EP4597022A1

EP4597022A1 - Indoor heat exchanger, and air conditioner

Info

Publication number: EP4597022A1
Application number: EP23872492.6A
Authority: EP
Inventors: Shutaro YAMAMOTO; Hiroyuki Nakano; Yoshiyuki Matsumoto; Shota AGO
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2022-09-30
Filing date: 2023-09-27
Publication date: 2025-08-06
Also published as: JP7426456B1; CN119654535B; JP2024052099A; CN119654535A; EP4597022A4; WO2024071270A1

Abstract

An object of the present disclosure is to suppress the increase in size of a plate stacked body in a surface direction of the plate stacked body.

A refrigerant passage 30m of a plate stacked body 30 includes: a first refrigerant passage 30m1 formed of each of slots 321y, 322y, 323y, and 324a formed on a plate 32; and a second refrigerant passage 30m2 formed of round holes 323x and 324x formed on the plate 32, round holes formed on plates 31 and 33, and a slot 342x formed on a plate 34. The first refrigerant passage 30m1 intersects with the second refrigerant passage 30m2 when viewed in a left-right direction (stacked direction).

Description

[Technical Field]

The present disclosure relates to an indoor heat exchanger and an air conditioner including this indoor heat exchanger.

[Background]

Patent Literature 1 discloses an air-conditioning indoor unit used for an air conditioner. In this air-conditioning indoor unit, in order to save space, a plate-shaped distribution member formed of stacked plates is connected to a heat transfer pipe of a heat exchanger main body.

[Citation List]

[Patent Literatures]

[Patent Literature 1] Japanese Laid-Open Patent Publication No. 2006-125652

[Summary of the Invention]

[Technical Problem]

In Patent Literature 1, among three plates forming the plate-shaped distribution member, a refrigerant passage is formed in a center plate, and an under plate and an over plate define this refrigerant passage. In this case, depending on the structure of the refrigerant passage, a bypass needs to be provided in a flat surface of the center plate. Therefore, the size of the plate-shaped distribution member (equivalent to a "plate stacked body" of the present disclosure) is increased in a surface direction along the flat surface of each plate.
An object of the present disclosure is to provide (i) an indoor heat exchanger making it possible to suppress the increase in size of a plate stacked body in a surface direction of the plate stacked body and (ii) an air conditioner including this indoor heat exchanger.

[Solution to Problem]

