JPWO2020165973A1 - Indoor unit of air conditioner and air conditioner - Google Patents

Abstract

A casing in which a suction port is formed in the upper part and an air outlet is formed in the lower part, a blower that creates an air flow from the suction port to the air outlet, and a heat exchanger provided between the blower and the air outlet in the casing. Indoor unit of air conditioner equipped with. The heat exchanger has a plurality of heat transfer portions including a plurality of heat transfer tubes arranged at intervals and a plurality of fin portions which are laminated at intervals and through which the plurality of heat transfer tubes penetrate. The heat transfer section includes a first heat transfer section arranged on the most wind side and a second heat transfer section arranged on the leeward side of the first heat transfer section, and ventilates the first heat transfer section. The resistance is larger than the ventilation resistance of the second heat transfer section.

Description

The present invention relates to an indoor unit and an air conditioner of an air conditioner provided with a heat exchanger that exchanges heat between air and a refrigerant.

In a suction type indoor unit where the fan is installed on the leeward side of the heat exchanger, the front heat exchanger located in front of the casing is closer to the fan than the rear heat exchanger located behind the casing. .. Therefore, the front heat exchanger is easier for air to pass through than the back heat exchanger (see, for example, Patent Document 1). Further, in a push-in type indoor unit in which a fan is installed on the windward side of a heat exchanger, the wind speed at the center of the fan tends to be relatively low, and the wind speed at the blades of the fan tends to be relatively high. .. Therefore, the wind speed distribution of the air passing through the heat exchanger varies depending on the positional relationship with the fan.

Japanese Unexamined Patent Publication No. 2010-65599

In this way, if the air velocity distribution of the air passing through the heat exchanger varies, the load distribution to the refrigerant passing through each heat transfer tube becomes uneven, resulting in an imbalance in the amount of heat exchange in the heat exchanger. Heat exchange performance is reduced.

The present invention has been made to solve the above problems, and an object of the present invention is to provide an indoor unit and an air conditioner of an air conditioner that improve heat exchange performance in a heat exchanger.

The indoor unit of the air conditioner according to the present invention is provided between a casing having a suction port formed at the upper part and an air outlet formed at the lower part and between the suction port and the air outlet in the casing, and blows from the suction port. A blower that creates an air flow toward the outlet and a heat exchanger provided between the blower and the outlet in the casing are provided, and the heat exchangers are spaced by a plurality of heat transfer tubes arranged at intervals. It has a plurality of fin portions including a plurality of fin portions through which a plurality of heat transfer tubes penetrate, and the plurality of heat transfer portions are the first heat transfer portion arranged on the most wind side. It has a second heat transfer section arranged on the leeward side of the first heat transfer section, and the ventilation resistance of the first heat transfer section is larger than the ventilation resistance of the second heat transfer section.

The air conditioner according to the present invention includes the above-mentioned indoor unit and an outdoor unit including a compressor, an expansion valve, and a heat source side heat exchanger, and also includes a compressor, a heat exchanger, an expansion valve, and a heat source side. It has a refrigerant circuit formed by connecting heat exchangers with refrigerant pipes.

According to the present invention, since the ventilation resistance of the first heat transfer portion on the uppermost wind side is larger than the ventilation resistance of the second heat transfer portion, it is possible to alleviate the variation in the wind velocity distribution of the air passing through the heat exchanger. Therefore, the heat exchange performance of the heat exchanger can be improved.

FIG. 5 is a schematic configuration diagram illustrating the overall configuration of the air conditioner according to the first embodiment of the present invention. It is a front view of the indoor unit of FIG. It is a schematic cross-sectional view along the line AA of the indoor unit of FIG. It is explanatory drawing which shows the heat exchanger and the load side blower shown in FIG. 3, and the wind speed distribution corresponding thereto. It is a top view of the heat exchanger of FIG. It is explanatory drawing which shows the mode that the air passes through the free passage region of the heat exchanger of FIG. It is schematic cross-sectional view of the heat exchanger which the indoor unit of the air conditioner which concerns on Embodiment 2 of this invention has. It is a front view of the heat exchanger of FIG. It is a perspective view of the heat exchanger of FIG. It is schematic cross-sectional view of the heat exchanger which the indoor unit of the air conditioner which concerns on Embodiment 3 of this invention has. It is a front view of the heat exchanger of FIG. It is a perspective view of the heat exchanger of FIG. It is schematic cross-sectional view of the indoor unit of the air conditioner which concerns on Embodiment 4 of this invention. It is a top view of the heat exchange unit of FIG. It is explanatory drawing which shows the mode that the air passes through the free passage region of the heat exchange unit of FIG. It is a schematic cross-sectional view of the heat exchange unit which the indoor unit of the air conditioner which concerns on the modification 4-1 of Embodiment 4 of this invention has. It is the schematic sectional drawing of the indoor unit of the air conditioner which concerns on Embodiment 5 of this invention. It is a top view of the heat exchange unit of FIG. It is schematic cross-sectional view of the heat exchange unit which the indoor unit of the air conditioner which concerns on modification 5-1 of Embodiment 5 of this invention has.

Embodiment 1.
FIG. 1 is a schematic configuration diagram illustrating the overall configuration of the air conditioner according to the first embodiment of the present invention. The overall configuration of the air conditioner 500 will be described with reference to FIG. When explaining the contents common to the equivalent constituent members, the reference numerals may be omitted. The same applies to each embodiment described later.

As shown in FIG. 1, the air conditioner 500 includes an indoor unit 100 installed indoors and an outdoor unit 200 installed outdoors. The indoor unit 100 and the outdoor unit 200 are connected by a refrigerant pipe R.

The indoor unit 100 includes a heat exchanger 10 and a blower 50. The heat exchanger 10 is composed of, for example, a fin-and-tube heat exchanger, and exchanges heat between indoor air and a refrigerant. The blower 50 is attached to the heat exchanger 10 and sends air to the heat exchanger 10. In the first embodiment, an example is shown in which the indoor unit 100 has two blowers 50.

The outdoor unit 200 includes a compressor 61, a four-way valve 62, an expansion valve 63, a heat source side heat exchanger 64, and a heat source side blower 70. The compressor 61 is driven by, for example, an inverter to compress the refrigerant. The four-way valve 62 is connected to the discharge side of the compressor 61 to switch the flow path of the refrigerant. For example, the four-way valve 62 is switched to the solid line flow path of FIG. 1 during the heating operation, and is switched to the broken line flow path of FIG. 1 during the cooling operation and the defrosting operation. The expansion valve 63 is composed of, for example, an electronic expansion valve, and decompresses and expands the refrigerant. The heat source side heat exchanger 64 is composed of, for example, a fin and tube type heat exchanger, and exchanges heat between the outside air and the refrigerant. The heat source side blower 70 is attached to the heat source side heat exchanger 64 and sends air to the heat source side heat exchanger 64.

