Indoor heat exchanger and air conditioner

Abstract

The purpose of the present invention is to suppress enlargement of a plate laminate in the plane direction. A refrigerant flow path (30m) of a plate laminated body (30) includes: first refrigerant flow paths (30m1) each configured from elongated holes (321y, 322y, 323y, 324a) formed in a plate (32), and second refrigerant flow paths (30m2) each configured from elongated holes (321y, 322y, 323y, 324a) formed in the plate (32); and a second refrigerant flow path (30m2) configured from circular holes (323x, 324x) formed in the plate (32), circular holes formed in the plates (31, 33), and elongated holes (342x) formed in the plate (34). The first refrigerant flow path (30m1) and the second refrigerant flow path (30m2) intersect when viewed from the left-right direction (lamination direction).

Description

Technical Field

[0001] The present disclosure relates to an indoor heat exchanger and an air conditioner including the indoor heat exchanger. Background Art

[0002] Patent Document 1 discloses an indoor unit for air conditioning used in an air conditioner. In this indoor unit for air conditioning, a plate-shaped distribution member formed by stacking a plurality of plates is connected to a heat transfer tube of a heat exchanger body in order to save space.

[0003] Prior art literature

[0004] Patent Literature

[0005] Patent Document 1: Japanese Patent Application Publication No. 2006-125652 Summary of the invention

[0006] Problems to be solved by the invention

[0007] In Patent Document 1, a refrigerant flow path is formed on the center plate of the three plates constituting the plate-shaped distribution member, and the bottom plate and the top plate define the refrigerant flow path. In this case, due to the structure of the refrigerant flow path, a detour needs to be provided within the plane of the center plate. Therefore, in the surface direction along the plane of the plate, the plate-shaped distribution member (equivalent to the "plate stack" of the present disclosure) becomes larger.

[0008] An object of the present disclosure is to provide an indoor heat exchanger capable of suppressing an increase in size of a plate stack in a surface direction, and an air conditioner including the indoor heat exchanger.

[0009] Means for solving problems

[0010] The indoor heat exchanger of the first aspect of the present disclosure comprises: a heat exchange portion, which includes fins and a plurality of heat transfer tubes passing through the fins; and a plate stack, which forms a plurality of refrigerant flow paths connected to the plurality of heat transfer tubes, the plurality of refrigerant flow paths including a first refrigerant flow path and a second refrigerant flow path, the plate stack includes a first plate and a second plate stacked in a stacking direction at a position farther from the plurality of heat transfer tubes than the first plate, a first cut, a third cut and a fourth cut are formed on the first plate, a second cut connected to the third cut and the fourth cut is formed on the second plate, the first cut forms a first refrigerant flow path, the second cut, the third cut and the fourth cut form a second refrigerant flow path, and the first refrigerant flow path intersects with the second refrigerant flow path when viewed from the stacking direction.

[0011] According to the first aspect of the present disclosure, instead of providing a detour path in the plane of the plate, the first refrigerant flow path and the second refrigerant flow path are made to intersect with each other. This can suppress an increase in size of the plate stack in the plane direction.

[0012] The indoor heat exchanger of the second aspect of the present disclosure may be that in the above-mentioned first aspect, the plurality of heat transfer tubes include a first heat transfer tube serving as an evaporation zone and a second heat transfer tube serving as a superheat zone, the plurality of refrigerant flow paths include an evaporation flow path connected to the first heat transfer tube and a superheat flow path connected to the second heat transfer tube, and when viewed from the stacking direction, the evaporation flow path and the superheat flow path do not intersect. If the flow paths with a large temperature difference (evaporation flow path and superheat flow path) intersect with each other, the thermal efficiency may deteriorate due to heat conduction between the flow paths at the intersection. In this regard, in the present structure, the flow paths with a large temperature difference (evaporation flow path and superheat flow path) do not intersect with each other, thereby being able to suppress this problem.

[0013] The indoor heat exchanger of the third aspect of the present disclosure may be that in the above-mentioned first or second aspect, the plurality of heat transfer tubes include a first heat transfer tube that becomes an evaporation zone and a second heat transfer tube that becomes a superheat zone, the plurality of refrigerant flow paths include: an evaporation flow path that is connected to the first heat transfer tube and constitutes one of the first refrigerant flow path and the second refrigerant flow path; and a superheat flow path that is connected to the second heat transfer tube and constitutes the other of the first refrigerant flow path and the second refrigerant flow path, and the plate stack further includes a third plate that is arranged between the first plate and the second plate in the stacking direction, and the thickness of the third plate is greater than at least one of the first plate and the second plate. In this case, the heat conduction between the evaporation flow path and the superheat flow path is suppressed by the third plate having a large thickness. Thus, the deterioration of thermal efficiency can be effectively suppressed.

