JP7426456B1 - Indoor heat exchanger and air conditioner - Google Patents

Abstract

An object of the present invention is to suppress the increase in size of a plate stack in the planar direction. A refrigerant flow path 30m of a plate laminate 30 includes a first refrigerant flow path 30m1 each formed of elongated holes 321y, 322y, 323y, and 324a formed in a plate 32, and a circle formed in the plate 32. The second refrigerant flow path 30m2 includes holes 323x, 324x, circular holes formed in the plates 31, 33, and an elongated hole 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 and right direction (stacking direction). [Selection diagram] Figure 5

Description

The present disclosure relates to an indoor heat exchanger and an air conditioner equipped with the same.

Patent Document 1 discloses that in an air conditioning indoor unit used in an air conditioner, space is saved by connecting a plate-shaped distribution member made of a plurality of stacked plates to the heat exchanger tube of the heat exchanger main body. It is disclosed that this can be achieved.

Japanese Patent Application Publication No. 2006-125652

In Patent Document 1, a refrigerant flow path is formed in the center plate of three plates forming a plate-shaped distribution member, and an under plate and an overplate define the refrigerant flow path. In this case, depending on the configuration of the refrigerant flow path, it may be necessary to provide a detour within the plane of the center plate. ) becomes large.

An object of the present disclosure is to provide an indoor heat exchanger that can suppress the increase in size of a plate stack in the planar direction, and an air conditioner equipped with the same.

An indoor heat exchanger according to a first aspect of the present disclosure includes a heat exchange section including fins and a plurality of heat transfer tubes passing through the fins, and a plurality of refrigerant flow paths connected to the plurality of heat transfer tubes. a plate laminate, the plurality of refrigerant channels include a first refrigerant channel and a second refrigerant channel, and the plate laminate has a structure in which the first plate and the first plate are stacked in a stacking direction. a second plate laminated at a position farther from the plurality of heat exchanger tubes than the first plate, the first plate having a first notch, a third notch, and a fourth notch formed therein; A second notch connected to the third notch and the fourth notch is formed in the second plate, the first notch forms a first refrigerant flow path, and the second notch, the third notch, and the fourth notch are connected to each other. The fourth notch forms a second refrigerant flow path, and the first refrigerant flow path and the second refrigerant flow path intersect when viewed from the stacking direction.

According to the first aspect of the present disclosure, the first refrigerant flow path and the second refrigerant flow path intersect with each other instead of providing a detour within the plane of the plate, thereby increasing the size of the plate stack in the planar direction. It can be suppressed.

In the indoor heat exchanger according to a second aspect of the present disclosure, in the first aspect, the plurality of heat exchanger tubes include a first heat exchanger tube serving as an evaporation area and a second heat exchanger tube serving as a superheating area, 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 the evaporation flow path and the superheat flow path are , do not need to intersect when viewed from the stacking direction. When channels with a large temperature difference (evaporation channel and superheating channel) intersect with each other, thermal efficiency may deteriorate due to heat conduction between the channels at the intersection. In this regard, in the present configuration, the problem can be suppressed because the channels having a large temperature difference (the evaporation channel and the superheating channel) do not intersect with each other.

In the indoor heat exchanger according to a third aspect of the present disclosure, in the first or second aspect, the plurality of heat exchanger tubes include a first heat exchanger tube serving as an evaporation area, a second heat exchanger tube serving as a superheating area, , the plurality of refrigerant flow paths are connected to the first heat exchanger tube and are connected to an evaporation flow path that constitutes one of the first refrigerant flow path and the second refrigerant flow path, and the second heat exchanger tube. and a superheated flow path constituting the other of the first refrigerant flow path and the second refrigerant flow path, and the plate stack includes a superheated flow path between the first plate and the second plate in the stacking direction. The device may further include a third plate that is arranged and has a thickness greater than at least one of the first plate and the second plate. In this case, heat conduction between the evaporation channel and the superheating channel is suppressed by the third plate having a large thickness, and deterioration of thermal efficiency can be effectively suppressed.

