JP6807766B2 - Indoor unit of air conditioner and air conditioner equipped with this - Google Patents

Description

The present invention relates to an indoor unit of an air conditioner and an air conditioner including the indoor unit.

In Patent Document 1, in addition to the main heat exchanger, a sub heat exchanger having a shape different from that of the main heat exchanger is arranged, and the step pitch of the heat transfer tube of the sub heat exchanger is shorter than that of the main heat exchanger. Harmonizers are listed.

Japanese Unexamined Patent Publication No. 2000-337652

However, in the heat exchanger of the air conditioner described in Patent Document 1, by providing the sub heat exchanger, air passes through the main heat exchanger at the lower part (upstream side in the air flow direction) of the sub heat exchanger. There is a problem that it becomes difficult and the heat exchange efficiency is impaired.

The present invention solves the above-mentioned conventional problems, and an object of the present invention is to provide an indoor unit of an air conditioner capable of performing heat exchange with high efficiency and an air conditioner including the indoor unit.

The present invention comprises a heat exchanger having a plurality of fins and a plurality of flat heat transfer tubes having a flat cross-sectional shape penetrating the plurality of fins, and air exchanged in the heat exchanger outside the housing. The heat exchanger includes a front upper heat exchanger arranged so as to incline forward from the upper end to the lower end on the front side of the blower, and the front upper heat exchanger. A front lower heat exchanger arranged so as to incline rearward from the upper end to the lower end is provided on the lower side, and the plurality of flat heat transfer tubes are arranged in a plurality of rows and arranged in the longitudinal direction of the fins. A direction in which the long axis direction of the flat heat transfer tube is orthogonal to the longitudinal direction of the fin, and is composed of a wind-up flat tube arranged on the air introduction side and a leeward-side flat tube arranged on the blower side. The angle of a part of the leeward flat tube and the angle of the leeward flat tube at the boundary between the front upper heat exchanger and the front lower heat exchanger are different from each other, and the front upper heat is different. When the direction of gravity is 0 degrees, the exchanger is in the counterclockwise direction in the right side view in the rotation axis direction of the blower when the front upper heat exchanger of a part of the wind upper flat tube is viewed from the front . The angle θ10 in the counterclockwise direction in the right side view in the rotation axis direction of the leeward flat tube is larger than the angle θ91, and the front lower heat exchanger is the wind upper flat tube when the gravity direction is 0 degrees. the clockwise direction in the rotation axis direction right side view of the leeward side the flat tubes from the clockwise direction angle θ92 in the direction of the axis of rotation right side view of the blower when viewing the portion of the lower front heat exchanger from the front The angle θ40 is large, the angle of a part of the wind-up flat tube in the front upper heat exchanger and the front lower heat exchanger is less than 45 degrees, and the angle of the leeward flat tube is 45 degrees or more. It is a feature.

According to the present invention, it is possible to provide an indoor unit of an air conditioner capable of performing heat exchange with high efficiency and an air conditioner including the indoor unit.

It is a block diagram which shows the refrigerant circuit of the air conditioner which concerns on 1st Embodiment. It is sectional drawing which shows the indoor unit of the air conditioner which concerns on 1st Embodiment. It is sectional drawing which shows the indoor unit of the air conditioner which concerns on Comparative Example 1. FIG. It is sectional drawing which shows the indoor unit of the air conditioner which concerns on 2nd Embodiment. It is sectional drawing which shows the indoor unit of the air conditioner which concerns on 3rd Embodiment. It is sectional drawing which shows the indoor unit of the air conditioner which concerns on Comparative Example 2. FIG. It is sectional drawing which shows the indoor unit of the air conditioner which concerns on 4th Embodiment. It is sectional drawing which shows the indoor unit of the air conditioner which concerns on 5th Embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, the same reference numerals are given to the common parts in each figure, and duplicate description is omitted. The first to third embodiments are used as reference examples.
(First Embodiment)
FIG. 1 is a configuration diagram showing a refrigerant circuit of the air conditioner according to the first embodiment.
As shown in FIG. 1, the air conditioner 100 includes an outdoor unit 1 installed outdoors (non-air-conditioned space) on the heat source side and an indoor unit 2 (air conditioner 2) installed indoors (air-conditioned space) on the user side. The indoor unit) and the outdoor unit 1 and the indoor unit 2 are connected by the refrigerant pipes 3 and 3.