That is, the air conditioner 500 has a refrigerant circuit 80 formed by connecting a compressor 61, a four-way valve 62, a heat exchanger 10, an expansion valve 63, and a heat source side heat exchanger 64 by a refrigerant pipe R. There is. During the heating operation, the heat exchanger 10 functions as a condenser, and the heat source side heat exchanger 64 functions as an evaporator. During the cooling operation, the heat exchanger 10 functions as an evaporator, and the heat source side heat exchanger 64 functions as a condenser.

FIG. 2 is a front view of the indoor unit of FIG. FIG. 3 is a schematic cross-sectional view taken along the line AA of the indoor unit of FIG. FIG. 2 shows an example in which the indoor unit 100 is attached to the wall 800 in the room. In FIGS. 2 and 3, the front-rear direction of the casing 101 corresponds to the x-axis direction, the left-right direction of the casing 101 corresponds to the y-axis direction, and the vertical direction of the casing 101 corresponds to the z-axis direction. In particular, the x-axis positive direction corresponds to the front direction of the casing 101, and the x-axis negative direction corresponds to the rear direction of the casing 101. Further, the z-axis positive direction corresponds to the downward direction of the casing 101, and the z-axis negative direction corresponds to the upward direction of the casing 101. The same applies to the following figures. In the first embodiment, the heat transfer tube group is shown only in FIG. 3 in order to avoid complicating the drawings.

As shown in FIGS. 2 and 3, the indoor unit 100 has a casing 101 in which the suction port 102 is formed in the upper portion and the air outlet 103 is formed in the lower portion. The blower 50 is provided between the suction port 102 and the air outlet 103 in the casing 101, and creates an air flow from the suction port 102 toward the air outlet 103. The heat exchanger 10 is provided between the blower 50 and the outlet 103 in the casing 101. Therefore, the air sucked from the suction port 102 flows in the casing 101 and is blown out from the air outlet 103 as shown by the white arrow in FIG. That is, the air sucked from the suction port 102 passes through the heat exchanger 10 in the positive direction of the z-axis. Hereinafter, the z-axis positive direction is also referred to as a “ventilation direction”.

The heat exchanger 10 has a plurality of heat transfer portions including a plurality of heat transfer tubes arranged at intervals and a plurality of fin portions which are laminated at intervals and through which the plurality of heat transfer tubes penetrate. There is. In the first embodiment, the plurality of heat transfer units include a first heat transfer unit 11 arranged on the windward side and a second heat transfer unit 12 arranged on the leeward side of the first heat transfer unit 11. It is composed of.

The first heat transfer portion 11 includes a plurality of heat transfer tubes 11a arranged at intervals, and a plurality of fin portions 11b laminated at intervals and penetrated by the plurality of heat transfer tubes 11a. The first heat transfer unit 11 has a heat transfer tube group 11 g composed of a row of heat transfer tubes 11a. In the heat transfer tube group 11g, a plurality of heat transfer tubes 11a are arranged at predetermined intervals along the same direction. Further, the second heat transfer portion 12 includes a plurality of heat transfer tubes 12a arranged at intervals, and a plurality of fin portions 12b laminated at intervals and through which the plurality of heat transfer tubes 12a penetrate. .. The second heat transfer unit 12 has a heat transfer tube group 12 g composed of a row of heat transfer tubes 12a. The heat transfer tube group 12g is a group in which a plurality of heat transfer tubes 12a are arranged at predetermined intervals along the same direction.

The ventilation resistance of the first heat transfer portion 11 on the leeward side is larger than the ventilation resistance of the second heat transfer portion 12 on the leeward side. In the heat exchanger 10 of the first embodiment, the outer diameter O ₁ of each heat transfer tube 11a of the first heat transfer section 11 is larger than _{the outer diameter O 2} of each heat transfer tube 12a of the second heat transfer section 12. ing. That is, the ratio of the outer diameter O ₁ to the outer diameter O _{2 (O 1} / O ₂ ) is a value larger than 1. The ratio of the outer diameter O ₁ to the outer diameter O _2, i.e. the outer diameter O ₂ of the outer diameter O ₁ and the heat transfer tube 12a of the heat transfer tube 11a, when appropriately changed depending on the capacity zone and load conditions of the air conditioner 500 good. In the first embodiment, the fin portion 11b and the fin portion 12b are integrally formed to form one fin.

FIG. 4 is an explanatory diagram showing the heat exchanger and the load side blower shown in FIG. 3 and the wind speed distribution corresponding thereto. More specifically, FIG. 4A is a diagram showing the heat exchanger 10 and the blower 50 extracted from FIG. In FIG. 4B, with respect to the heat exchanger 10 of FIG. 4A, the position in the x-axis direction is taken on the horizontal axis, and the wind speed corresponding to the position in the x-axis direction is taken on the vertical axis.

In FIG. 4B, the graph D ₀ shown by the broken line shows the wind speed distribution on the assumption that the outer diameter of the heat transfer tube 11a and the outer diameter of the heat transfer tube 12a in the heat exchanger 10 are tentatively equalized. On the other hand, graph D ₁ indicated by a solid line in FIG. 4 (b) is a graph illustrating the air velocity distribution in the heat exchanger 10 of the first embodiment. In the heat exchanger 10 of the first embodiment, the outer diameter O ₁ of each heat transfer tube 11a of the first heat transfer section 11 is larger than _{the outer diameter O 2} of each heat transfer tube 12a of the second heat transfer section 12. Therefore, the ventilation resistance of the first heat transfer unit 11 is larger than the ventilation resistance of the second heat transfer unit 12. Therefore, as in the graph D ₁ of the FIG. 4 (b), the can mitigate variations in the velocity distribution of the air passing through the heat exchanger 10.

FIG. 5 is a plan view of the heat exchanger of FIG. FIG. 6 is an explanatory view showing how air passes through the free passage region of the heat exchanger of FIG.

As shown in FIG. 5, a gap is formed between the adjacent heat transfer tubes 11a and the heat transfer tubes 12a in a plan view. In FIG. 5, in a plan view, the distance between the heat transfer tubes 11a and the heat transfer tubes 12a arranged along the x-axis positive direction is defined as the width S, and the distance between the heat transfer tubes 12a and the heat transfer tubes 11a arranged along the x-axis positive direction is defined as the width S. The width is T. The width S and the width T may be different or equal.

