Indoor unit and air conditioner

Abstract

The present invention provides an indoor unit that enhances the heat exchange efficiency between the heat exchanger and the airflow. [Solution] One embodiment of the indoor unit according to the present disclosure comprises a heat exchanger, a blower, a drain pan, an air passage, and a housing, wherein the housing has a front wall portion, a rear wall portion, and an intake port provided in the lower part of the front wall portion, the heat exchanger has a front heat exchanger and a rear heat exchanger, the air passage includes a front air passage through which air flows toward the front heat exchanger and a rear air passage through which air flows toward the rear heat exchanger, the rear wall portion has a first rear wall portion facing the drain pan in the front-rear direction and a second rear wall portion located toward the front as it moves toward the bottom, the drain pan has a bottom portion, a front wall portion projecting upward from the front end of the bottom portion, and a rear wall portion projecting upward from the rear end of the bottom portion, and if the distance between the upper end of the front wall portion and the front wall portion is G1 and the distance between the drain pan and the second rear wall portion is G2, then the relationship 0.50 ≤ G2 / (G1 + G2) ≤ 0.60 is satisfied.

Description

Technical Field

[0001] The present invention relates to an indoor unit and an air conditioner. Background Art

[0002] Among indoor units for air conditioners, floor-standing indoor units that are placed on an indoor floor are known. A floor-standing indoor unit is disclosed, which comprises: a suction port provided at a lower portion of a front surface of a main body; an air outlet provided at an upper portion of the main body; a front-side heat exchanger disposed on a front side of the main body and allowing an airflow flowing through an air duct on the front side to pass therethrough; a rear-side heat exchanger disposed on a rear side relative to the front-side heat exchanger and allowing an airflow flowing through an air duct on the rear side to pass therethrough; and a drain pan disposed below the front-side heat exchanger and the rear-side heat exchanger (see, for example, Patent Document 1). Prior Art Literature Patent Literature

[0003] Patent Document 1 Japanese Patent No. 5805305 Summary of the Invention Problem to be Solved by the Invention

[0004] In the above-mentioned indoor unit, the gap between the drain pan and the wall surface of the rear-side air duct in the rear-side air duct is small, so there is a risk that the pressure loss of the airflow in the rear-side air duct may increase. As a result, in the above-mentioned indoor unit, it is difficult to increase the flow rate of the airflow flowing through the rear-side air duct, so the difference between the flow rate of the airflow passing through the front-side heat exchanger and the flow rate of the airflow passing through the rear-side heat exchanger becomes large. Therefore, it is difficult to equalize the flow rates of the airflows passing through the two heat exchangers, and thus it is difficult to improve the heat exchange efficiency between the heat exchangers and the airflows.

[0005] In view of the above circumstances, an object of the present disclosure is to provide an indoor unit and an air conditioner that can improve the heat exchange efficiency between heat exchangers and an airflow. Means for Solving the Problem

[0006] One embodiment of the indoor unit according to the present disclosure is an indoor unit for an air conditioner, and is a floor-standing indoor unit, comprising: a heat exchanger; a blower that generates an airflow passing through the heat exchanger; a drain pan positioned vertically below the heat exchanger; an air passage through which the airflow passes; and a housing that accommodates the heat exchanger, the blower, and the drain pan, respectively, wherein the housing has a front wall portion positioned in front of the heat exchanger and the drain pan, a rear wall portion positioned behind the heat exchanger and the drain pan, an intake port provided in the portion of the front wall portion vertically below the blower, and an outlet portion provided vertically above the blower, wherein the heat exchanger has a front heat exchanger and a rear heat exchanger positioned behind the front heat exchanger, and the air passage is partly connected to the drain pan and the front wall portion The rear wall portion includes a front air passage formed between the drain pan and the rear wall portion, through which the airflow from the intake port toward the front heat exchanger flows, and a rear air passage, partly formed between the drain pan and the rear wall portion, through which the airflow from the intake port toward the rear heat exchanger flows, wherein the rear wall portion includes a first rear wall portion extending vertically and facing the drain pan in the front-rear direction, and a second rear wall portion connected to the lower end of the first rear wall portion and located toward the front as it extends downward in the vertical direction The drain pan has a wall portion and a bottom portion that extends in a direction perpendicular to the vertical direction, a front wall portion that protrudes vertically upward from the front end of the bottom portion, and a rear wall portion that protrudes vertically upward from the rear end of the bottom portion. If the distance in the front-rear direction between the vertically upper end of the front wall portion and the front wall portion is G1, and the distance between the drain pan and the second rear wall portion is G2, then the relationship 0.50 ≤ G2 / (G1 + G2) ≤ 0.60 is satisfied.

[0007] One embodiment of the air conditioner according to this disclosure comprises the above-described indoor unit and an outdoor unit connected to the indoor unit by a circulation path through which a refrigerant circulates. [Effects of the Invention]

[0008] According to this disclosure, the heat exchange efficiency between the heat exchanger and the airflow in indoor units and air conditioners can be improved. [Brief explanation of the drawing]

[0009] [Figure 1] This is a schematic diagram showing the general configuration of an air conditioner in an embodiment. [Figure 2] This is a perspective view showing the indoor unit in the embodiment. [Figure 3] This is a longitudinal cross-sectional view showing the indoor unit in the embodiment. [Figure 4] This is a first perspective view showing a part of the indoor unit in the embodiment. [Figure 5] This is a second perspective view showing a part of the indoor unit in the embodiment. [Figure 6] This is a partially enlarged longitudinal cross-sectional view showing a part of the indoor unit in the embodiment. [Figure 7] This is the first figure showing the average energy efficiency ratio (Rcop) for heating and cooling of the air conditioner in the embodiment. [Figure 8] This is the second figure showing the average energy efficiency ratio (Rcop) for heating and cooling of the air conditioner in the embodiment. [Modes for carrying out the invention]

[0010] Embodiments of this disclosure will be described below with reference to the drawings. However, the scope of this disclosure is not limited to the embodiments described below, and can be modified at will within the scope of the technical concept of this disclosure. Furthermore, in the following drawings, the scale and number of components in each structure may differ from those in the actual structure in order to make each component easier to understand.

[0011] The Z-axis is shown in the drawings as appropriate. The Z-axis is the vertical direction. Of the vertical directions, the side in which the Z-axis arrow points (+Z side) is the "upper vertical side," and the side opposite to the direction in which the Z-axis arrow points (-Z side) is the "downward vertical side." In the following explanation, the "upper vertical side" may be simply referred to as the "upper side," and the "downward vertical side" may be simply referred to as the "downward side."

[0012] The X-axis is shown in the drawings as appropriate. The X-axis represents the front-to-back direction of the indoor unit. In the following description, the front-to-back direction of the indoor unit will simply be referred to as the "front-to-back direction." In this embodiment, the front-to-back direction is perpendicular to the vertical direction. In the following description, the side of the front-to-back direction in which the X-axis arrow points (+X side) will be referred to as the "front side," and the side opposite to the direction in which the X-axis arrow points (-X side) will be referred to as the "rear side."