According to a first aspect of the present disclosure, an indoor heat exchanger comprises: a heat exchanging portion including a fin and heat transfer pipes penetrating the fin; and a plate stacked body in which refrigerant passages connected to the heat transfer pipes are formed, the refrigerant passages including a first refrigerant passage and a second refrigerant passage, the plate stacked body including a first plate and a second plate stacked at a position which is far from the heat transfer pipes in a stacked direction as compared to the first plate, the first plate being provided with a first cutout, a third cutout, and a fourth cutout, the second plate being provided with a second cutout connected to the third cutout and the fourth cutout, the first cutout forming the first refrigerant passage, the second cutout, the third cutout, and the fourth cutout forming the second refrigerant passage, and the first refrigerant passage intersecting with the second refrigerant passage viewed in the stacked direction.
According to the first aspect of the present disclosure, a bypass is not provided on a flat surface of each plate, and the refrigerant passage intersects with the second refrigerant passage. This suppresses the increase in size of the plate stacked body in a surface direction of the plate stacked body.
According to a second aspect of the present disclosure, the indoor heat exchanger of the first aspect may be arranged such that the heat transfer pipes include a first heat transfer pipe which functions as a vaporization area and a second heat transfer pipe which functions as an overheated area, the refrigerant passages include a vaporization passage connected to the first heat transfer pipe and an overheated passage connected to the second heat transfer pipe, and the vaporization passage does not intersect with the overheated passage viewed in the stacked direction. When passages (the vaporization passage and the overheated passage) with significantly different temperatures intersect with each other, heat conduction may occur at an intersection between these passages so that heat efficiency is deteriorated. According to this aspect of the present disclosure, because the passages (the vaporization passage and the overheated passage) with significantly different temperatures do not intersect with each other, this problem is suppressed.
According to a third aspect of the present disclosure, the indoor heat exchanger of the first or second aspect may be arranged such that the heat transfer pipes include the first heat transfer pipe which functions as the vaporization area and the second heat transfer pipe which functions as the overheated area, the refrigerant passages include (i) the vaporization passage which is connected to the first heat transfer pipe and which forms one of the first refrigerant passage and the second refrigerant passage and (ii) the overheated passage which is connected to the second heat transfer pipe and which forms the other of the first refrigerant passage and the second refrigerant passage which is not formed by the vaporization passage, and the plate stacked body is provided between the first plate and the second plate in the stacked direction and further includes a third plate which is thicker than at least one of the first plate and the second plate. In this case, the thick third plate suppresses the heat conduction between the vaporization passage and the overheated passage. This effectively suppresses the deterioration of heat efficiency.
According to a fourth aspect of the present disclosure, the indoor heat exchanger of any one of the first to third aspects may be arranged such that the heat transfer pipes include the first heat transfer pipe which functions as the vaporization area and the second heat transfer pipe which functions as the overheated area, the refrigerant passages include (i) the vaporization passage which is connected to the first heat transfer pipe and which forms the one of the first refrigerant passage and the second refrigerant passage and (ii) the overheated passage which is connected to the second heat transfer pipe and which forms the other of the first refrigerant passage and the second refrigerant passage which is not formed by the vaporization passage, and the plate stacked body is provided between the first plate and the second plate in the stacked direction and further includes the third plate whose heat conductivity is lower than the heat conductivity of the at least one of the first plate and the second plate. In this case, the third plate with low heat conductivity suppresses the heat conduction between the vaporization passage and the overheated passage. This effectively suppresses the deterioration of heat efficiency.
According to a fifth aspect of the present disclosure, the indoor heat exchanger of any one of the second to fourth aspects may be arranged such that the plate stacked body includes a void where a refrigerant does not flow, and the void is provided between the vaporization passage and the overheated passage. In this case, the void suppresses the heat conduction between the vaporization passage and the overheated passage. This effectively suppresses the deterioration of heat efficiency.
According to a sixth aspect of the present disclosure, the indoor heat exchanger of any one of the first to fifth aspects may be arranged such that the number of second refrigerant passages is equal to or smaller than the number of first refrigerant passages. When (i) a plate is provided between the first plate and the second plate and (ii) the number of the second refrigerant passages is large, the number of through holes formed on the plate provided between the first plate and the second plate is also large and a formation step of the through holes becomes complex. According to this aspect of the present disclosure, because the number of the second refrigerant passages is small, the above-described problem is suppressed.
According to a seventh aspect of the present disclosure, the indoor heat exchanger of any one of the first to sixth aspects may be arranged such that the length of each of the second refrigerant passages is equal to or longer than the length of each of the first refrigerant passages. When the length of the each of the second refrigerant passages is short, the thickness of the first plate is small at a position provided between the each of the second refrigerant passages and the each of the first refrigerant passages, with the result that strength and processability are deteriorated. According to this aspect of the present disclosure, because the length of the each of the second refrigerant passages is long, the above-described problem is suppressed.
According to an eighth aspect of the present disclosure, the indoor heat exchanger of any one of the first to seventh aspects may be arranged such that the heat exchanging portion includes a first heat exchanging portion and a second heat exchanging portion, the heat transfer pipes include the first heat transfer pipe included in the first heat exchanging portion and the second heat transfer pipe included in the second heat exchanging portion, and the first plate is provided with a connecting passage connecting the first heat transfer pipe to the second heat transfer pipe. The second plate is stacked at the position which is far from the heat transfer pipes as compared to the first plate. When the connecting passage is provided on the second plate, the distance from an end face of each of the heat transfer pipes to the connecting passage formed on the second plate may be long in the stacked direction so that pressure loss is large. According to this aspect of the present disclosure, because the connecting passage is provided on the first plate, (i) the above-described distance is suppressed from being long and (ii) the pressure loss is therefore suppressed.
According to a ninth aspect of the present disclosure, an air conditioner comprises the indoor heat exchanger according to any one of the first to eighth aspects.

[Brief Description of Drawings]

FIG. 1 is a front view of an air conditioner of First Embodiment of the present disclosure, from which an exterior panel is detached.
FIG. 2 is a right side view of an indoor heat exchanger included in the air conditioner shown in FIG. 1.
FIG. 3 is a perspective view of a plate stacked body shown in FIG. 1.
FIG. 4 is a plan view of the leftmost one of five plates forming the plate stacked body shown in FIG. 3.
FIG. 5 is a plan view of the second leftmost one of the five plates forming the plate stacked body shown in FIG. 3.
FIG. 6 is a plan view of the third leftmost one of the five plates forming the plate stacked body shown in FIG. 3.
FIG. 7 is a plan view of the fourth leftmost one of the five plates forming the plate stacked body shown in FIG. 3.
FIG. 8 is a plan view of the rightmost one of the five plates forming the plate stacked body shown in FIG. 3.
FIG. 9 is a cross section of the plate stacked body, taken along a line IX-IX shown in FIG. 5.
FIG. 10 shows an indoor heat exchanger of a second embodiment of the present disclosure, and corresponds to FIG. 5.
FIG. 11 is a cross section of the plate stacked body and a heat exchanging portion, taken along a line XI-XI shown in FIG. 10.