[0014] The indoor heat exchanger of the fourth aspect of the present disclosure may be, in any one of the first to third aspects, the plurality of heat transfer tubes include a first heat transfer tube that becomes an evaporation zone and a second heat transfer tube that becomes a superheat zone, the plurality of refrigerant flow paths include: an evaporation flow path that is connected to the first heat transfer tube and constitutes one of the first refrigerant flow path and the second refrigerant flow path; and a superheat flow path that is connected to the second heat transfer tube and constitutes the other of the first refrigerant flow path and the second refrigerant flow path, the plate stack further includes a third plate that is arranged between the first plate and the second plate in the stacking direction, and the thermal conductivity of the third plate is lower than that of at least one of the first plate and the second plate. In this case, the heat conduction between the evaporation flow path and the superheat flow path is suppressed by the third plate having a low thermal conductivity. Thus, the deterioration of thermal efficiency can be effectively suppressed.

[0015] The indoor heat exchanger of the fifth aspect of the present disclosure may be, in any one of the second to fourth aspects, the plate stack has a gap between the evaporation flow path and the superheat flow path through which the refrigerant does not flow. In this case, the heat conduction between the evaporation flow path and the superheat flow path is suppressed by the gap. Thus, the deterioration of thermal efficiency can be effectively suppressed.

[0016] The indoor heat exchanger of the sixth aspect of the present disclosure may be, in any one of the first to fifth aspects, the number of the second refrigerant flow paths is less than the number of the first refrigerant flow paths. In the case where a plate is provided between the first plate and the second plate, if the number of the second refrigerant flow paths is large, the number of through holes formed on the plate between the first plate and the second plate increases, and the formation process of the through holes becomes complicated. In this regard, in the present structure, since the number of the second refrigerant flow paths is small, the above-mentioned problem can be suppressed.

[0017] The indoor heat exchanger of the seventh aspect of the present disclosure may be, in any one of the first to sixth aspects, the length of the second refrigerant flow path is greater than the length of the first refrigerant flow path. If the length of the second refrigerant flow path is shorter, the wall thickness between the second refrigerant flow path and the first refrigerant flow path in the first plate becomes smaller, thereby causing a reduction in strength or a deterioration in processability. In this regard, in the present structure, since the length of the second refrigerant flow path is longer, the above-mentioned problem can be suppressed.

[0018] The indoor heat exchanger of the 8th aspect of the present disclosure may be, in any one of the above-mentioned 1st to 7th aspects, the heat exchange part includes a 1st heat exchange part and a 2nd heat exchange part, the plurality of heat transfer tubes include a 1st heat transfer tube of the 1st heat exchange part and a 2nd heat transfer tube of the 2nd heat exchange part, and a connecting flow path connecting the 1st heat transfer tube with the 2nd heat transfer tube is provided on the 1st plate. The 2nd plate is stacked at a position farther from the 1st plate than the 1st plate than the 1st plate. If a connecting flow path is provided on the 2nd plate, the distance in the stacking direction from the end face of the heat transfer tube to the connecting flow path formed on the 2nd plate becomes longer, so that the pressure loss may become larger. In this regard, in the present structure, by providing a connecting flow path on the 1st plate, it is possible to suppress the following situation: the above-mentioned distance becomes longer, and the pressure loss becomes larger.

[0019] An air conditioner according to a ninth aspect of the present disclosure includes the indoor heat exchanger according to any one of the first to eighth aspects. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 It is a front view of the air conditioner according to the first embodiment of the present disclosure, in a state where the exterior panel is removed.

[0021] Figure 2 yes Figure 1 A right side view of an indoor heat exchanger included in the air conditioner is shown.

[0022] Figure 3 yes Figure 1 A perspective view of the plate stack shown.

[0023] Figure 4 It is composed Figure 3 The plan view of the leftmost plate of the five plates in the plate stack shown.

[0024] Figure 5 It is composed Figure 3 A top view of the second plate from the left of the five plates in the plate stack shown.

[0025] Figure 6 It is composed Figure 3 A top view of the third plate from the left of the five plates in the plate stack shown.

[0026] Figure 7 It is composed Figure 3 A top view of the fourth plate from the left of the five plates in the plate stack shown.

[0027] Figure 8 It is composed Figure 3 A plan view of the rightmost plate of the five plates in the plate stack shown.

[0028] Fig. 9 It is along Figure 5 A cross-sectional view of the plate stack taken along line IX-IX is shown.

[0029] Fig.10 The indoor heat exchanger of the second embodiment of the present disclosure is Figure 5 The corresponding figure.

[0030] Fig.11 It is along Fig.10 A cross-sectional view of the plate stack and the heat exchange portion taken along line XI-XI is shown. DETAILED DESCRIPTION

[0031] <First Embodiment>

[0032] First, refer to Figure 1 , the overall structure of the air conditioner 1 according to the first embodiment of the present disclosure is described. In addition, in the following description, the directions of "up", "down", "right", "left", "front", and "rear" indicate the directions of the air conditioner 1. Figure 1 The state sets the state of the direction.