In the indoor heat exchanger according to a fourth aspect of the present disclosure, in any of the first to third aspects, 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 superheating region. a heat tube, the plurality of refrigerant flow paths are connected to the first heat transfer tube and constitute one of the first refrigerant flow path and the second refrigerant flow path; and the second refrigerant flow path. a superheating channel that is connected to a heat tube and constitutes the other of the first refrigerant channel and the second refrigerant channel, and the plate stack includes the first plate and the second plate in the stacking direction. It may further include a third plate disposed between the two plates and having a lower thermal conductivity than at least one of the first plate and the second plate. In this case, heat conduction between the evaporation channel and the superheating channel is suppressed by the third plate having low thermal conductivity, and deterioration of thermal efficiency can be effectively suppressed.

In the indoor heat exchanger according to a fifth aspect of the present disclosure, in any one of the first to fourth aspects, the plate stack has a structure in which a refrigerant does not flow between the evaporation channel and the superheating channel. It may have voids. In this case, the voids suppress heat conduction between the evaporation channel and the superheating channel, and deterioration of thermal efficiency can be effectively suppressed.

In the indoor heat exchanger according to a sixth aspect of the present disclosure, in any of the first to fifth aspects, the number of the second refrigerant channels may be equal to or less than the number of the first refrigerant channels. When a plate is provided between the first plate and the second plate, if the number of second refrigerant channels is large, the number of through holes formed in the plate between the first plate and the second plate will be large. , the process of forming the through holes becomes complicated. In this regard, in this configuration, since the number of second refrigerant channels is small, the above problem can be suppressed.

In the indoor heat exchanger according to a seventh aspect of the present disclosure, in any of the first to sixth aspects, the length of the second refrigerant flow path is equal to or longer than the length of the first refrigerant flow path. good. When 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, which causes problems such as a decrease in strength and deterioration of workability. In this regard, in this configuration, since the length of the second refrigerant flow path is long, the above-mentioned problem can be suppressed.

In the indoor heat exchanger according to an eighth aspect of the present disclosure, in any one of the first to seventh aspects, the heat exchange section includes a first heat exchange section and a second heat exchange section, and the plurality of heat exchange sections The heat tube includes a first heat exchanger tube that the first heat exchanger has and a second heat exchanger tube that the second heat exchanger has, and the first heat exchanger tube and the second heat exchanger tube are attached to the first plate. A connection channel may be provided to connect the two. The second plate is stacked at a position farther from the plurality of heat exchanger tubes than the first plate. When the connecting channel is provided in the second plate, the distance in the stacking direction from the end surface of the heat exchanger tube to the connecting channel formed in the second plate becomes long, which may increase pressure loss. In this regard, in this configuration, by providing the connection flow path in the first plate, it is possible to suppress the distance from becoming longer and, by extension, from increasing the pressure loss.

An air conditioner according to a ninth aspect of the present disclosure includes the indoor heat exchanger according to the first aspect.

FIG. 1 is a front view of the air conditioner according to the first embodiment of the present disclosure with an exterior panel removed. FIG. 2 is a right side view of an indoor heat exchanger included in the air conditioner shown in FIG. 1. FIG. FIG. 2 is a perspective view of the plate stack shown in FIG. 1. FIG. 4 is a plan view of the leftmost plate among the five plates forming the plate stack shown in FIG. 3. FIG. 4 is a plan view of the second plate from the left among the five plates that constitute the plate stack shown in FIG. 3. FIG. FIG. 4 is a plan view of the third plate from the left among the five plates constituting the plate stack shown in FIG. 3. FIG. FIG. 4 is a plan view of the fourth plate from the left among the five plates constituting the plate stack shown in FIG. 3. FIG. 4 is a plan view of the rightmost plate among the five plates forming the plate stack shown in FIG. 3. FIG. 6 is a cross-sectional view of the plate stack taken along line IX-IX shown in FIG. 5. FIG. FIG. 6 is a diagram corresponding to FIG. 5 of an indoor heat exchanger according to a second embodiment of the present disclosure. 11 is a cross-sectional view of the plate stack and the heat exchange section taken along the line XI-XI shown in FIG. 10. FIG.

