heat exchanger unit (U) according to any one of the first to fourteenth aspects.

[0035] A sixteenth aspect is a refrigeration cycle apparatus including a refrigerant circuit (11) to which a heat exchanger unit (U) according to any one of the first to fourteenth aspects is connected. [Brief description of the drawings]

[0036] [Figure 1] FIG. 1 is a piping diagram of an air conditioner according to an embodiment. [Diagram 2] FIG. 2 is a front view of the air conditioning indoor unit. [Diagram 3] FIG. 3 is a cross-sectional view of the air conditioning indoor unit taken along line AA. [Figure 4] FIG. 4 is a front view showing the internal structure of the air conditioning indoor unit. [Diagram 5] FIG. 5 is a cross-sectional view showing a connection structure between a heat transfer tube and a plate stack. [Figure 6] FIG. 6 is a perspective view of a main part of the heat exchanger unit. [Figure 7] FIG. 7 is an exploded perspective view of the front plate assembly. [Figure 8] FIG. 8 is a perspective view of a main part of the flow division channel. [Figure 9] FIG. 9 is an enlarged side view of the flow dividing passage of the third front plate, and corresponds to the portion surrounded by the dashed line R9 in FIG. [Figure 10] FIG. 10 is an enlarged side view of the flow dividing passage of the second front plate, and corresponds to the portion surrounded by the dashed line R10 in FIG. [Figure 11] FIG. 11 is an enlarged side view of the flow dividing passage of the fourth front plate, and corresponds to the portion surrounded by the dashed line R11 in FIG. [Figure 12] FIG. 12 is a cross-sectional view of the shunt channel. [Figure 13] FIG. 13 is a cross-sectional view of the flow dividing channel of the first modified example. [Figure 14] FIG. 14 is a cross-sectional view of the flow dividing channel of the second modification. [Figure 15] FIG. 15 is a cross-sectional view of the flow dividing channel of the third modification. [Figure 16] FIG. 16 is a cross-sectional view of the flow dividing channel of the fourth modification. [Figure 17] FIG. 17 is a cross-sectional view of the flow dividing channel of the fifth modification. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0037] Hereinafter, the embodiments of the present disclosure will be described in detail with reference to the drawings. Note that the present disclosure is not limited to the embodiments shown below, and various modifications are possible within the scope of the technical idea of ​​the present disclosure. Since each drawing is intended to conceptually explain the present disclosure, dimensions, ratios, or numbers may be exaggerated or simplified as necessary for easy understanding.

[0038] (1) Overall configuration of air conditioning system This embodiment is an air conditioner (10) including a heat exchanger unit (U). The air conditioner (10) adjusts the temperature of air in an indoor space (5), which is a target space.

[0039] As shown in Fig. 1, the air conditioner (10) is an example of a refrigeration cycle device including a refrigerant circuit (11). The refrigerant circuit (11) is filled with a refrigerant. The refrigerant circuit (11) performs a refrigeration cycle by circulating the refrigerant.

[0040] The air conditioner (10) includes an outdoor unit (20), an indoor unit (30), a first connecting pipe (12), and a second connecting pipe (13). The air conditioner (10) is a pair type having one outdoor unit (20) and one indoor unit (30). The first connecting pipe (12) is a gas connecting pipe, and the second connecting pipe (13) is a liquid connecting pipe. In the air conditioner (10), a refrigerant circuit (11) is formed by connecting the outdoor unit (20) and the indoor unit (30) with the first connecting pipe (12) and the second connecting pipe (13).

[0041] The outdoor unit (20) is installed outdoors and includes an outdoor casing (20a), a compressor (21) housed in the outdoor casing (20a), an outdoor heat exchanger (22), an outdoor expansion valve (23), a four-way switching valve (24), and an outdoor fan (25).

[0042] The compressor (21) is a rotary compressor such as a swing piston type, rotary type, or scroll type. The outdoor heat exchanger (22) exchanges heat between the refrigerant and outdoor air. The outdoor heat exchanger (22) is a fin-and-tube air heat exchanger. The outdoor expansion valve (23) reduces the pressure of the refrigerant. The outdoor expansion valve (23) is an electronic expansion valve. The four-way switching valve (24) switches between a first state (a state shown by a solid line in FIG. 1) and a second state (a state shown by a dashed line in FIG. 1). In the first state, the four-way switching valve (24) communicates between the discharge portion of the compressor (21) and the gas end of the outdoor heat exchanger (22) and also communicates between the suction portion of the compressor (21) and the first connection pipe (12). The four-way switching valve (24) in the second state communicates the discharge portion of the compressor (21) with the first connection pipe (12) and also communicates the suction portion of the compressor (21) with the gas end of the outdoor heat exchanger (22). The outdoor fan (25) transports the air flowing through the outdoor heat exchanger (22). The outdoor fan (25) is a propeller fan.

[0043] The indoor unit (30) includes a casing (31), an indoor fan (32), and a heat exchanger unit (U). The indoor fan (32) and the heat exchanger unit (U) are housed in the casing (31).

[0044] (2) Indoor unit The indoor unit (30) which is an indoor air conditioner will be described in detail with reference to Figs. 2 to 4. The indoor unit (30) of this embodiment is a wall-mounted type provided on a wall of the indoor space (5). Note that the terms "upper", "lower", "right", "left", "front", and "rear" described below correspond to the directions of the arrows shown in Figs. 2 and 3 and indicate the directions when the casing (31) is viewed from the front side.

[0045] (2-1) Casing The casing (31) is formed in a horizontally elongated box shape and has a front plate (31a), a rear plate (31b), an upper plate (31c), a lower plate (31d), a first side plate (31e), and a second side plate (31f).

[0046] The front plate (31a) is formed on the front side of the casing (31) and constitutes the front surface of the casing (31). The rear plate (31b) is formed on the rear side of the casing (31) and constitutes the rear surface of the casing (31). The upper plate (31c) is formed on the upper side of the casing (31) and constitutes the upper surface of the casing (31). The lower plate (31d) is formed on the lower side of the casing (31) and constitutes the lower surface of the casing (31). The first side plate (31e) is formed on the right side of the casing (31) and constitutes the right surface of the casing (31). The second side plate (31f) is formed on the left side of the casing (31) and constitutes the left surface of the casing (31).

[0047] An intake port (33) is formed in the upper plate (31c), and an exhaust port (34) is formed in the lower plate (31d). An air passage (38) is formed inside the casing (31) from the intake port (33) to the exhaust port (34). The intake port (33) extends in the longitudinal direction (left-right direction) of the casing (31). The intake port (33) is an opening for taking air from the indoor space (5) into the air passage (38). An exhaust port (34) is formed in the lower plate (31d). The exhaust port (34) extends in the longitudinal direction of the casing (31). The exhaust port (34) is an opening for blowing air from the air passage (38) into the indoor space (5).

[0048] (2-2) Filter The indoor unit (30) includes a filter (35). The filter (35) is disposed on the rear side of the suction port (33) and upstream of the indoor heat exchanger (40). The filter (35) collects dust in the air sent from the suction port (33) to the indoor heat exchanger (40). The indoor unit (30) may include a dust removal mechanism that removes the dust collected by the filter (35).

[0049] (2-3) Heat exchange unit The heat exchanger unit (U) includes an indoor heat exchanger (40), an intermediate pipe (66), an indoor expansion valve (37), a liquid relay pipe (67), and a gas relay pipe (68). The indoor heat exchanger (40) includes a heat exchanger body (B) and two plate stacks (50, 60) connected to the heat exchanger body (B). These will be described in detail later.

