Indoor heat exchanger and air conditioner

Abstract

Suppress the enlargement of the plate laminate in the plane direction. The refrigerant flow path (30m) of the plate laminate (30) includes: a first refrigerant flow path (30m1) formed by elongated holes (321y, 322y, 323y, 324a) formed in the plate (32); and a second refrigerant flow path (30m2) formed by 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). When viewed from the left-right direction (lamination direction), the first refrigerant flow path (30m1) intersects with the second refrigerant flow path (30m2).

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] In Patent Document 1, an indoor unit for an air conditioner used in an air conditioner is disclosed. In this indoor unit for an air conditioner, in order to achieve space saving, a plate-like distribution member formed by laminating a plurality of plates is connected to a heat transfer tube of a heat exchanger main body.

[0003] Prior Art Documents

[0004] Patent Documents

[0005] Patent Document 1: Japanese Unexamined 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 in a center plate among three plates constituting the plate-like distribution member, and a bottom plate and a top plate define the refrigerant flow path. In this case, depending on the structure of the refrigerant flow path, it is necessary to provide a detour in the plane of the center plate. Therefore, in the plane direction along the plane of the plate, the plate-like distribution member (corresponding to the "plate laminate" in the present disclosure) is enlarged.

[0008] An object of the present disclosure is to provide an indoor heat exchanger capable of suppressing enlargement of a plate laminate in a plane direction and an air conditioner including the indoor heat exchanger.

[0009] Means for Solving the Problems

[0010] The indoor heat exchanger according to a first aspect of the present disclosure includes: a heat exchange unit including fins and a plurality of heat transfer tubes passing through the fins; and a plate laminate in which a plurality of refrigerant flow paths connected to the plurality of heat transfer tubes are formed. The plurality of refrigerant flow paths include a first refrigerant flow path and a second refrigerant flow path. The plate laminate includes a first plate and a second plate laminated in a lamination direction at a position farther from the plurality of heat transfer tubes than the first plate. A first cutout, a third cutout, and a fourth cutout are formed in the first plate, and a second cutout connected to the third cutout and the fourth cutout is formed in the second plate. The first cutout forms the first refrigerant flow path, and the second cutout, the third cutout, and the fourth cutout form the second refrigerant flow path. When viewed from the lamination direction, the first refrigerant flow path intersects the second refrigerant flow path.

[0011] According to the first aspect of the present disclosure, instead of providing a detour within the plane of the plate, the first refrigerant flow path intersects the second refrigerant flow path. Thereby, it is possible to suppress the increase in size of the plate laminate in the plane direction.

[0012] The indoor heat exchanger according to the second aspect of the present disclosure may be such that, in the first aspect described above, the plurality of heat transfer tubes include a first heat transfer tube that forms an evaporation region and a second heat transfer tube that forms a superheat region, 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 (the evaporation flow path and the superheat flow path) intersect each other, due to the heat conduction between the flow paths at the intersection, the thermal efficiency may deteriorate. Regarding this point, in this structure, the flow paths with a large temperature difference (the evaporation flow path and the superheat flow path) do not intersect each other, thereby being able to suppress this problem.

[0013] The indoor heat exchanger according to the third aspect of the present disclosure may be such that, in the first or second aspect described above, the plurality of heat transfer tubes include a first heat transfer tube that forms an evaporation region and a second heat transfer tube that forms a superheat region, 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 laminate further includes a third plate, the third plate is disposed 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 with a large thickness. Thereby, it is possible to effectively suppress the deterioration of the thermal efficiency.

[0014] The indoor heat exchanger according to the fourth aspect of the present disclosure may be such that, in any one of the first to third aspects described above, the plurality of heat transfer tubes include a first heat transfer tube that forms an evaporation region and a second heat transfer tube that forms a superheat region, 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 laminate further includes a third plate, the third plate is disposed between the first plate and the second plate in the stacking direction, and the thermal conductivity of the third plate is lower 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 with a low thermal conductivity. Thereby, it is possible to effectively suppress the deterioration of the thermal efficiency.