[0013] The drawings will show the Y-axis where appropriate. The Y-axis represents the left-right direction of the indoor unit. In this embodiment, the left-right direction is perpendicular to both the front-back direction and the vertical direction. In the following description, the side of the left-right direction to which the Y-axis arrow points (+Y side) will be referred to as the "right side," and the side opposite to the side to which the Y-axis arrow points (-Y side) will be referred to as the "left side." Note that the terms upper side, lower side, front side, rear side, right side, and left side are merely names used to describe the relative positional relationships of each part, and the actual arrangement may differ from those indicated by these names.

[0014] Figure 1 is a schematic diagram showing the general configuration of the air conditioner 1 in the embodiment. Figure 2 is a perspective view showing the indoor unit 20 in the embodiment. Figure 3 is a longitudinal cross-sectional view showing the indoor unit 20 in the embodiment. Figure 4 is a first perspective view showing a part of the indoor unit 20 in the embodiment. Figure 5 is a second perspective view showing a part of the indoor unit 20 in the embodiment. As shown in Figure 1, the air conditioner 1 of the embodiment comprises an outdoor unit 10, an indoor unit 20, a circulation path section 18, and a refrigerant 19. The outdoor unit 10 is located outdoors. The indoor unit 20 is located indoors. The outdoor unit 10 and the indoor unit 20 are connected to each other by a circulation path section 18 through which the refrigerant 19 circulates. The air conditioner 1 adjusts the temperature of the indoor air by performing heat exchange between the refrigerant 19 circulating in the circulation path section 18 and the air in the room where the indoor unit 20 is located. As the refrigerant 19, a fluorine-based refrigerant or a hydrocarbon-based refrigerant with a low global warming potential can be used.

[0015] The outdoor unit 10 comprises a housing 11, a compressor 12, an outdoor heat exchanger 13, a flow control valve 14, a blower fan 15, a four-way valve 16, and a control unit 17. The compressor 12, outdoor heat exchanger 13, flow control valve 14, blower fan 15, four-way valve 16, and control unit 17 are housed inside the housing 11. The compressor 12, outdoor heat exchanger 13, flow control valve 14, and four-way valve 16 are each located in the portion of the circulation path 18 that is inside the housing 11. The compressor 12, outdoor heat exchanger 13, flow control valve 14, and four-way valve 16 are each connected by the portion of the circulation path 18 that is located inside the housing 11.

[0016] The four-way valve 16 is installed in the part of the circulation path 18 that is connected to the discharge side of the compressor 12. The four-way valve 16 reverses the direction in which the refrigerant 19 circulates within the circulation path 18 by switching a part of the circulation path 18. If the path connected to the four-way valve 16 is the path shown by the solid line on the four-way valve 16 in Figure 1, the refrigerant 19 flows within the circulation path 18 in the direction shown by the solid arrow in Figure 1. If the path connected to the four-way valve 16 is the path shown by the dashed line on the four-way valve 16 in Figure 1, the refrigerant 19 flows within the circulation path 18 in the direction shown by the dashed arrow in Figure 1.

[0017] As shown in Fig. 2, the indoor unit 20 is a floor-standing indoor unit. The indoor unit 20 is placed on an indoor floor F. Although not shown in the drawings, a portion on the rear side (-X side) of the indoor unit 20 is fixed to an indoor wall W. As shown in Fig. 3, the indoor unit 20 includes a housing 21, a heat exchanger 41, a blower 45, a drain pan 47, an air duct 50, and a filter 60. Further, as shown in Fig. 1, the indoor unit 20 includes a control device 70. As shown in Fig. 3, each of the heat exchanger 41, the blower 45, the drain pan 47, and the filter 60 is housed inside the housing 21. That is, the housing 21 houses each of the heat exchanger 41, the blower 45, the drain pan 47, and the filter 60. Further, although not shown in the drawings, the control device 70 is housed inside the housing 21. The indoor unit 20 performs a cooling operation for cooling indoor air and a heating operation for heating indoor air.

[0018] When the indoor unit 20 performs the cooling operation, the refrigerant 19 flowing in the circulation path portion 18 flows in the direction indicated by the solid line arrow in Fig. 1. That is, the refrigerant 19 flowing in the circulation path portion 18 passes through the compressor 12, the outdoor heat exchanger 13 included in the outdoor unit 10, the flow rate adjustment valve 14, and the heat exchanger 41 included in the indoor unit 20 in this order, and returns to the compressor 12. In the cooling operation, the outdoor heat exchanger 13 included in the outdoor unit 10 functions as a condenser, and the heat exchanger 41 included in the indoor unit 20 functions as an evaporator.

[0019] When the indoor unit 20 performs the heating operation, the refrigerant 19 flowing in the circulation path portion 18 flows in the direction indicated by the broken line in Fig. 1. That is, the refrigerant 19 flowing in the circulation path portion 18 passes through the compressor 12, the heat exchanger 41 included in the indoor unit 20, the flow rate adjustment valve 14, and the outdoor heat exchanger 13 included in the outdoor unit 10 in this order, and returns to the compressor 12. In the heating operation, the outdoor heat exchanger 13 included in the outdoor unit 10 functions as an evaporator, and the heat exchanger 41 included in the indoor unit 20 functions as a condenser.

[0020] Next, the indoor unit 20 of the embodiment will be described in detail. As shown in Figure 2, the housing 21 is a roughly rectangular box shape. The housing 21 has a housing body 22, a front panel 30, and a front wall portion 32. The housing 21 is also provided with an intake port 31 and an outlet port 22c.

[0021] The housing body 22 is a roughly rectangular box shape. As shown in Figure 3, the housing body 22 houses the heat exchanger 41, the blower 45, the drain pan 47, and the filter 60, respectively. As shown in Figure 4, the housing body 22 has a front wall 23, an upper wall 24, a first side wall 26a, and a second side wall 26c. Also, as shown in Figure 3, the housing body 22 has a lower wall 25 and a rear wall 27.

[0022] The housing front wall portion 23 covers the internal space of the housing 21 from the front (+X side). As shown in Figure 4, the housing front wall portion 23 is provided with an opening 23a that penetrates the housing front wall portion 23 in the front-to-back direction (X-axis direction). Viewed from the front-to-back direction, the opening 23a is substantially rectangular in shape with its long side extending in the left-to-right direction (Y-axis direction). Viewed from the front-to-back direction, the opening 23a may also have other shapes, such as a circular shape. As shown in Figure 3, the upper end 23b of the opening 23a is located above the heat exchanger 41 and the filter 60. As shown in Figure 4, the housing front wall portion 23 has an upper cover 23c. The upper cover 23c is the portion of the housing front wall portion 23 above the opening 23a. Viewed from the front-to-back direction, the upper cover 23c is substantially rectangular in shape with its long side extending in the left-to-right direction.

[0023] The upper wall portion 24 is plate-shaped, extending in a direction perpendicular to the vertical direction. When viewed from the vertical direction, the upper wall portion 24 is roughly rectangular in shape, with its longer side extending in the left-right direction (Y-axis direction). The upper wall portion 24 covers the internal space of the housing 21 from above.