[0050] (2-4) Indoor fan The indoor fan (32) is disposed in the air passage (38). The indoor fan (32) is disposed in the air passage (38) downstream of the indoor heat exchanger (40). The indoor fan (32) is a crossflow fan. The indoor fan (32) has a fan rotor that extends in the longitudinal direction of the casing (31).

[0051] (2-5) Flap The indoor unit (30) has a flap (36) that adjusts the direction of air blown out of the air outlet (34). The flap (36) adjusts the air direction in the vertical direction. The indoor unit (30) may have a plurality of flaps (36). The flap (36) may adjust the air direction in the horizontal direction.

[0052] (3) Details of indoor heat exchanger The indoor heat exchanger (40) will be described in detail with reference to Figs. 3 to 9. The indoor heat exchanger (40) exchanges heat between air and a refrigerant. The indoor heat exchanger (40) is a fin-and-tube air heat exchanger. The indoor heat exchanger (40) includes a heat exchanger body (B) and two plate stacks (50) connected to the heat exchanger body (B).

[0053] (3-1) Heat exchanger body 4 and 5, the heat exchanger body (B) has a plurality of fins (41) arranged in the longitudinal direction of the casing (31) and a plurality of heat transfer tubes (42) extending in the arrangement direction of the fins (41). The plate stacks (50, 60) have therein refrigerant flow paths (51, 61) that communicate with the heat transfer tubes (42).

[0054] The arrangement direction of the fins (41) corresponds to the longitudinal direction (here, the left-right direction) of the casing (31). The fins (41) are rectangular plate-shaped having long sides and short sides. The thickness direction of the fins (41) corresponds to the arrangement direction of the fins (41). The multiple fins (41) are arranged at predetermined intervals in the thickness direction. This interval defines an air flow path. The material of the fins (41) is an aluminum alloy.

[0055] The heat transfer tubes (42) are made of an aluminum alloy. A refrigerant flow path is formed inside the heat transfer tubes (42). The heat transfer tubes (42) extend parallel to one another and penetrate the fins (41). One end of the heat transfer tubes (42), which is a right end, protrudes to the right of the fins (41). One end of the heat transfer tubes (42) is connected to the plate stack (50, 60). Of the other ends of the heat transfer tubes (42), which are left ends, the left ends of two adjacent heat transfer tubes (42) are connected to each other by a U-shaped tube (49). The two adjacent heat transfer tubes (42) and the U-shaped tube (49) connecting them are formed integrally and seamlessly.

[0056] The indoor heat exchanger (40) of this embodiment has a front heat exchange section (40A) which is a first heat exchange section, and a rear heat exchange section (40B) which is a second heat exchange section. The front heat exchange section (40A) is located toward the front side of the casing (31), and the rear heat exchange section (40B) is located toward the rear side of the casing (31). The front heat exchange section (40A) and the rear heat exchange section (40B) are arranged in the front-to-rear direction on both sides of the indoor fan (32). The front-to-rear direction is a direction perpendicular to the axial direction and the up-down direction of the heat transfer tube (42).

[0057] The front heat exchange section (40A) includes a front main heat exchange section (43), a first auxiliary heat exchange section (44), and a second auxiliary heat exchange section (45).

[0058] The front main heat exchange section (43) is disposed closer to the indoor fan (32) in the front heat exchange section (40A). The front main heat exchange section (43) has an outer shape formed in a V-shape when viewed in the axial direction of the heat transfer tubes (42). The tip of the V-shape faces forward. The fins (41) constituting the front main heat exchange section (43) have a first portion (41a) extending obliquely upward toward the rear side, and a second portion (41b) extending obliquely downward toward the rear side. The angle between the extending direction of the first portion (41a) and the extending direction of the second portion (41b) is approximately 90° to 110°. The first portion (41a) and the second portion (41b) may be integrally formed or may be separate.

[0059] The first auxiliary heat exchange section (44) is provided on the inlet side (front side) of the first front main heat exchange section (43a). The lengths of the long sides and the short sides of the fins (41) of the first auxiliary heat exchange section (44) are shorter than those of the fins (41) of the first front main heat exchange section (43a). The number of heat transfer tubes (42) in the direction along the long sides (hereinafter referred to as the number of stages) of the first auxiliary heat exchange section (44) is smaller than the number of stages of the heat transfer tubes (42) of the first front main heat exchange section (43a). The number of heat transfer tubes (42) in the direction along the short sides (hereinafter referred to as the number of rows) of the first auxiliary heat exchange section (44) is smaller than the number of rows of the heat transfer tubes (42) of the first front main heat exchange section (43a).

[0060] The second auxiliary heat exchange section (45) is provided on the inlet side (front side) of the second front main heat exchange section (43b). The lengths of the long sides and the short sides of the fins (41) of the second auxiliary heat exchange section (45) are shorter than those of the fins (41) of the second front main heat exchange section (43b). The number of stages and rows of the heat transfer tubes (42) of the second auxiliary heat exchange section (45) is smaller than the number of stages and rows of the heat transfer tubes (42) of the second front main heat exchange section (43b).

[0061] The rear heat exchange section (40B) has a rear main heat exchange section (46) and a third auxiliary heat exchange section (47). The rear main heat exchange section (46) is disposed closer to the indoor fan (32) in the rear heat exchange section (40B). The third auxiliary heat exchange section (47) is provided on the inlet side (rear side) of the rear main heat exchange section (46). The lengths of the long and short sides of the fins (41) of the third auxiliary heat exchange section (47) are shorter than the lengths of the long and short sides of the fins (41) of the rear main heat exchange section (46). The number of stages and rows of the heat transfer tubes (42) of the third auxiliary heat exchange section (47) is smaller than the number of stages and rows of the heat transfer tubes (42) of the rear main heat exchange section (46).

[0062] As shown in Fig. 5, one end of the heat transfer tube (42) has a flare portion (48) that is flared. The flare portion (48) has an expanded diameter portion (48a) whose diameter increases as it approaches the plate stack (50, 60), and a cylindrical portion (48b) that extends in the axial direction with the same diameter as the expanded diameter portion (48a) from the end of the plate stack (50, 60) side. As will be described in detail later, the flare portion (48) is a portion that is connected to a heat transfer tube side connection portion (53, 63) of the plate stack (50, 60).

[0063] (3-2) Plate stack The plate stack (50, 60) is disposed to the right of the rightmost fin (41) and in parallel with the fin (41). The plate stack (50, 60) is connected to one end of the heat transfer tube (42). As shown in FIG. 6, the plate stack (50, 60) includes a front plate stack (50) connected to the heat transfer tube (42) of the front heat exchange section (40A) and a rear plate stack (60) connected to the heat transfer tube (42) of the rear heat exchange section (40B). The front plate stack (50) is disposed so as to overlap the front heat exchange section (40A) in the axial direction of the heat transfer tube (42). The rear plate stack (60) is disposed so as to overlap the rear heat exchange section (40B) in the axial direction of the heat transfer tube (42).

[0064] (3-2-1) Front plate assembly The front plate stack (50) has a front main body portion (52) having a refrigerant flow path therein (strictly speaking, a first refrigerant flow path (51)), and a plurality of front connection portions (53) connecting the plurality of heat transfer tubes (42) of the front heat exchange section (40A) to the first refrigerant flow path (51).

[0065] 5 to 7, the front main body portion (52) is a thick plate-like member formed by stacking five front plates. The stacking direction of the front plates is the same as the axial direction of the heat transfer tubes (42).