[Preferred Embodiment of Invention]

The following will describe the overall structure of an air conditioner 1 of First Embodiment of the present disclosure, with reference to FIG. 1. In the following description, the directions such as "up/upward", "down/downward", "right/rightward", "left/leftward", "front/forward", and "rear/rearward" will be used on the premise that the air conditioner 1 is oriented as shown in FIG. 1.
The air conditioner 1 includes an indoor heat exchanger 10, a fan and a filter (not illustrated), a frame 1f, and an exterior panel (not illustrated).
The frame 1f forms a bottom portion and rear portion of the air conditioner 1. The frame 1f is long in one direction, and is attached to a wall surface of a room via an attaching plate (not illustrated) so that this one direction extends along the left-right direction of FIG. 1. The fan, the exterior panel, and the indoor heat exchanger 10 are attached to the frame 1f. The filter is attached to the exterior panel.
The indoor heat exchanger 10 is long in one direction (the left-right direction of FIG. 1) in the same manner as the frame 1f.
The following will detail the structure of the indoor heat exchanger 10 with reference to FIG. 1 to FIG. 9.
As shown in FIG. 1, the indoor heat exchanger 10 includes a heat exchanging portion 10u, a plate stacked body 30, U-bend pipes 22, and communication pipes 23. A part of one of the U-bend pipes 22 overlaps the plate stacked body 30 in a side view, and FIG. 1 illustrates this part by dotted lines.
The heat exchanging portion 10u includes fins 11, heat transfer pipes 12, and a pipe plate 14.
The fins 11 are thin plate-shaped, and provided so that a plate surface of each fin 11 extends along the up-down direction and the front-rear direction. The fins 11 are aligned in the left-right direction at regular intervals.
The heat transfer pipes 12 extend in the left-right direction, and penetrate the fins 11.
For simplification, FIG. 1 illustrates only one or more of the heat transfer pipes 12 and partially illustrates only one or more of the fins 11.
A left end of each heat transfer pipe 12 is connected to that of another heat transfer pipe 12 via a U-shaped bent portion 21. A right end of each heat transfer pipe 12 is connected to that of another heat transfer pipe 12 via a U-bend pipe 22, a communication pipe 23, or the plate stacked body 30. The bent portions 21 are provided to the left of the fins 11. The U-bend pipes 22, the communication pipes 23, and the plate stacked body 30 are provided to the right of the fins 11.
The bent portions 21 are formed integrally with the heat transfer pipes 12 and, by bending a single pipe, (i) a pair of heat transfer pipes 12 and (ii) a bent portion 21 are formed as each U-shaped pipe. Meanwhile, each U-bend pipe 22 and each communication pipe 23 are welded to open ends of an U-shaped pipe (right ends of heat transfer pipes 12) bent as described above.
The plate stacked body 30 includes five plates 31 to 35 (see FIG. 3) stacked in the left-right direction (stacked direction) . Each U-bend pipe 22, each communication pipe 23, and the plate stacked body 30 are provided with refrigerant passages.
As shown in FIG. 1, a diverter 18, an expansion valve 19, etc. are provided in the vicinity of the U-bend portions 22, the communication pipes 23, and the plate stacked body 30.
The pipe plate 14 is arranged so that a plate surface of the pipe plate 14 extends along the up-down direction and the front-rear direction, and provided to the right of the fins 11. The heat transfer pipes 12 penetrate the pipe plate 14. There is hardly a gap between the pipe plate 14 and each heat transfer pipe 12, and the pipe plate 14 supports the fins 11 and the heat transfer pipes 12. The U-bend pipes 22, the communication pipes 23, and the plate stacked body 30 are provided to the right of the pipe plate 14, i.e., to be opposite to the fins 11 over the pipe plate 14.
Although not illustrated, another pipe plate is provided to the left of the fins 11.
The heat transfer pipes 12 slightly protrude rightward as compared to a right side surface of the pipe plate 14. That is, end faces 12x of the heat transfer pipes 12 are positioned slightly to the right of the right side surface of the pipe plate 14.
As shown in FIG. 2, the pipe plate 14 includes a first pipe plate 141, a second pipe plate 142, a third pipe plate 143, and a fourth pipe plate 144. The indoor heat exchanger 10 is a bent-type. More specifically, the first to fourth pipe plates 141 to 144 are arranged so that each adjacent two of the plates 141 to 144 are inclined from one another. The heat transfer pipes 12 penetrate each of the first to fourth pipe plates 141 to 144. In each U-shaped pipe (formed of (i) a pair of heat transfer pipes 12 and (ii) a bent portion 21 which are formed of a single bent pipe), the pair of heat transfer pipes 12 penetrate the same one of the first to fourth plates 141 to 144.
The heat exchanging portion 10u is formed of a rear heat exchanging portion 10u1 including the first pipe plate 141 and a front heat exchanging portion 10u2 including the second to fourth pipe plates 142 to 144.
Among the heat transfer pipes 12 included in the rear heat exchanging portion 10u1, two adjacent heat transfer pipes 121a and 122a are connected to each other via a refrigerant passage 22m of a U-bend pipe 22. These two heat transfer pipes 121a and 122a form different U-shaped pipes (each of which is formed of (i) a pair of heat transfer pipes 12 and (ii) a bent portion 21 which are formed of a single bent pipe) .
One (heat transfer pipe 121b) of the heat transfer pipes 12 included in the rear heat exchanging portion 10u1 is connected to one (heat transfer pipe 122b) of the heat transfer pipes 12 included in the front heat exchanging portion 10u2 via a refrigerant passage 23m of one communication pipe 23. One (heat transfer pipe 121c) of the heat transfer pipes 12 included in the rear heat exchanging portion 10u1 is connected to one (heat transfer pipe 122c) of the heat transfer pipes 12 included in the front heat exchanging portion 10u2 via a refrigerant passage 23m of another communication pipe 23. One (heat transfer pipe 121d) of the heat transfer pipes 12 included in the rear heat exchanging portion 10u1 is connected to one (heat transfer pipe 122d) of the heat transfer pipes 12 included in the front heat exchanging portion 10u2 via a refrigerant passage 23m of another communication pipe 23. One (heat transfer pipe 121e) of the heat transfer pipes 12 included in the rear heat exchanging portion 10u1 is connected to one (heat transfer pipe 122e) of the heat transfer pipes 12 included in the front heat exchanging portion 10u2 via a refrigerant passage 23m of another communication pipe 23.
The heat transfer pipe 121c is also connected to the expansion valve 19. The expansion valve 19 is attached to one communication pipe 23 connecting the heat transfer pipes 121c and 122c.
Except six heat transfer pipes 121a, 122a, 121b, 121c, 121d, and 121e connected to U-bend pipes 22 or communication pipes 23, the heat transfer pipes 12 included in the rear heat exchanging portion 10u1 are connected to the plate stacked body 30 on the right side of the fins 11 in the left-right direction.