[0024] The first side wall portion 26a is plate-shaped, extending in a direction perpendicular to the left-right direction (Y-axis direction). When viewed from the left-right direction, the first side wall portion 26a is roughly rectangular in shape with its longer side extending vertically. The first side wall portion 26a covers the internal space of the housing 21 from the right side (+Y side). Although not shown in the illustration, the second side wall portion 26c is plate-shaped, extending in a direction perpendicular to the left-right direction. Although not shown in the illustration, when viewed from the left-right direction, the second side wall portion 26c is roughly rectangular in shape with its longer side extending vertically. The second side wall portion 26c covers the internal space of the housing 21 from the left side (-Y side).

[0025] The lower wall portion 25 is plate-shaped, extending in a direction perpendicular to the vertical direction. Although not shown in the illustration, when viewed from the vertical direction, the lower wall portion 25 is roughly rectangular in shape, with its longer side extending in the left-right direction (Y-axis direction). As shown in Figure 3, the lower wall portion 25 covers the internal space of the housing 21 from below.

[0026] The rear wall portion 27 covers the internal space of the housing 21 from the rear (-X side). The rear wall portion 27 is positioned behind both the heat exchanger 41 and the drain pan 47. The rear wall portion 27 faces both the heat exchanger 41 and the drain pan 47 with a gap in the front-rear direction (X-axis direction). The rear wall portion 27 has a first rear wall portion 27a, a second rear wall portion 27c, a third rear wall portion 27e, and a fourth rear wall portion 27g. Each of the first rear wall portion 27a, the second rear wall portion 27c, the third rear wall portion 27e, and the fourth rear wall portion 27g is a part of the rear wall portion 27.

[0027] The first rear wall portion 27a is plate-shaped and extends in a direction perpendicular to the front-to-back direction (X-axis direction). Although not shown in the figure, when viewed from the front-to-back direction, the first rear wall portion 27a is roughly rectangular in shape with its longer side extending in the left-to-right direction (Y-axis direction). When viewed from the left-to-right direction, the first rear wall portion 27a extends vertically. The upper end of the first rear wall portion 27a is located above the rear heat exchanger 43, which will be described later. The lower end of the first rear wall portion 27a is located below the drain pan 47. The first rear wall portion 27a faces the rear heat exchanger 43 and the drain pan 47 in the front-to-back direction with a gap between them. The first rear wall portion 27a has a gutter portion 28. That is, the rear wall portion 27 has a gutter portion 28.

[0028] As shown in Figure 5, the gutter section 28 is plate-shaped and protrudes forward (+X side) from the first rear wall section 27a. As shown in Figure 3, in the vertical direction, the gutter section 28 is positioned vertically above the drain pan 47. As shown in Figure 5, the gutter section 28 has a first gutter section 28a and a second gutter section 28c. The first gutter section 28a is plate-shaped and is located downwards as it is directed to the left side (-Y side). The right side (+Y side) end of the first gutter section 28a is located approximately in the center of the first rear wall section 27a in the left-right direction (Y-axis direction). The left side end of the first gutter section 28a is located at the left end of the first rear wall section 27a. The left side end of the first gutter section 28a is connected to the rear side (-X side) end of the first connecting section 29a. The first connecting section 29a is plate-shaped and is located downwards as it is directed to the front. The front end of the first connection part 29a is located on the upper part of the drain pan 47.

[0029] The second gutter section 28c is plate-shaped and located on the lower side as it extends to the right (+Y side). The left end (-Y side) of the second gutter section 28c is located approximately in the center of the first rear wall section 27a in the left-right direction (Y-axis direction) and is connected to the right end of the first gutter section 28a. The right end of the second gutter section 28c is located at the right end of the first rear wall section 27a. Although not shown in the diagram, the right end of the second gutter section 28c is connected to the rear (-X side) end of the second connection section 29c. The second connection section 29c is plate-shaped and located on the lower side as it extends to the front. The front end of the second connection section 29c is located on the upper part of the drain pan 47.

[0030] As described above, the first rear wall 27a is spaced apart from the rear heat exchanger 43 and faces it in the front-to-back direction (X-axis direction). Therefore, when the indoor unit 20 is operating in cooling mode, condensed water WT generated by condensation adheres to the front-facing (+X side) surface of the first rear wall 27a. The condensed water WT adhering to the front-facing surface of the first rear wall 27a flows downward along the front-facing surface of the first rear wall 27a due to gravity and reaches the upper-facing surface of the gutter 28. The condensed water WT that reaches the first gutter 28a flows to the left (-Y side) along the upper-facing surface of the first gutter 28a, and then flows forward along the upper-facing surface of the first connection part 29a and drips into the drain pan 47. Furthermore, the condensed water WT that reaches the second trough 28c flows with the upper surface of the second trough 28c facing to the right (+Y side), then flows with the upper surface of the second connection 29c facing forward, and drips into the drain pan 47. In this way, the condensed water WT adhering to the front surface of the first rear wall 27a can be recovered into the drain pan 47.

[0031] As shown in Figure 3, when viewed from the left-right direction (Y-axis direction), the second rear wall portion 27c is plate-shaped and is located towards the front (+X side) as it extends downward in the vertical direction. The upper end of the second rear wall portion 27c is connected to the lower end of the first rear wall portion 27a.

[0032] The third rear wall portion 27e is located above the first rear wall portion 27a. The lower end of the third rear wall portion 27e connects to the upper end of the first rear wall portion 27a. The upper end of the third rear wall portion 27e connects to the upper wall portion 24. The front (+X) side of the third rear wall portion 27e is curved and convex towards the rear (-X) side. The third rear wall portion 27e is spaced apart from the blower 45 and faces it in the front-rear direction (X-axis direction).

[0033] The fourth rear wall portion 27g is plate-shaped and extends in a direction perpendicular to the front-to-back direction (X-axis direction). The upper end of the fourth rear wall portion 27g connects to the lower end of the second rear wall portion 27c. The lower end of the fourth rear wall portion 27g connects to the lower wall portion 25.

[0034] As shown in Figure 4, the air outlet 22c is a hole that spans the upper wall portion 24 and the upper cover 23c. As shown in Figure 3, the air outlet 22c is located vertically above the blower 45 and the heat exchanger 41, respectively. As shown in Figure 4, the portion of the air outlet 22c located on the upper wall portion 24 is substantially rectangular in shape, with its longer side extending in the left-right direction (Y-axis direction) when viewed from the vertical direction. The portion of the air outlet 22c located on the upper cover 23c is substantially rectangular in shape, with its longer side extending in the left-right direction when viewed from the front-back direction (X-axis direction). As shown in Figure 3, the air outlet 22c is fitted with a plurality of wind direction vanes 34 that control the direction in which the third airflow AF3 blown out from inside the housing 21 flows. In this embodiment, the control device 70 controls the direction of the third airflow AF3 blown out from the air outlet 22c to the outside of the housing 21 by rotating each wind direction vane 34.