[0066] In the front plate stack (50), a first front plate (FP1), a second front plate (FP2), a third front plate (FP3), a fourth front plate (FP4), and a fifth front plate (FP5) are stacked in order from the side closest to the front heat exchange section (40A). The first front plate (FP1) is a cover plate on the heat exchanger body (B) side in the axial direction of the heat transfer tubes (42). The fifth front plate (FP5) is a cover plate on the opposite side to the heat exchanger body (B) in the axial direction of the heat transfer tubes (42) (the first side plate (31e) side of the casing (31)). The second front plate (FP2), the third front plate (FP3), and the fourth front plate (FP4) are intermediate plates sandwiched between the first front plate (FP1) and the fifth front plate (FP5). The five front plates are flat members having the same outer edge shape. Each front plate is made of the same material as the heat transfer tube (42) and the front connection part (53). In this embodiment, each front plate is made of an aluminum alloy. The first front plate (FP1) and the fifth front plate (FP5) have a thickness of 1.5 mm. The second front plate (FP2), the third front plate (FP3), and the fourth front plate (FP4) have a thickness of 3.0 mm. The front plates are joined to each other by furnace brazing. Note that the number of front plates is an example, and the number of front plates may be four or less, or six or more. Hereinafter, when there is no need to distinguish between the front plates, they are simply referred to as front plates.

[0067] (3-2-2) Rear plate assembly The rear plate stack (60) has a rear main body portion (62) having a refrigerant flow path (more precisely, a second refrigerant flow path (61)) therein, and a plurality of rear connection portions (63) that connect the plurality of heat transfer tubes (42) of the rear heat exchange portion (40B) to the second refrigerant flow path (61).

[0068] 5 and 6, the rear body portion (62) is a thick plate-like member formed by stacking five rear plates. The stacking direction of the rear plates is the same as the axial direction of the heat transfer tubes (42).

[0069] In the rear plate stack (60), a first rear plate (BP1), a second rear plate (BP2), a third rear plate (BP3), a fourth rear plate (BP4), and a fifth rear plate (BP5) are stacked in order from the side closest to the rear heat exchange section (40B). The first rear plate (BP1) is a cover plate on the heat exchanger body (B) side in the axial direction of the heat transfer tubes (42). The fifth rear plate (BP5) is a cover plate on the opposite side to the heat exchanger body (B) in the axial direction of the heat transfer tubes (42) (the side of the first side plate (31e) of the casing (31)). The second rear plate (BP2), the third rear plate (BP3), and the fourth rear plate (BP4) are intermediate plates sandwiched between the first rear plate (BP1) and the fifth rear plate (BP5). The five rear plates are flat members having the same outer edge shape. Each rear plate is made of the same material as the heat transfer tube (42) and the rear connection part (63). In this embodiment, each rear plate is made of an aluminum alloy. The first rear plate (BP1) and the fifth rear plate (BP5) have a thickness of 1.5 mm. The second rear plate (BP2), the third rear plate (BP3), and the fourth rear plate (BP4) have a thickness of 3.0 mm. The rear plates are joined to each other by furnace brazing. Note that the number of rear plates is an example, and the number of rear plates may be four or less, or six or more. Hereinafter, when it is not necessary to distinguish between the rear plates, they will simply be referred to as rear plates. Furthermore, the front plates and the rear plates will also be collectively referred to as plates (P).

[0070] (3-2-3) Heat transfer tube side connection 5, the plate stack (50, 60) has a plurality of front connection portions (53) and a plurality of rear connection portions (63). The plurality of front connection portions (53) are provided on the front plate stack (50), and the plurality of rear connection portions (63) are provided on the rear plate stack (60). When there is no need to distinguish between the front connection portions (53) and the rear connection portions (63), they are also referred to as heat transfer tube side connection portions (53, 63).

[0071] The front connection portion (53) is provided on the heat exchanger body (B) side of the first front plate (FP1) of the front main body portion (52). The front connection portion (53) protrudes from the front main body portion (52) toward the front heat exchange portion (40A) in the axial direction of the heat transfer tube (42).

[0072] The rear connection portion (63) is provided on the heat exchanger body (B) side of the first rear plate (BP1) of the rear main body portion (62). The rear connection portion (63) protrudes from the rear main body portion (62) toward the rear heat exchange portion (40B) in the axial direction of the heat transfer tube (42).

[0073] The heat transfer tube side connection parts (53, 63) are circular tubes. The material of the heat transfer tube side connection parts (53, 63) is an aluminum alloy. As shown in FIG. 5 , the tip parts of the heat transfer tube side connection parts (53, 63) are inserted into the ends of the corresponding heat transfer tubes (42). In other words, the ends of the heat transfer tubes (42) are inserted outside the heat transfer tube side connection parts (53, 63). The heat transfer tube side connection parts (53, 63) are inserted into the flare parts (48) of the corresponding heat transfer tubes (42). The heat transfer tube side connection parts (53, 63) are inserted into the flare parts (48) and joined to the cylindrical parts (48b) of the flare parts (48) by burner brazing.

[0074] (3-3) Intermediate piping 6, the heat exchanger unit (U) has an intermediate pipe (66). The intermediate pipe (66) connects the front heat exchange section (40A) and the rear heat exchange section (40B). In this embodiment, the intermediate pipe (66) is connected to an indoor expansion valve (37).

[0075] One end of the intermediate pipe (66) is connected to the front plate stack (50). Specifically, one end of the intermediate pipe (66) is connected to a surface of the front main body portion (52) opposite the front heat exchange portion (40A). One end of the intermediate pipe (66) is connected to the first refrigerant flow path (51). The other end of the intermediate pipe (66) is connected to the rear plate stack (60). Specifically, the other end of the intermediate pipe (66) is connected to a surface of the rear main body portion (62) opposite the rear heat exchange portion (40B). The other end of the intermediate pipe (66) is connected to the second refrigerant flow path (61).

[0076] (3-4) Indoor expansion valve The indoor expansion valve (37) is disposed on the right side of the heat exchanger body (B). The indoor expansion valve (37) is connected to the intermediate pipe (66). The indoor expansion valve (37) reduces the pressure of the refrigerant flowing through the intermediate pipe (66). The indoor expansion valve (37) is an electronic expansion valve.

[0077] (3-5) Liquid relay pipe 6, the heat exchanger unit (U) has a liquid relay pipe (67). One end of the liquid relay pipe (67) is connected to the front plate stack (50). The other end of the liquid relay pipe (67) is connected to the second connection pipe (13), which is a liquid connection pipe, outside the casing (31).

[0078] (3-6) Gas relay pipe 6, the heat exchanger unit (U) has a gas relay pipe (68). One end of the gas relay pipe (68) is connected to the rear plate assembly (60). The other end of the gas relay pipe (68) is connected to the first connection pipe (12), which is a gas connection pipe, outside the casing (31).

[0079] (4) Diversion channel A diversion flow path (70) is formed in the front plate stack (50). The diversion flow path (70) is a part of the first refrigerant flow path (51). The diversion flow path (70) diverts the refrigerant inside the front plate stack (50). The diversion flow path (70) will be described in detail with reference to FIGS. 6 to 12. In the following description, the first direction corresponds to the stacking direction of the plates (P) (the left-right direction in FIG. 6), the second direction corresponds to the direction along the vertical direction (the up-down direction in FIG. 6), and the third direction corresponds to the direction perpendicular to the first direction and along the horizontal direction (the front-rear direction in FIG. 6).

[0080] (4-1) Basic configuration of the distribution channel The flow-division passage (70) is formed by stacking a plurality of plates (P). The flow-division passage (70) is located in a first region (A1) of the front plate stack (50) that is surrounded by a dashed line in FIG. 7. The first region (A1) is a region that does not overlap with the front heat exchange section (40A) in the first direction. The first region (A1) is located in an upper portion and toward the front of the front plate stack (50).

[0081] As shown in FIG. 8, the flow division channel (70) has one inflow channel (71), one flow division space (80), and three outflow channels (91, 92, 93).