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

[0016] The indoor heat exchanger according to the sixth aspect of the present disclosure may be such that, in any one of the first to fifth aspects described above, the number of the second refrigerant flow paths is less than or equal to the number of the first refrigerant flow paths. When 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 in the plate between the first plate and the second plate increases, and the process of forming the through-holes becomes complicated. In this regard, in this structure, since the number of the second refrigerant flow paths is small, the above problem can be suppressed.

[0017] The indoor heat exchanger according to the seventh aspect of the present disclosure may be such that, in any one of the first to sixth aspects described above, the length of the second refrigerant flow path is greater than or equal to the length of the first refrigerant flow path. If the length of the second refrigerant flow path is short, the wall thickness between the second refrigerant flow path and the first refrigerant flow path in the first plate becomes small, and thus, reduction of strength or deterioration of workability becomes a problem. In this regard, in this structure, since the length of the second refrigerant flow path is long, the above problem can be suppressed.

[0018] The indoor heat exchanger according to the eighth aspect of the present disclosure may be such that, in any one of the first to seventh aspects described above, the heat exchange section includes a first heat exchange section and a second heat exchange section, the plurality of heat transfer tubes include a first heat transfer tube included in the first heat exchange section and a second heat transfer tube included in the second heat exchange section, and a connection flow path for connecting the first heat transfer tube and the second heat transfer tube is provided on the first plate. The second plate is laminated at a position farther from the plurality of heat transfer tubes than the first plate. If a connection flow path is provided on the second plate, the distance in the lamination direction from the end face of the heat transfer tube to the connection flow path formed in the second plate becomes long, and thus the pressure loss may increase. In this regard, in this structure, by providing the connection flow path on the first plate, the following situation can be suppressed: the above distance becomes long and the pressure loss increases accordingly.

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

[0020] Figure 1 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 Is Figure 1 The right side view of the indoor heat exchanger included in the air conditioner shown in the figure.

[0022] Figure 3 Is Figure 1 The perspective view of the laminate shown in the figure.

[0023] Figure 4 Is the component of Figure 3 The top view of the leftmost plate among the five plates that make up the laminate shown in the figure.

[0024] Figure 5 Is the component of Figure 3 The top view of the second plate from the left among the five plates that make up the laminate shown in the figure.

[0025] Figure 6 Is the component of Figure 3 The top view of the third plate from the left among the five plates that make up the laminate shown in the figure.

[0026] Figure 7 Is the component of Figure 3 The top view of the fourth plate from the left among the five plates that make up the laminate shown in the figure.

[0027] Figure 8 Is the component of Figure 3 The top view of the rightmost plate among the five plates that make up the laminate shown in the figure.

[0028] Figure 9 Is the cross-sectional view of the laminate along Figure 5 The IX-IX line shown in the figure.

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

[0030] Figure 11 Is the cross-sectional view of the laminate and the heat exchange part along Figure 10 The XI-XI line shown in the figure. Detailed implementation mode

[0031] <The First Embodiment>

[0032] First, with reference to Figure 1 , the overall structure of the air conditioner 1 of the first embodiment of the present disclosure will be described. In addition, in the following description, the directions of "up", "down", "right", "left", "front", and "back" indicate the directions in the state where the air conditioner 1 is set in the Figure 1 state.

[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 forms the bottom and rear of the air conditioner 1. The frame 1f is long in one direction and is Figure 1 mounted on the indoor wall surface in the manner that this one direction runs along the left - right direction via a mounting plate (not shown). 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 also long in one direction ( Figure 1 the left - right direction).

[0036] Next, with reference to Figures 1 - 9 , the structure of the indoor heat exchanger 10 will be described in detail.