[0035] The front panel 30 shown in Figure 2 is plate-shaped, extending in a direction perpendicular to the front-to-back direction (X-axis direction). Viewed from the front-to-back direction, the front panel 30 is roughly rectangular in shape, with its longer side extending in the left-to-right direction (Y-axis direction). The front panel 30 is detachably attached to the portion of the housing front wall 23 below the upper cover 23c. The front panel 30 closes the opening 23a shown in Figure 4 from the front. As shown in Figure 4, when the front panel 30 is removed from the housing body 22, the opening 23a is exposed to the outside of the housing 21. This connects the internal space of the housing body 22 to the outside of the housing body 22 through the opening 23a.

[0036] As shown in Figure 2, in this embodiment, the front wall portion 32 is composed of an upper cover 23c and a front panel 30. As shown in Figure 3, the front wall portion 32 is positioned in front of (towards the +X side of) both the heat exchanger 41 and the drain pan 47. The front wall portion 32 faces both the heat exchanger 41 and the drain pan 47 with a gap between them in the front-to-back direction (X-axis direction).

[0037] The suction port 31 is a hole that penetrates the lower part of the front panel 30 in the front-to-back direction (X-axis direction). Thus, the housing 21 has a suction port 31. As shown in Figure 2, when viewed from the front-to-back direction, the suction port 31 is a substantially rectangular hole with its longer side extending in the left-to-right direction (Y-axis direction). As shown in Figure 3, the outside of the housing 21 and the internal space of the housing 21 are connected through the suction port 31. The suction port 31 is provided in the part of the front wall 32 that is vertically below the blower 45. In this embodiment, when viewed from the front-to-back direction, the upper end of the suction port 31 overlaps with the drain pan 47. The upper end of the suction port 31 may be located below the drain pan 47 or above the drain pan 47.

[0038] The blower 45 is a fan that generates an airflow, which is the flow of air from the intake port 31 to the outlet port 22c. In this embodiment, the airflow includes a first airflow AF1, a second airflow AF2, and a third airflow AF3. The first airflow AF1 and the second airflow AF2 are the airflow that passes through the filter 60 and the heat exchanger 41, respectively. The third airflow AF3 is the airflow that is blown out from the outlet port 22c to the outside of the housing 21. Although not shown in the figures, the blower 45 is substantially cylindrical in shape and extends in the left-right direction (Y-axis direction). The blower 45 is located in the upper part of the internal space of the housing 21. The blower 45 is positioned opposite the third rear wall portion 27e in the front-rear direction (X-axis direction) with a gap between them. The control device 70 can rotate the multiple impellers (not shown) of the blower 45 around the rotation axis J. In this embodiment, the rotation axis J is a virtual axis that extends in the left-right direction and passes through the center of the blower 45. When multiple impellers rotate around the rotation axis J, airflows AF1, AF2, and AF3 are generated.

[0039] The heat exchanger 41 adjusts the temperature of the third airflow AF3 blown out of the housing 21 from the outlet 22c by exchanging heat with the first airflow AF1 and the second airflow AF2, respectively. As described above, when the indoor unit 20 is in cooling operation, the heat exchanger 41 functions as an evaporator, and when the indoor unit 20 is in heating operation, the heat exchanger 41 functions as a condenser. The heat exchanger 41 has a front heat exchanger 42 and a rear heat exchanger 43.

[0040] Although not shown in the diagram, the front heat exchanger 42 is a roughly rectangular parallelepiped extending in the left-right direction (Y-axis direction). In this embodiment, the front heat exchanger 42 is positioned towards the front (+X side) as it moves upward. In the front-rear direction (X-axis direction), the upper part of the front heat exchanger 42 is positioned between the front wall 32 and the blower 45. In this embodiment, the upper end of the front heat exchanger 42 is located above the rotation axis J. The lower end of the front heat exchanger 42 is located above the drain pan 47.

[0041] Although not shown in the diagram, the rear heat exchanger 43 is a roughly rectangular parallelepiped extending in the left-right direction (Y-axis direction). In the front-back direction (X-axis direction), the rear heat exchanger 43 is positioned between the rear wall portion 27 and the front heat exchanger 42. In this embodiment, the rear heat exchanger 43 is positioned towards the rear (-X side) as it moves upward. The rear heat exchanger 43 is positioned behind the front heat exchanger 42. As a result, when viewed from the left-right direction, the front heat exchanger 42 and the rear heat exchanger 43 are arranged in a V-shape that opens upward. In this embodiment, the rear heat exchanger 43 is positioned below the blower 45. The lower end of the rear heat exchanger 43 is located above the drain pan 47.

[0042] The drain pan 47 is a container for temporarily storing condensed water generated in the heat exchanger 41. As shown in Figure 5, the drain pan 47 extends in the left-right direction (Y-axis direction) and opens upwards. As shown in Figure 3, the drain pan 47 is located below both the front heat exchanger 42 and the rear heat exchanger 43. That is, the drain pan 47 is located vertically below the heat exchanger 41. The drain pan 47 is positioned opposite the front wall portion 32 and the rear wall portion 27 in the front-rear direction (X-axis direction) with a gap between them. The front (+X side) end of the drain pan 47 is located in front of the lower end of the front heat exchanger 42, and the rear (-X side) end of the drain pan 47 is located behind the lower end of the rear heat exchanger 43. As a result, the condensed water generated in the heat exchanger 41 drips into the drain pan 47. The location of the drain pan 47 within the housing 21 and the detailed configuration of the drain pan 47 will be described in detail later.

[0043] The air passage 50 is a passage through which airflows AF1, AF2, and AF3 flow inside the housing 21. The air passage 50 includes a front air passage 51, a rear air passage 52, and a discharge air passage 53. The front air passage 51 is an air passage through which the first airflow AF1 flows from the intake port 31 toward the front heat exchanger 42. The front air passage 51 is composed of the front heat exchanger 42, the drain pan 47, and the front wall 32. The front air passage 51 is a space enclosed by the front heat exchanger 42, the drain pan 47, and the front wall 32. A portion of the front air passage 51 is formed between the drain pan 47 and the front wall 32.

[0044] The rear air passage 52 is an air passage through which the second airflow AF2 flows from the intake port 31 toward the rear heat exchanger 43. The rear air passage 52 is composed of the rear heat exchanger 43, the drain pan 47, the lower wall portion 25, and the rear wall portion 27. More specifically, the rear air passage 52 is composed of the rear heat exchanger 43, the drain pan 47, the lower wall portion 25, the fourth rear wall portion 27g, the second rear wall portion 27c, and the first rear wall portion 27a. The rear air passage 52 is composed of the space between the drain pan 47 and the lower wall portion 25, the space between the drain pan 47 and the second rear wall portion 27c, and the space between the rear heat exchanger 43 and the drain pan 47 and the first rear wall portion 27a. A portion of the rear air passage 52 is formed between the drain pan 47 and the rear wall portion 27.

[0045] The air outlet passage 53 is an air passage through which the third airflow AF3 blows out from the outlet 22c to the outside of the housing 21. The air outlet passage 53 is composed of the blower 45, the third rear wall 27e, the upper wall 24, and the upper cover 23c. The air outlet passage 53 is the space enclosed by the blower 45, the third rear wall 27e, the upper wall 24, and the upper cover 23c.