[0082] The inflow passage (71) is a flow path for allowing the refrigerant to flow into the flow-division space (80). An outlet (O) located at an outlet end of the inflow passage (71) is connected to the flow-division space (80). The outlet (O) opens toward the flow-division space (80).

[0083] The flow dividing space (80) is a space for dividing the refrigerant into the respective outflow paths (91, 92, 93). The flow dividing space (80) is constituted by a second plate space (82), a first plate space (81), and a third plate space (83), which are successively arranged from the front side to the rear side.

[0084] The outflow channels (91, 92, 93) are channels into which the refrigerant diverted in the diversion space (80) flows. The three outflow channels (91, 92, 93) are composed of a first outflow channel (91), a second outflow channel (92), and a third outflow channel (93). An inflow port (first inflow port (I1)) located at an inflow end of the first outflow channel (91) connects to the diversion space (80). The first inflow port (I1) opens toward the diversion space (80). An inflow port (second inflow port (I2)) located at an inflow end of the second outflow channel (92) connects to the diversion space (80). The second inflow port (I2) opens toward the diversion space (80). An inflow port (third inflow port (I3)) located at an inflow end of the third outflow channel (93) connects to the diversion space (80). The third inlet (I3) opens toward the flow division space (80).

[0085] (4-2) Front plate configuration 7, the flow division flow path (70) is configured by connecting spaces formed in the second front plate (FP2), the third front plate (FP3), and the fourth front plate (FP4). The second front plate (FP2), the third front plate (FP3), and the fourth front plate (FP4) each form a plate space (81, 82, 83) and configure flow division plates adjacent to each other in the first direction. The first front plate (FP1) and the fifth front plate (FP5) configure closing plates for closing the flow division flow path (70).

[0086] The third front plate (FP3) corresponds to the first plate. The second front plate (FP2) corresponds to the second plate arranged at one end side (left side in FIG. 6) of the third front plate (FP3) in the thickness direction. The fourth front plate (FP4) corresponds to the third plate arranged at the other end side (right side in FIG. 6) of the third front plate (FP3) in the thickness direction. The third front plate (FP3) is arranged between the second front plate (FP2) and the fourth front plate (FP4).

[0087] (4-2-1) 3rd front plate 9, the third front plate (FP3) is formed with an inlet relay path (75), a first plate space (81), and a first outlet path (91) as elements for forming the branch flow path (70). The inlet relay path (75), the first plate space (81), and the first outlet path (91) are formed by holes penetrating the third front plate (FP3) in the thickness direction (first direction).

[0088] The inlet relay channel (75) constitutes a part of the inlet channel (71). The inlet relay channel (75) extends in the second direction. An inlet end (lower end) of the inlet relay channel (75) is formed in a substantially circular shape. The inlet relay channel (75) is formed with a reduced section (75a) that reduces the cross-sectional area of ​​the flow path toward the downstream side (upward in FIG. 9). The reduced section (75a) is formed in a tapered shape that reduces the length (hereinafter also referred to as width) of the inlet channel (71) in the third direction toward the downstream side. The outlet section of the inlet relay channel (75) is formed in a rectangular parallelepiped shape.

[0089] The first plate space (81) has a horizontally elongated shape extending in the third direction. In other words, the longitudinal direction of the first plate space (81) corresponds to the third direction. The first plate space (81) is formed in a rectangular parallelepiped shape.

[0090] The outlet (O), which is the outlet end of the inlet relay channel (75), is continuous with the first plate space (81). The outlet (O) is located on the lower side of the first plate space (81). The outlet (O) is located in the middle of the first plate space (81) in the third direction.

[0091] The first outlet path (91) has a vertically elongated shape extending in the second direction. A first inlet (I1) which is an inlet end of the first outlet path (91) is continuous with the first plate space (81). The first inlet (I1) is located on the upper side of the first plate space (81). The first inlet (I1) is located near one end (near the rear end) in the third direction of the first plate space (81). Specifically, the first inlet (I1) is located at one end (rear end) of the first plate space (81) in the third direction. One end of the first plate space (81) and the first inlet (I1) are continuous without any step.

[0092] The third front plate (FP3) is formed with a first communication hole (76) and a second communication hole (77) as flow paths continuous with the branch flow path (70). The first communication hole (76) is located in front of the outlet end of the first outlet path (91). The second communication hole (77) is located above the first communication hole (76) and the first outlet path (91). The first communication hole (76) and the second communication hole (77) are formed in a circular shape.

[0093] (4-2-2) Second front plate 10, the second front plate (FP2) is formed with an inlet passage (78), a second plate space (82), and a second outlet passage (92) as elements for forming the branch flow path (70). The inlet passage (78), the second plate space (82), and the second outlet passage (92) are formed by holes penetrating the second front plate (FP2) in the thickness direction (first direction).

[0094] The introduction path (78) is a part of the inflow path (71). In this embodiment, the introduction path (78) is curved in a U-shape. An outlet end of the introduction path (78) overlaps with an inflow end of the inflow relay path (75) in the first direction. A flow path cross-sectional area of ​​the introduction path (78) is larger than each of the flow path cross-sectional areas of the outlet paths (91, 92, 93).

[0095] The second plate space (82) has a horizontally elongated shape extending in the third direction. In other words, the longitudinal direction of the second plate space (82) corresponds to the third direction. The second plate space (82) is formed in a rectangular parallelepiped shape.

[0096] The second outlet passage (92) has a vertically elongated shape extending in the second direction. The second inlet (I2), which is an inlet end of the second outlet passage (92), is continuous with the second plate space (82). The second inlet (I2) is located on the upper side of the second plate space (82). The second inlet (I2) is located near the other end in the third direction (near the front end) of the second plate space (82). Specifically, the second inlet (I2) is located at the other end (front end) in the third direction of the second plate space (82). The other end in the third direction of the second plate space (82) and the second inlet (I2) are continuous without any step.

[0097] The second front plate (FP2) is formed with a first relay flow path (94), a second relay flow path (95), and a third relay flow path (96) as flow paths continuous with the branch flow path (70). The first relay flow path (94), the second relay flow path (95), and the third relay flow path (96) are formed by holes penetrating the second front plate (FP2) in the thickness direction (first direction).

[0098] The first relay flow path (94) is connected to the first outlet path (91) at the second front plate (FP2). An inflow end of the second relay flow path (95) overlaps with the first communication hole (76) in the first direction. The second relay flow path (95) communicates with the third outlet path (93) via the first communication hole (76). An inflow end of the third relay flow path (96) overlaps with the first outlet path (91) in the first direction. The third relay flow path (96) communicates with the first outlet path (91).

[0099] (4-2-3) 4th front plate 11, a third plate space (83) and a third outlet path (93) are formed in the fourth front plate as elements for forming the branch flow path (70). The third plate space (83) and the third outlet path (93) are formed by holes penetrating the fourth front plate (FP4) in the thickness direction (first direction).

[0100] The third plate space (83) has a horizontally elongated shape extending in the third direction. In other words, the longitudinal direction of the third plate space (83) corresponds to the third direction. The third plate space (83) is formed in a rectangular parallelepiped shape.

[0101] The third outlet path (93) has a vertically elongated shape extending in the second direction. The third inlet (I3), which is an inlet end of the third outlet path (93), is continuous with the third plate space (83). The third inlet (I3) is located on the upper side of the third plate space (83). The third inlet (I3) is located near the other end in the third direction (near the front end) of the third plate space (83). Specifically, the third inlet (I3) is located at the other end (front end) in the third direction of the third plate space (83). The other end in the third direction of the third plate space (83) is continuous with the third inlet (I3) without any step.