[0033] The air conditioner 1 includes an indoor heat exchanger 10, a fan and a filter (not shown), a frame 1f, and an exterior panel (not shown).

[0034] The frame 1f constitutes the bottom and rear of the air conditioner 1. The frame 1f is long in one direction and Figure 1 The fan, the exterior panel, and the indoor heat exchanger 10 are mounted on the frame 1f. The filter is mounted on the exterior panel.

[0035] The indoor heat exchanger 10 is similar to the frame 1f in one direction ( Figure 1 The left-right direction is longer.

[0036] Next, refer to Figures 1 to 9 , the structure of the indoor heat exchanger 10 is described in detail.

[0037] like Figure 1 As shown in FIG. 1 , the indoor heat exchanger 10 includes a heat exchange portion 10u, a plate stack 30, a plurality of U-shaped bends 22, and a plurality of connecting pipes 23. Figure 1 In FIG. 1 , a portion where one of the plurality of U-bend pipes 22 overlaps with the plate stack 30 in a side view is depicted by a dotted line.

[0038] The heat exchange unit 10 u includes a plurality of fins 11 , a plurality of heat transfer tubes 12 , and a tube sheet 14 .

[0039] The plurality of fins 11 are each in the shape of a thin plate, and are arranged so that the plate surface is along the up-down direction and the front-back direction. The plurality of fins 11 are arranged at equal intervals in the left-right direction.

[0040] The plurality of heat transfer tubes 12 extend in the left-right direction and penetrate the plurality of fins 11 .

[0041] In addition, Figure 1 In the figure, for simplicity, only a portion of the plurality of heat transfer tubes 12 is depicted, and only a portion of the plurality of fins 11 is partially depicted.

[0042] The left end of each heat transfer tube 12 is connected to the left end of another heat transfer tube 12 via a U-shaped bent portion 21. The right end of each heat transfer tube 12 is connected to the right end of another heat transfer tube 12 via a U-shaped bent pipe 22, a connecting pipe 23, or a plate stack 30. The bent portion 21 is located on the left side relative to the plurality of fins 11. The U-shaped bent pipe 22, the connecting pipe 23, and the plate stack 30 are located on the right side relative to the plurality of fins 11.

[0043] The bend 21 is formed integrally with the heat transfer tube 12, and a pair of heat transfer tubes 12 and the bend 21 are formed into a U-shaped tube by bending one tube. On the other hand, the U-shaped bend 22 and the connecting pipe 23 are welded to the open end (the right end of the heat transfer tube 12) of the U-shaped tube formed by bending as described above.

[0044] The plate stack 30 includes five plates 31 to 35 stacked in the left-right direction (stacking direction) (see Figure 3 A refrigerant flow path is formed in each of the U-shaped bent pipe 22 , the connecting pipe 23 , and the plate stack 30 .

[0045] like Figure 1 As shown, the flow divider 18 , the expansion valve 19 , and the like are arranged near the U-bend pipe 22 , the connecting pipe 23 , and the plate stack 30 .

[0046] The tube sheet 14 is arranged so that the plate surface is along the up-down direction and the front-back direction, and is located on the right side relative to the plurality of fins 11. The plurality of heat transfer tubes 12 penetrate the tube sheet 14. There is almost no gap between the tube sheet 14 and each heat transfer tube 12, and the tube sheet 14 supports the fins 11 and the plurality of heat transfer tubes 12. On the right side of the tube sheet 14, that is, on the side opposite to the plurality of fins 11 relative to the tube sheet 14, a U-shaped bend 22, a connecting pipe 23, and a plate stack 30 are arranged.

[0047] Although not shown in the figure, a tube sheet is also arranged on the left side with respect to the plurality of fins 11 .

[0048] The plurality of heat transfer tubes 12 slightly protrude to the right from the right side of the tube plate 14. That is, the end faces 12x of the plurality of heat transfer tubes 12 are located slightly to the right of the right side of the tube plate 14.

[0049] like Figure 2 As shown, the tube sheet 14 includes a first tube sheet 141, a second tube sheet 142, a third tube sheet 143, and a fourth tube sheet 144. The indoor heat exchanger 10 is a bending type in which the first to fourth tube sheets 141 to 144 are arranged at an angle to the adjacent tube sheets 141 to 144. A plurality of heat transfer tubes 12 penetrate the first to fourth tube sheets 141 to 144, respectively. A pair of heat transfer tubes 12 in each U-shaped tube (a U-shaped tube formed by bending one tube and including a pair of heat transfer tubes 12 and a bent portion 21) does not penetrate two different tube sheets in the first to fourth tube sheets 141 to 144.

[0050] The heat exchange section 10u is composed of a rear heat exchange section 10u1 including a first tube sheet 141 and a front heat exchange section 10u2 including second to fourth tube sheets 142 to 144.