<First embodiment>
First, with reference to FIG. 1, the overall configuration of an air conditioner 1 according to a first embodiment of the present disclosure will be described. In the following description, the directions "top", "bottom", "right", "left", "front", and "rear" refer to the directions when the air conditioner 1 is installed in the state shown in FIG.

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).

The frame 1f constitutes the bottom and rear part of the air conditioner 1. The frame 1f is long in one direction, and is attached to the wall surface of the room via a mounting plate (not shown) so that the one direction is along the left-right direction in FIG. The fan, exterior panel, and 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 in FIG. 1) similarly to the frame 1f.

Next, the configuration of the indoor heat exchanger 10 will be described in detail with reference to FIGS. 1 to 9.

As shown in FIG. 1, the indoor heat exchanger 10 includes a heat exchange section 10u, a plate stack 30, a plurality of U-bend pipes 22, and a plurality of communication pipes 23. In FIG. 1, a portion of one of the plurality of U-bend pipes 22 that overlaps the plate stack 30 in a side view is drawn with a broken line.

The heat exchange section 10u includes a plurality of fins 11, a plurality of heat exchanger tubes 12, and a tube plate 14.

The plurality of fins 11 each have a thin plate shape, and are arranged so that the plate surfaces extend in the up-down direction and the front-back direction. The plurality of fins 11 are arranged at equal intervals in the left-right direction.

The plurality of heat exchanger tubes 12 each extend in the left-right direction and pass through the plurality of fins 11.

In addition, in FIG. 1, for simplification, only some of the plurality of heat exchanger tubes 12 are depicted, and only some of the plurality of fins 11 are partially depicted.

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

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

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

As shown in FIG. 1, a flow divider 18, an expansion valve 19, etc. are arranged near the U-bend pipe 22, the connecting pipe 23, and the plate stack 30.

The tube plate 14 is arranged so that its plate surface extends in 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 exchanger tubes 12 penetrate through the tube sheet 14 . There is almost no gap between the tube sheet 14 and each heat exchanger tube 12, and the tube sheet 14 supports the fins 11 and the plurality of heat exchanger tubes 12. A U-bend pipe 22, a connecting pipe 23, and a plate stack 30 are arranged on the right side of the tube sheet 14, that is, on the opposite side of the tube sheet 14 from the plurality of fins 11.

Although not shown, a tube plate is also arranged on the left side of the plurality of fins 11.

The plurality of heat exchanger tubes 12 slightly protrude to the right from the right side surface of the tube sheet 14. That is, the end surfaces 12x of the plurality of heat exchanger tubes 12 are located slightly to the right of the right side surface of the tube plate 14.

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, as shown in FIG. The indoor heat exchanger 10 is of a bent type in which first to fourth tube sheets 141 to 144 are arranged at angles with adjacent tube sheets 141 to 144, respectively. A plurality of heat exchanger tubes 12 penetrate each of the first to fourth tube sheets 141 to 144. A pair of heat exchanger tubes 12 in each U-shaped tube (a U-shaped tube formed by a pair of heat exchanger tubes 12 and a bent portion 21 by bending one tube) are connected to the first to fourth tube plates 141 to 144. It does not penetrate two different tube sheets.

The heat exchange section 10u includes a post heat exchange section 10u1 including a first tube sheet 141, and a pre heat exchange section 10u2 including second to fourth tube sheets 142 to 144.

Among the plurality of heat transfer tubes 12 included in the post-heat exchange section 10u1, two adjacent heat transfer tubes 121a and 122a are connected to each other via the refrigerant flow path 22m of the U-bend tube 22. The two heat exchanger tubes 121a and 122a constitute separate U-shaped tubes (U-shaped tubes formed by a pair of heat exchanger tubes 12 and bent portion 21 by bending one tube). .