[0102] The fourth front plate (FP4) is formed with a fourth relay flow path (97), a fifth relay flow path (98), and a sixth relay flow path (99) as flow paths continuous with the branch flow path (70). The fourth relay flow path (97), the fifth relay flow path (98), and the sixth relay flow path (99) are formed by holes penetrating the fourth front plate (FP4) in the thickness direction (first direction).

[0103] The fourth relay flow path (97) is connected to the third outlet path (93) at the fourth front plate (FP4). An inflow end of the fifth relay flow path (98) overlaps with the second communication hole (77) in the first direction. The fifth relay flow path (98) communicates with the second outlet path (92) via the second communication hole (77). An inflow end of the sixth relay flow path (99) overlaps with the first outlet path (91) in the first direction. The sixth relay flow path (99) communicates with the first outlet path (91).

[0104] (4-4) Diversion space In the front plate laminate (50), by laminating each plate (P), a flow splitting space (80) is formed inside. As shown in FIG. 8, the flow splitting space (80) is configured by the second plate space (82), the first plate space (81), and the third plate space (83) being continuous in the first direction. The first plate space (81), the second plate space (82), and the third plate space (83) overlap each other in the first direction. The first plate space (81), the second plate space (82), and the third plate space (83) preferably have the same shape. The first plate space (81), the second plate space (82), and the third plate space (83) preferably all overlap each other in the first direction.

[0105] The flow splitting space (80) is formed in a rectangular parallelepiped shape. Assuming the length of the flow splitting space (80) in the first direction is L1, the length in the second direction is L2, and the length in the third direction is L3, the flow splitting space (80) of the present embodiment satisfies the relationship of L2 < L1 < L3.

[0106] The length L2 of the flow splitting space (80) in the second direction is 1 mm or more and 6 mm or less. By setting L2 to 1 mm or more, the flow path resistance of the flow splitting space (80) can be reduced. By setting L2 to 6 mm or less, it is possible to suppress the distance between the outlet (O) and each inlet (I1, I2, I3) and the outlet (O) from becoming too long. L1 is preferably 9 mm or more, and L3 is preferably 15 mm or more. L1 and L3 are larger than the thickness of the flow splitting plates (FP2, FP3, FP4) (for example, 3 mm).

[0107] (4-5) Positional relationship between the outlet and each inlet FIG. 12 is a cross-sectional view of the flow splitting space. The outlet (O) of the inflow path (71) is formed on the lower surface (80a) that defines the flow splitting space (80). Each inlet (I1, I2, I3) of each outflow path (91, 92, 93) is formed on the upper surface (80b) that defines the flow splitting space (80). The outlet (O) and each inlet (I1, I2, I3) are arranged on opposite sides with the flow splitting space (80) interposed therebetween.

[0108] The cross section of the outlet (O) is rectangular. The cross section of the outlet (O) is horizontally elongated extending in the third direction. In this manner, the outlet (O) is extended along the front and back surfaces of the plate (P) perpendicular to the flow direction, thereby increasing the flow path cross-sectional area of ​​the outlet (O).

[0109] The outlet (O) is disposed in a middle portion of the flow division space (80) in the first direction. When viewed in the second direction, the outlet (O) is located so as to overlap with the center line (first center line (M1)) of the flow division space (80) in the first direction. The outlet (O) is disposed in a middle portion of the flow division space (80) in the third direction. When viewed in the second direction, the outlet (O) is located so as to overlap with the center line (second center line (M2)) of the flow division space (80) in the third direction. In this way, the outlet (O) is located in the center of the flow division space (80) when viewed in the first direction.

[0110] The cross section of each of the inlets (I1, I2, I3) is rectangular. The cross section of each of the inlets (I1, I2, I3) is horizontally elongated extending in the third direction. In this manner, the flow path cross-sectional area of ​​the inlets (I1, I2, I3) can be enlarged by extending the inlets (I1, I2, I3) along the front and back surfaces of the plate (P) perpendicular to the flow direction. The first inlet (I1), second inlet (I2), and third inlet (I3) are arranged in a staggered manner when viewed in the second direction.

[0111] The first inlet (I1) and the outlet (O) are offset from each other when viewed in the second direction. The first inlet (I1) and the outlet (O) are disposed in the middle of the flow-division space (80) in the first direction. Specifically, the first inlet (I1) and the outlet (O) are disposed on the first center line (M1) when viewed in the second direction. The outlet (O) is disposed on the second center line (M2) when viewed in the second direction. The first inlet (I1) is located at the other end (rear end) in the third direction. The first inlet (I1) is disposed so as to be flush with the rear surface (80c) that defines the flow-division space (80).

[0112] The second inlet (I2) and the outlet (O) are offset from each other when viewed in the second direction. The second inlet (I2) is disposed at one end (left end) of the flow division space (80) in the first direction. The second inlet (I2) is disposed at one end (front end) of the flow division space (80) in the third direction. In this manner, the second inlet (I2) is located at a corner of the flow division space (80) when viewed in the second direction. By disposing the second inlet (I2) at the corner of the flow division space (80), it is possible to prevent the distance between the outlet (O) and the second inlet (I2) from becoming too short. The second inlet (I2) is disposed so as to be flush with the left face (80d) and the front face (80e) that define the flow division space (80).

[0113] The third inlet (I3) and the outlet (O) are offset from each other when viewed in the second direction. The third inlet (I3) is disposed at the other end (right end) of the flow division space (80) in the first direction. The third inlet (I3) is disposed at one end (front end) of the flow division space (80) in the third direction. In this manner, the third inlet (I3) is located at a corner of the flow division space (80) when viewed in the second direction. By disposing the third inlet (I3) at the corner of the flow division space (80), it is possible to prevent the distance between the outlet (O) and the third inlet (I3) from becoming too short. The third inlet (I3) is disposed so as to be flush with the right face (80f) and the front face (80e) that define the flow division space (80).

[0114] (5) Driving behavior The air conditioner (10) performs a cooling operation, a heating operation, and a dehumidifying operation.

[0115] (5-1) Cooling operation In the cooling operation, the controller of the air conditioner (10) operates the compressor (21), the outdoor fan (25), and the indoor fan (32), sets the four-way switching valve (24) to the first state (the state shown by the solid line in FIG. 1), appropriately adjusts the opening degree of the outdoor expansion valve (23), and fully opens the indoor expansion valve (37).

[0116] In the cooling operation, the refrigerant circuit (11) performs a refrigeration cycle in which the outdoor heat exchanger (22) functions as a condenser (heat radiator) and the indoor heat exchanger (40) functions as an evaporator.

[0117] The indoor unit (30) draws indoor air from the indoor space (5) into the air passage (38) through the inlet (33). The air in the air passage (38) is cooled by the indoor heat exchanger (40). The cooled air is supplied to the indoor space (5) through the air outlet (34).

[0118] In the heat exchanger unit (U), the refrigerant that has flowed into the liquid relay pipe (67) flows into the front plate stack (50) of the front heat exchange section (40A). In the front heat exchange section (40A), the refrigerant absorbs heat from the indoor air while passing through the heat transfer tubes (42). The refrigerant then passes through the front plate stack (50) and flows into the first internal pipe (71a), and passes through the indoor expansion valve (37) and the second internal pipe (71b) in this order, and flows into the rear plate stack (60) of the rear heat exchange section (40B). In the rear heat exchange section (40B), the refrigerant absorbs heat from the indoor air while passing through the heat transfer tubes (42). The refrigerant then passes through the rear plate stack (60) and flows into the gas relay pipe (68), and flows out of the heat exchanger unit (U).