In the indoor unit 100, the air sent from the blower 50 freely passes through each space of width S and each space of width T along the y-axis direction of the heat exchanger 10, as shown by the white arrows in FIG. be able to. That is, each space having a width S and each space having a width T along the y-axis direction of the heat exchanger 10 are free passage regions through which the air sent from the blower 50 can freely pass. The free passage region is a region in which the air flowing into the heat exchanger 10 in the vertical direction passes through the heat exchanger 10 without contacting the heat transfer tube. On the other hand, the first heat transfer portion 11, prevents the passage of air sent from the blower 50 through the heat transfer tube 11a having an outer diameter of O _1. The second heat transfer portion 12, prevents the passage of air sent from the blower 50 through the heat transfer tube 12a having an outer diameter of O _2.

As described above, in the heat exchanger 10 of the first embodiment, the ventilation resistance of the first heat transfer unit 11 arranged on the windward side is arranged on the leeward side of the first heat transfer unit 11. 2 It is larger than the ventilation resistance of the heat transfer unit 12. In other words, the heat exchanger 10, the outer diameter _{O 1} of each heat transfer tube 11a of the first heat transfer portion 11 is larger than the outer diameter _{O 2} of each heat transfer tube 12a of the second heat transfer portion 12. Therefore, since the air pressure loss due to the heat transfer tube group 11 g is larger than the air pressure loss due to the heat transfer tube group 12 g, it is possible to alleviate the variation in the air velocity distribution of the air passing through the heat exchanger 10. The heat exchange performance of the heat exchanger 10 can be improved.

In the above description, the case where the first heat transfer section 11 includes a row of heat transfer tube groups 11 g and the second heat transfer section 12 includes a row of heat transfer tube groups 12 g is illustrated, but the present invention is not limited thereto. The first heat transfer unit 11 may include a plurality of rows of heat transfer tube groups 11 g, and the second heat transfer unit 12 may include a plurality of rows of heat transfer tube groups 12 g. That is, at least one of the first heat transfer section 11 and the second heat transfer section 12 may include a plurality of rows of heat transfer tube groups.

For example, in the heat exchanger 10, the heat transfer tube group 11g of the first heat transfer section 11 is combined into one, the heat transfer tube group 12g of the second heat transfer section 12 is combined into two, and so on. The number may be less than the number of rows of the heat transfer tube group 12 g. Further, in the heat exchanger 10, the heat transfer tube group 11g of the first heat transfer section 11 is combined into two, the heat transfer tube group 12g of the second heat transfer section 12 is combined into one, and so on. The number may be larger than the number of rows of the heat transfer tube group 12 g. In this way, the ventilation resistance of the heat exchanger 10 can be adjusted according to the structure of the indoor unit 100 and the characteristics of the actuator such as the blower 50. Therefore, the wind speed distribution of the air passing through the heat exchanger 10 The variation can be alleviated more accurately.

Here, in the heat exchanger 10, the number of heat transfer tubes constituting each heat transfer tube group is not limited to the example in each figure, and can be appropriately changed according to the capacity band of the air conditioner 500, the load conditions, and the like. .. Further, the ventilation resistance of the heat exchanger 10 may be adjusted by combining the change in the number of heat transfer tubes constituting each heat transfer tube group and the change in the ratio of the outer diameter O _{1 to the outer diameter O 2.} Incidentally, changing the ratio of the outer diameter O ₁ to the outer diameter O ₂ can be performed by changing at least one of the outer diameter O ₂ of the outer diameter O ₁ and the heat exchanger tube 12a of the heat transfer tube 11a. The same applies to each embodiment described later.

The numbers of the fin portions 11b and the fin portions 12b are not limited to the examples of FIGS. 2 and 5, and can be appropriately changed according to the size of the heat exchanger 10 and the like. Further, in FIGS. 2 to 6, the vertical width of the fin portion 11b and the vertical width of the fin portion 12b are equal to each other, but the present invention is not limited to this. In the heat exchanger 10, the vertical width of the fin portion 11b may be longer than the vertical width of the fin portion 12b, or may be shorter than the vertical width of the fin portion 12b. Further, FIGS. 2 to 6 show an example in which the thickness of the fin portion 11b in the left-right direction is equal to the thickness of the fin portion 12b in the left-right direction, but the present invention is not limited to this. In the heat exchanger 10, the thickness of the fin portion 11b in the left-right direction may be thicker than the thickness of the fin portion 12b in the left-right direction, or may be thinner than the thickness of the fin portion 112b in the left-right direction.

Embodiment 2.
FIG. 7 is a schematic cross-sectional view of a heat exchanger included in the indoor unit of the air conditioner according to the second embodiment of the present invention. FIG. 8 is a front view of the heat exchanger of FIG. 7. 9 is a perspective view of the heat exchanger of FIG. 7. FIG. The configuration of the air conditioner in the second embodiment is the same as the examples of FIGS. 1 to 3 used in the above-described first embodiment. The configuration of the heat exchanger 110 of the second embodiment will be described with reference to FIGS. 7 to 9. The same reference numerals are used for the components equivalent to those in the first embodiment, and the description thereof will be omitted.

The heat exchanger 110 is a first heat transfer unit 111 including a plurality of heat transfer tubes 111a arranged at intervals and a plurality of fin portions 111b laminated at intervals and through which the plurality of heat transfer tubes 111a penetrate. have. The first heat transfer unit 111 has a heat transfer tube group 111 g composed of a row of heat transfer tubes 111a. Further, the heat exchanger 110 includes a plurality of heat transfer tubes 112a arranged at intervals and a plurality of fin portions 112b which are laminated at intervals and through which the plurality of heat transfer tubes 112a penetrate. It has a part 112. The second heat transfer unit 112 has a heat transfer tube group 112 g composed of a row of heat transfer tubes 112a.

The ventilation resistance of the first heat transfer portion 111 on the leeward side is larger than the ventilation resistance of the second heat transfer portion 112 on the leeward side. In the heat exchanger 110 of the second embodiment, the interval _{P 1} between each fin portion 111b of the first heat transfer portion 111 arranged on the windward side, each fin portion 112b of the second heat transfer portion 112 of the leeward It is smaller than the distance P ₂ of each other. That is, the ratio of the interval P _{1 to the interval P 2 (P 1} / P ₂ ) is smaller than 1. For example, the interval _{P 1} and the interval _{P 2,} the ratio of spacing _{P 1} relative spacing _{P 2} is set to be approximately from 0.83 to 0.92. However, the ratio of the distance P ₁ relative spacing P _2, that is, the distance P ₁ and spacing P _2, can be appropriately changed depending on the capacity zone and load conditions of the air conditioning apparatus 500. The fin portion 111b and the fin portion 112b are formed as separate bodies.

In this way, in a plan view, the area of the fin portion 111b is larger than the area of the fin portion 112b, so that the ventilation resistance of the first heat transfer portion 111 is larger than the ventilation resistance of the second heat transfer portion 112. Become. Therefore, similar to the graph D ₁ illustrated in FIG. 4 (b), it is possible to alleviate the variation of the velocity distribution of the air passing through the heat exchanger 110.