One of the plurality of heat transfer tubes 12 (heat transfer tube 121b) included in the post-heat exchange section 10u1 and one of the plurality of heat transfer tubes 12 (heat transfer tube 122b) included in the pre-heat exchange section 10u2 are in communication. It is connected via a refrigerant flow path 23m of the piping 23. One of the plurality of heat transfer tubes 12 (heat transfer tube 121c) included in the post-heat exchange section 10u1 and one of the plurality of heat transfer tubes 12 (heat transfer tube 122c) included in the pre-heat exchange section 10u2 are in communication. It is connected via a refrigerant flow path 23m of the piping 23. One of the plurality of heat transfer tubes 12 (heat transfer tube 121d) that the post-heat exchange section 10u1 has and one of the plurality of heat transfer tubes 12 (heat transfer tube 122d) that the pre-heat exchange section 10u2 has are connected. It is connected via a refrigerant flow path 23m of the piping 23. One of the plurality of heat transfer tubes 12 (heat transfer tube 121e) included in the post-heat exchange section 10u1 and one of the plurality of heat transfer tubes 12 (heat transfer tube 122e) included in the pre-heat exchange section 10u2 are in communication. It is connected via a refrigerant flow path 23m of the piping 23.

The heat transfer tube 121c is further connected to the expansion valve 19. The expansion valve 19 is attached to a connecting pipe 23 that connects the heat exchanger tube 121c and the heat exchanger tube 122c.

On the right side with respect to the plurality of fins 11, six heat transfer tubes 121a, 122a, 121b, 121c, 121d, which are connected to the U-bend pipe 22 or the communication pipe 23, among the plurality of heat transfer tubes 12 included in the post-heat exchange section 10u1. The heat exchanger tubes 12 except for 121e are connected to the plate stack 30.

Note that the plate stack 30 shown in FIG. 3 is attached to the post-heat exchange section 10u1. The plate stack attached to the preheat exchange section 10u2 has the same configuration as the plate stack 30, and illustration and description thereof will be omitted.

The plate laminate 30 is attached to the heat transfer tube 12 that is not connected to the U-bend pipe 22 or the communication pipe 23 among the plurality of heat transfer tubes 12 included in the post-heat exchange section 10u1 via the plurality of connection parts 40. . Each of the plurality of connection parts 40 has a cylindrical shape and has a refrigerant flow path therein. Each connecting portion 40 extends in the left-right direction and connects the heat exchanger tube 12 and the plate laminate 30 in the left-right direction. Each connecting portion 40 has a left end connected to the end surface 12x of the heat exchanger tube 12, and a right end connected to the left side surface of the plate 31 in the plate stack 30.

The plate stack 30 is provided with recesses 30x and 30y in a part (rear part) of the outer periphery. The recesses 30x, 30y penetrate the plate stack 30 in the left-right direction. The recesses 30x and 30y are voids formed in the shape of plates 31 to 35 cut out. The U-bend pipe 22 is arranged at a position corresponding to the recess 30y (see FIGS. 4 to 8).

The length of the connecting portion 40 in the left-right direction is shorter than the length of the U-bend pipe 22 in the left-right direction. The first distance D1 in the left-right direction (stacking direction) from the end surface 12x of the heat exchanger tube 12 to the surface of the plate laminate 30 closest to the end surface 12x of the heat exchanger tube 12 (the left side surface of the plate 31) is It is shorter than the second distance D2 in the left-right direction (stacking direction) from the end surface 12x to the surface of the U-bend tube 22 farthest from the end surface 12x of the heat exchanger tube 12 (the top of the U-shape) (see FIG. 1). Therefore, as shown in FIG. 1, the U-bend pipe 22 overlaps the plate stack 30 when viewed from the front and rear directions.

Next, with reference to FIGS. 4 to 9, the coolant flow path 30m formed in the plate stack 30 will be described in detail.

The coolant flow path 30m is constituted by through holes formed in each of the plates 31 to 35 constituting the plate stack 30.