[0051] Two heat transfer tubes 121a and 122a adjacent to each other among the plurality of heat transfer tubes 12 included in the rear heat exchange unit 10u1 are connected via the refrigerant flow path 22m of the U-shaped bend tube 22. The two heat transfer tubes 121a and 122a respectively constitute different U-shaped tubes (U-shaped tubes formed by bending one tube and a pair of heat transfer tubes 12 and the bend 21).

[0052] One of the plurality of heat transfer tubes 12 (heat transfer tube 121b) included in the rear heat exchange section 10u1 is connected to one of the plurality of heat transfer tubes 12 (heat transfer tube 122b) included in the front heat exchange section 10u2 via the refrigerant flow path 23m of the connecting pipe 23. One of the plurality of heat transfer tubes 12 (heat transfer tube 121c) included in the rear heat exchange section 10u1 is connected to one of the plurality of heat transfer tubes 12 (heat transfer tube 122c) included in the front heat exchange section 10u2 via the refrigerant flow path 23m of the connecting pipe 23. One of the plurality of heat transfer tubes 12 (heat transfer tube 121d) included in the rear heat exchange section 10u1 is connected to one of the plurality of heat transfer tubes 12 (heat transfer tube 122d) included in the front heat exchange section 10u2 via the refrigerant flow path 23m of the connecting pipe 23. One (heat transfer tube 121 e ) of the plurality of heat transfer tubes 12 included in the rear heat exchange section 10 u 1 and one (heat transfer tube 122 e ) of the plurality of heat transfer tubes 12 included in the front heat exchange section 10 u 2 are connected via a refrigerant flow path 23 m of the connecting pipe 23 .

[0053] The heat transfer tube 121c is also connected to the expansion valve 19. The expansion valve 19 is attached to the connection pipe 23 connecting the heat transfer tube 121c and the heat transfer tube 122c.

[0054] On the right side relative to the multiple fins 11, among the multiple heat transfer tubes 12 of the rear heat exchange part 10u1, except for the six heat transfer tubes 121a, 122a, 121b, 121c, 121d, and 121e connected to the U-shaped bend 22 or the connecting pipe 23, the heat transfer tubes 12 are connected to the plate stack 30.

[0055] also, Figure 3 The plate stack 30 shown is attached to the rear heat exchange section 10u1. The plate stack attached to the front heat exchange section 10u2 has the same structure as the plate stack 30, and its illustration and description are omitted.

[0056] The plate stack 30 is mounted on the heat transfer tube 12 not connected to the U-bend 22 or the connecting pipe 23 among the plurality of heat transfer tubes 12 in the rear heat exchange section 10u1 via a plurality of connecting parts 40. The plurality of connecting parts 40 are cylindrical and have a refrigerant flow path inside. Each connecting part 40 extends in the left-right direction and connects the heat transfer tube 12 and the plate stack 30 in the left-right direction. Each connecting part 40 has a left end connected to the end face 12x of the heat transfer tube 12 and a right end connected to the left side face of the plate 31 in the plate stack 30.

[0057] Concave portions 30x and 30y are provided at a portion (rear portion) of the outer periphery of the plate stack 30. The concave portions 30x and 30y penetrate the plate stack 30 in the left-right direction. The concave portions 30x and 30y are gaps formed in a shape in which the plates 31 to 35 are cut away. A U-shaped bend pipe 22 (see FIG. 2 ) is arranged at a position corresponding to the concave portion 30y. Figures 4 to 8 ).

[0058] The length of the connecting portion 40 in the left-right direction is shorter than the length of the U-shaped bend 22 in the left-right direction. A first distance D1 in the left-right direction (stacking direction) from the end face 12x of the heat transfer tube 12 to the surface closest to the end face 12x of the heat transfer tube 12 in the plate stack 30 (the left side surface of the plate 31) is shorter than a second distance D2 in the left-right direction (stacking direction) from the end face 12x of the heat transfer tube 12 to the surface farthest from the end face 12x of the heat transfer tube 12 in the U-shaped bend 22 (the top of the U shape) (see FIG. 1 ). Figure 1 ). Therefore, if Figure 1 As shown, the U-bend pipe 22 overlaps the plate stack 30 when viewed from the front-rear direction.

[0059] Next, refer to Figures 4 to 9 , the refrigerant flow path 30m formed in the plate stack 30 will be described in detail.

[0060] The refrigerant flow path 30 m is formed by through holes formed in the plates 31 to 35 constituting the plate stack 30 .

[0061] like Figure 4 As shown, a plurality of circular holes (including circular holes 313a and 314a described later) are formed on the plate 31. The connecting parts 40 (see Figure 3 ) on the right side.

[0062] like Figure 5 As shown, a plurality of circular holes (including circular holes 323x, 324x, 323a described later) and a plurality of elongated holes (including elongated holes 321y, 322y, 323y, 324a described later) are formed on the plate 32. These circular holes and elongated holes are connected to one or two of the plurality of circular holes formed on the plate 31.