The plate stacked body 30 shown in FIG. 3 is attached to the rear heat exchanging portion 10u1. Another plate stacked body attached to the front heat exchanging portion 10u2 is structured in the same manner as the plate stacked body 30, and thus not illustrated and explained.
Among the heat transfer pipes 12 included in the rear heat exchanging portion 10u1, the plate stacked body 30 is attached via connectors 40 to heat transfer pipes 12 which are not connected to U-bend pipes 22 or communication pipes 23. The connectors 40 are cylindrical in shape, and refrigerant passages are provided inside the connectors 40. Each connector 40 extends in the left-right direction, and connects one of the above-described heat transfer pipes 12 to the plate stacked body 30 in the left-right direction. A left end of each connector 40 is connected to the end face 12x of one of the above-described heat transfer pipes 12, and a right end of each connector 40 is connected to a left side surface of the plate 31 of the plate stacked body 30.
Recesses 30x and 30y are provided on a part (rear part) of the outer periphery of the plate stacked body 30. The recesses 30x and 30y penetrate the plate stacked body 30 in the left-right direction. The recesses 30x and 30y are portions where the plates 31 to 35 are notched, i.e., cutouts on the plates 31 to 35. The U-bend pipes 22 are provided at positions corresponding to the recess 30y (see FIG. 4 to FIG. 8).
The length of the connectors 40 in the left-right direction is shorter than that of the U-bend pipes 22 in the left-right direction. One surface of the plate stacked body 30 (a left side surface of the plate 31) is closest to the end face 12x of each heat transfer pipe 12 among other surfaces of the plate stacked body 30, a part (top part) of each U-bend pipe 22 is furthest from the end face 12x of each heat transfer pipe 12 among the remaining part of each U-bend pipe 22, and the first distance D1 from the end face 12x of each heat transfer pipe 12 to this surface of the plate stacked body 30 in the left-right direction (stacked direction) is shorter (see FIG. 1) than the second distance D2 from the end face 12x of each heat transfer pipe 12 to this part of each U-bend pipe 22 in the left-right direction (stacked direction). Therefore, as shown in FIG. 1, each U-bend pipe 22 overlaps the plate stacked body 30 viewed in the front-rear direction.
The following will detail a refrigerant passage 30m formed in the plate stacked body 30, with reference to FIG. 4 to FIG. 9.
The refrigerant passage 30m is formed of through holes formed on the plates 31 to 35 forming the plate stacked body 30.
As shown in FIG. 4, the plate 31 is provided with round holes (including round holes 313a and 314a described later). Into each of these round holes, the right end of a connector 40 (see FIG. 3) is inserted.
As shown in FIG. 5, the plate 32 is provided with round holes (including round holes 323x, 324x, and 323a described later) and slots (including slots 321y, 322y, 323y, and 324a described later). Each of these round holes and slots is communicated with one or two of the round holes formed on the plate 31.
As shown in FIG. 6, the plate 33 is provided with round holes (including a round hole 334a described later). Each of these round holes is communicated with one round hole or slot formed on the plate 32.
As shown in FIG. 7, the plate 34 is provided with slots (including slots 342x and 343a described later). Each of these slots is communicated with two of the round holes formed on the plate 33.
As shown in FIG. 8, the plate 35 is provided with a single round hole 35x. The round hole 35x is communicated with one of the slots formed on the plate 34.
The through holes (round holes or slots) formed on the plates 31 to 35 are communicated with each other so that the refrigerant passage 30m is formed.
Two heat transfer pipes 123a and 124a (two of the heat transfer pipes 12 included in the rear heat exchanging unit 10u1) shown in FIG. 2 are connected to each other via the refrigerant passage 30m formed of: the round holes 313a and 314a formed on the plate 31; the round hole 323a and the slot 324a formed on the plate 32; the round holes 333a and 334a formed on the plate 33; and the slot 343a formed on the plate 34. These two heat transfer pipes 123a and 124a form different U-shaped pipes (each of which is formed of (i) a pair of heat transfer pipes 12 and (ii) a bent portion 21 which are formed of a single bent pipe).
As shown in FIG. 9, the slot 342x (see FIG. 7) formed on the plate 34 is formed across the four slots 321y, 322y, 323y, and 324a (see FIG. 5) formed on the plate 32. Each of the slots 321y, 322y, 323y, and 324a forms a first refrigerant passage 30m1 of the refrigerant passage 30m, and equivalent to a "first cutout" of the present disclosure. The round holes 323x and 324x on the plate 32, the round holes on the plates 31 and 33, and the slot 342x on the plate 34 form a second refrigerant passage 30m2 of the refrigerant passage 30m. The round hole 323x is equivalent to a "third cutout" of the present disclosure, the round hole 324x is equivalent to a "fourth cutout" of the present disclosure, and the slot 342x is equivalent to a "second cutout" of the present disclosure. One end of the slot 342x is connected to the round hole 323x, and the other end of the slot 342x is connected to the round hole 324x. Each first refrigerant passage 30m1 intersects with the second refrigerant passage 30m2 when viewed in the left-right direction (stacked direction; see FIG. 5).
The plate 32 is equivalent to a "first plate" of the present disclosure. The plate 34 is stacked at a position which is far from the heat transfer pipes 12 in the left-right direction (stacked direction) as compared to the plate 32, and equivalent to a "second plate" of the present disclosure.
The number (one) of second refrigerant passages 30m2 is smaller than the number (four) of first refrigerant passages 30m1. When viewed in the left-right direction, the length of the second refrigerant passage 30m2 (the length of the slot 342x shown in FIG. 7) is longer than the length of each of the four refrigerant passages 30m1 (the length of each of the slots 321y, 322y, 323y, and 324a shown in FIG. 5).
The heat transfer pipes 12 connected to the refrigerant passage 30m include first heat transfer pipes which function as vaporization areas and second heat transfer pipes which function as overheated areas. The vaporization areas and the overheated areas are switched under the control of the indoor heat exchanger 10, and each heat transfer pipe may be switched to a vaporization area or an overheated area under the control of the indoor heat exchanger 10.
The four slots 321y, 322y, 323y, and 324a forming the first refrigerant passages 30m1 are connected to heat transfer pipes 125a to 125d (see FIG. 4). The round holes 323x and 324x forming the second refrigerant passage 30m2 are connected to heat transfer pipes 126a and 126b (see FIG. 4).