[0046] The filter 60 is a filter that collects dust and other foreign matter contained in the airflow AF1 and AF2 that flows into the housing 21 from the intake port 31. The filter 60 is positioned in the air passage 50. When viewed from the left-right direction (Y-axis direction), the filter 60 is a straight line that is located towards the front (+X side) as it moves upward. The airflow AF1 and AF2 can pass through the filter 60 in the thickness direction of the filter 60.

[0047] In the vertical direction, the upper end of the filter 60 is located below the upper end 23b of the opening 23a. Also in the vertical direction, the upper end of the filter 60 is located above the rotation axis J of the blower 45. The upper portion of the filter 60 is located in the front air passage 51. The upper portion of the filter 60 is located in front of (+X side of) both the front heat exchanger 42 and the drain pan 47. The upper portion of the filter 60 extends linearly along the front heat exchanger 42. The first airflow AF1 passes through the upper portion of the filter 60. As a result, the filter 60 collects dust and other foreign matter contained in the first airflow AF1.

[0048] The lower portion of the filter 60 is positioned in the rear air passage 52. In this embodiment, the lower end of the filter 60 is in contact with the lower wall portion 25. The lower end of the filter 60 may also be in contact with the second rear wall portion 27c or the fourth rear wall portion 27g. The second airflow AF2 passes through the lower portion of the filter 60. As a result, the lower portion of the filter 60 collects foreign matter such as dust contained in the second airflow AF2.

[0049] Next, the flow of airflows AF1, AF2, and AF3 will be described. When the control device 70 rotates the blower 45 around the rotation axis J, the air in the room flows into the housing 21 through the intake port 31. A portion of the air that flows into the housing 21 flows upward through the front air passage 51 as the first airflow AF1, and is dust-removed as it passes through the upper part of the filter 60. As the first airflow AF1 that has passed through the filter 60 passes through the front heat exchanger 42, it is cooled or heated by heat exchange with the refrigerant 19 flowing inside the front heat exchanger 42. The first airflow AF1 that has passed through the front heat exchanger 42 reaches the blower 45.

[0050] Another portion of the air that flows into the housing 21 flows as a second airflow AF2 towards the rear (-X side) through the rear air passage 52, and is dust-removed as it passes through the lower part of the filter 60. After passing through the filter 60, the second airflow AF2 flows upward between the drain pan 47 and the rear wall 27, and then, as it passes through the rear heat exchanger 43, it is cooled or heated by heat exchange with the refrigerant 19 flowing inside the rear heat exchanger 43. After passing through the rear heat exchanger 43, the second airflow AF2 reaches the blower 45.

[0051] The first airflow AF1 and the second airflow AF2 that reach the blower 45 are then directed by the blower 45 as a third airflow AF3, flowing through the outlet 53 towards the outlet 22c and blown out of the housing 21 through the outlet 22c. The control device 70 controls the direction of the third airflow AF3 blown out of the housing 21 from the outlet 22c by rotating each airflow vane 34 to a predetermined angle. This allows the third airflow AF3 at a predetermined temperature to be delivered to a predetermined location in the room.

[0052] Figure 6 is a partially enlarged longitudinal cross-sectional view showing a part of the indoor unit 20 in the embodiment. Next, the position in which the drain pan 47 is arranged within the housing 21 and the detailed configuration of the drain pan 47 will be described. As described above, the drain pan 47 is a container that opens upwards. The drain pan 47 is also located vertically below the heat exchanger 41. As shown in Figure 6, the drain pan 47 has a bottom portion 48 and a side wall portion 49.

[0053] The bottom portion 48 is plate-shaped, extending in a direction perpendicular to the vertical direction. The plate surface of the bottom portion 48 faces the vertical direction. As shown in Figure 5, when viewed from the vertical direction, the bottom portion 48 is roughly rectangular in shape, with its longer side extending in the left-right direction (Y-axis direction). The side wall portion 49 is cylindrical, projecting vertically upward from the outer edge of the bottom portion 48. The side wall portion 49 is open on the upper side. When viewed from the vertical direction, the side wall portion 49 is roughly rectangular and annular in shape. The side wall portion 49 has a front side wall portion 49a and a rear side wall portion 49c. That is, the drain pan 47 has a front side wall portion 49a and a rear side wall portion 49c.

[0054] The front side wall portion 49a is the portion of the side wall portion 49 located on the front side (+X side). The front side wall portion 49a is plate-shaped and extends in the left-right direction (Y axis direction). As shown in Figure 6, the front side wall portion 49a protrudes vertically upward from the front end of the bottom portion 48. The front side wall portion 49a is spaced apart from the front wall portion 32 and faces it in the front-rear direction (X axis direction). As shown in Figure 5, the rear side wall portion 49c is the portion of the side wall portion 49 located on the rear side (-X side). The rear side wall portion 49c is plate-shaped and extends in the left-right direction. As shown in Figure 6, the rear side wall portion 49c protrudes vertically upward from the rear end of the bottom portion 48. The rear side wall portion 49c is spaced apart from the first rear wall portion 27a and faces it in the front-rear direction.

[0055] In this embodiment, the front-rear dimension T1 of the rear wall portion 49c is smaller than the front-rear dimension T2 of the front wall portion 49a. In other words, the thickness of the rear wall portion 49c is thinner than the thickness of the front wall portion 49a. Therefore, in this embodiment, it is easier to increase the third spacing G3, which is the front-rear distance between the upper vertical end of the rear wall portion 49c and the first rear wall portion 27a. As a result, in this embodiment, it is easier to reduce the pressure loss of the second airflow AF2 in the portion of the rear air passage 52 between the drain pan 47 and the first rear wall portion 27a.

[0056] As described above, the filter 60 is linear in shape and is located towards the front (+X side) as it moves upward. Therefore, the air that flows into the housing 21 from the intake port 31 easily flows along the filter 60 towards the front air passage 51 upward. Consequently, the second airflow AF2 has difficulty passing through the lower part of the filter 60 and flowing into the rear air passage 52, making it difficult to increase the flow rate of the second airflow AF2 flowing through the rear air passage 52. Furthermore, if the second gap G2 and the third gap G3, which are the distances between the drain pan 47 and the second rear wall portion 27c, become too small, the pressure loss of the second airflow AF2 in the rear air passage 52 increases, making it even more difficult to increase the flow rate of the second airflow AF2 flowing through the rear air passage 52. As a result, when the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43 becomes large, it becomes difficult to equalize the flow rates of the airflows AF1 and AF2 passing through the heat exchanger 41. Therefore, it becomes difficult to improve the heat exchange efficiency between the heat exchanger 41, the airflow, and AF1 and AF2.