As described above, in the heat exchanger 110 of the second embodiment, the ventilation resistance of the first heat transfer unit 111 arranged on the windward side is arranged on the leeward side of the first heat transfer unit 111. 2 It is larger than the ventilation resistance of the heat transfer unit 112. That is, in the heat exchanger 110, the distance between the fins 111b of the first heat transfer unit 111 is smaller than the distance between the fins 112b of the second heat transfer unit 112. Therefore, since the air pressure loss due to the plurality of fin portions 111b is larger than the air pressure loss due to the plurality of fin portions 112b, it is possible to alleviate the variation in the air velocity distribution of the air passing through the heat exchanger 110. Therefore, the heat exchange performance can be improved.

Here, in FIGS. 7 to 9, the vertical width of the fin portion 111b and the vertical width of the fin portion 112b are equal to each other, but the present invention is not limited to this. In the heat exchanger 110, the vertical width of the fin portion 111b may be longer than the vertical width of the fin portion 112b, or may be shorter than the vertical width of the fin portion 112b. In this way, the ventilation resistance of the heat exchanger 110 can be adjusted by changing the vertical widths of the fin portion 111b and the fin portion 112b according to the characteristics of the actuator such as the blower 50 and the structure of the indoor unit 100. Therefore, the variation in the wind speed distribution of the air passing through the heat exchanger 10 can be mitigated more accurately.

In the second embodiment, the case where the first heat transfer section 111 includes a row of heat transfer tube groups 111 g and the second heat transfer section 112 includes a row of heat transfer tube groups 112 g is illustrated, but the present invention is limited to this. Not done. The first heat transfer unit 111 may include a plurality of heat transfer tube groups 111 g, and the second heat transfer unit 112 may include a plurality of heat transfer tube groups 112 g. That is, at least one of the first heat transfer unit 111 and the second heat transfer unit 112 may include a plurality of heat transfer tube groups. For example, the number of rows of each heat transfer tube group may be adjusted according to the width of the fin portion 111b and the fin portion 112b in the vertical direction.

Further, FIGS. 7 to 9 show an example in which the thickness of the fin portion 111b in the left-right direction is equal to the thickness of the fin portion 112b in the left-right direction, but the present invention is not limited to this. In the heat exchanger 110, the thickness of the fin portion 111b in the left-right direction may be thicker than the thickness of the fin portion 112b in the left-right direction, or may be thinner than the thickness of the fin portion 112b in the left-right direction. In this way, the variation in the wind speed distribution of the air passing through the heat exchanger 10 can be alleviated more accurately.

However, the numbers of the fin portions 111b and the fin portions 112b are not limited to the examples of FIGS. 8 and 9, and can be appropriately changed according to the size of the heat exchanger 110 and the like. Further, the respective number of changes of the fin portion 111b and the fin part 112b, by combining the change in the ratio between the interval P ₁ relative spacing P _2, may adjust the air flow resistance of the heat exchanger 110.

Embodiment 3.
FIG. 10 is a schematic cross-sectional view of a heat exchanger included in the indoor unit of the air conditioner according to the third embodiment of the present invention. FIG. 11 is a front view of the heat exchanger of FIG. FIG. 12 is a perspective view of the heat exchanger of FIG. The configuration of the air conditioner according to the third embodiment is the same as the examples of FIGS. 1 to 3 used in the above-described first embodiment. The configuration of the heat exchanger 210 according to the third embodiment will be described with reference to FIGS. 10 to 12. The same reference numerals are used for the components equivalent to those of the first and second embodiments, and the description thereof will be omitted.

The heat exchanger 210 is a first heat transfer unit 211 including a plurality of heat transfer tubes 11a arranged at intervals and a plurality of fin portions 111b which are laminated at intervals and through which the plurality of heat transfer tubes 11a penetrate. have. The first heat transfer unit 211 has a heat transfer tube group 11 g composed of a row of heat transfer tubes 11a. Further, the heat exchanger 210 includes a plurality of heat transfer tubes 12a arranged at intervals and a plurality of fin portions 112b which are laminated at intervals and through which the plurality of heat transfer tubes 12a penetrate. It has a part 212. The second heat transfer unit 212 has a heat transfer tube group 12 g composed of a row of heat transfer tubes 12a. In the third embodiment, the fin portion 111b and the fin portion 112b are formed as separate bodies.

The ventilation resistance of the first heat transfer portion 211 on the leeward side is larger than the ventilation resistance of the second heat transfer portion 212 on the leeward side. That is, in the heat exchanger 210, the outer diameter O ₁ of each heat transfer tube 11a of the first heat transfer section 211 is larger than _{the outer diameter O 2} of each heat transfer tube 12a of the second heat transfer section 212. In the heat exchanger 210, the interval _{P 1} between each fin portion 111b of the first heat transfer portion 211 which is disposed on the windward side, the distance P of each fin portion 112b to each other of the second heat transfer portion 212 of the leeward _It is smaller than 2.

The ratio of the outer diameter O ₁ to the outer diameter O ₂ of the heat exchanger 210 is smaller than the ratio of the outer diameter O _{1 to the outer diameter O 2} of the heat exchanger 10 in the first embodiment. The ratio of the distance _{P 1} relative spacing _{P 2} of the heat exchanger 210 is greater than the ratio of the distance _{P 1} relative spacing _{P 2} of the heat exchanger 110 in the second embodiment. The heat exchanger 210, the ratio of the outer diameter O ₁ to the outer diameter O _2, by adjusting the ratio of the distance P ₁ relative spacing P _2, the variation in the velocity distribution of the air passing through the heat exchanger 210, It can be relaxed more accurately. Other configurations and alternative configurations of the heat exchanger 210 are similar to the heat exchanger 10 of the first embodiment and the heat exchanger 110 of the second embodiment.

As described above, in the heat exchanger 210 of the third embodiment, the ventilation resistance of the first heat transfer unit 211 on the windward side is larger than the ventilation resistance of the second heat transfer unit 212. _{That is, the outer diameter O 1} of each heat transfer tube 11a of the first heat transfer section 211 is larger than _{the outer diameter O 2} of each heat transfer tube 12a of the second heat transfer section 212. Further, the distance between the fin portions 11b of the first heat transfer portion 211 is smaller than the distance between the fin portions 12b of the second heat transfer portion 212. Therefore, since the air pressure loss by the first heat transfer unit 211 is larger than the air pressure loss by the second heat transfer unit 212, it is possible to alleviate the variation in the wind velocity distribution in the heat exchanger 210. The heat exchange performance can be improved.