[0119] (5-2) Heating operation In the heating operation, the controller of the air conditioner (10) operates the compressor (21), the outdoor fan (25), and the indoor fan (32), sets the four-way switching valve (24) to the second state (the state shown by the dashed line in FIG. 1), adjusts the opening degree of the outdoor expansion valve (23) to a predetermined opening degree, and fully opens the indoor expansion valve (37).

[0120] In the heating operation, the refrigerant circuit (11) performs a refrigeration cycle in which the indoor heat exchanger (40) functions as a condenser (heat radiator) and the outdoor heat exchanger (22) functions as an evaporator.

[0121] The indoor unit (30) draws indoor air from the indoor space (5) into the air passage (38) through the inlet (33). The air in the air passage (38) is heated by the indoor heat exchanger (40). The heated air is supplied to the indoor space (5) through the air outlet (34).

[0122] In the heat exchanger unit (U), the refrigerant that has flowed into the gas relay pipe (68) flows into the rear plate stack (60) of the rear heat exchange section (40B). In the rear heat exchange section (40B), the refrigerant dissipates heat to the indoor air while passing through the heat transfer tubes (42). The refrigerant then flows through the rear plate stack (60) into the second internal pipe (71b), passes through the indoor expansion valve (37) and the first internal pipe (71a) in this order, and flows into the front plate stack (50) of the front heat exchange section (40A). In the front heat exchange section (40A), the refrigerant dissipates heat to the indoor air while passing through the heat transfer tubes (42). The refrigerant then flows through the front plate stack (50) into the liquid relay pipe (67), and flows out of the heat exchanger unit (U).

[0123] (5-3) Dehumidification operation In the dehumidification operation, a controller of the air conditioner (10) operates the compressor (21), the outdoor fan (25), and the indoor fan (32), sets the four-way switching valve (24) to the first state (the state shown by the solid line in FIG. 1), and appropriately adjusts the openings of the outdoor expansion valve (23) and the indoor expansion valve (37).

[0124] During dehumidification operation, the refrigerant circuit (11) performs a refrigeration cycle in which the outdoor heat exchanger (22) and the front heat exchange section (40A) of the indoor heat exchanger (40) function as a condenser (heat radiator), and the rear heat exchange section (40B) of the indoor heat exchanger (40) functions as an evaporator.

[0125] The indoor unit (30) draws room air from the indoor space (5) into the air passage (38) through the air inlet (33). The rear heat exchanger (40B) cools the air in the air passage (38) to a temperature equal to or lower than the dew point temperature. The front heat exchanger (40A) heats the air in the air passage (38). The air passing through both the rear heat exchanger and the front heat exchanger mix in the air passage (38) to become low-humidity air. The air dehumidified in this manner is supplied to the indoor space (5) through the air outlet (34).

[0126] In the heat exchanger unit (U), the refrigerant that has flowed into the liquid relay pipe (67) flows into the front plate stack (50) of the front heat exchange section (40A). In the front heat exchange section (40A), the refrigerant dissipates heat to the indoor air while passing through the heat transfer tubes (42). The refrigerant then passes through the front plate stack (50) and flows into the first internal pipe (71a), is reduced in pressure when passing through the indoor expansion valve (37), and then flows through the second internal pipe (71b) and into the rear plate stack (60) of the rear heat exchange section (40B). In the rear heat exchange section (40B), the refrigerant absorbs heat from the indoor air while passing through the heat transfer tubes (42). The refrigerant then passes through the rear plate stack (60) and flows into the gas relay pipe (68), and flows out of the heat exchanger unit (U).

[0127] (5-4) Flow in the branch channel When the air conditioner (10) is in operation, the refrigerant inside the front plate assembly (50) flows through the branch flow passage (70). An example of the flow of the refrigerant in the branch flow passage (70) will be described.

[0128] 8, the refrigerant flowing through the introduction passage (78) flows through the contracted portion (75a) of the inlet relay passage (75). The flow velocity of the refrigerant increases through the contracted portion (75a). As a result, the flow velocity of the refrigerant increases through the flow division space (80), thereby improving the flow division performance of the flow division space (80).

[0129] The refrigerant that has passed through the reduction portion (75a) flows out from the outlet (O) into the flow-division space (80). The refrigerant that has been diverted into the flow-division space (80) is dispersed so as to be directed toward the first inlet (I1), the second inlet (I2), and the third inlet (I3).

[0130] If the outlet (O) and a certain inlet overlap when viewed in the second direction, the refrigerant is likely to be biased toward the inlet. In contrast, in this embodiment, the outlet (O) and each inlet (I1, I2, I3) are offset from each other when viewed in the second direction. This makes it possible to prevent the refrigerant diverted from the outlet (O) from being biased toward some of the outlets (O).

[0131] In this embodiment, the distance between the outlet (O) and the first inlet (I1), the distance between the outlet (O) and the second inlet (I2), and the distance between the outlet (O) and the third inlet (I3) are short to each other, so that the refrigerant diverted from the outlet (O) is prevented from flowing unevenly into some of the inlets (I1, I2, I3).

[0132] The refrigerant diverted to the first inlet (I1) of the third front plate (FP3) flows through the first outlet channel (91). The refrigerant in the first outlet channel (91) is further diverted to the third relay channel (96) of the second front plate (FP2) and the sixth relay channel (99) of the fourth front plate (FP4).

[0133] The refrigerant diverted to the second inlet (I2) of the second front plate (FP2) flows through the second outlet path (92). Part of the refrigerant in the second outlet path (92) flows through the first relay path (94) of the second front plate (FP2). The remainder of the refrigerant passes through the second communication hole (77) of the third front plate (FP3) and then flows through the fifth relay path (98) of the fourth front plate (FP4).

[0134] The refrigerant diverted to the third inlet (I3) of the fourth front plate (FP4) flows through the third outlet path (93). A part of the refrigerant in the third outlet path (93) flows through the fourth relay path (97) of the fourth front plate (FP4). The remainder of the refrigerant passes through the first communication hole (76) of the third front plate (FP3) and then flows through the third relay path (96) of the second front plate (FP2).

[0135] (6) Effects of the embodiment (6-1) The plate stack (50, 60) is formed with a flow-division passage (70) for dividing the refrigerant. The flow-division passage (70) includes an inlet passage (71) extending in a second direction along the vertical direction, a flow-division space (80) connected to an outlet (O) of the inlet passage (71), and a plurality of outlet passages (91, 92, 93) each having an inlet (I1, I2, I3) connected to the flow-division space (80) and extending in the second direction. The plurality of plates (P) includes a plurality of flow-division plates (FP2, FP3, FP4) each having a plate space (81, 82, 83) and adjacent to each other in the first direction. The flow-division space (80) is formed by the plate spaces (81, 82, 83) of the plurality of flow-division plates (FP2, FP3, FP4) being continuous in the first direction.

[0136] Since the flow division space (80) extends across the plurality of flow division plates (FP2, FP3, FP4), the volume of the flow division space (80) can be made larger than when the flow division space (80) is formed on a single plate (P). This makes it easier to equalize the distance between the outlet (O) and each of the inlets (I1, I2, I3), thereby preventing the refrigerant from flowing unevenly toward some of the inlets (I1, I2, I3). As a result, the flow division performance of the flow division channel (70) can be improved. This effect is particularly noticeable when there are three or more outlet channels (91, 92, 93).

[0137] In addition, by forming the flow division space (80) using the plurality of plate spaces (81, 82, 83), the flow path cross-sectional area of ​​the flow division space (80) can be increased, and thus the flow velocity of the refrigerant can be reduced, thereby reducing the pressure loss of the refrigerant flowing through the flow division space (80).

[0138] (6-2) The outlet (O) is disposed on the opposite side of the flow division space (80) to the inlets (I1, I2, I3). Compared to a case in which the outlet (O) and the inlets (I1, I2, I3) are located on the same side of the flow division space (80), the overall flow resistance of the flow division channel (70) can be reduced.