[0057] In this embodiment, if the distance in the front-to-back direction (X-axis direction) between the upper vertical end of the front side wall portion 49a and the front wall portion 32 is defined as the first interval G1, and the distance between the drain pan 47 and the second rear wall portion 27c is defined as the second interval G2, then the drain pan 47 is positioned to satisfy the relationship 0.50 ≤ G2 / (G1+G2) ≤ 0.60. Therefore, since the relationship 0.50 ≤ G2 / (G1+G2) is satisfied, it is possible to prevent the second interval G2 from becoming too small. Also, since the relationship G2 / (G1+G2) ≤ 0.60 is satisfied, it is possible to prevent the first interval G1 from becoming too small. In the following description, G2 / (G1+G2) may be referred to as the first ratio R1.

[0058] Figure 7 is the first figure showing the average heating and cooling energy efficiency ratio Rcop of the air conditioner 1 in the embodiment. The horizontal axis of Figure 7 is the first ratio R1. The vertical axis of Figure 7 is the average heating and cooling energy efficiency ratio Rcop of the air conditioner 1. The average heating and cooling energy efficiency ratio Rcop is the ratio of the average heating and cooling energy efficiency (COP) of the air conditioner 1 in the embodiment to the average heating and cooling energy efficiency (COP) of an air conditioner with a first spacing G1 of 63.5 mm, a second spacing G2 of 56.7 mm, and a third spacing G3 of 32.3 mm (hereinafter referred to as the comparative air conditioner). The average heating and cooling energy efficiency is calculated from the heating and cooling capacity relative to the power consumption of the air conditioner. In other words, the average heating and cooling energy efficiency is an indicator of the energy-saving performance of the air conditioner. Air conditioners with a higher average heating and cooling energy efficiency have higher energy-saving performance, and air conditioners with a lower average heating and cooling energy efficiency have lower energy-saving performance. Therefore, when the average energy efficiency ratio for heating and cooling, Rcop, is 100% or higher, the energy-saving performance of the air conditioner 1 of the embodiment is greater than or equal to that of the comparative air conditioner, and when the average energy efficiency ratio for heating and cooling, Rcop, is less than 100%, the energy-saving performance of the air conditioner 1 of the embodiment is inferior to that of the comparative air conditioner.

[0059] As shown in Figure 7, when the first ratio R1 is less than 0.50, the average energy efficiency ratio Rcop for heating and cooling becomes less than 100%. When the first ratio R1 is less than 0.50, the second spacing G2 becomes too small, causing the pressure loss of the second airflow AF2 in the portion of the rear air passage 52 between the drain pan 47 and the second rear wall 27c to become too large. As a result, the flow rate of the second airflow AF2 decreases, and the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43 becomes large. Consequently, the flow rates of the airflows AF1 and AF2 passing through the heat exchanger 41 become uneven, reducing the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2. As a result, the average energy efficiency ratio Rcop for heating and cooling becomes less than 100%.

[0060] Furthermore, if the first ratio R1 is greater than 0.60, the average energy efficiency ratio Rcop for heating and cooling will be less than 100%. When the first ratio R1 is greater than 0.60, the first spacing G1 becomes too small, causing the pressure loss of the first airflow AF1 in the portion of the front air passage 51 between the drain pan 47 and the front wall 32 to become too large. As a result, the flow rate of the first airflow AF1 decreases, and the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43 becomes large. Consequently, the flow rates of the airflows AF1 and AF2 passing through the heat exchanger 41 become uneven, reducing the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2. As a result, the average energy efficiency ratio Rcop for heating and cooling will be less than 100%.

[0061] In contrast, when the first ratio R1 is between 0.50 and 0.60, the average energy efficiency ratio Rcop for heating and cooling becomes 100% or more. When the first ratio R1 is between 0.50 and 0.60, it is possible to prevent the first interval G1 and the second interval G2 from becoming too small. This prevents the pressure loss of the second airflow AF2 in the portion of the rear air passage 52 between the drain pan 47 and the second rear wall 27c, and the pressure loss of the first airflow AF1 in the portion of the front air passage 51 between the drain pan 47 and the front wall 32 from becoming too large. Therefore, the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43 can be reduced. Consequently, the flow rates of the airflows AF1 and AF2 passing through the heat exchanger 41 can be made more uniform. Therefore, the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2 can be increased. As a result, the average energy efficiency ratio for heating and cooling (Rcop) will exceed 100%, improving the heating and cooling performance of the air conditioner 1.

[0062] As shown in Figure 6, in this embodiment, the drain pan 47 is arranged to satisfy the relationship 0.40 ≤ G3 / (G1+G3) ≤ 0.60. Therefore, since the relationship 0.40 ≤ G3 / (G1+G3) is satisfied, it is possible to prevent the third interval G3 from becoming too small. Also, since the relationship G3 / (G1+G3) ≤ 0.60 is satisfied, it is possible to prevent the first interval G1 from becoming too small. In the following description, G3 / (G1+G3) may be referred to as the second ratio R2.

[0063] Figure 8 is a second figure showing the average heating and cooling energy efficiency ratio Rcop of the air conditioner 1 in the embodiment. The horizontal axis of Figure 8 is the second ratio R2. The vertical axis of Figure 8 is the average heating and cooling energy efficiency ratio Rcop of the air conditioner 1. As shown in Figure 8, when the second ratio R2 is less than 0.40, the average heating and cooling energy efficiency ratio Rcop is less than 100%. When the second ratio R2 is less than 0.40, the third spacing G3 becomes too small, causing the pressure loss of the second airflow AF2 in the portion of the rear air passage 52 between the drain pan 47 and the first rear wall 27a to become too large. As a result, the flow rate of the second airflow AF2 decreases, and the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43 becomes large. Consequently, the airflow rates of AF1 and AF2 passing through the heat exchanger 41 become uneven, reducing the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2. As a result, the average energy efficiency ratio for heating and cooling, Rcop, falls below 100%.

[0064] Furthermore, if the second ratio R2 is greater than 0.60, the average energy efficiency ratio Rcop for heating and cooling will be less than 100%. When the second ratio R2 is greater than 0.60, the first spacing G1 becomes too small, causing the pressure loss of the first airflow AF1 in the portion of the front air passage 51 between the drain pan 47 and the front wall 32 to become too large. As a result, the flow rate of the first airflow AF1 decreases, and the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43 becomes large. Consequently, the flow rates of the airflows AF1 and AF2 passing through the heat exchanger 41 become uneven, reducing the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2. As a result, the average energy efficiency ratio Rcop for heating and cooling will be less than 100%.

[0065] In contrast, when the second ratio R2 is between 0.40 and 0.60, the average energy efficiency ratio Rcop for heating and cooling becomes 100% or more. When the second ratio R2 is between 0.40 and 0.60, it is possible to prevent the first interval G1 and the third interval G3 from becoming too small. This prevents the pressure loss of the second airflow AF2 in the portion of the rear air passage 52 between the drain pan 47 and the first rear wall 27a, and the pressure loss of the first airflow AF1 in the portion of the front air passage 51 between the drain pan 47 and the front wall 32 from becoming too large. Therefore, the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43 can be reduced. Consequently, the flow rates of the airflows AF1 and AF2 passing through the heat exchanger 41 can be made more uniform. Therefore, the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2 can be increased. As a result, the average energy efficiency ratio for heating and cooling (Rcop) will exceed 100%, improving the heating and cooling performance of the air conditioner 1.