When the heat transfer pipes 125a to 125d (first heat transfer pipes) function as vaporization areas, the heat transfer pipes 126a and 126b (second heat transfer pipes) may function as overheated areas. In this case, each first refrigerant passage 30m1 is equivalent to a "vaporization passage" of the present disclosure, and the second refrigerant passage 30m2 is equivalent to an "overheated passage" of the present disclosure. When the heat transfer pipes 125a to 125d (second heat transfer pipes) function as overheated areas, the heat transfer pipes 126a and 126b (first heat transfer pipes) function as vaporization areas. In this case, each first refrigerant passage 30m1 is equivalent to the "overheated passage" of the present disclosure, and the second refrigerant passage 30m2 is equivalent to the "vaporization passage" of the present disclosure.
That is, among each first refrigerant passage 30m1 intersecting with the second refrigerant passage 30m2 viewed in the left-right direction (stacked direction), when one of the first refrigerant passage 30m1 and the second refrigerant passage 30m2 is the vaporization passage, the other of the first refrigerant passage 30m1 and the second refrigerant passage 30m2 may be the overheated passage. In this case, the thickness of the plate 33 provided between the first refrigerant passage 30m1 and the slot 342x forming the second refrigerant passage 30m2 is larger than that of each of the plates 32 and 34 (see FIG. 9), and the heat conductivity of the plate 33 is lower than that of each of the plates 32 and 34.
The plate 33 is provided between the plates 32 and 34, and equivalent to a "third plate" of the present disclosure.
The plate 33 is provided with a void 50 where a refrigerant does not flow (see FIG. 9). The void 50 is positioned between the first refrigerant passage 30m1 and the second refrigerant passage 30m2 in the left-right direction (stacked direction). For example, the plate 33 may be formed of two plates, these two plates may be half-etched, etc. so that recesses are formed, and the void 50 may be formed by combining these recesses with each other.
The slot 342x formed on the plate 34 (see FIG. 7) is not formed across (does not overlap with) a slot 329 formed on the plate 32. When viewed in the left-right direction (stacked direction), the slot 342x does not intersect with the slot 329.
The slot 329 is connected to a heat transfer pipe 125e (see FIG. 4). When the heat transfer pipe 125e (first heat transfer pipe) functions as a vaporization area, the heat transfer pipes 126a and 126b (second heat transfer pipes) may function as overheated areas. In this case, the slot 329 is equivalent to the "vaporization passage" of the present disclosure, and the second refrigerant passage 30m2 is equivalent to the "overheated passage" of the present disclosure. When the heat transfer pipe 125e (second heat transfer pipe) functions as an overheated area, the heat transfer pipes 126a and 126b (first heat transfer pipes) function as vaporization areas. In this case, the slot 329 is equivalent to the "overheated passage" of the present disclosure, and the second refrigerant passage 30m2 is equivalent to the "vaporization passage" of the present disclosure.
In the present embodiment described above, the refrigerant passage 30m of the plate stacked body 30 includes: the first refrigerant passage 30m1 (see FIG. 5) formed of each of the slots 321y, 322y, 323y, and 324a formed on the plate 32; and the second refrigerant passage 30m2 (see FIG. 5 to FIG. 7) formed of the round holes 323x and 324x formed on the plate 32, the round holes formed on the plates 31 and 33, and the slot 342x formed on the plate 34. Each first refrigerant passage 30m1 intersects with the second refrigerant passage 30m2 when viewed in the left-right direction (stacked direction; see FIG. 5). In this case, a bypass is not provided on a flat surface of each of the plates 31 to 35, and the first refrigerant passage 30m1 intersects with the second refrigerant passage 30m2 so as to suppress the increase in size of the plate stacked body 30 in a surface direction along the flat surface of each of the plates 31 to 35.
When viewed in the left-right direction (stacked direction), the vaporization passage (e.g., the slot 329 formed on the plate 32) does not intersect with the overheated passage (e.g., the slot 342x which is formed on the plate 34 and which forms the second refrigerant passage 30m2; see FIG. 5). When passages (the vaporization passage and the overheated passage) with significantly different temperatures intersect with each other, heat conduction may occur at an intersection between these passages so that heat efficiency is deteriorated. In the present embodiment, because the passages (the vaporization passage and the overheated passage) with significantly different temperatures do not intersect with each other, this problem is suppressed.
When the first refrigerant passage 30m1 is the vaporization passage while the second refrigerant passage 30m2 is the overheated passage, the thickness of the plate 33 provided between the first refrigerant passage 30m1 and the slot 342x forming the second refrigerant passage 30m2 is larger than that of each of the plates 32 and 34 (see FIG. 9). In this case, the plate 33 with a large thickness suppresses the heat conduction between the vaporization passage and the overheated passage. This effectively suppresses the deterioration of heat efficiency.
When the first refrigerant passage 30m1 is the vaporization passage while the second refrigerant passage 30m2 is the overheated passage, the heat conductivity of the plate 33 provided between the first refrigerant passage 30m1 and the slot 342x forming the second refrigerant passage 30m2 is lower than that of each of the plates 32 and 34. In this case, the plate 33 with low heat conductivity suppresses the heat conduction between the vaporization passage and the overheated passage. This effectively suppresses the deterioration of heat efficiency.
The plate stacked body 30 includes the void 50 (see FIG. 9) where the refrigerant does not flow, and the void 50 is provided between the refrigerant passage (e.g., the first refrigerant passage 30m1) and the overheated passage (e.g., the second refrigerant passage 30m2). In this case, the void 50 suppresses the heat conduction between the vaporization passage and the overheated passage. This effectively suppresses the deterioration of heat efficiency.
The number (one) of second refrigerant passages 30m2 is smaller than the number (four) of first refrigerant passages 30m1. When the number of the second refrigerant passages 30m2 is large, the number of through holes formed on the plate 33 is also large and a formation step of the through holes becomes complex. In the present embodiment, because the number of the second refrigerant passages 30m2 is small, the above-described problem is suppressed.
The length of the second refrigerant passage 30m2 (the length of the slot 342x shown in FIG. 7) is longer than the length of each of the four refrigerant passages 30m1 (the length of each of the slots 321y, 322y, 323y, and 324a shown in FIG. 5). When the length of the second refrigerant passage 30m2 is short, the thickness of the plate 32 is small at a position between the second refrigerant passage 30m2 and the first refrigerant passage 30m1, with the result that strength and processability are deteriorated. In the present embodiment, because the length of the second refrigerant passage 30m2 is long, the above-described problem is suppressed.