Embodiment 4.
FIG. 13 is a schematic cross-sectional view of an indoor unit of the air conditioner according to the fourth embodiment of the present invention. FIG. 14 is a plan view of the heat exchange unit of FIG. FIG. 15 is an explanatory view showing how air passes through the free passage region of the heat exchange unit of FIG. The configuration of the air conditioner in the fourth embodiment is the same as the examples of FIGS. 1 and 2 used in the above-described first embodiment. That is, the air conditioner 500 according to the fourth embodiment has a refrigerant circuit 80 formed by connecting a compressor 61, a heat exchange unit 310V, an expansion valve 63, and a heat source side heat exchanger 64 by a refrigerant pipe R. doing. The configuration of the heat exchange unit 310V according to the fourth embodiment will be described with reference to FIGS. 13 to 15. The same reference numerals are used for the components equivalent to those of the first to third embodiments, and the description thereof will be omitted. Further, in FIGS. 13 to 15, one of the reference numerals of the constituent members overlapping between the first heat exchanger 10A and the second heat exchanger 10B is partially omitted.

The heat exchange unit 310V is composed of a first heat exchanger 10A provided on the front side in the casing 101 and a second heat exchanger 10B provided on the rear side in the casing 101. That is, the second heat exchanger 10B is arranged behind the first heat exchanger 10A. The first heat exchanger 10A and the second heat exchanger 10B are configured in the same manner as the heat exchanger 10 of the first embodiment described above.

The first heat exchanger 10A and the second heat exchanger 10B are arranged in a V-shape in cross section so that the distance between the surfaces facing each other becomes shorter from the windward side to the leeward side. That is, the distance between the inner surface 31A of the first heat exchanger 10A and the inner surface 31B of the second heat exchanger 10B is shortened from the windward side to the leeward side. The inner surface 31A and the inner surface 31B are virtual surfaces in which the end faces of the plurality of fin portions 11b and the gaps between the fin portions 11b are combined.

As shown in FIG. 14, the first heat exchanger 10A in a plan view, the gap width U ₁ between the two heat transfer tubes 11a of the rear side is formed, between the two front heat transfer tube 12a A gap having a width of U _{2 is formed.} Further, the second heat exchanger 10B, in plan view, the two front gap width U ₁ between the heat transfer tubes 11a are formed, behind the wide U ₂ between the two heat transfer tubes 12a A gap is formed. That is, in the indoor unit 100 of the fourth embodiment, the air sent from the blower 50 is a space having _{a width U 1} along the y-axis direction of the first heat exchanger 10A and as shown by the white arrow in FIG. It can freely pass through the space of width U _{2. That is, the space of the width U 1 and} the space of the width U ₂ along the y-axis direction of the first heat exchanger 10A are free passage regions through which the air sent from the blower 50 can freely pass. Further, in the indoor unit 100 of the fourth embodiment, the air sent from the blower 50 is a space having _{a width U 1} along the y-axis direction of the second heat exchanger 10B as shown by the white arrows in FIG. It can freely pass through the space of width U _{2. That is, the space of the width U 1 and} the space of the width U ₂ along the y-axis direction of the second heat exchanger 10B are free passage regions through which the air sent from the blower 50 can freely pass.

On the other hand, in each of the first heat exchanger 10A and the second heat exchanger 10B, the adjacent heat transfer tubes are viewed in plan view, and at least one heat transfer tube of one heat transfer tube group is one of the other heat transfer tubes. Or it overlaps with the heat transfer tube of 2. That is, in both the first heat exchanger 10A and the second heat exchanger 10B, in a plan view, at least one heat transfer tube of one heat transfer tube group is a heat transfer tube of 1 or 2 of the other heat transfer tube group. They are arranged so as to overlap each other so as to form a predetermined inclination angle with respect to the ventilation direction.

In the example of FIGS. 13 to 15, in the first heat exchanger 10A, in a plan view, a part of the uppermost heat transfer tube 11a of the heat transfer tube group 11g is a part of the lower two heat transfer tubes 12a of the heat transfer tube group 12g. It overlaps with a part. Further, in the first heat exchanger 10A, in a plan view, a part of the second heat transfer tube 11a from the top of the heat transfer tube group 11g overlaps with a part of the lowermost heat transfer tube 12a of the heat transfer tube group 12g. There is. In other words, in the first heat exchanger 10A, in a plan view, a part of the lowermost heat transfer tube 12a of the heat transfer tube group 12g overlaps with a part of the upper two heat transfer tubes 11a of the heat transfer tube group 11g. There is. Further, in the first heat exchanger 10A, in a plan view, a part of the second heat transfer tube 12a from the bottom of the heat transfer tube group 12g overlaps with a part of the uppermost heat transfer tube 11a of the heat transfer tube group 11g. ..

Similarly, in the second heat exchanger 10B, in a plan view, a part of the uppermost heat transfer tube 11a of the heat transfer tube group 11g overlaps a part of the lower two heat transfer tubes 12a of the heat transfer tube group 12g. .. Further, in the second heat exchanger 10B, in a plan view, a part of the second heat transfer tube 11a from the top of the heat transfer tube group 11g overlaps with a part of the lowermost heat transfer tube 12a of the heat transfer tube group 12g. There is. In other words, in the second heat exchanger 10B, in a plan view, a part of the lowermost heat transfer tube 12a of the heat transfer tube group 12g overlaps with a part of the upper two heat transfer tubes 11a of the heat transfer tube group 11g. There is. Further, in the second heat exchanger 10B, in a plan view, a part of the second heat transfer tube 12a from the bottom of the heat transfer tube group 12g overlaps with a part of the uppermost heat transfer tube 11a of the heat transfer tube group 11g. ..

Here, the outer diameter O ₂ of the heat transfer tube 12a is smaller than _{the outer diameter O 1} of the heat transfer tube 11a. Therefore, in the first heat exchanger 10A and the second heat exchanger 10B, the entire heat transfer tube 12a of the heat transfer tube group 12g may be a heat transfer tube depending on the inclination angle with respect to the ventilation direction and the arrangement of the heat transfer tube 11a and the heat transfer tube 12a. It will overlap with a part of the heat transfer tube 11a of the group 11g.

As described above, in the heat exchange unit 310V of the fourth embodiment, the ventilation resistance of the first heat transfer unit 11 arranged on the most upwind side is arranged on the leeward side of the first heat transfer unit 11. 2 It is larger than the ventilation resistance of the heat transfer unit 12. In other words, the heat exchange unit 310V, the outer diameter _{O 1} of each heat transfer tube 11a of the first heat transfer portion 11 is larger than the outer diameter _{O 2} of each heat transfer tube 12a of the second heat transfer portion 12. Therefore, since the air pressure loss due to the heat transfer tube group 11g is larger than the air pressure loss due to the heat transfer tube group 11g, it is possible to alleviate the variation in the air velocity distribution of the air passing through the heat exchange unit 310V. The heat exchange performance can be improved.