The outdoor unit 1 includes a compressor 4, a four-way valve 5, an outdoor heat exchanger 6, an outdoor fan 7, and an expansion valve 9. A propeller fan is usually used as the outdoor fan 7. The indoor unit 2 includes an indoor heat exchanger 8 (8A, 8B, 8C, 8D, 8E) and a blower 10 including a once-through fan.

Next, the basic operation of the air conditioner 100 will be described separately for heating operation and cooling operation.
In the case of heating operation, the gas-state refrigerant compressed by the compressor 4 flows to the indoor heat exchanger 8 via the four-way valve 5, and the refrigerant is gas by exchanging heat with the indoor air by the airflow generated by the blower 10. It condenses from the state and changes to the liquid state. The refrigerant in the liquid state flows to the outdoor heat exchanger 6 via the expansion valve 9, absorbs the heat of the outdoor air by the airflow generated by the outdoor fan 7, and exchanges heat, so that the refrigerant is released from the liquid state. It evaporates into a gas state and flows to the compressor 4.

In the cooling operation, the direction in which the refrigerant flows is opposite to that in the heating operation by switching the four-way valve 5. The gas-state refrigerant compressed by the compressor 4 flows into the outdoor heat exchanger 6 via the four-way valve 5, and the airflow generated by the outdoor fan 7 releases heat to the outdoor air to exchange heat, thereby performing the gas state. Condenses and changes to a liquid state. The liquid refrigerant flows to the indoor heat exchanger 8 via the expansion valve 9, absorbs heat from the indoor air with the air flow generated by the blower 10, and evaporates to become a gas state and flows to the compressor 4. ..

The air conditioner 100 provided with the indoor unit 2 of the present embodiment is equipped with both a heating operation mode and a cooling operation mode, a unit equipped with only a cooling operation mode, a heating operation mode and a cooling operation mode. In addition to this, a dehumidifying operation mode may be installed.

FIG. 2 is a cross-sectional view showing an air conditioner according to the first embodiment.
As shown in FIG. 2, the indoor unit 2 includes an indoor heat exchanger 8A and a blower 10. Further, the indoor unit 2 includes a housing 11 molded into a horizontally long box shape by a synthetic resin, and houses an indoor heat exchanger 8A and a blower 10.

The blower 10 is composed of, for example, a once-through fan, has a plurality of fan blades 10a and an annular support plate 10b, and the fan blades 10a are arranged on the support plate 10b at equal intervals in the circumferential direction. ing. Further, the blower 10 has a substantially tubular shape and extends along the indoor heat exchanger 8A (along the direction perpendicular to the paper surface of FIG. 2). Further, in the blower 10, one end in the axial direction is rotatably supported toward the housing 11, and the other end in the axial direction is connected to a motor (not shown).

The housing 11 is provided with air suction ports 11a and 11b for sucking indoor air on the upper surface and the front surface, and an air outlet 11c for blowing out air whose temperature and humidity are harmonized by heat exchange on the lower surface. Filters 12a and 12b for purifying the indoor air and taking it into the housing 11 are attached to the air suction ports 11a and 11b. The air outlet 11c is provided with a left-right wind direction plate (not shown) that deflects the air flow in the left-right direction and a vertical wind direction plate 13 that deflects the air flow in the vertical direction.

Further, the housing 11 includes a back casing 14 and a front casing 15. Further, a front panel 16 is rotatably attached to the front surface of the housing 11 so as to open and close the air suction port 11b by a driving force of a motor (not shown).

The back casing 14 is located on the back side of the blower 10, is continuously formed at the air outlet 11c, and has a curved surface 14a as an air flow path wall surface. The curved surface 14a is arranged so that the concave surface faces forward, and is curved so as to gradually approach the blower 10 from the edge of the air outlet 11c.