The following will describe an indoor heat exchanger of Second Embodiment of the present disclosure with reference to FIG. 10 and FIG. 11.
In Second Embodiment, one (heat transfer pipe 121f) of heat transfer pipes 12 included in a rear heat exchanging portion 10u1 is connected to one (heat transfer pipe 122f) of heat transfer pipes 12 included in a front heat exchanging portion 10u2 via a connecting passage 60 formed in a plate 32 of a plate stacked body 30.
The rear heat exchanging portion 10u1 is equivalent to a "first heat exchanging portion" of the present disclosure, and the front heat exchanging portion 10u2 is equivalent to a "second heat exchanging portion" of the present disclosure. The heat transfer pipe 121f is equivalent to the "first heat transfer pipe" of the present disclosure, and the heat transfer pipe 122f is equivalent to the "second heat transfer pipe" of the present disclosure.
In the present embodiment, the plate stacked body 30 is formed across the rear heat exchanging portion 10u1 and the front heat exchanging portion 10u2. The connecting passage 60 is formed on the plate 32 and a plate 31, and is not formed in the other plates (plates 33 to 35).
The plate 34 is stacked at a position which is far from the heat transfer pipes 12 as compared to the plate 32. When the connecting passage 60 is formed in the plate 34, the distance from an end face 12x of each heat transfer pipe 12 to the connecting passage 60 formed in the plate 34 may be long in the left-right direction so that pressure loss is large. In the present embodiment, because the connecting passage 60 is provided on the plate 32, (i) the above-described distance is suppressed from being long and (ii) the pressure loss is therefore suppressed.