As shown in FIG. 4, the plate 31 has a plurality of circular holes (including circular holes 313a and 314a described later) formed therein. The right end of the connecting portion 40 (see FIG. 3) is inserted into each of the circular holes.

As shown in FIG. 5, the plate 32 has a plurality of circular holes (including circular holes 323x, 324x, and 323a described later) and a plurality of elongated holes (including elongated holes 321y, 322y, 323y, and 324a described later). .) is formed. These circular holes and elongated holes communicate with one or two of the plurality of circular holes formed in the plate 31.

As shown in FIG. 6, the plate 33 has a plurality of circular holes (including a circular hole 334a described later) formed therein. The circular holes each communicate with one of the circular holes or slotted holes formed in the plate 32.

As shown in FIG. 7, the plate 34 has a plurality of elongated holes (including elongated holes 342x and 343a, which will be described later). Each of the elongated holes communicates with two of the plurality of circular holes formed in the plate 33.

As shown in FIG. 8, one 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.

The through holes (circular holes or elongated holes) formed in each of the plates 31 to 35 communicate with each other to form a coolant flow path 30m.

The two heat exchanger tubes 123a and 124a (two of the plurality of heat exchanger tubes 12 included in the post-heat exchange section 10u1) shown in FIG. are connected to each other via a refrigerant flow path 30m composed of circular holes 323a and elongated holes 324a, circular holes 333a and 334a formed in the plate 33, and elongated holes 343a formed in the plate 34. There is. The two heat exchanger tubes 123a and 124a constitute separate U-shaped tubes (U-shaped tubes formed by a pair of heat exchanger tubes 12 and bent portion 21 by bending one tube). .

As shown in FIG. 9, the elongated hole 342x (see FIG. 7) formed in the plate 34 straddles four elongated holes 321y, 322y, 323y, and 324a (see FIG. 5) formed in the plate 32. . The elongated holes 321y, 322y, 323y, and 324a each constitute the first refrigerant flow path 30m1 of the refrigerant flow path 30m, and correspond to the "first notch" 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 a second refrigerant flow path 30m2 of the refrigerant flow path 30m. do. The circular hole 323x corresponds to the "third notch" of the present disclosure, the circular hole 324x corresponds to the "fourth notch" of the present disclosure, and the elongated hole 342x corresponds to the "second notch" 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. The first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 intersect when viewed from the left and right direction (the stacking direction) (see FIG. 5).

Plate 32 corresponds to the "first plate" of the present disclosure. The plate 34 is stacked at a position farther from the heat exchanger tube 12 than the plate 32 in the left-right direction (stacking direction), and corresponds to the "second plate" of the present disclosure.

The number of second refrigerant flow paths 30m2 (one) is smaller than the number of first refrigerant flow paths 30m1 (four). Also, when viewed from the left and right, the length of the second refrigerant flow path 30m2 (the length of the elongated hole 342x shown in FIG. 7) is the length of the four first refrigerant flow paths 30m1 (the length of the elongated hole 342x shown in FIG. 321y, 322y, 323y, 324a).

The plurality of heat exchanger tubes 12 connected to the refrigerant flow path 30m include a first heat exchanger tube serving as an evaporation area and a second heat exchanger tube serving as a superheating area. The evaporation region and the superheating region are switched according to the control of the indoor heat exchanger 10, and one heat transfer tube may be in the evaporation region or in the superheating region depending on the control of the indoor heat exchanger 10. There is.

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

When the heat exchanger tubes 125a to 125d (first heat exchanger tubes) are in the evaporation region, the heat exchanger tubes 126a and 126b (second heat exchanger tubes) may be in the overheating 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 exchanger tubes 125a to 125d (second heat exchanger tubes) are in the overheating region, the heat exchanger tubes 126a and 126b (first heat exchanger tubes) are in the evaporation region. In this case, the first refrigerant flow path 30m1 corresponds to the "superheating flow path" of the present disclosure, and the second refrigerant flow path 30m2 corresponds to the "evaporation flow path" of the present disclosure.