By the way, when the heat exchangers are arranged so that the heat transfer tubes are parallel to each other in the left-right direction as in the above-described first to third embodiments, the adjacent heat transfer tubes are arranged as illustrated in FIGS. 5 and 6. In the plan view of, free passage regions exist at regular intervals between each heat transfer tube of one heat transfer tube group and each heat transfer tube of the other heat transfer tube group. In this regard, in the heat exchange unit 310V, in each of the first heat exchanger 10A and the second heat exchanger 10B, the adjacent heat transfer tubes are viewed in plan view, and at least one heat transfer tube of one heat transfer tube group is used. It overlaps with one or two heat transfer tubes of the other heat transfer tube group. That is, if the heat exchanger is arranged as in the fourth embodiment, the free passage area is reduced as compared with the case where the heat exchanger is arranged as in the first to third embodiments, so that the heat exchanger flows into the heat exchanger. Since the air easily comes into contact with the heat transfer tube, the heat exchange performance can be further improved.

In the case of a push-in type indoor unit in which air is pushed from the blower into the heat exchange unit, if the heat exchange unit has an inverted V shape in cross section, the air hits the upper part of the heat exchanger and flows from the outside to the inside, but the cross section V With the letter-shaped heat exchange unit 310V, air flows from the inside to the outside. That is, the indoor unit 100 of the fourth embodiment, which is a push-in type, has a heat exchange unit 310V in which the first heat exchanger 10A and the second heat exchanger 10B are arranged in a V shape in a cross-sectional view. .. Therefore, the ventilation resistance of the heat exchange unit 310V is smaller than that of the heat exchange unit having an inverted V shape in cross section. Therefore, according to the indoor unit 100, air can be efficiently passed through the heat exchange unit 310V, so that the heat exchange efficiency can be improved.

Here, the width U ₁ and the width U ₂ of the gap formed in the first heat exchanger 10A, the width U ₁ and the width U ₂ of a gap formed in the second heat exchanger 10B, may be equal , May be different. The inclination angle of the first heat exchanger 10A with respect to the ventilation direction and the inclination angle of the second heat exchanger 10B with respect to the ventilation direction may be equal or different. The same applies to each heat exchanger of the fifth embodiment described later.

By the way, FIGS. 13 to 15 show an example in which the first heat exchanger 10A and the second heat exchanger 10B are configured in the same manner as the heat exchanger 10 of the first embodiment, but the present invention is not limited thereto. For example, the first heat exchanger 10A and the second heat exchanger 10B may be configured in the same manner as the heat exchanger 110 of the second embodiment, or may be configured in the same manner as the heat exchanger 210 of the third embodiment. May be good.

<Modification 4-1>
FIG. 16 is a schematic cross-sectional view of a heat exchange unit included in the indoor unit of the air conditioner according to the modified example 4-1 of the fourth embodiment of the present invention. The air conditioner 500 in the modified example 4-1 has a refrigerant circuit 80 formed by connecting a compressor 61, a heat exchange unit 410V, an expansion valve 63, and a heat source side heat exchanger 64 by a refrigerant pipe R. ing. The heat exchange unit 410V has a first heat exchanger 410A provided on the front side in the casing 101 and a second heat exchanger 410B provided on the rear side in the casing 101. The first heat exchanger 410A and the second heat exchanger 410B are arranged so that the distance between the surfaces facing each other becomes shorter from the windward side to the leeward side.

The first heat exchanger 410A and the second heat exchanger 410B each include a secondary heat exchanger 411 including at least one heat transfer tube group 411 g and a main heat exchange including a plurality of heat transfer tube groups 412 g as two heat transfer units. It has a vessel 412 and. FIG. 16 illustrates a case where the auxiliary heat exchanger 411 has one heat transfer tube group 411 g and the main heat exchanger 412 has two heat transfer tube groups 412 g.

The sub heat exchanger 411 is arranged on the windward side of the main heat exchanger 412. The auxiliary heat exchanger 411 has a plurality of heat transfer tubes 11a arranged at intervals, and a plurality of fin portions 411b which are laminated at intervals and through which the plurality of heat transfer tubes 11a penetrate. The sub-heat exchanger 411 has a heat transfer tube group 411 g composed of a row of heat transfer tubes 11a. The main heat exchanger 412 is arranged on the leeward side of the sub heat exchanger 411. The main heat exchanger 412 has a plurality of heat transfer tubes 12a arranged at intervals, and a plurality of fin portions 412b which are laminated at intervals and through which the plurality of heat transfer tubes 12a penetrate. The main heat exchanger 412 has a heat transfer tube group 412 g composed of a row of heat transfer tubes 12a. The area of the surface of the fin portion 411b through which the heat transfer tube 11a penetrates is smaller than the area of the surface of the fin portion 412b through which the heat transfer tube 12a penetrates.

In the example of FIG. 16, the first heat exchanger 410A and the second heat exchanger 410B are both outside diameter _{O 1} of each heat transfer tube 11a of the auxiliary heat exchanger 411, the heat transfer tubes of the main heat exchanger 412 It is larger than the outer diameter O _{2 of 12a.} However, in the first heat exchanger 410A and the second heat exchanger 410B of the present modification 4-1 the distance between each fin portion 411b of the secondary heat exchanger 411 on the windward side is leeward, as in the third embodiment. It may be smaller than the distance between the fin portions 412b of the main heat exchanger 412 on the side. At that time, the first heat exchanger 410A and the second heat exchanger 410B of this modification 4-1, as in the second embodiment, the heat transfer tubes so that the outer diameter _{O 1} and the outer diameter of _{O 2} equal 11a And the heat transfer tube 12a may be configured.

In FIGS. 13 to 15, the case where the fin portions constituting each of the two or more heat transfer portions has the same shape is illustrated, but the present invention is not limited to this, and as in the example of FIG. 16, the two or more heat transfer portions have the same shape. The shapes of the fin portions constituting each of them may be different from each other. The configuration of the present modification 4-1 can also be applied to the configurations of the above-described embodiments 2 and 3. That is, the heat exchanger 110 may be a secondary heat exchanger in which the first heat transfer unit 111 includes at least one heat transfer tube group 111 g, and the second heat transfer unit 112 includes a plurality of heat transfer tube groups 112 g. It may be a main heat exchanger. Further, the heat exchanger 210 may be an auxiliary heat exchanger in which the first heat transfer unit 211 includes at least one heat transfer tube group 11 g, and the second heat transfer unit 212 includes a plurality of heat transfer tube groups 12 g. It may be a main heat exchanger.