Further, the back casing 14 has a back nose portion 14b (also referred to as a rear guider) protruding between the blower 10 and the rear heat exchanger 23 described later. Further, the surface 14b1 of the back nose portion 14b on the blower 10 side extends so as to be a gentle continuous surface with no step from the curved surface 14a. Further, the tip of the back nose portion 14b extends to the extent that it is located substantially in the center of the rear heat exchanger 23 in the longitudinal direction. Further, the surface 14b2 of the back nose portion 14b opposite to the blower 10 is formed substantially parallel to the rear heat exchanger 23.

Although not shown, the curved surface 14a and the back nose portion 14b of the back casing 14 extend from one end to the other end of the blower 10 along the axial direction (vertical direction of the paper surface) of the blower 10. There is.

Further, in the back casing 14, a flow path wall surface 14c extending upward in the vertical direction is formed behind the back nose portion 14b. Further, the back casing 14 is formed with a recess 14d into which a part (about the lower half) of the rear heat exchanger 23 is inserted between the back nose portion 14b and the flow path wall surface 14c.

The front casing 15 is located substantially in front of the blower 10 and has a wall surface 15a that extends continuously toward the blower 10 at the air outlet 11c in the vicinity below the front lower heat exchanger 22. Further, a front nose portion 15b (also referred to as a stabilizer) bent and formed in a substantially rectangular shape is integrally formed at the tip of the front casing 15. Although not shown, the front nose portion 15b extends from one end to the other end of the blower 10 along the axial direction (vertical direction on the paper surface) of the blower 10.

As shown in FIG. 2, the indoor heat exchanger 8A is arranged on the upstream side of the blower 10 between the blower 10 and the air suction ports 11a and 11b. Further, the indoor heat exchanger 8A includes a front upper heat exchanger 21A located on the front side from substantially the center in the front-rear direction of the housing 11, and a front lower heat exchanger 22 located on the lower side of the front upper heat exchanger 21A. A rear heat exchanger 23 located on the rear side from substantially the center in the front-rear direction of the housing 11 is provided.

The front upper heat exchanger 21A and the rear heat exchanger 23 are combined above the blower 10 and arranged in an inverted V shape in a side view. Further, the front upper heat exchanger 21A and the front lower heat exchanger 22 are combined in front of the blower 10 to form a boomerang shape (dogleg shape) in a side view.

The front upper heat exchanger 21A is made of, for example, fins 31 (plurality of fins) formed by arranging a plurality of thin plates made of aluminum or aluminum alloy in the plate thickness direction, and aluminum having a flat cross-sectional shape penetrating the fins 31. , A flat tube group 32 (a plurality of flat heat transfer tubes) made of aluminum alloy or the like. As described above, aluminum has a lower material cost and is excellent in extrusion processability as compared with the conventional copper product.

The fin 31 has an elongated shape from the upper end 31a to the lower end 31b when viewed from the side of the blower 10 in the direction of the rotation axis (rotation center O). Further, the front end 31c and the rear end 31d of the fin 31 are inclined forward from the upper end 31a to the lower end 31b, and the front end 31c and the rear end 31d are parallel to each other. Further, the upper end 31a and the lower end 31b of the fin 31 extend in the horizontal direction, and the upper end 31a and the lower end 31b are parallel to each other.

The flat tube group 32 is composed of two rows (plurality of rows) from the outside of the indoor heat exchanger 8A toward the blower 10 side (toward the air flow direction). That is, the flat tube group 32 has a windward flat tube 32A arranged on the side where air is introduced (air introduction side) and a leeward flat tube 32B arranged on the blower 10 side. The windward flat tube 32A is composed of a plurality of flat heat transfer tubes 32a arranged along the longitudinal direction s1 of the fin 31. The leeward side flat tube 32B is composed of a plurality of flat heat transfer tubes 32b and 32c arranged along the longitudinal direction s1 of the fin 31. The flat heat transfer tube 32c is located on the upper end side in the arrangement direction of the flat heat transfer tubes 32b and 32c.