In other words, when one of the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 that intersect when viewed from the left-right direction (the stacking direction) becomes an evaporation flow path, the other may become a superheat flow path. In such a case, the plate 33 interposed between the first refrigerant flow path 30m1 and the elongated hole 342x forming the second refrigerant flow path 30m2 is thicker than either of the plates 32 and 34 (see FIG. 9). ), the thermal conductivity is lower than either of the plates 32 and 34.

Plate 33 is a plate disposed between plate 32 and plate 34, and corresponds to the "third plate" of the present disclosure.

A gap 50 through which the refrigerant does not flow is formed in the plate 33 (see FIG. 9). The void 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, a recessed portion may be formed in each of the two plate members by half etching, etc., and the void 50 may be formed by combining the recessed portions.

The elongated hole 342x (see FIG. 7) formed in the plate 34 does not span the elongated hole 329 formed in the plate 32. The elongated hole 342x and the elongated hole 329 do not intersect when viewed from the left and right direction (the stacking direction).

The elongated hole 329 is connected to the heat exchanger tube 125e (see FIG. 4). When heat exchanger tube 125e (first heat exchanger tube) becomes an evaporation region, heat exchanger tubes 126a and 126b (second heat exchanger tube) may become an overheating region. In this case, the elongated hole 329 corresponds to the "evaporation channel" of the present disclosure, and the second refrigerant channel 30m2 corresponds to the "superheating channel" of the present disclosure. When the heat exchanger tube 125e (second heat exchanger tube) becomes an overheating region, the heat exchanger tubes 126a, 126b (first heat exchanger tube) become an evaporation region. In this case, the elongated hole 329 corresponds to the "superheating channel" of the present disclosure, and the second refrigerant channel 30m2 corresponds to the "evaporation channel" of the present disclosure.

As described above, according to the present embodiment, the refrigerant flow path 30m of the plate laminate 30 is the first refrigerant flow path 30m1, which is configured of the elongated holes 321y, 322y, 323y, and 324a formed in the plate 32, respectively. (See FIG. 5), a second refrigerant flow path 30m2 ( (see FIGS. 5 to 7). The first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 intersect when viewed from the left and right direction (the stacking direction) (see FIG. 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 intersect with each other in the plane direction along the plane of the plates 31 to 35. It is possible to suppress the plate stack 30 from increasing in size.

The evaporation flow path (for example, the elongated hole 329 formed in the plate 32) and the superheating flow path (for example, the elongated hole 342x formed in the plate 34, which constitutes the second refrigerant flow path 30m2) are (see Figure 5). When channels with a large temperature difference (evaporation channel and superheating channel) intersect with each other, thermal efficiency may deteriorate due to heat conduction between the channels at the intersection. In this regard, in the present configuration, the problem can be suppressed because the channels having a large temperature difference (the evaporation channel and the superheating channel) do not intersect with each other.

When the first refrigerant flow path 30m1 is an evaporation flow path and the second refrigerant flow path 30m2 is a superheating flow path, an elongated hole 342x forming the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 is interposed. The plate 33 is thicker than both the plates 32 and 34 (see FIG. 9). In this case, the thick plate 33 suppresses heat conduction between the evaporation channel and the superheating channel, effectively suppressing deterioration of thermal efficiency.

When the first refrigerant flow path 30m1 is an evaporation flow path and the second refrigerant flow path 30m2 is a superheating flow path, an elongated hole 342x forming the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 is interposed. Plate 33 has a lower thermal conductivity than both plates 32 and 34. In this case, heat conduction between the evaporation channel and the superheating channel is suppressed by the plate 33 having low thermal conductivity, and deterioration of thermal efficiency can be effectively suppressed.

The plate stack 30 has a gap 50 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) through which the refrigerant does not flow ( (See Figure 9). In this case, the voids 50 suppress heat conduction between the evaporation channel and the superheating channel, and deterioration of thermal efficiency can be effectively suppressed.

The number of second refrigerant flow paths 30m2 (one) is smaller than the number of first refrigerant flow paths 30m1 (four). When the number of second refrigerant channels 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 configuration, since the number of second refrigerant channels 30m2 is small, the above problem can be suppressed.