[0037] As Figure 1 shown, the indoor heat exchanger 10 includes a heat exchange section 10u, a plate laminate 30, a plurality of U - shaped elbows 22, and a plurality of connecting pipes 23. In Figure 1 , a portion of one U - shaped elbow 22 among the plurality of U - shaped elbows 22 that overlaps with the plate laminate 30 when viewed from the side is depicted by a dashed line.

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

[0039] The plurality of fins 11 are each in a thin plate shape and are arranged in such a manner that the plate surfaces are along the up - down direction and the front - rear direction. The plurality of fins 11 are arranged at equal intervals in the left - right direction.

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

[0041] In addition, in Figure 1 , for simplicity, only a part of the plurality of heat transfer pipes 12 and only a part of the plurality of fins 11 are depicted.

[0042] The left end of each heat transfer pipe 12 is connected to the left end of other heat transfer pipes 12 via a U - shaped bending portion 21. The right end of each heat transfer pipe 12 is connected to the right end of other heat transfer pipes 12 via a U - shaped elbow 22, a connecting pipe 23, or the plate laminate 30. The bending portion 21 is located on the left side with respect to the plurality of fins 11. The U - shaped elbows 22, the connecting pipes 23, and the plate laminate 30 are located on the right side with respect to the plurality of fins 11.

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

[0044] The plate laminate 30 includes five plates 31 to 35 laminated in the left-right direction (the lamination direction) (see Figure 3 ). Refrigerant flow paths are formed in the U-bend 22, the connecting pipe 23, and the plate laminate 30.

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

[0046] The tube sheet 14 is arranged with its plate surface along the up-down direction and the front-back direction, and is located on the right side with respect to the plurality of fins 11. A plurality of heat transfer tubes 12 penetrate through 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 with respect to the tube sheet 14, the U-bend 22, the connecting pipe 23, and the plate laminate 30 are arranged.

[0047] In addition, 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 protrude slightly to the right from the right side surface of the tube sheet 14. That is, the end surfaces 12x of the plurality of heat transfer tubes 12 are located slightly to the right of the right side surface of the tube sheet 14.

[0049] As Figure 2 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 bent type in which the first to fourth tube sheets 141 to 144 are arranged at an angle with respect to the adjacent tube sheets 141 to 144. The plurality of heat transfer tubes 12 respectively penetrate through the first to fourth tube sheets 141 to 144. In each U-shaped tube (the U-shaped tube formed by bending a single tube and consisting of a pair of heat transfer tubes 12 and the bent portion 21), the pair of heat transfer tubes 12 do not penetrate through two different tube sheets among the first to fourth tube sheets 141 to 144.

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

[0051] Two adjacent heat transfer tubes 121a and 122a among the multiple heat transfer tubes 12 of the post heat exchange section 10u1 are connected via the refrigerant flow path 22m of the U-shaped pipe 22. The two heat transfer tubes 121a and 122a respectively form different U-shaped tubes (U-shaped tubes formed by bending a single tube and consisting of a pair of heat transfer tubes 12 and a bending section 21).

[0052] One of the multiple heat transfer tubes 12 of the post heat exchange section 10u1 (heat transfer tube 121b) is connected to one of the multiple heat transfer tubes 12 of the pre heat exchange section 10u2 (heat transfer tube 122b) via the refrigerant flow path 23m of the connecting pipe 23. One of the multiple heat transfer tubes 12 of the post heat exchange section 10u1 (heat transfer tube 121c) is connected to one of the multiple heat transfer tubes 12 of the pre heat exchange section 10u2 (heat transfer tube 122c) via the refrigerant flow path 23m of the connecting pipe 23. One of the multiple heat transfer tubes 12 of the post heat exchange section 10u1 (heat transfer tube 121d) is connected to one of the multiple heat transfer tubes 12 of the pre heat exchange section 10u2 (heat transfer tube 122d) via the refrigerant flow path 23m of the connecting pipe 23. One of the multiple heat transfer tubes 12 of the post heat exchange section 10u1 (heat transfer tube 121e) is connected to one of the multiple heat transfer tubes 12 of the pre heat exchange section 10u2 (heat transfer tube 122e) via the refrigerant flow path 23m of the connecting pipe 23.