In the embodiments above, the refrigerant passage 30m of the plate stacked body 30 is formed of the through holes formed on the plates 31 to 35. However, the disclosure is not limited to this. For example, a part of or all of the refrigerant passage 30m may be formed of bottomed grooves which are half-etched, etc. and formed on the plates 31 to 35. Similarly, the "first cutout", the "second cutout", the "third cutout", and the "fourth cutout" of the present disclosure are not limited to the through holes. These cutouts of the present disclosure may be bottomed grooves which are half-etched, etc. and formed on the plates 31 to 35.
In the embodiments above, the U-bend pipes 22 (refrigerant pipes) are provided at positions corresponding to the recess 30y formed on the outer periphery of the plate stacked body 30. However, the disclosure is not limited to this. For example, the refrigerant pipes may be provided at positions corresponding to through holes or a recess which are/is formed on the center of the plate stacked body.
In the embodiments above, the thickness of the plate 33 is larger than that of each of the plates 32 and 34. However, in a third aspect of the present disclosure, the thickness of the plate 33 may be differently arranged as long as it is larger than that of at least one of the plates 32 and 34.
In the embodiments above, the heat conductivity of the plate 33 is lower than that of each of the plates 32 and 34. However, in a fourth aspect of the present disclosure, the heat conductivity of the plate 33 may be differently arranged as long as it is lower than that of at least one of the plates 32 and 34.
In the embodiments above, an example of a void provided between the vaporization passage and the overheated passage is the void 50 (see FIG. 9) positioned between the first refrigerant passage 30m1 and the second refrigerant passage 30m2 in the left-right direction (stacked direction). However, the disclosure is not limited to this. For example, a void may be provided between the vaporization passage and the overheated passage in a surface direction of the plates 31 to 35.
In the embodiments above, the number of second refrigerant passages 30m2 is smaller than that of first refrigerant passages 30m1. However, the number of the second refrigerant passages 30m2 may be the same as that of the first refrigerant passages 30m1 as long as it is equal to or smaller than that of the first refrigerant passages 30m1.
In the embodiments above, the length of the second refrigerant passage 30m2 is longer than that of each of the four first refrigerant passages 30m1. However, the length of the second refrigerant passage 30m2 may be the same as that of any of the four first refrigerant passages 30m1 as long as it is equal to or longer than that of each of the four first refrigerant passages 30m1.
In the embodiments above, examples of the first heat exchanging portion and the second heat exchanging portion are the rear heat exchanging portion 10u1 and the front heat exchanging portion 10u2 between which a bent part of the bent-type indoor heat exchanger 10 is provided. However, the disclosure is not limited to this. For example, the first heat exchanging portion and the second heat exchanging portion may be two heat exchanging portions which are aligned to be linear and between which the bent part of the indoor heat exchanger is not provided.
Although Embodiments have been described above, it will be understood that various changes in form and details are possible as long as the changes do not depart from the spirit and scope of the claims.