[0139] (6-3) The outlet (O) and each of the inlets (I1, I2, I3) are offset from each other when viewed from the second direction. Since the outlet (O) and a certain inlet (I1, I2, I3) do not overlap when viewed from the second direction, it is possible to prevent the refrigerant from being biased toward a certain inlet (I1, I2, I3).

[0140] (6-4) At least two of the multiple inlets (I1, I2, I3) are formed in different flow distribution plates (FP2, FP3, FP4). Specifically, at least three of the three inlets (I1, I2, I3) are formed in different flow distribution plates (FP2, FP3, FP4). In this example, all of the three inlets (I1, I2, I3) are formed in different flow distribution plates (FP2, FP3, FP4). This makes it easier to make the distance between the outlet (O) and each of the inlets (I1, I2, I3) uniform. Note that, in a configuration in which the number of inlets is greater than the number of three or more flow distribution plates, at least three inlets may be formed in different flow distribution plates, and two or more inlets may be formed in the same flow distribution plate.

[0141] (6-5) The multiple distribution plates (FP2, FP3, FP4) include a third front plate (FP3) in which an outlet (O) is formed, a second front plate (FP2) arranged at one end in the thickness direction of the third front plate (FP3) and in which a second inlet (I2) is formed, and a fourth front plate (FP4) arranged at the other end in the thickness direction of the third front plate (FP3) and in which a third inlet (I3) is formed.

[0142] This configuration makes it easier to equalize the distance between the outlet (O) and the second inlet (I2) and the distance between the outlet (O) and the third inlet (I3), thereby preventing uneven flow of the refrigerant between the second outlet passage (92) and the third outlet passage (93).

[0143] (6-6) When viewed in the second direction, the plate spaces (81, 82, 83) have a horizontally elongated shape extending in a third direction that is perpendicular to the first direction and aligned horizontally.

[0144] This allows the flow-division space (80) defined by the plate spaces (81, 82, 83) to be large, making it easier to equalize the distances between the outlet (O) and the inlets (I1, I2, I3).The cross-sectional area of ​​the flow path of the flow-division space (80) can be increased.The pressure loss of the refrigerant in the flow-division space (80) can be reduced.

[0145] (6-7) The plate spaces (81, 82, 83) are holes penetrating the flow dividing plates (FP2, FP3, FP4) in the thickness direction. Therefore, the plate spaces (81, 82, 83) can be easily formed in the plate (P). By forming the plate spaces (81, 82, 83) as holes, the plate spaces (81, 82, 83) can be extended to the maximum extent in the thickness direction.

[0146] Since the plate spaces (81, 82, 83) have the same shape, it is easier to process the plate spaces (81, 82, 83), and the volume of the flow dividing space (80) can be maximized.

[0147] (6-8) The outlet (O) is disposed in a middle portion of the flow division space (80) in the third direction, and the second inlet (I2) and the third inlet (I3) are disposed near the ends of the flow division space (80) in the third direction. This makes it possible to prevent the distance between the outlet (O) and the second inlet (I2) and the distance between the outlet (O) and the third inlet (I3) from becoming short. As a result, it is possible to prevent the refrigerant from being biased toward the second inlet (I2) or the third inlet (I3).

[0148] (6-9) The inflow passage (71) is formed with a narrowing portion (75a) whose cross section narrows toward the downstream side, thereby improving the flow division performance of the refrigerant in the flow division space (80).

[0149] (6-10) The number of the outflow channels (91, 92, 93) is preferably equal to or greater than 3 and equal to or less than 5. Even if the number of the outflow channels (91, 92, 93) is three, the flow division space (80) can be enlarged to prevent uneven flow of the refrigerant.

[0150] By limiting the number of the outlet channels (91, 92, 93) to five or less, the distance between the outlet (O) and each of the inlets (I1, I2, I3) can be prevented from becoming uneven, and the structures of the flow-diversion channel (70) and the plate stack (50, 60) can be prevented from becoming complicated.

[0151] Preferably, the number of outlet passages (91, 92, 93) is odd.

[0152] The length of the flow division space (80) in the second direction is 1 mm or more and 6 mm or less. By setting L2 to 1 mm or more, the flow path resistance of the flow division space (80) can be reduced. By setting L2 to 6 mm or less, the distance between the outlet (O) and each of the inlets (I1, I2, I3) can be prevented from becoming too long.

[0153] (6-11) The front plate stack (50) is formed with a first region (A1) that does not overlap with the front heat exchange section (40A) in the first direction. The flow division channel (70) is formed in the first region (A1).

[0154] If the branch flow passage (70) overlaps with the front heat exchange section (40A) in the first direction, it becomes difficult to ensure a region (second region) in the front plate stack (50) that is connected to the heat transfer tubes (42). In contrast, since the first region (A1) does not overlap with the front heat exchange section (40A) in the first direction, the second region can be sufficiently ensured.

[0155] (7) Variations The above-described embodiment may be modified as follows. The following describes the differences from the above-described embodiment.

[0156] (7-1) Variation 1 In Modification 1 shown in Fig. 13, the outlet (O) and the inlets (I1, I2, I3) are located on the same side of the flow division space (80). The outlet (O) and the inlets (I1, I2, I3) are formed in the lower surface (80a) that defines the flow division space (80). The outlet (O) and the inlets (I1, I2, I3) may be formed in the upper surface (80b) that defines the flow division space (80).

[0157] (7-2) Variation 2 In the second modification shown in FIG. 14, a plurality of inlets are formed in one same plate (P). In this example, the first inlet (I1) and the second inlet (I2) are formed in the second front plate (FP2), and the third inlet (I3) and the fourth inlet (I4) are formed in the fourth front plate (FP4). The fourth inlet (I4) constitutes an inlet of a fourth outlet path. The first inlet (I1) is located near one end in the third direction of the flow-division space (80), and the second inlet (I2) is located near the other end in the third direction of the flow-division space (80). The third inlet (I3) is located near one end in the third direction of the flow-division space (80), and the fourth inlet (I4) is located near the other end in the third direction of the flow-division space (80).

[0158] (7-3) Variation 3 In the third modification shown in FIG. 15, the first inlet (I1), the second inlet (I2), and the third inlet (I3) are located slightly closer to the middle part of the flow division space (80) than to the ends in the third direction.

[0159] (7-4) Variation 4 The front plate stack (50) of the fourth modification shown in FIG. 16 includes, in order from the side closer to the heat exchange section (40A), a first front plate (FP1), a second front plate (FP2), a third front plate (FP3), a fourth front plate (FP4), a fifth front plate (FP5), a sixth front plate (FP6), and a seventh front plate (FP7). The fourth front plate (FP4) is formed with an outlet (O) and a first inlet (I1). The third front plate (FP3) is formed with a second inlet (I2), and the fifth front plate (FP5) is formed with a third inlet (I3). That is, the second inlet (I2) and the third inlet (I3) are located slightly closer to the middle than to the ends in the first direction of the flow division space (80). In the fourth modification, the second inlet (I2) may be formed in the second front plate (FP2), and the third inlet (I3) may be formed in the sixth front plate (FP6).

[0160] (7-5) Variation 5 In the fifth modification shown in Fig. 17, plate spaces (81, 82, 83) are defined by grooves formed in the plate (P). The second front plate (FP2) has a second plate space (82) recessed in the first direction (leftward in Fig. 17) from the third front plate (FP3) side. The fourth front plate (FP4) has a second plate space (82) recessed in the first direction (rightward in Fig. 17) from the third front plate (FP3) side.