The length of the second refrigerant flow path 30m2 (the length of the elongated hole 342x shown in FIG. 7) is the length of the four first refrigerant flow paths 30m1 (the length of the elongated hole 321y, 322y, 323y, 324a shown in FIG. 5). length). 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 will become smaller, resulting in problems such as a decrease in strength and deterioration of workability. Become. In this regard, in this configuration, since the length of the second refrigerant flow path 30m2 is long, the above-mentioned problem can be suppressed.

<Second embodiment>
Next, an indoor heat exchanger according to a second embodiment of the present disclosure will be described with reference to FIGS. 10 and 11.

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 and one of the plurality of heat transfer tubes 12 (heat transfer tube 121f) included in the pre-heat exchange section 10u2 are used. 122f) are connected to each other via a connecting channel 60 formed in the plate 32 of the plate stack 30.

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 exchanger tube 121f corresponds to the "first heat exchanger tube" of the present disclosure, and the heat exchanger tube 122f corresponds to the "second heat exchanger tube" of the present disclosure.

In this embodiment, the plate stack 30 is disposed across the post-heat exchange section 10u1 and the pre-heat exchange section 10u2. The connection channel 60 is formed in the plate 32 and the plate 31, and is not formed in the other plates (plates 33 to 35).

The plate 34 is stacked at a position farther from the plurality of heat exchanger tubes 12 than the plate 32 is. When the connection channel 60 is provided in the plate 34, the distance in the left-right direction from the end surface 12x of the heat exchanger tube 12 to the connection channel 60 formed in the plate 34 becomes long, which may increase pressure loss. In this regard, in this configuration, by providing the connection flow path 60 in the plate 32, it is possible to suppress the distance from becoming longer and, by extension, from increasing the pressure loss.

<Modified example>
In the embodiment described above, the coolant flow path 30m of the plate stack 30 is formed by the through holes formed in each of the plates 31 to 35, but the present invention is not limited thereto. For example, part or all of the coolant flow path 30m may be formed by a bottomed groove formed in each of the plates 31 to 35 by half etching or the like. Similarly, the "first notch", "second notch", "third notch", and "fourth notch" of the present disclosure are not limited to through holes, but are bottomed holes formed in each of the plates 31 to 35 by half etching or the like. It may be a groove.

In the embodiment described above, the U-bend pipe 22 (refrigerant pipe) is arranged at a position corresponding to the recess 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 center of the plate stack, and a refrigerant pipe may be arranged at a position corresponding to the through hole or recessed portion.

In the embodiment described above, the plate 33 is thicker than both the plates 32 and 34, but in the third aspect of the present disclosure, the plate 33 only needs to be thicker than at least one of the plates 32 and 34.

In the embodiment described above, the plate 33 has a lower thermal conductivity than both the plates 32 and 34, but in the fourth aspect of the present disclosure, it is sufficient that the plate 33 has a lower thermal conductivity than at least one of the plates 32 and 34.

In the above embodiment, the gap 50 located between the first refrigerant flow path 30m1 and the second refrigerant flow path 30m2 in the left-right direction (stacking direction) is the gap provided between the evaporation flow path and the superheat flow path. (See FIG. 9) is shown as an example, but the present invention is not limited thereto. For example, a gap may be provided between the evaporation channel and the superheating channel in the plane direction of the plates 31 to 35.

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 is sufficient that the number of the second refrigerant flow paths 30m1 is equal to or less than the number of the first refrigerant flow paths 30m1. It may be the same as the number.

In the above-described embodiment, the length of the second refrigerant flow path 30m2 is longer than any of the four first refrigerant flow paths 30m1, but it may be longer than the length of the first refrigerant flow path 30m1. , may be the same as any of the lengths of the four first refrigerant flow paths 30m1.