[0063] like Figure 6 As shown, a plurality of circular holes (including a circular hole 334 a described later) are formed in the plate 33. The circular holes are connected to one of the circular holes or the elongated holes formed in the plate 32, respectively.

[0064] like Figure 7 As shown, a plurality of elongated holes (including elongated holes 342x and 343a described later) are formed in the plate 34. The elongated holes are connected to two of the plurality of circular holes formed in the plate 33, respectively.

[0065] like Figure 8 As shown, a circular hole 35x is formed in the plate 35. The circular hole 35x communicates with one of the plurality of elongated holes formed in the plate 34.

[0066] The through holes (circular holes or elongated holes) formed in the plates 31 to 35 communicate with each other, thereby forming a refrigerant flow path 30 m.

[0067] Figure 2 The two heat transfer tubes 123a and 124a shown (two of the plurality of heat transfer tubes 12 included in the rear heat exchange section 10u1) are connected to each other via a refrigerant flow path 30m, wherein the refrigerant flow path 30m is composed of circular holes 313a and 314a formed in the plate 31, a circular hole 323a and an elongated hole 324a formed in the plate 32, circular holes 333a and 334a formed in the plate 33, and an elongated hole 343a formed in the plate 34. The two heat transfer tubes 123a and 124a respectively constitute different U-shaped tubes (U-shaped tubes formed by bending one tube and a pair of heat transfer tubes 12 and a bent portion 21).

[0068] like Fig. 9 As shown, the elongated hole 342x (see Figure 7 ) straddles four elongated holes 321y, 322y, 323y, 324a formed in the plate 32 (see Figure 5 ). The elongated holes 321y, 322y, 323y, and 324a respectively constitute the first refrigerant flow path 30m of the refrigerant flow path 30m, which is equivalent to the "first incision" of the present disclosure. The circular holes 323x and 324x formed in the plate 32, the circular holes formed in the plates 31 and 33, and the elongated hole 342x formed in the plate 34 constitute the second refrigerant flow path 30m2 of the refrigerant flow path 30m. The circular hole 323x is equivalent to the "third incision" of the present disclosure, the circular hole 324x is equivalent to the "fourth incision" of the present disclosure, and the elongated hole 342x is equivalent to the "second incision" of the present disclosure. One end of the elongated hole 342x is connected to the circular hole 323x, and the other end of the elongated hole 342x is connected to the circular hole 324x. When viewed from the left and right direction (stacking direction), the first refrigerant flow path 30m1 intersects with the second refrigerant flow path 30m2 (refer to Figure 5 ).

[0069] The plate 32 corresponds to the “first plate” of the present disclosure. The plate 34 is stacked at a position farther from the heat transfer tube 12 than the plate 32 in the left-right direction (stacking direction), and corresponds to the “second plate” of the present disclosure.

[0070] The number of the second refrigerant flow paths 30m2 (one) is less than the number of the first refrigerant flow paths 30m1 (four). Figure 7 The length of the elongated hole 342x shown in FIG. 1 is greater than the length of the four first refrigerant flow paths 30m1 ( Figure 5 Any of the lengths of the elongated holes 321y, 322y, 323y, 324a shown is longer.

[0071] The plurality of heat transfer tubes 12 connected to the refrigerant flow path 30m include a first heat transfer tube serving as an evaporation zone and a second heat transfer tube serving as a superheat zone. The evaporation zone and the superheat zone are switched according to the control of the indoor heat exchanger 10, and one heat transfer tube may serve as an evaporation zone or a superheat zone according to the control of the indoor heat exchanger 10.

[0072] The four elongated holes 321y, 322y, 323y, and 324a constituting the first refrigerant flow path 30m1 are respectively connected to the heat transfer tubes 125a to 125d (see Figure 4 ) are connected. The circular holes 323x and 324x constituting the second refrigerant flow path 30m2 are connected to the heat transfer pipes 126a and 126b (see Figure 4 )connect.

[0073] When the heat transfer tubes 125a to 125d (the first heat transfer tube) become the evaporation zone, the heat transfer tubes 126a and 126b (the second heat transfer tube) sometimes become the superheat zone. In this case, the first refrigerant flow path 30m1 is equivalent to the "evaporation flow path" of the present disclosure, and the second refrigerant flow path 30m2 is equivalent to the "superheat flow path" of the present disclosure. When the heat transfer tubes 125a to 125d (the second heat transfer tube) become the superheat zone, the heat transfer tubes 126a and 126b (the first heat transfer tube) become the evaporation zone. In this case, the first refrigerant flow path 30m1 is equivalent to the "superheat flow path" of the present disclosure, and the second refrigerant flow path 30m2 is equivalent to the "evaporation flow path" of the present disclosure.

[0074] That is, regarding the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 that intersect when viewed from the left and right direction (stacked direction), when one becomes an evaporation flow path, the other may become a superheating flow path. In this case, the plate 33 between the first refrigerant flow path 30m1 and the elongated hole 342x constituting the second refrigerant flow path 30m2 has a thickness greater than that of either of the plates 32 and 34 (see Fig. 9 ), whose thermal conductivity is lower than that of either plate 32 or 34.