The flat heat transfer tubes 32a of the leeward flat tube 32A and the flat heat transfer tubes 32b and 32c of the leeward flat tube 32B have opposite flat portions (straight sections) and one ends and the other ends of the flat portions (straight sections), respectively. It is configured to include a curved portion for connecting the above. Further, the inside of the flat heat transfer tubes 32a, 32b, 32c is partitioned into a plurality of refrigerant flow paths by a plurality of partition walls extending from the inner wall surface of one flat portion toward the inner wall surface of the other flat portion. By partitioning the inside of the flat heat transfer tubes 32a, 32b, 32c with partition walls in this way, the heat transfer area in the tubes can be expanded and the heat transfer performance can be improved.

The flat heat transfer tubes 32a are located outside the front upper heat exchanger 21A and are arranged side by side along the longitudinal direction s1 of the fins 31. Further, in the plurality of flat heat transfer tubes 32a, adjacent flat heat transfer tubes 32a are formed at equal intervals. The intervals between the adjacent flat heat transfer tubes 32a do not necessarily have to be equal. Further, the plurality of flat heat transfer tubes 32a are oriented in a direction in which the long axis direction x1 of the flat heat transfer tubes 32a is orthogonal to the longitudinal direction s1.

The flat heat transfer tubes 32b are located on the blower 10 side of the front upper heat exchanger 21A, and are arranged side by side along the longitudinal direction s1 of the fins 31. Further, in the plurality of flat heat transfer tubes 32b, adjacent flat heat transfer tubes 32b are formed at equal intervals. The intervals between the adjacent flat heat transfer tubes 32b do not necessarily have to be equal. Further, the plurality of flat heat transfer tubes 32b are oriented in a direction in which the long axis direction x1 of the flat heat transfer tubes 32b is orthogonal to the longitudinal direction s1.

The flat heat transfer tube 32c has a major axis direction x2 different from that of the flat heat transfer tube 32a described above. As described above, the angle of the flat heat transfer tube 32a of the windward flat tube 32A and the angle of the flat heat transfer tube 32c of the leeward flat tube 32B in the front upper heat exchanger 21A are different. Further, in the front upper heat exchanger 21A, when the gravity direction G is 0 degree, the angle θ10 of the flat heat transfer tube 32a of the windward flat tube 32A is larger than the angle θ20 of the flat heat transfer tube 32c of the leeward flat tube 32B. It has been set. The angle θ10 means an angle formed by the gravity direction G and the longitudinal direction x1 of the flat heat transfer tube 32a. Further, the angle θ20 means an angle formed by the gravity direction G and the longitudinal direction x2 of the flat heat transfer tube 32c. Specifically, the angle θ10 of the leeward flat tube 32A is set to 45 degrees or more, and the angle θ20 of the flat heat transfer tube 32c of the leeward flat tube 32B is set to less than 45 degrees.

As a result, the direction of the flat heat transfer tube 32c (direction of the major axis direction x2) is substantially parallel to the flow direction of the wind introduced from above the front upper heat exchanger 21A (upper end 31a of the fin 31) (see arrow A1). It is arranged so as to be in a close direction (see arrow A2), and is configured so that the resistance becomes smaller as the bending of the air flow (A1 → A2) becomes smaller.

Further, as shown by the white arrows A1, arrows A2 and arrows A3, the air can pass through the front upper heat exchanger 21A without significantly bending in the air flow direction.

Further, the flat heat transfer tubes 32a, 32b, 32c are inserted into the flat holes formed in the fins 31 and joined to the fins 31 by brazing. Further, the flat heat transfer tubes 32a, 32b, 32c and the fins 31 may be fixed by mechanically expanding the flat heat transfer tubes 32a, 32b, 32c from the inside and crimping the fins 31. A U-shaped notch may be formed in the front end 31c or the rear end 31d of the fin 31 in the longitudinal direction s1, and the flat heat transfer tubes 32a, 32b, 32c may be inserted and joined by brazing.

The front lower heat exchanger 22 is composed of, for example, fins 33 and a flat tube group 34 made of the same material as the front upper heat exchanger 21A.

The fins 33 have an elongated shape from the upper end 33a to the lower end 33b when viewed from the side from the direction of the rotation axis (rotation center O) of the blower 10. Further, the front end 33c and the rear end 33d of the fin 33 are inclined rearward from the upper end 33a toward the lower end 33b, and the front end 33c and the rear end 33d are parallel to each other. Further, the upper end 33a and the lower end 33b of the fin 33 extend in the horizontal direction, and the upper end 33a and the lower end 33b are parallel to each other. Further, the lower end 31b of the fin 31 and the upper end 33a of the fin 33 are combined so as to be in linear contact with each other.