[Reference Signs List]

1 air conditioner
10 indoor heat exchanger
10u heat exchanging portion
10u1 rear heat exchanging portion (first heat exchanging portion)
10u2 front heat exchanging portion (second heat exchanging portion)
11 fin
12 heat transfer pipe
30 plate stacked body
30m refrigerant passage
30m1 first refrigerant passage
30m2 second refrigerant passage
32 plate (first plate)
321y,322y,323y,324a slot (first cutout)
323x round hole (third cutout)
324x round hole (fourth cutout)
33 plate (third plate)
34 plate (second plate)
342x slot (second cutout)
50 void
60 connecting passage

Claims

An indoor heat exchanger comprising: a heat exchanging portion including a fin and heat transfer pipes penetrating the fin; and
a plate stacked body in which refrigerant passages connected to the heat transfer pipes are formed,

the refrigerant passages including a first refrigerant passage and a second refrigerant passage,

the plate stacked body including a first plate and a second plate stacked at a position which is far from the heat transfer pipes in a stacked direction as compared to the first plate,

the first plate being provided with a first cutout, a third cutout, and a fourth cutout,

the second plate being provided with a second cutout connected to the third cutout and the fourth cutout,

the first cutout forming the first refrigerant passage,

the second cutout, the third cutout, and the fourth cutout forming the second refrigerant passage, and

the first refrigerant passage intersecting with the second refrigerant passage viewed in the stacked direction.
The indoor heat exchanger according to claim 1, wherein, the heat transfer pipes include a first heat transfer pipe which functions as a vaporization area and a second heat transfer pipe which functions as an overheated area,
the refrigerant passages include a vaporization passage connected to the first heat transfer pipe and an overheated passage connected to the second heat transfer pipe, and

the vaporization passage does not intersect with the overheated passage viewed in the stacked direction.
The indoor heat exchanger according to claim 1 or 2, wherein, the heat transfer pipes include the first heat transfer pipe which functions as the vaporization area and the second heat transfer pipe which functions as the overheated area,
the refrigerant passages include (i) the vaporization passage which is connected to the first heat transfer pipe and which forms one of the first refrigerant passage and the second refrigerant passage and (ii) the overheated passage which is connected to the second heat transfer pipe and which forms the other of the first refrigerant passage and the second refrigerant passage, and

the plate stacked body is provided between the first plate and the second plate in the stacked direction and further includes a third plate which is thicker than at least one of the first plate and the second plate.
The indoor heat exchanger according to any one of claims 1 to 3, wherein, the heat transfer pipes include the first heat transfer pipe which functions as the vaporization area and the second heat transfer pipe which functions as the overheated area,
the refrigerant passages include (i) the vaporization passage which is connected to the first heat transfer pipe and which forms the one of the first refrigerant passage and the second refrigerant passage and (ii) the overheated passage which is connected to the second heat transfer pipe and which forms the other of the first refrigerant passage and the second refrigerant passage, and

the plate stacked body is provided between the first plate and the second plate in the stacked direction and further includes the third plate whose heat conductivity is lower than the heat conductivity of the at least one of the first plate and the second plate.
The indoor heat exchanger according to any one of claims 2 to 4, wherein, the plate stacked body includes a void where a refrigerant does not flow, and the void is provided between the vaporization passage and the overheated passage.
The indoor heat exchanger according to any one of claims 1 to 5, wherein, the number of second refrigerant passages is equal to or smaller than the number of first refrigerant passages.
The indoor heat exchanger according to any one of claims 1 to 6, wherein, the length of each of the second refrigerant passages is equal to or longer than the length of each of the first refrigerant passages.
The indoor heat exchanger according to any one of claims 1 to 7, wherein, the heat exchanging portion includes a first heat exchanging portion and a second heat exchanging portion, the heat transfer pipes include the first heat transfer pipe included in the first heat exchanging portion and the second heat transfer pipe included in the second heat exchanging portion, and
the first plate is provided with a connecting passage connecting the first heat transfer pipe to the second heat transfer pipe.
An air conditioner comprising the indoor heat exchanger according to any one of claims 1 to 8.