[0075] The plate 33 is a plate disposed between the plate 32 and the plate 34 , and corresponds to the “third plate” in the present disclosure.

[0076] The plate 33 has a gap 50 through which the refrigerant does not flow (see Fig. 9 The gap 50 is located between the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 in the left-right direction (stacked direction). For example, the plate 33 may be composed of two plate members, and recesses are formed on each of the two plate members by half etching or the like, and the recesses are combined to form the gap 50.

[0077] The elongated hole 342x (see Figure 7 ) does not straddle the elongated hole 329 formed in the plate 32. When viewed from the left-right direction (stacking direction), the elongated hole 342x does not intersect with the elongated hole 329.

[0078] The elongated hole 329 and the heat transfer tube 125e (see Figure 4 ) is connected. When the heat transfer tube 125e (the first heat transfer tube) becomes the evaporation zone, the heat transfer tubes 126a, 126b (the second heat transfer tube) sometimes become the superheat zone. In this case, the elongated hole 329 is equivalent to the "evaporation flow path" of the present disclosure, and the second refrigerant flow path 30m2 is equivalent to the "superheat flow path" of the present disclosure. When the heat transfer tube 125e (the second heat transfer tube) becomes the superheat zone, the heat transfer tubes 126a, 126b (the first heat transfer tube) become the evaporation zone. In this case, the elongated hole 329 is equivalent to the "superheat flow path" of the present disclosure, and the second refrigerant flow path 30m2 is equivalent to the "evaporation flow path" of the present disclosure.

[0079] As described above, according to the present embodiment, the refrigerant flow path 30m of the plate stack 30 includes: the first refrigerant flow path 30m1 (see Figure 5 ), which is formed by the elongated holes 321y, 322y, 323y, 324a formed in the plate 32, respectively; and the second refrigerant flow path 30m2 (refer to Figure 5 to Figure 7 ), which is composed of circular holes 323x and 324x formed in the plate 32, circular holes formed in the plates 31 and 33, and an elongated hole 342x formed in the plate 34. When viewed from the left and right direction (stacked direction), the first refrigerant flow path 30m1 intersects with the second refrigerant flow path 30m2 (refer to Figure 5 In this case, instead of providing a detour in the plane of the plates 31 to 35 , the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 are intersected, thereby suppressing the enlargement of the plate stack 30 in the surface direction along the plane of the plates 31 to 35 .

[0080] When viewed from the left-right direction (stacked direction), the evaporation flow path (e.g., the elongated hole 329 formed in the plate 32) and the superheat flow path (e.g., the elongated hole 342x formed in the plate 34 constituting the second refrigerant flow path 30m2) do not intersect (refer to Figure 5 ). If the flow paths with a large temperature difference (evaporation flow path and superheat flow path) intersect each other, the thermal efficiency may be deteriorated due to heat conduction between the flow paths at the intersection. In this regard, in the present structure, the flow paths with a large temperature difference (evaporation flow path and superheat flow path) do not intersect each other, thereby suppressing this problem.

[0081] When the first refrigerant flow path 30m1 becomes an evaporation flow path and the second refrigerant flow path 30m2 becomes a superheat flow path, the thickness of the plate 33 between the first refrigerant flow path 30m1 and the elongated hole 342x constituting the second refrigerant flow path 30m2 is greater than that of the plates 32 and 34 (see Fig. 9 In this case, the heat conduction between the evaporation flow path and the superheat flow path is suppressed by the thick plate 33. Thus, the deterioration of thermal efficiency can be effectively suppressed.

[0082] When the first refrigerant flow path 30m1 becomes an evaporation flow path and the second refrigerant flow path 30m2 becomes a superheat flow path, the thermal conductivity of the plate 33 between the first refrigerant flow path 30m1 and the elongated hole 342x constituting the second refrigerant flow path 30m2 is lower than that of either the plate 32 or the plate 34. In this case, the heat conduction between the evaporation flow path and the superheat flow path is suppressed by the plate 33 having a low thermal conductivity. Thus, the deterioration of the thermal efficiency can be effectively suppressed.

[0083] The plate stack 30 has a gap 50 (see FIG. 1 ) through which no refrigerant flows between the evaporation flow path (for example, the first refrigerant flow path 30m1) and the superheat flow path (for example, the second refrigerant flow path 30m2). Fig. 9 In this case, the heat conduction between the evaporation flow path and the superheat flow path is suppressed by the gap 50. Thus, the deterioration of the thermal efficiency can be effectively suppressed.

[0084] The number of the second refrigerant flow paths 30m2 (one) is less than the number of the first refrigerant flow paths 30m1 (four). If the number of the second refrigerant flow paths 30m2 is large, the number of through holes formed in the plate 33 increases, and the process of forming the through holes becomes complicated. In this regard, in this structure, the number of the second refrigerant flow paths 30m2 is small, so the above-mentioned problem can be suppressed.