The flat tube group 34 is composed of a plurality of flat heat transfer tubes 34a and 34b in two rows (plural rows) from the outside of the indoor heat exchanger 8A toward the blower 10 side (toward the air flow direction). There is. That is, the flat tube group 34 has a windward flat tube 34A arranged on the side where air is introduced (air introduction side) and a leeward flat tube 34B arranged on the blower 10 side. The windward flat tube 34A is composed of a plurality of flat heat transfer tubes 34a arranged along the longitudinal direction s2 of the fins 31. The leeward side flat tube 34B is composed of a plurality of flat heat transfer tubes 34b arranged along the longitudinal direction s2 of the fin 31. The flat heat transfer tubes 34a and 34b are configured in the same manner as the flat heat transfer tubes 32a, 32b and 32c described above.

The flat heat transfer tubes 34a are located in the outer row of the front lower heat exchanger 22 and are arranged side by side along the longitudinal direction s2 of the fins 33. Further, the adjacent flat heat transfer tubes 34a are formed at equal intervals. The intervals between adjacent flat heat transfer tubes 34a do not necessarily have to be equal. Further, the flat heat transfer tube 34a faces a direction in which the long axis direction x3 of the flat heat transfer tube 34a is orthogonal to the longitudinal direction s2.

The flat heat transfer tubes 34b are located on the blower 10 side of the front lower heat exchanger 22 and are arranged side by side along the longitudinal direction s2 of the fins 33. Further, the adjacent flat heat transfer tubes 34b are formed at equal intervals. The intervals between adjacent flat heat transfer tubes 34b do not necessarily have to be equal. The flat heat transfer tube 34b faces a direction in which the long axis direction x3 of the flat heat transfer tube 34b is orthogonal to the longitudinal direction s2.

The rear heat exchanger 23 is composed of, for example, fins 35 and a flat tube group 36 made of the same materials as the front upper heat exchanger 21A and the front lower heat exchanger 22. That is, the flat tube group 36 has a windward flat tube 36A arranged on the side where air is introduced (air introduction side) and a leeward flat tube 36B arranged on the blower 10 side. The windward flat tube 36A is composed of a plurality of flat heat transfer tubes 36a arranged along the longitudinal direction s3 of the fins 31. The leeward side flat tube 36B is composed of a plurality of flat heat transfer tubes 36b arranged along the longitudinal direction s3 of the fin 31. The flat heat transfer tubes 36a and 36b are configured in the same manner as the flat heat transfer tubes 32a, 32b and 32c described above.

The fins 35 have an elongated shape from the upper end 35a to the lower end 35b when viewed from the side of the blower 10 in the direction of the rotation axis (rotation center O). Further, the front end 35c and the rear end 35d of the fin 35 are inclined rearward from the upper end 35a toward the lower end 35b, and the front end 35c and the rear end 35d are parallel to each other.

The flat tube group 36 is composed of a plurality of flat heat transfer tubes 36a and 36b in two rows (plural rows) from the outside of the indoor heat exchanger 8A toward the blower 10 side (toward the air flow direction). There is.

The flat heat transfer tubes 36a are located outside the rear heat exchanger 23 and are arranged side by side along the longitudinal direction s3 of the fins 35. Further, the adjacent flat heat transfer tubes 36a are formed at equal intervals. The intervals between the adjacent flat heat transfer tubes 36a do not necessarily have to be equal. Further, the flat heat transfer tube 36a faces a direction in which the long axis direction x4 of the flat heat transfer tube 36a is orthogonal to the longitudinal direction s3.

The flat heat transfer tubes 36b are located on the blower 10 side of the rear heat exchanger 23, and are arranged side by side along the longitudinal direction s3 of the fins 35. Further, in the plurality of flat heat transfer tubes 36b, adjacent flat heat transfer tubes 36b are formed at equal intervals. The intervals between the adjacent flat heat transfer tubes 36b do not necessarily have to be equal. Further, the flat heat transfer tube 36b faces a direction in which the long axis direction x4 of the flat heat transfer tube 36b is orthogonal to the longitudinal direction s3.