In the above-described embodiment, as the first heat exchange part and the second heat exchange part, the post heat exchange part 10u1 and the pre heat exchange part 10u2, which have a bending part in the foldable indoor heat exchanger 10 interposed therebetween, are exemplified. , but not limited to. For example, two heat exchange parts that are arranged in a straight line and have no intervening bending parts may be used as the first heat exchange part and the second heat exchange part.

Although the embodiments have been described above, it will be understood that various changes in form and details can be made without departing from the spirit and scope of the claims.

1 Air conditioner 10 Indoor heat exchanger 10u Heat exchange section 10u1 After heat exchange section (first heat exchange section)
10u2 Preheat exchange section (second heat exchange section)
11 Fin 12 Heat transfer tube 30 Plate laminate 30m Refrigerant flow path 30m1 First refrigerant flow path 30m2 Second refrigerant flow path 32 Plate (first plate)
321y, 322y, 323y, 324a Elongated hole (first notch)
323x circular hole (third notch)
324x circular hole (4th notch)
33 Plate (3rd plate)
34 Plate (second plate)
342x slotted hole (second notch)
50 void 60 connection channel

Claims (9)

a heat exchange section including a fin and a plurality of heat exchanger tubes passing through the fin;
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 stack includes a first plate and a second plate stacked at a position farther from the plurality of heat exchanger tubes than the first plate in the stacking direction,
A first notch, a third notch, and a fourth notch are formed in the first plate,
A second notch connected to the third notch and the fourth notch is formed in the second plate,
the first notch forms the first refrigerant flow path;
The second notch, the third notch, and the fourth notch form the second refrigerant flow path,
The indoor heat exchanger wherein the first refrigerant flow path and the second refrigerant flow path intersect when viewed from the stacking direction. The plurality of heat exchanger tubes include a first heat exchanger tube serving as an evaporation area and a second heat exchanger tube serving as a superheating area,
The plurality of refrigerant flow paths include an evaporation flow path connected to the first heat exchanger tube and a superheat flow path connected to the second heat exchanger tube,
The indoor heat exchanger according to claim 1, wherein the evaporation channel and the superheating channel do not intersect when viewed from the stacking direction. The plurality of heat exchanger tubes include a first heat exchanger tube serving as an evaporation area and a second heat exchanger tube serving as a superheating area,
The plurality of refrigerant flow paths are connected to the first heat exchanger tube, and are connected to an evaporation flow path that constitutes one of the first refrigerant flow path and the second refrigerant flow path, and the second heat exchanger tube, and the a superheated flow path 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 and having a thickness greater than at least one of the first plate and the second plate. The indoor heat exchanger according to item 1. The plurality of heat exchanger tubes include a first heat exchanger tube serving as an evaporation area and a second heat exchanger tube serving as a superheating area,
The plurality of refrigerant flow paths are connected to the first heat exchanger tube, and are connected to an evaporation flow path that constitutes one of the first refrigerant flow path and the second refrigerant flow path, and the second heat exchanger tube, and the a superheated flow path constituting the other of the first refrigerant flow path and the second refrigerant flow path,
The plate stack further includes a third plate that is disposed between the first plate and the second plate in the stacking direction and has a lower thermal conductivity than at least one of the first plate and the second plate. , The indoor heat exchanger according to claim 1. The indoor heat exchanger according to any one of claims 2 to 4, wherein the plate stack has a gap between the evaporation channel and the superheating channel through which a refrigerant does not flow. The indoor heat exchanger according to claim 1, wherein the number of the second refrigerant channels is less than or equal to the number of the first refrigerant channels. The indoor heat exchanger according to claim 1, wherein the length of the second refrigerant flow path is greater than or equal to the length of the first refrigerant flow path. The heat exchange section includes a first heat exchange section and a second heat exchange section,
The plurality of heat exchanger tubes include a first heat exchanger tube included in the first heat exchanger and a second heat exchanger tube included in the second heat exchanger,
The indoor heat exchanger according to claim 1, wherein the first plate is provided with a connection flow path that connects the first heat exchanger tube and the second heat exchanger tube. An air conditioner comprising the indoor heat exchanger according to claim 1.

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