[0085] The length of the second refrigerant flow path 30m2 ( Figure 7 The length of the elongated hole 342x shown in FIG. 1 is greater than the length of the four first refrigerant flow paths 30m1 ( Figure 5If the length of the second refrigerant flow path 30m2 is short, the wall thickness between the second refrigerant flow path 30m2 and the first refrigerant flow path 30m1 in the plate 32 becomes smaller, thereby causing a reduction in strength or a deterioration in processability. In this regard, in the present structure, the length of the second refrigerant flow path 30m2 is long, so that the above-mentioned problem can be suppressed.

[0086] <Second Embodiment>

[0087] Next, refer to Fig.10 and Fig.11 An indoor heat exchanger according to a second embodiment of the present disclosure will be described.

[0088] In the second embodiment, one of the plurality of heat transfer tubes 12 (heat transfer tube 121f) of the rear heat exchange section 10u1 and one of the plurality of heat transfer tubes 12 (heat transfer tube 122f) of the front heat exchange section 10u2 are connected via a connecting flow path 60 formed on the plate 32 of the plate stack 30.

[0089] The rear heat exchanger 10u1 corresponds to the "first heat exchanger" of the present disclosure, and the front heat exchanger 10u2 corresponds to the "second heat exchanger" of the present disclosure. The heat transfer tube 121f corresponds to the "first heat transfer tube" of the present disclosure, and the heat transfer tube 122f corresponds to the "second heat transfer tube" of the present disclosure.

[0090] In the present embodiment, the plate stack 30 is arranged across the rear heat exchange section 10u1 and the front heat exchange section 10u2. The connecting flow path 60 is formed in the plate 32 and the plate 31, but is not formed in the other plates (plates 33 to 35).

[0091] The plate 34 is stacked at a position farther from the plurality of heat transfer tubes 12 than the plate 32. If the connecting flow path 60 is provided on the plate 34, the distance in the left-right direction from the end surface 12x of the heat transfer tube 12 to the connecting flow path 60 formed on the plate 34 becomes longer, and the pressure loss may become larger. In this regard, in the present structure, by providing the connecting flow path 60 on the plate 32, it is possible to suppress the following situation: the above distance becomes longer, and the pressure loss becomes larger.

[0092] <Modification>

[0093] In the above-mentioned embodiment, the refrigerant flow path 30m of the plate stack 30 is formed by a through hole formed in each plate 31 to plate 35, but it is not limited to this. For example, a part or all of the refrigerant flow path 30m may also be formed by a bottomed groove formed on each plate 31 to plate 35 by half etching or the like. Similarly, the "first incision", "second incision", "third incision", and "fourth incision" of the present disclosure are not limited to through holes, but may also be a bottomed groove formed on each plate 31 to plate 35 by half etching or the like.

[0094] In the above-mentioned embodiment, the U-bend pipe 22 (refrigerant pipe) is arranged at a position corresponding to the recessed portion 30y provided on the outer periphery of the plate stack 30, but the present invention is not limited thereto. For example, a through hole or a recessed portion may be formed in the central portion of the plate stack, and the refrigerant pipe may be arranged at a position corresponding to the through hole or the recessed portion.

[0095] In the above-described embodiment, the thickness of the plate 33 is larger than that of any one of the plates 32 and 34 . However, in the third aspect of the present disclosure, the thickness of the plate 33 only needs to be larger than that of at least one of the plates 32 and 34 .

[0096] In the above-described embodiment, the thermal conductivity of the plate 33 is lower than that of either of the plates 32 and 34 . However, in the fourth aspect of the present disclosure, the thermal conductivity of the plate 33 only needs to be lower than that of at least one of the plates 32 and 34 .

[0097] In the above-mentioned embodiment, as the gap provided between the evaporation flow path and the superheat flow path, the gap 50 (see FIG. 1 ) located between the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 in the left-right direction (stack direction) is exemplified. Fig. 9 For example, a gap may be provided between the evaporation flow path and the superheat flow path in the surface direction of the plates 31 to 35.

[0098] In the above embodiment, the number of the second refrigerant flow paths 30m2 is smaller than the number of the first refrigerant flow paths 30m1, but it only needs to be less than the number of the first refrigerant flow paths 30m1 and may be the same as the number of the first refrigerant flow paths 30m1.

[0099] In the above-mentioned embodiment, the length of the second refrigerant flow path 30m2 is longer than any of the lengths of the four first refrigerant flow paths 30m1, but it only needs to be longer than the length of the first refrigerant flow path 30m1, and may be the same as any of the lengths of the four first refrigerant flow paths 30m1.