[0066] According to the embodiment, the indoor unit 20 is an indoor unit 20 provided by the air conditioner 1, and is a floor-standing indoor unit 20 comprising a heat exchanger 41, a blower 45 that generates airflows AF1 and AF2 that pass through the heat exchanger 41, a drain pan 47 positioned vertically below the heat exchanger 41, an air passage 50 through which the airflows AF1 and AF2 flow, and a housing 21 that accommodates the heat exchanger 41, the blower 45, and the drain pan 47, respectively. The housing 21 has a front wall portion 32 positioned in front of (+X side) the heat exchanger 41 and the drain pan 47, a rear wall portion 27 positioned behind (-X side) the heat exchanger 41 and the drain pan 47, an intake port 31 provided in the portion of the front wall portion 32 that is vertically below the blower 45, and an outlet port 22c provided vertically above the blower 45. The heat exchanger 41 has a front heat exchanger 42 and a rear heat exchanger 43 positioned behind the front heat exchanger 42. The air passage 50 is formed in part between the drain pan 47 and the front wall portion 32, and has a front air passage 51 through which a first airflow AF1 flows from the intake port 31 toward the front heat exchanger 42, and has a front air passage 51 through which a first airflow AF1 flows from the intake port 31 toward the rear heat exchanger 43. The rear wall portion 27 includes a rear air passage 52 through which a second airflow AF2 flows, and the rear wall portion 27 has a first rear wall portion 27a that extends vertically and faces the drain pan 47 in the front-rear direction (X-axis direction), and a second rear wall portion 27c that connects to the lower end of the first rear wall portion 27a and is located towards the front as it goes downward in the vertical direction, and the drain pan 47 has a bottom portion 48 that spreads in a direction perpendicular to the vertical direction, and a lead from the front end of the bottom portion 48 The drain pan 47 has a front side wall portion 49a that protrudes perpendicularly upward, and a rear side wall portion 49c that protrudes vertically upward from the rear end of the bottom portion 48. The first interval G1, that is, the distance in the front-rear direction between the vertically upper end of the front side wall portion 49a and the front wall portion 32, and the second interval G2, that is, the distance between the drain pan 47 and the second rear wall portion 27c, satisfy the relationship 0.50 ≤ G2 / (G1 + G2) ≤ 0.60. Therefore, as described above, it is possible to suppress the second interval G2 from becoming too small. As a result, as described above, it is possible to suppress the increase in pressure loss of the second airflow AF2 in the portion of the rear air passage 52 between the drain pan 47 and the second rear wall portion 27c, and thus the flow rate of the second airflow AF2 can be increased.Therefore, the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43 can be reduced, thereby making the flow rates of the airflows AF1 and AF2 passing through the heat exchanger 41 more uniform. This improves the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2. As a result, the heating and cooling performance of the air conditioner 1 can be improved.

[0067] Furthermore, in this embodiment, as described above, the relationship G2 / (G1+G2)≦0.60 is satisfied between the first interval G1 and the second interval G2, so that the first interval G1 does not become too small. This prevents the pressure loss of the first airflow AF1 in the portion of the front air passage 51 between the drain pan 47 and the front wall portion 32 from becoming too large. Therefore, the flow rate of the first airflow AF1 does not become too small. This makes it possible to more effectively reduce the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43. Consequently, the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2 can be more effectively increased. Therefore, the heating and cooling performance of the air conditioner 1 can be more effectively improved.

[0068] According to this embodiment, the relationship between the first spacing G1 and the third spacing G3, that is, the spacing in the front-rear direction between the vertically upper end of the rear wall portion 49c and the first rear wall portion 27a, satisfies 0.40 ≤ G3 / (G1 + G3) ≤ 0.60. Therefore, as described above, it is possible to suppress the third spacing G3 from becoming too small. Consequently, it is possible to suppress an increase in the pressure loss of the second airflow AF2 in the portion of the rear air passage 52 between the drain pan 47 and the first rear wall portion 27a, and thus the flow rate of the second airflow AF2 can be more favorably increased. As a result, the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43 can be more favorably reduced. Therefore, the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2 can be more favorably increased.

[0069] Furthermore, in this embodiment, as described above, the relationship between the first interval G1 and the third interval G3 satisfies G3 / (G1+G3)≦0.60, which more effectively prevents the first interval G1 from becoming too small. This more effectively prevents an increase in the pressure loss of the first airflow AF1 in the portion of the front air passage 51 between the drain pan 47 and the front wall portion 32. Therefore, this more effectively prevents the flow rate of the first airflow AF1 from becoming too small. This makes it possible to more effectively reduce the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43. Consequently, the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2 can be increased.

[0070] According to this embodiment, the front-rear dimension T1 of the rear wall portion 49c is smaller than the front-rear dimension T2 of the front wall portion 49a. Therefore, as described above, it is easier to increase the third spacing G3. Consequently, the pressure loss of the second airflow AF2 in the portion of the rear air passage 52 between the drain pan 47 and the first rear wall portion 27a can be more effectively reduced, and the flow rate of the second airflow AF2 can be more effectively increased. This makes it possible to more effectively reduce the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43. Consequently, the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2 can be more effectively increased.

[0071] According to this embodiment, the rear wall portion 27 has a trough portion 28 that protrudes forward (+X side) from the first rear wall portion 27a, and in the vertical direction, the trough portion 28 is positioned vertically above the drain pan 47. Therefore, the distance between the drain pan 47 and the trough portion 28 can be increased compared to the case where the trough portion 28 is positioned opposite the drain pan 47 in the front-rear direction (X-axis direction). Consequently, the pressure loss of the second airflow AF2 in the portion of the rear air passage 52 between the drain pan 47 and the trough portion 28 can be easily reduced, and the flow rate of the second airflow AF2 can be more favorably increased. As a result, the difference between the flow rate of the first airflow AF1 passing through the front heat exchanger 42 and the flow rate of the second airflow AF2 passing through the rear heat exchanger 43 can be more favorably reduced. Consequently, the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2 can be more favorably increased.

[0072] According to this embodiment, the indoor unit 20 is equipped with a filter 60 located in the air passage 50 that collects dust contained in the airflows AF1 and AF2. Therefore, dust accumulation on the surface of the heat exchanger 41 can be suppressed during long-term use of the indoor unit 20. As a result, the decrease in the surface area of ​​the heat exchanger 41 that is in direct contact with the airflows AF1 and AF2 can be effectively suppressed during long-term use of the indoor unit 20. This allows for a more favorable improvement in the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2. Consequently, the heating and cooling performance of the air conditioner 1 can be more favorably improved.

[0073] According to this embodiment, the air conditioner 1 comprises an indoor unit 20 and an outdoor unit 10 connected to the indoor unit 20 by a circulation path 18 through which the refrigerant 19 circulates. As described above, in the indoor unit 20 of this embodiment, the flow rates of the airflows AF1 and AF2 passing through the heat exchanger 41 can be made uniform, thereby increasing the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2. Therefore, the heating and cooling performance of the air conditioner 1 can be improved.