[0053] The heat transfer tube 121c is also connected to the expansion valve 19. The expansion valve 19 is installed on the connecting pipe 23 that connects the heat transfer tube 121c and the heat transfer tube 122c.

[0054] On the right side with respect to the multiple fins 11, the heat transfer tubes 12 among the multiple heat transfer tubes 12 of the post heat exchange section 10u1, excluding the six heat transfer tubes 121a, 122a, 121b, 121c, 121d, and 121e connected to the U-shaped pipe 22 or the connecting pipe 23, are connected to the plate laminate 30.

[0055] In addition, Figure 3 The shown plate laminate 30 is installed on the post heat exchange section 10u1. The plate laminate installed on the pre heat exchange section 10u2 has the same structure as the plate laminate 30, and the illustration and description thereof are omitted.

[0056] The laminate 30 is mounted on the heat transfer tubes 12 of the rear heat exchange section 10u1 that are not connected to the U-shaped elbows 22 or the connecting pipes 23 via a plurality of connecting sections 40. The plurality of connecting sections 40 are each cylindrical and have a refrigerant flow path inside. Each connecting section 40 extends in the left-right direction and connects the heat transfer tube 12 and the laminate 30 in the left-right direction. Each connecting section 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 laminate 30.

[0057] A recess 30x, 30y is provided in a part (rear part) of the outer periphery of the laminate 30. The recesses 30x, 30y penetrate the laminate 30 in the left-right direction. The recesses 30x, 30y are void portions formed in a shape that cuts off the plates 31 to 35. The U-shaped elbow 22 is disposed at a position corresponding to the recess 30y (see Figures 4 - 8 ).

[0058] The length of the connecting section 40 in the left-right direction is shorter than the length of the U-shaped elbow 22 in the left-right direction. The first distance D1 in the left-right direction (lamination direction) from the end face 12x of the heat transfer tube 12 to the face (left side face of the plate 31) closest to the end face 12x of the heat transfer tube 12 in the laminate 30 is shorter than the second distance D2 in the left-right direction (lamination direction) from the end face 12x of the heat transfer tube 12 to the face (the top of the U-shape) farthest from the end face 12x of the heat transfer tube 12 in the U-shaped elbow 22 (see Figure 1 ). Therefore, as shown in Figure 1 , when viewed from the front-rear direction, the U-shaped elbow 22 overlaps the laminate 30.

[0059] Next, with reference to Figures 4 - 9 , the refrigerant flow path 30m formed in the laminate 30 will be described in detail.

[0060] The refrigerant flow path 30m is constituted by through holes formed in each of the plates 31 to 35 constituting the laminate 30.

[0061] As shown in Figure 4 , a plurality of round holes (including the round holes 313a and 314a described later) are formed in the plate 31. The right ends of the connecting sections 40 (see Figure 3 ) are respectively inserted into these round holes.

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

[0063] As shown inFigure 6 As shown, a plurality of round holes (including round hole 334a described later) are formed in plate 33. Each of these round holes communicates with one of the round holes or elongated holes formed in plate 32.

[0064] As Figure 7 shown, a plurality of elongated holes (including elongated holes 342x and 343a described later) are formed in plate 34. Each of these elongated holes communicates with two of the plurality of round holes formed in plate 33.

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

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

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

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

[0069] The plate 32 corresponds to the "first plate" of the present disclosure. The plate 34 is laminated in the left - right direction (lamination direction) at a position farther from the heat transfer tube 12 than the plate 32, 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). Further, when viewed in the left - right direction, the length of the second refrigerant flow path 30m2 ( Figure 7 the length of the elongated hole 342x shown) is longer than any one of the lengths of the four first refrigerant flow paths 30m1 ( Figure 5 the lengths of the elongated holes 321y, 322y, 323y, 324a shown).