Further, the upper end 35a of the rear heat exchanger 23 and the upper end 31a of the front upper heat exchanger 21A are parallel to each other, and both are arranged at the same height position.

In the indoor unit 2 configured in this way, indoor air is introduced from the air suction ports 11a and 11b by rotating the blower 10 with the front panel 16 open, and the filters 12a and 12b and the indoor heat exchanger It is blown out from the air outlet 11c through 8A and the blower 10.

At this time, the indoor air is sucked from above at the upper air suction port 11a. The indoor air sucked from the air suction port 11a is sucked from the front of the front upper heat exchanger 21A, and by passing through the front upper heat exchanger 21A, the indoor air and the refrigerant passing through the flat heat transfer tubes 32a, 32b, 32c Heat exchange takes place with. Further, the indoor air sucked from the air suction port 11a is sucked from the front of the front lower heat exchanger 22 and passes through the front lower heat exchanger 22 to pass through the indoor air and the flat heat transfer tubes 34a and 34b. Heat exchange takes place with. Further, the indoor air sucked from the air suction port 11a is sucked into the rear heat exchanger 23 from the rear of the rear heat exchanger 23, and is between the indoor air and the refrigerant passing through the flat heat transfer tubes 36a and 36b. Heat exchange takes place at.

Further, the indoor air sucked from the air suction port 11b is sucked from the front of the front upper heat exchanger 21A and passes through the front upper heat exchanger 21A to pass through the indoor air and the flat heat transfer tubes 32a, 32b and 32c. Heat exchange takes place with the passing refrigerant. Further, the indoor air sucked from the air suction port 11b is sucked from the front of the front lower heat exchanger 22 and passes through the front lower heat exchanger 22 to pass through the indoor air and the flat heat transfer tubes 34a and 34b. Heat exchange takes place with.

FIG. 3 is a cross-sectional view showing an air conditioner according to Comparative Example 1. Note that FIG. 3 collectively shows comparative examples with respect to the first embodiment, the third embodiment, the fourth embodiment, and the fifth embodiment. In FIG. 3, the white arrows A200 to A220 are comparative examples corresponding to the first embodiment, the arrows A230 to A260 are comparative examples corresponding to the third embodiment, and the arrows A270 correspond to the fourth embodiment. The arrow A280 is a comparative example corresponding to the fifth embodiment.

The indoor unit 200 shown in FIG. 3 is provided with flat heat transfer tubes 32b and 32b in place of the flat heat transfer tubes 32c and 32c (see FIG. 2) of the front upper heat exchanger 21A of the first embodiment. The flat heat transfer tube 32b has the same spacing and orientation as the flat heat transfer tube 32b in the first embodiment. Other configurations are the same as those in the first embodiment.

By the way, as shown in FIG. 3, in the indoor heat exchanger 200 shown as a comparative example, the indoor air sucked from above the front upper heat exchanger 21 (see the white arrow A200) is shown by the white arrow A210. In addition, the air flows in a large direction so as to pass between the flat heat transfer tube 32b and the flat heat transfer tube 32b. Then, the indoor air flowing out from the front upper heat exchanger 21 turns to the blower 10 side and flows as shown by the white arrow A220.

Further, due to restrictions on the shape of the indoor unit, the indoor heat exchanger 200 often has a curved or bent shape instead of a plate shape. When a flat heat transfer tube is applied to the indoor heat exchanger 200, the flat heat transfer tubes are often arranged in parallel with each other at an angle so as to face the rotation center O of the once-through fan (blower 10). However, at this time, the angle of the ventilation flow path (see arrow A220) from the indoor heat exchanger 200 to the once-through fan (blower 10) does not change significantly, but the air entering the indoor heat exchanger 200 from outside the indoor heat exchanger 200. The ventilation flow path of the room has a large angle depending on the portion, which increases the ventilation resistance of the indoor heat exchanger 200. Further, not only this, a dead water area (region P surrounded by a circle in FIG. 3) in which air stagnates is generated in a part of the flat heat transfer tube 32b, and the heat exchange efficiency may decrease.