[0074] Furthermore, in this embodiment, as described above, the heat exchange efficiency between the heat exchanger 41 and the airflows AF1 and AF2 can be suitably increased, thereby reducing the flow rate of the refrigerant 19 supplied to the heat exchanger 41. This reduces the power consumed by the compressor 12 of the outdoor unit 10. Therefore, the air conditioner 1 can be made more energy-efficient.

[0075] While embodiments of this disclosure have been described above, this disclosure is not limited to the configurations of the embodiments described above, and the following configurations and methods may also be adopted.

[0076] The shape of the filter is not limited to the shape of the embodiment; part of the filter may be curved, or the filter may have a bent shape.

[0077] Furthermore, the upper end of the front heat exchanger may be located below the axis of rotation, or above the upper end of the opening.

[0078] This disclosure may also be in the following embodiments. (1) One embodiment of the present disclosure is an indoor unit for an air conditioner, and is a floor-standing indoor unit, comprising: a heat exchanger; a blower that generates an airflow passing through the heat exchanger; a drain pan positioned vertically below the heat exchanger; an air passage through which the airflow flows; and a housing that houses the heat exchanger, the blower, and the drain pan, wherein the housing has a front wall portion positioned in front of the heat exchanger and the drain pan, a rear wall portion positioned behind the heat exchanger and the drain pan, an intake port provided in the portion of the front wall portion vertically below the blower, and an outlet portion provided vertically above the blower, wherein the heat exchanger has a front heat exchanger and a rear heat exchanger positioned behind the front heat exchanger, and the air passage is formed in part between the drain pan and the front wall portion The rear wall comprises a front air passage through which the airflow from the intake port toward the front heat exchanger flows, and a rear air passage through which the airflow from the intake port toward the rear heat exchanger flows, the rear wall having a first rear wall extending vertically and facing the drain pan in the front-rear direction, and a second rear wall connecting to the lower end of the first rear wall and located toward the front as it extends downward in the vertical direction. The drain pan has a bottom portion that extends in a direction perpendicular to the vertical direction, a front wall portion that protrudes vertically upward from the front end of the bottom portion, and a rear wall portion that protrudes vertically upward from the rear end of the bottom portion. If the distance in the front-rear direction between the vertically upper end of the front wall portion and the front wall portion is G1, and the distance between the drain pan and the second rear wall portion is G2, then the indoor unit satisfies the relationship 0.50 ≤ G2 / (G1 + G2) ≤ 0.60. (2) Another embodiment of this disclosure is an indoor unit as described in (1), wherein if G3 is the distance in the front-rear direction between the vertically upper end of the rear side wall and the first rear wall, then the relationship 0.40 ≤ G3 / (G1 + G3) ≤ 0.60 is satisfied. (3) Another embodiment of this disclosure is an indoor unit as described in (1) or (2), wherein the front-rear dimension of the rear side wall is smaller than the front-rear dimension of the front side wall. (4) Another embodiment of this disclosure is an indoor unit according to any one of (1) to (3), wherein the rear wall portion has a gutter portion that protrudes forward from the first rear wall portion, and in the vertical direction, the gutter portion is positioned vertically above the drain pan. (5) Another embodiment of this disclosure is an indoor unit according to any one of (1) to (4), comprising a filter disposed in the air passage for collecting dust contained in the airflow. (6) Another embodiment of this disclosure is an air conditioner comprising an indoor unit as described in any of (1) to (5) and an outdoor unit connected to the indoor unit by a circulation path through which a refrigerant circulates.

[0079] The configurations and methods described herein can be combined as appropriate, provided they are not mutually inconsistent. [Explanation of Symbols]

[0080] 1... Air conditioner, 20... Indoor unit, 21... Housing, 22c... Outlet, 27... Rear wall section, 27a... First rear wall section, 27c... Second rear wall section, 28... Gutter section, 31... Suction port, 32... Front wall section, 4 1... Heat exchanger, 42... Front heat exchanger, 43... Rear heat exchanger, 45... Air blower, 47... Drain pan, 48... Bottom, 49... Side wall, 49a... Front wall, 49c... Rear wall, 50... Air path, 5 1…Front air passage, 52…Rear air passage, 60…Filter, G1…First interval (distance in the front-rear direction between the upper vertical end of the front wall and the front wall), G2…Second interval (distance between the drain pan and the second rear wall), G3…Third interval (distance in the front-rear direction between the upper vertical end of the rear wall and the first rear wall), T1…Front-rear dimension of the rear wall, T2…Front-rear dimension of the front wall

Claims

1. It is an indoor unit of an air conditioner, and is a floor-standing indoor unit. Heat exchanger, A blower that generates an airflow passing through the heat exchanger, A drain pan is positioned vertically below the heat exchanger, The air passage through which the aforementioned airflow flows, A housing that houses the heat exchanger, the blower, and the drain pan, Equipped with, The aforementioned housing is A front wall portion positioned in front of the heat exchanger and the drain pan, A rear wall portion positioned behind the heat exchanger and the drain pan, An intake port is provided in the portion of the front wall that is vertically lower than the blower, An outlet is provided vertically above the aforementioned blower, It has, The heat exchanger comprises a front heat exchanger and a rear heat exchanger positioned behind the front heat exchanger. The aforementioned air passage is A portion of which is formed between the drain pan and the front wall portion, and a front air passage through which the airflow from the intake port toward the front heat exchanger flows, A portion of which is formed between the drain pan and the rear wall portion, and a rear air passage through which the airflow from the intake port toward the rear heat exchanger flows, Includes, The aforementioned rear wall portion is A first rear wall portion extending vertically and facing the drain pan in the front-rear direction, A second rear wall portion is connected to the lower end of the first rear wall portion and is located towards the front as it extends vertically downward, It has, The drain pan has a bottom portion that extends in a direction perpendicular to the vertical direction, a front wall portion that protrudes vertically upward from the front end of the bottom portion, and a rear wall portion that protrudes vertically upward from the rear end of the bottom portion. If G1 is the distance in the front-rear direction between the upper vertical end of the front side wall and the front wall, and G2 is the distance between the drain pan and the second rear wall, An indoor unit that satisfies the relationship 0.50 ≤ G2 / (G1 + G2) ≤ 0.

60.

2. If G3 is the distance in the front-rear direction between the upper vertical end of the rear side wall portion and the first rear wall portion, The indoor unit according to claim 1, satisfying the relationship 0.40 ≤ G3 / (G1 + G3) ≤ 0.

60.

3. The indoor unit according to claim 1 or 2, wherein the front-to-rear dimension of the rear side wall is smaller than the front-to-rear dimension of the front side wall.

4. The rear wall portion has a gutter portion that protrudes forward from the first rear wall portion. The indoor unit according to claim 1 or 2, wherein, in the vertical direction, the gutter portion is positioned vertically above the drain pan.

5. The indoor unit according to claim 1 or 2, further comprising a filter arranged in the air passage for collecting dust contained in the airflow.

6. An indoor unit according to claim 1 or 2, An outdoor unit connected to the indoor unit by a circulation path through which refrigerant circulates, An air conditioner equipped with [a specific feature].

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