[0071] The plurality of heat transfer tubes 12 connected to the refrigerant flow path 30m include a first heat transfer tube that becomes an evaporation region and a second heat transfer tube that becomes a superheat region. The evaporation region and the superheat region are switched according to the control of the indoor heat exchanger 10, and one heat transfer tube exists in a state of becoming an evaporation region and a state of becoming a superheat region according to the control of the indoor heat exchanger 10.

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

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

[0074] That is, with respect to the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 that cross when viewed in the left - right direction (lamination direction), when one becomes the evaporation flow path, the other sometimes becomes the superheat flow path. In such a case, for the plate 33 interposed between the first refrigerant flow path 30m1 and the elongated hole 342x constituting the second refrigerant flow path 30m2, its thickness is larger than any one of the plates 32, 34 (refer to Figure 9 ), and its thermal conductivity is lower than any one of the plates 32, 34.

[0075] The plate 33 is a plate disposed between the plate 32 and the plate 34, corresponding to the "third plate" of the present disclosure.

[0076] A gap 50 through which refrigerant does not flow is formed in the plate 33 (see Figure 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 (stacking direction). For example, the plate 33 may be composed of two plate members, and recesses are formed on the two plate members by half - etching or the like, and the recesses are combined to form the gap 50.

[0077] The elongated holes 342x formed in the plate 34 (see Figure 7 ) do not straddle the elongated holes 329 formed in the plate 32. When observed from the left - right direction (stacking direction), the elongated holes 342x and the elongated holes 329 do not cross.

[0078] The elongated holes 329 are connected to the heat transfer tubes 125e (see Figure 4 ). When the heat transfer tube 125e (the first heat transfer tube) becomes an evaporation region, the heat transfer tubes 126a, 126b (the second heat transfer tubes) may become a superheat region. In this case, the elongated holes 329 correspond to the "evaporation flow path" of the present disclosure, and the second refrigerant flow path 30m2 corresponds to the "superheat flow path" of the present disclosure. When the heat transfer tube 125e (the second heat transfer tube) becomes a superheat region, the heat transfer tubes 126a, 126b (the first heat transfer tubes) become an evaporation region. In this case, the elongated holes 329 correspond to the "superheat flow path" of the present disclosure, and the second refrigerant flow path 30m2 corresponds 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 laminate 30 includes: a first refrigerant flow path 30m1 (see Figure 5 ), which is composed of the elongated holes 321y, 322y, 323y, 324a formed in the plate 32; and a second refrigerant flow path 30m2 (see Figures 5 - 7 ), which is composed of the circular holes 323x, 324x formed in the plate 32, the circular holes formed in the plates 31, 33, and the elongated holes 342x formed in the plate 34. When observed from the left - right direction (stacking direction), the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 cross (see Figure 5 ). In this case, instead of providing a detour in the plane of the plates 31 - 35, the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 cross each other, thereby being able to suppress the enlargement of the plate laminate 30 in the plane direction along the plane of the plates 31 - 35.

[0080] When viewed from the left - right direction (the stacking 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 that constitutes the second refrigerant flow path 30m2) do not cross (refer to Figure 5 ). If flow paths with a large temperature difference (the evaporation flow path and the superheat flow path) cross each other, due to heat conduction between the flow paths at the crossing part, the thermal efficiency may deteriorate. Regarding this point, in this structure, the flow paths with a large temperature difference (the evaporation flow path and the superheat flow path) do not cross each other, thereby being able to suppress this problem.

[0081] When the first refrigerant flow path 30m1 is an evaporation flow path and the second refrigerant flow path 30m2 is a superheat flow path, the thickness of the plate 33 between the first refrigerant flow path 30m1 and the elongated hole 342x that constitutes the second refrigerant flow path 30m2 is larger than that of either of the plates 32 and 34 (refer to Figure 9 ). In this case, the thick plate 33 suppresses heat conduction between the evaporation flow path and the superheat flow path. Thereby, the deterioration of the thermal efficiency can be effectively suppressed.