As described above, the air flow before the indoor air enters the front upper heat exchanger 21 (arrow A200), during heat exchange (arrow A210), and after exiting the front upper heat exchanger 21A (arrow A220). The direction of is changing greatly. At the portion from the arrow A200 to the arrow A210 and the portion from the arrow A210 to the arrow A220, the pressure loss becomes large, which may lead to a decrease in the performance of the front upper heat exchanger 21.

Therefore, in the first embodiment, as shown as flat heat transfer tubes 32c and 32c (a part of the leeward side flat tube 32B) in FIG. 2, the flat heat transfer tubes 32b are flattened so as to reduce the ventilation resistance as compared with the case where the flat heat transfer tubes 32b are arranged. The directions of the heat transfer tubes 32c and 32c are changed by rotating the heat transfer tubes 32b with respect to the flat heat transfer tubes 32b. That is, when the air flow direction in front of the front upper heat exchanger 21A is arrow A1 (similar to A200), the air flow direction between the flat heat transfer tubes 32c and 32c is arrow A2, and the front upper heat exchanger After exiting 21A, it becomes arrow A3. In this way, the directions of the flat heat transfer tubes 32c and 32c are changed so that the flow direction of the air passing through the front upper heat exchanger 21A is substantially along the air flow in front of the front upper heat exchanger 21A. To do. In this way, the heat exchange efficiency in the front upper heat exchanger 21A is improved by changing the direction of the flat heat transfer tubes 32c and 32c, which are places where the ventilation resistance is high as it is, so as to reduce the ventilation resistance. As a result, the indoor unit 2 having improved performance of the indoor heat exchanger 8A can be realized.

As described above, the indoor unit 2 of the air conditioner of the first embodiment has fins 31, 33, 35 and a plurality of flat heat transfer tubes 32a, 32b having a flat cross section penetrating the fins 31, 33, 35. , 32c, 34a, 34b, 36a, 36b, and an indoor heat exchanger 8A, and a blower 10 for discharging the heat-exchanged air in the indoor heat exchanger 8A to the outside of the housing 11. Further, the plurality of flat heat transfer tubes 32a, 32b, 32c are arranged in a plurality of rows along the longitudinal direction s1 of the fins 31 and are arranged on the windward flat tube 32A and the blower 10 side arranged on the air introduction side. It is composed of the leeward flat tube 32B, and the angle θ10 of the leeward flat tube 32A (flat heat transfer tube 32a) is different from the angle θ20 of a part of the leeward flat tube 32B (flat heat transfer tube 32c). According to this, it is possible to reduce the air flow resistance from above the indoor heat exchanger 8A (see arrow A2 in FIG. 2), and it is possible to improve the heat exchange efficiency in the front upper heat exchanger 21A.

Further, in the first embodiment, when the gravity direction G is 0 degree, the angle θ20 of a part of the leeward side flat tube 32B (flat heat transfer tube 32c) of the front upper heat exchanger 32A is that of the leeward flat tube 32A. It is smaller than the angle of (flat heat transfer tube 32a). As a result, the leeward side flat tube 32B (flat heat transfer tube 32c) in the upper part of the indoor heat exchanger 8A can be easily directed to the blower 10 side, so that the ventilation resistance can be reduced.

Further, in the first embodiment, the angle of the leeward flat tube 32A is 45 degrees or more, and the angle of the leeward flat tube 32B (flat heat transfer tube 32c) is less than 45 degrees. As a result, the leeward side flat tube 32B (flat heat transfer tube 32c) in the upper part of the indoor heat exchanger 8A can be easily directed to the blower 10 side, so that the ventilation resistance can be easily reduced.

Further, by applying the indoor unit 2 of the first embodiment to the air conditioner 100, the air conditioner 100 having excellent operating efficiency can be realized.