Embodiment 5.
FIG. 17 is a schematic cross-sectional view of an indoor unit of the air conditioner according to the fifth embodiment of the present invention. FIG. 18 is a plan view of the heat exchange unit of FIG. The configuration of the air conditioner in the fifth embodiment is the same as the examples of FIGS. 1 and 2 used in the above-described first embodiment. That is, the air conditioner 500 according to the fifth embodiment includes a refrigerant circuit 80 formed by connecting a compressor 61, a heat exchange unit 510W, an expansion valve 63, and a heat source side heat exchanger 64 by a refrigerant pipe R. doing. FIG. 17 illustrates a state in which the indoor unit 100 is attached to the wall 800 in the room. The configuration of the heat exchange unit 510W according to the fifth embodiment will be described with reference to FIGS. 17 and 18. The same reference numerals are used for the constituent members equivalent to those of the first to fourth embodiments, and a description and a part of the reference numerals are omitted.

The heat exchange unit 510W of the fifth embodiment is the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchange arranged in order from the front to the rear in the casing 101. It has a vessel 510D.

The first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D are configured in the same manner as the heat exchanger 210 of the third embodiment. The positional relationship between the first heat exchanger 510A and the second heat exchanger 510B and the positional relationship between the third heat exchanger 510C and the fourth heat exchanger 510D are the first heat exchangers in the fourth embodiment, respectively. This is the same as the positional relationship between the 10A and the second heat exchanger 10B. The second heat exchanger 510B and the third heat exchanger 510C are arranged so that the distance between the surfaces facing each other increases from the windward side to the leeward side. That is, the heat exchange unit 510W is formed in a W shape as a whole by the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D. ..

As shown in FIGS. 17 and 18, in each of the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D, the adjacent heat transfer tubes are flat. Visually, at least one heat transfer tube in one heat transfer tube group overlaps one or two heat transfer tubes in the other heat transfer tube group. The inclination angles of the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D with respect to the vertical direction are the size of the casing 101 and the size of each heat exchanger. It is changed as appropriate according to the size.

In the examples of FIGS. 17 and 18, the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D are all the heat transfer portions 211. _{The outer diameter O 1} of the heat transfer tube 11a is larger than _{the outer diameter O 2} of each heat transfer tube 12a of the second heat transfer section 212. However, the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D of the fifth embodiment are the same as the heat exchanger 10 of the first embodiment. It may be configured, or may be configured in the same manner as the heat exchanger 110 of the second embodiment.

As described above, in the heat exchange unit 510W of the fifth embodiment, the ventilation resistance of the first heat transfer unit 211 arranged on the windward side is arranged on the leeward side of the first heat transfer unit 211. 2 It is larger than the ventilation resistance of the heat transfer unit 212. Therefore, since the air pressure loss due to the heat transfer tube group 11g is larger than the air pressure loss due to the heat transfer tube group 11g, it is possible to alleviate the variation in the air velocity distribution of the air passing through the heat exchange unit 510W. The heat exchange performance can be improved. Further, in the heat exchange unit 510W, in each of the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D, the adjacent heat transfer tubes are viewed in plan view. , At least one heat transfer tube of one heat transfer tube group overlaps with one or two heat transfer tubes of the other heat transfer tube group. According to the heat exchange unit 510W in which each heat exchanger is arranged in this way, the free passage area can be reduced as compared with the case where the heat exchangers are arranged parallel to the left-right direction. Therefore, the air flowing into each heat exchanger easily comes into contact with the heat transfer tube, so that the heat exchange performance can be further improved.

<Modification 5-1>
FIG. 19 is a schematic cross-sectional view of a heat exchange unit included in the indoor unit of the air conditioner according to the modified example 5-1 of the fifth embodiment of the present invention. The air conditioner 500 in the modified example 5-1 has a refrigerant circuit 80 formed by connecting a compressor 61, a heat exchange unit 610 W, an expansion valve 63, and a heat source side heat exchanger 64 by a refrigerant pipe R. ing. The heat exchange unit 610W has a first heat exchanger 610A, a second heat exchanger 610B, a third heat exchanger 610C, and a fourth heat exchanger 610D arranged in order from the front to the rear in the casing 101. There is.

The first heat exchanger 610A, the second heat exchanger 610B, the third heat exchanger 610C, and the fourth heat exchanger 610D are the same as the first heat exchanger 410A and the second heat exchanger 410B of the modified example 4-1. It is configured in the same way. The positional relationship between the first heat exchanger 610A and the second heat exchanger 610B and the positional relationship between the third heat exchanger 610C and the fourth heat exchanger 610D are the first heat exchanges in the modified example 4-1. The positional relationship between the vessel 410A and the second heat exchanger 410B is the same. The second heat exchanger 610B and the third heat exchanger 610C are arranged so that the distance between the surfaces facing each other increases from the windward side to the leeward side. That is, the heat exchange unit 610W is formed in a W shape as a whole by the first heat exchanger 610A, the second heat exchanger 610B, the third heat exchanger 610C, and the fourth heat exchanger 610D. ..

In the example of FIG. 19, the first heat exchanger 610A, the second heat exchanger 610B, the third heat exchanger 610C, and the fourth heat exchanger 610D are all of the heat transfer tubes 11a of the auxiliary heat exchanger 411. The outer diameter O ₁ is larger than _{the outer diameter O 2} of each heat transfer tube 12a of the main heat exchanger 412. However, the first heat exchanger 610A, the second heat exchanger 610B, the third heat exchanger 610C, and the fourth heat exchanger 610D of the present modification 5-1 are secondary to the wind side as in the third embodiment. The distance between the fins 411b of the heat exchanger 411 may be smaller than the distance between the fins 412b of the main heat exchanger 412 on the leeward side. At that time, the first heat exchanger 410A and the second heat exchanger 410B of this modification 5-1, as in the second embodiment, configured so that the outer diameter O ₁ and the outer diameter of O ₂ equal May be good.

Each of the above embodiments is a suitable specific example of an indoor unit of an air conditioner and an air conditioner, and the technical scope of the present invention is not limited to these embodiments. For example, when the heat exchanger has three or more heat transfer portions, the outer diameter of the heat transfer tubes constituting each heat transfer portion may be gradually reduced from the windward side to the leeward side. When the heat exchanger has three or more heat transfer portions and the fin portions of each heat transfer portion are formed as separate bodies, the distance between the fin portions constituting each heat transfer portion is from the leeward side. It may be gradually reduced toward the windward side. Further, in each of the above embodiments, the pipe having a circular cross section is exemplified as the pipe constituting the heat exchanger, but the pipe constituting the heat exchanger is not limited to this, and the pipe constituting the heat exchanger is a flat pipe or a pipe having an elliptical cross section. Etc., various pipes may be included. Further, the distance between the fins in each heat transfer tube does not have to be constant, and the distance between the fins may change depending on the position.