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

[0083] The plate stack 30 has a gap 50 through which no refrigerant flows between the evaporation flow path (e.g., the first refrigerant flow path 30m1) and the superheat flow path (e.g., the second refrigerant flow path 30m2) (refer to Figure 9 ). In this case, the gap 50 suppresses heat conduction between the evaporation flow path and the superheat flow path. Thereby, 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 becomes large, and the formation process of the through - holes becomes complicated. Regarding this point, 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) is shorter than the length of the four first refrigerant flow paths 30m1 ( Figure 5Any of the lengths of the elongated holes 321y, 322y, 323y, and 324a shown is long. If 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 small, and thus, a decrease in strength or deterioration in workability becomes a problem. Regarding this point, in this structure, since the length of the second refrigerant flow path 30m2 is long, the above problems can be suppressed.

[0086] <Second Embodiment>

[0087] Next, refer to Figure 10 and Figure 11 to describe the indoor heat exchanger according to the second embodiment of the present disclosure.

[0088] In the second embodiment, one of the plurality of heat transfer tubes 12 (heat transfer tube 121f) included in the post heat exchange section 10u1 is connected to one of the plurality of heat transfer tubes 12 (heat transfer tube 122f) included in the pre heat exchange section 10u2 via a connection flow path 60 formed on the plate 32 of the plate laminate 30.

[0089] The post heat exchange section 10u1 corresponds to the "first heat exchange section" of the present disclosure, and the pre heat exchange section 10u2 corresponds to the "second heat exchange section" 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 laminate 30 is disposed across the post heat exchange section 10u1 and the pre heat exchange section 10u2. The connection flow path 60 is formed in the plates 32 and 31 and is not formed in the other plates (plates 33 to 35).

[0091] The plate 34 is laminated at a position farther from the plurality of heat transfer tubes 12 than the plate 32. If the connection flow path 60 is provided on the plate 34, the distance in the left - right direction from the end face 12x of the heat transfer tube 12 to the connection flow path 60 formed in the plate 34 becomes long, and thus the pressure loss may increase. Regarding this point, in this structure, by providing the connection flow path 60 on the plate 32, it is possible to suppress the following situation: the above - mentioned distance becomes long and the pressure loss increases.

[0092] <Modification Example>

[0093] In the above-described embodiment, the refrigerant flow path 30m of the plate laminate 30 is formed by through-holes formed in each of the plates 31 to 35, but it is not limited thereto. For example, part or all of the refrigerant flow path 30m may also be formed by bottomed grooves formed in each of the plates 31 to 35 by semi-etching or the like. Similarly, the "first cut", "second cut", "third cut", and "fourth cut" of the present disclosure are not limited to through-holes, and may also be bottomed grooves formed in each of the plates 31 to 35 by semi-etching or the like.

[0094] In the above-described embodiment, the U-shaped bend 22 (refrigerant pipe) is disposed at a position corresponding to the recess 30y provided on the outer periphery of the plate laminate 30, but it is not limited thereto. For example, a through-hole or a recess may be formed in the central portion of the plate laminate, and the refrigerant pipe may be disposed at a position corresponding to the through-hole or the recess.

[0095] In the above-described embodiment, the thickness of the plate 33 is greater than either of the plates 32 and 34, but in the third aspect of the present disclosure, the thickness of the plate 33 only needs to be greater than 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 either of the plates 32 and 34, but in the fourth aspect of the present disclosure, the thermal conductivity only needs to be lower than at least one of the plates 32 and 34.

[0097] In the above-described embodiment, as the gap provided between the evaporation flow path and the superheat flow path, for example, the gap 50 located between the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 in the left-right direction (lamination direction) is exemplified (see Figure 9 ), but it is not limited thereto. For example, a gap may also be provided between the evaporation flow path and the superheat flow path in the plane direction of the plates 31 to 35.