[0161] (8) Other embodiments In the above-described embodiment and each of the modified examples, the following configurations may be adopted.

[0162] In the branch flow path (70), the refrigerant may flow downward in the second direction through the inlet path (71) and the outlet paths (91, 92, 93).

[0163] The outlet (O) and the inlets (I1, I2, I3) may partially overlap in the second direction.

[0164] In the plate stack (50, 60), a flow dividing channel (70) may be formed in a region overlapping with the heat exchange section (40A) in the first direction.

[0165] The inflow passage (71) may be configured without the reduced portion (75a).

[0166] The branch channel (70) may have two or more inlets (71).

[0167] The rear plate assembly (60) may have a flow splitter channel (70) formed therein.

[0168] The refrigeration cycle device (10) may be any device that performs a vapor compression refrigeration cycle and is not limited to an air conditioner. The refrigeration cycle device may be a cooling device that cools the interior of a refrigerator or a refrigerated warehouse, a chiller device that cools or heats a heat medium such as water, or a heat pump type water heater that heats water to generate hot water.

[0169] The air conditioner (10) does not have to be of a pair type, but may be of a multi-type.

[0170] The indoor unit (30) may be of a ceiling-mounted or floor-standing type.

[0171] The direction in which the front heat exchange section (40A) and the rear heat exchange section (40B) are arranged is not limited to the front-rear direction, and may be, for example, the up-down direction.

[0172] The valve connected to the intermediate pipe (66) does not have to be an expansion valve, and may be a solenoid valve, a check valve, a three-way valve, a four-way switching valve, a shutoff valve, or the like.

[0173] The heat exchanger unit (U) may be applied to an outdoor heat exchanger (22) of an outdoor unit (20).

[0174] The indoor heat exchanger (40) does not have to be of a fin-and-tube type and may be of, for example, a corrugated type in which corrugated fins are arranged between adjacent heat transfer tubes.

[0175] The heat exchanger body (B) may have one heat exchange section, not including the front heat exchange section (40A) and the rear heat exchange section (40B). In this case, a plate stack is provided corresponding to the one heat exchange section. The flow dividing passage (70) is formed in the plate stack.

[0176] The heat transfer tubes (42) and the fins (41) of the heat exchanger body (B) may be made of a copper material. In this case, the plate stack (50, 60) and the refrigerant pipes connected to the plate stack (50, 60) are preferably made of a copper material. The plate stack (50, 60) and the refrigerant pipes connected to the plate stack (50, 60) may be made of a stainless steel material.

[0177] Although the embodiment and modifications have been described above, it will be understood that various modifications in form and details are possible without departing from the spirit and scope of the claims. Elements of the above embodiment, modifications, and other embodiments may be appropriately combined or substituted.

[0178] The descriptions "first," "second," "third," etc. mentioned above are used to distinguish the words to which these descriptions are attached, and do not limit the number or order of the words. [Industrial Applicability]

[0179] INDUSTRIAL APPLICABILITY As described above, the present disclosure is useful for a heat exchanger unit, an air conditioner indoor unit, and a refrigeration cycle apparatus. [Explanation of symbols]

[0180] 10 Air conditioning equipment (refrigeration cycle equipment) 11 Refrigerant circuit 40A Heat exchange section 41 Finn 42 Heat transfer tube 50 Plate stack 51 Coolant flow path 70 Diversion channel 71 Inflow channel 75a Reduced section 80 Diversion space 81, 82, 83 Plate Space 91 1st outflow channel 92 2nd outflow channel 93 Third outflow channel A1 1st area FP2 2nd front plate (2nd plate, flow divider plate) FP3 3rd front plate (1st plate, flow divider plate) FP4 4th front plate (3rd plate, flow divider plate) I1 1st inlet I2 2nd inlet I3 3rd inlet O Outlet P-Plate U Heat Exchanger Unit

Claims

1. a heat exchange section (40A) having fins (41) and a heat transfer tube (42); a plate stack (50, 60) including a plurality of plates (P) stacked in a first direction along a horizontal direction, and in which a refrigerant flow path (51) communicating with the heat transfer tube (42) is formed; The plate stack (50) is formed with a flow dividing passage (70) for dividing the flow of the refrigerant, The branch flow passage (70) an inlet passage (71) extending in a second direction along the vertical direction; a flow dividing space (80) connected to an outlet (O) of the inlet channel (71); a plurality of outlet paths (91, 92, 93) each having an inlet (I1, I2, I3) connected to the flow distribution space (80) and extending in the second direction, The plurality of plates (P) each include a plurality of flow dividing plates (FP2, FP3, FP4) that are adjacent to each other in the first direction and each have a plate space (81, 82, 83), The flow distribution space (80) is formed by the plate spaces (81, 82, 83) of the plurality of flow distribution plates (FP2, FP3, FP4) continuing in the first direction. Heat exchanger unit.

2. The outlet (O) is disposed on the opposite side of the flow dividing space (80) to the inlets (I1, I2, I3).

2. The heat exchanger unit of claim 1.

3. The outlet (O) and the inlets (I1, I2, I3) are offset from each other when viewed in the second direction.

3. A heat exchanger unit according to claim 2.

4. At least two of the plurality of inlets (I1, I2, I3) are formed in different flow distribution plates (FP2, FP3, FP4). A heat exchanger unit according to any one of claims 1 to 3.

5. The plurality of inlets (I1, I2, I3) are three or more, At least three of the plurality of inlets (I1, I2, I3) are formed in the flow distribution plates (FP2, FP3, FP4) that are different from each other.

5. A heat exchanger unit according to claim 4.

6. Multiple flow dividing plates (FP2, FP3, FP4) A first plate (FP3) in which the outlet (O) is formed; a second plate (FP2) disposed at one end side in a thickness direction of the first plate (FP3) and having the inlets (I1, I2, I3) formed therein; a third plate (FP4) disposed on the other end side of the first plate (FP3) in the thickness direction and in which the inlets (I1, I2, I3) are formed. A heat exchanger unit according to any one of claims 1 to 3.

7. When viewed in the second direction, the plate spaces (81, 82, 83) have a horizontally elongated shape extending in a third direction perpendicular to the first direction and aligned horizontally. A heat exchanger unit according to any one of claims 1 to 3.

8. The plate spaces (81, 82, 83) are holes penetrating the flow dividing plates (FP2, FP3, FP4) in the thickness direction. A heat exchanger unit according to any one of claims 1 to 3.

9. The plate spaces (81, 82, 83) have the same shape.

9. A heat exchanger unit according to claim 8.

10. the outlet (O) is disposed in a middle portion of the plate space (81, 82, 83) in the third direction, The inlets (I1, I2, I3) are disposed near the ends of the plate spaces (81, 82, 83) in the third direction. A heat exchanger unit according to claim 7.

11. The inflow passage (71) is formed with a narrowing portion (75a) whose cross section narrows toward the flow division space (80). A heat exchanger unit according to any one of claims 1 to 3.

12. The number of the outlet channels (91, 92, 93) is 3 or more and 5 or less. A heat exchanger unit according to any one of claims 1 to 3.

13. The length of the flow dividing space (80) in the second direction is equal to or greater than 1 mm and equal to or less than 6 mm. A heat exchanger unit according to any one of claims 1 to 3.

14. The plate stack (50) is formed with a first region (A1) that does not overlap with the heat exchange section (40A) in the first direction, The branch flow passage (70) is formed in the first region (A1). A heat exchanger unit according to any one of claims 1 to 3.

15. An air conditioning indoor unit comprising a heat exchanger unit (U) according to any one of claims 1 to 3.

16. A refrigerant circuit (11) to which the heat exchanger unit (U) according to any one of claims 1 to 3 is connected. Refrigeration cycle equipment.

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