In addition, in each of the above embodiments, the case where the flow path of the refrigerant in the refrigerant circuit 80 is switched by the four-way valve 62 is illustrated, but the present invention is not limited to this, and instead of the four-way valve 62, a two-way valve and a three-way valve are used. A combined configuration or the like may be used. However, the air conditioner 500 may configure the refrigerant circuit 80 without providing the flow path switching means such as the four-way valve 62, and may be specialized in the cooling operation or the heating operation.

10, 110, 210 heat exchangers, 10A, 410A, 510A, 610A 1st heat exchangers, 10B, 410B, 510B, 610B 2nd heat exchangers, 11, 111, 211 1st heat transfer parts, 12, 112, 212 2nd heat transfer part, 11a, 12a, 111a, 112a heat transfer tube, 11b, 12b, 111b, 112b, 411b, 412b fin part, 11g, 12g, 111g, 112g, 411g, 412g heat transfer tube group, 31A, 31B inner surface , 50 blower, 61 compressor, 62 four-way valve, 63 expansion valve, 64 heat source side heat exchanger, 70 heat source side blower, 80 refrigerant circuit, 100 indoor unit, 101 casing, 102 suction port, 103 outlet, 200 outdoor unit , 310V, 410V, 510W, 610W heat exchange unit, 411 secondary heat exchanger, 412 main heat exchanger, 500 air conditioner, 800 wall, D ₀ , D ₁ graph, O ₁ , O ₂ outer diameter, R refrigerant piping ..

The indoor unit of the air conditioner according to the present invention is provided between a casing having a suction port formed at the upper part and an air outlet formed at the lower part and between the suction port and the air outlet in the casing, and blows from the suction port. A blower that creates an air flow toward the outlet and a heat exchanger provided between the blower and the outlet in the casing are provided, and the heat exchangers are spaced by a plurality of heat transfer tubes arranged at intervals. It has a plurality of fin portions including a plurality of fin portions through which a plurality of heat transfer tubes penetrate, and the plurality of heat transfer portions are the first heat transfer portion arranged on the most wind side. , A second heat transfer part arranged on the leeward side of the first heat transfer part, and the distance between each fin part of the first heat transfer part is the distance between each fin part of the second heat transfer part. It is smaller than, the ventilation resistance of the first heat transfer portion is greater than the ventilation resistance of the second heat transfer portion.

Claims (11)

A casing with a suction port formed at the top and an air outlet formed at the bottom,
A blower provided between the suction port and the air outlet in the casing to create an air flow from the suction port to the air outlet.
A heat exchanger provided between the blower and the air outlet in the casing is provided.
The heat exchanger is
It has a plurality of heat transfer portions including a plurality of heat transfer tubes arranged at intervals and a plurality of fin portions which are laminated at intervals and through which the plurality of heat transfer tubes penetrate.
The plurality of heat transfer units
The first heat transfer section located on the windward side,
It has a second heat transfer section arranged on the leeward side of the first heat transfer section.
An indoor unit of an air conditioner in which the ventilation resistance of the first heat transfer section is larger than the ventilation resistance of the second heat transfer section. The plurality of heat transfer units
The indoor unit of the air conditioner according to claim 1, wherein the outer diameter of each heat transfer tube of the first heat transfer section is larger than the outer diameter of each heat transfer tube of the second heat transfer section. The plurality of heat transfer units
The indoor unit of the air conditioner according to claim 1 or 2, wherein the distance between the fins of the first heat transfer unit is smaller than the distance between the fins of the second heat transfer unit. At least one of the first heat transfer section and the second heat transfer section
The indoor unit of an air conditioner according to any one of claims 1 to 3, further comprising a group of heat transfer tubes composed of a row of heat transfer tubes. The second heat transfer unit is a main heat exchanger including a plurality of heat transfer tube groups composed of a row of heat transfer tubes.
The indoor unit of the air conditioner according to any one of claims 1 to 4, wherein the first heat transfer unit is an auxiliary heat exchanger including at least one group of heat transfer tubes. It has a heat exchange unit composed of the two heat exchangers.
The heat exchange unit is
The two heat exchange units include a first heat exchanger provided on the front side in the casing and a second heat exchanger provided on the rear side in the casing.
Any of claims 1 to 5, wherein the first heat exchanger and the second heat exchanger are arranged so that the distance between the surfaces facing each other becomes shorter from the windward side to the leeward side. The indoor unit of the air conditioner according to item 1. The first heat transfer section and the second heat transfer section both include a group of heat transfer tubes composed of a row of heat transfer tubes.
In each of the first heat exchanger and the second heat exchanger,
The sixth aspect of the invention, wherein the adjacent heat transfer tube group has at least one heat transfer tube of one of the heat transfer tube groups overlapped with one or two heat transfer tubes of the other heat transfer tube group in a plan view. Indoor unit of air conditioner. It has a heat exchange unit composed of the four heat exchangers.
The heat exchange unit is
The four heat exchangers include a first heat exchanger, a second heat exchanger, a third heat exchanger, and a fourth heat exchanger arranged in order from the front to the rear in the casing.
The first heat exchanger and the second heat exchanger are arranged so that the distance between the surfaces facing each other becomes shorter from the windward side to the leeward side.
Any of claims 1 to 5, wherein the third heat exchanger and the fourth heat exchanger are arranged so that the distance between the surfaces facing each other becomes shorter from the windward side to the leeward side. The indoor unit of the air conditioner according to item 1. Both the first heat transfer section and the second heat transfer section include one group of heat transfer tubes composed of a row of heat transfer tubes.
In each of the first heat exchanger, the second heat exchanger, the third heat exchanger, and the fourth heat exchanger.
According to claim 8, in the adjacent heat transfer tube group, at least one of the heat transfer tubes of one of the heat transfer tube groups overlaps with one or two of the heat transfer tubes of the other heat transfer tube group in a plan view. The indoor unit of the air conditioner described. The indoor unit of the air conditioner according to any one of claims 1 to 5.
It has an outdoor unit including a compressor, an expansion valve, and a heat source side heat exchanger, and has
An air conditioner having a refrigerant circuit formed by connecting the compressor, the heat exchanger, the expansion valve, and the heat source side heat exchanger by a refrigerant pipe. The indoor unit of the air conditioner according to any one of claims 6 to 9.
It has an outdoor unit including a compressor, an expansion valve, and a heat source side heat exchanger, and has
An air conditioner having a refrigerant circuit formed by connecting the compressor, the heat exchange unit, the expansion valve, and the heat source side heat exchanger by a refrigerant pipe.

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