[0098] In the above-described 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 equal to or less than the number of the first refrigerant flow paths 30m1, and may also be the same as the number of the first refrigerant flow paths 30m1.

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

[0100] In the above-described embodiment, as the first heat exchange unit and the second heat exchange unit, the rear heat exchange unit 10u1 and the front heat exchange unit 10u2 that sandwich the bent portion in the bent-type indoor heat exchanger 10 are illustrated, but it is not limited thereto. For example, two heat exchange units arranged in a straight line without a bent portion may be used as the first heat exchange unit and the second heat exchange unit.

[0101] The above describes the embodiment, but it can be understood that various changes in form or detailed structure can be made without departing from the gist and scope of the claims.

[0102] Reference Numeral Explanation

[0103] 1: Air conditioner;

[0104] 10: Indoor heat exchanger;

[0105] 10u: Heat exchange unit;

[0106] 10u1: Rear heat exchange unit (first heat exchange unit);

[0107] 10u2: Front heat exchange unit (second heat exchange unit);

[0108] 11: Fin;

[0109] 12: Heat transfer tube;

[0110] 30: Plate laminate;

[0111] 30m: Refrigerant flow path;

[0112] 30m1: First refrigerant flow path;

[0113] 30m2: Second refrigerant flow path;

[0114] 32: Plate (first plate);

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

[0116] 323x: Round hole (third cut);

[0117] 324x: Round hole (fourth cut);

[0118] 33: Plate (third plate);

[0119] 34: Plate (second plate);

[0120] 342x: Elongated hole (second cut);

[0121] 50: Gap;

[0122] 60: Connecting flow path.

Claims

1. An indoor heat exchanger, wherein, the indoor heat exchanger includes: a heat exchange section including fins and a plurality of heat transfer tubes passing through the fins; and a plate laminate having 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 laminate includes a first plate and a second plate laminated in the lamination direction at a position farther from the plurality of heat transfer tubes than the first plate, a first cutout, a third cutout, and a fourth cutout are formed in the first plate, a second cutout connected to the third cutout and the fourth cutout is formed in 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 lamination direction, the first refrigerant flow path intersects 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 region and a second heat transfer tube serving as a superheat region, 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 lamination direction, the evaporation flow path does not intersect the superheat flow path.

3. 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 region and a second heat transfer tube serving as a superheat region, the plurality of refrigerant flow paths include: an evaporation flow path connected to the first heat transfer tube, which constitutes 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, which constitutes the other of the first refrigerant flow path and the second refrigerant flow path, the plate laminate further includes a third plate disposed between the first plate and the second plate in the lamination direction, and the thickness of the third plate is greater than at least one of the first plate and the second plate.

4. 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 region and a second heat transfer tube serving as a superheat region, the plurality of refrigerant flow paths include: an evaporation flow path connected to the first heat transfer tube, which constitutes 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, which constitutes the other of the first refrigerant flow path and the second refrigerant flow path, the plate laminate further includes a third plate disposed between the first plate and the second plate in the lamination direction, and the thermal conductivity of the third plate is lower 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 laminate has a void in which refrigerant does not flow between the evaporation flow path and the superheat flow path.

6. The indoor heat exchanger according to claim 1, wherein, the number of the second refrigerant flow paths is equal to or less than the number of the first refrigerant flow paths.

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

8. The indoor heat exchanger according to claim 1, wherein the heat exchange section includes a first heat exchange section and a second heat exchange section, the plurality of heat transfer tubes include a first heat transfer tube included in the first heat exchange section and a second heat transfer tube included in the second heat exchange section, a connection flow path for connecting the first heat transfer tube and the second heat transfer tube is provided on the first plate.

9. An air conditioner, wherein the air conditioner includes the indoor heat exchanger according to claim 1.

Images