[0100] In the above-mentioned embodiment, as the first heat exchange part and the second heat exchange part, the rear heat exchange part 10u1 and the front heat exchange part 10u2 sandwiched between the bent part in the bent indoor heat exchanger 10 are exemplified, but the invention is not limited thereto. For example, two heat exchange parts arranged in a straight line and without a bent part may be used as the first heat exchange part and the second heat exchange part.

[0101] Although the embodiments have been described above, it should be understood that various modifications may be made to the form or detailed structure without departing from the spirit and scope of the claims.

[0102] Description of symbols

[0103] 1: Air conditioner;

[0104] 10: Indoor heat exchanger;

[0105] 10u: heat exchange part;

[0106] 10u1: rear heat exchange section (first heat exchange section);

[0107] 10u2: front heat exchange section (second heat exchange section);

[0108] 11: fin;

[0109] 12: heat transfer tube;

[0110] 30: Plate stack;

[0111] 30m: refrigerant flow path;

[0112] 30m1: 1st refrigerant flow path;

[0113] 30m2: 2nd refrigerant flow path;

[0114] 32: Plate (1st plate);

[0115] 321y, 322y, 323y, 324a: elongated hole (first incision);

[0116] 323x: round hole (3rd incision);

[0117] 324x: round hole (4th incision);

[0118] 33: Plate (3rd plate);

[0119] 34: Plate (2nd plate);

[0120] 342x: elongated hole (second incision);

[0121] 50: gap;

[0122] 60: Connect the flow path.

Claims

1. An indoor heat exchanger, wherein: The indoor heat exchanger comprises: a heat exchange portion, comprising fins and a plurality of heat transfer tubes penetrating the fins; and a plate stack having a plurality of refrigerant flow paths connected to the plurality of heat transfer tubes, The plurality of refrigerant flow paths include a first refrigerant flow path and a second refrigerant flow path, The plate stack includes a first plate and a second plate stacked at a position farther from the plurality of heat transfer tubes than the first plate in a stacking direction. The first plate is formed with a first notch, a third notch, and a fourth notch. A second notch connected to the third notch and the fourth notch is formed on the second plate. The first cutout forms the first refrigerant flow path. The second cutout, the third cutout, and the fourth cutout form the second refrigerant flow path. When viewed from the stacking direction, the first refrigerant flow path intersects with the second refrigerant flow path.

2. The indoor heat exchanger according to claim 1, wherein: The plurality of heat transfer tubes include a first heat transfer tube serving as an evaporation zone and a second heat transfer tube serving as a superheat zone. The plurality of refrigerant flow paths include an evaporation flow path connected to the first heat transfer tube and a superheat flow path connected to the second heat transfer tube. When viewed from the stacking direction, the evaporation flow path and the superheat flow path do not intersect with each other.

3. The indoor heat exchanger according to claim 1 or 2, wherein: The plurality of heat transfer tubes include a first heat transfer tube serving as an evaporation zone and a second heat transfer tube serving as a superheat zone. The plurality of refrigerant flow paths include: an evaporation flow path connected to the first heat transfer tube and constituting one of the first refrigerant flow path and the second refrigerant flow path; and a superheat flow path connected to the second heat transfer tube and constituting the other of the first refrigerant flow path and the second refrigerant flow path. The plate stack further includes a third plate, the third plate being arranged between the first plate and the second plate in the stacking direction, and the third plate having a thickness greater than at least one of the first plate and the second plate.

4. The indoor heat exchanger according to any one of claims 1 to 3, wherein: The plurality of heat transfer tubes include a first heat transfer tube serving as an evaporation zone and a second heat transfer tube serving as a superheat zone. The plurality of refrigerant flow paths include: an evaporation flow path connected to the first heat transfer tube and constituting one of the first refrigerant flow path and the second refrigerant flow path; and a superheat flow path connected to the second heat transfer tube and constituting the other of the first refrigerant flow path and the second refrigerant flow path. The plate stack further includes a third plate disposed between the first plate and the second plate in the stacking direction, wherein the third plate has a lower thermal conductivity than at least one of the first plate and the second plate.

5. The indoor heat exchanger according to any one of claims 2 to 4, wherein: The plate stack has a gap between the evaporation flow path and the superheat flow path through which no refrigerant flows.

6. The indoor heat exchanger according to any one of claims 1 to 5, wherein: The number of the second refrigerant flow paths is less than the number of the first refrigerant flow paths.

7. The indoor heat exchanger according to any one of claims 1 to 6, wherein: The length of the second refrigerant flow path is greater than or equal to the length of the first refrigerant flow path.

8. The indoor heat exchanger according to any one of claims 1 to 7, wherein: The heat exchange part includes a first heat exchange part and a second heat exchange part, The plurality of heat transfer tubes include a first heat transfer tube included in the first heat exchange portion and a second heat transfer tube included in the second heat exchange portion. The first plate is provided with a connection flow path that connects the first heat transfer tube and the second heat transfer tube.

9. An air conditioner, wherein: The air conditioner includes the indoor heat exchanger according to any one of claims 1 to 8.

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