In the first embodiment, the direction of the flat heat transfer tubes 32b (downwind side flat tubes 32B) in the row on the blower 10 side of the front upper heat exchanger 21A is changed (when the directions are changed to 32c and 32c). However, the present invention is not limited to this configuration, and for example, the flat heat transfer tube 32a (wind-upper flat tube 32A) at the top of the outer row of the front upper heat exchanger 21A. The orientation may be changed so that the ventilation resistance is reduced, or the flat heat transfer tube at the top of the flat heat transfer tube 36b (downwind side flat tube 36B) in the row on the blower 10 side of the rear heat exchanger 23. The direction of 36b may be changed so as to reduce the ventilation resistance in the same manner as in the flat heat transfer tube 32c.

(Second Embodiment)
FIG. 4 is a cross-sectional view showing the air conditioner according to the second embodiment.
As shown in FIG. 4, the indoor unit 2 of the second embodiment includes an indoor heat exchanger 8B and a blower 10. The indoor heat exchanger 8B includes a front upper heat exchanger 21, a front lower heat exchanger 22A, and a rear heat exchanger 23. The front lower heat exchanger 22A is composed of, for example, fins 33 and flat tube group 34 made of the same material as the front upper heat exchanger 21A.

The flat tube group 34 is composed of a plurality of flat heat transfer tubes 34b, 34c in two rows (plural rows) from the outside of the indoor heat exchanger 8B toward the blower 10 side (toward the air flow direction). There is. That is, the flat tube group 34 has a windward flat tube 34A arranged on the side where air is introduced (air introduction side) and a leeward flat tube 34B arranged on the blower 10 side. The windward flat tube 34A is composed of a plurality of flat heat transfer tubes 34c arranged along the longitudinal direction s2 of the fins 33. The leeward side flat tube 34B is composed of a plurality of flat heat transfer tubes 34b arranged along the longitudinal direction s2 of the fins 33. The flat heat transfer tubes 34b and 34c are configured in the same manner as the flat heat transfer tubes 32a, 32b and 32c described above.

The long axis direction x3a of the flat heat transfer tube 34c is different from the direction of the long axis direction x3 of the flat heat transfer tube 34b. As described above, the angle θ30 of the flat heat transfer tube 34c of the leeward flat tube 34A and the angle θ40 of the flat heat transfer tube 34b of the leeward flat tube 34B in the front lower heat exchanger 22A are different. Further, in the front lower heat exchanger 22A, when the gravity direction G is 0 degree, the angle θ30 of the flat heat transfer tube 34c of the windward flat tube 34A is smaller than the angle θ40 of the flat heat transfer tube 34b of the leeward flat tube 34B. .. The angle θ30 means an angle formed by the gravity direction G and the longitudinal direction x3a of the flat heat transfer tube 34c. Further, the angle θ40 means an angle formed by the gravity direction G and the longitudinal direction x3 of the flat heat transfer tube 34b. Specifically, the angle θ30 of the leeward flat tube 34A is set to less than 90 degrees, and the angle θ40 of the flat heat transfer tube 34b of the leeward flat tube 34B is set to 90 degrees or more.

The flat heat transfer tubes 34c are located in the outer row of the front lower heat exchanger 22A and are arranged side by side along the longitudinal direction s2 of the fins 33. Further, the adjacent flat heat transfer tubes 34c are formed at equal intervals. Further, the flat heat transfer tube 34c is oriented in a direction different from that of the flat heat transfer tube 34b, and the ventilation resistance is reduced as compared with the case where the flat heat transfer tube 34b is arranged (see the flat heat transfer tube 34a1 shown by the broken line). ing. That is, as shown in FIG. 4, when the air flow direction on the front side of the front lower heat exchanger 22A is arrow A4, the air flow direction between the flat heat transfer tubes 34c and 34c is arrow A5 and is flat. The flow direction of the air flowing between the heat transfer tubes 34b and 34b is indicated by the arrow A6.

As described above, in the second embodiment, the direction along the air flow in front of the front lower heat exchanger 22A (arrow A4) becomes the air flow direction (arrow A5) passing through the flat heat transfer tubes 34c and 34c. The angle at which the flat heat transfer tube 34c is changed from the arrow A4 to the arrow A5 is smaller than that of the flat heat transfer tube 34a1 shown by the broken line. As a result, the ventilation resistance is reduced, so that the occurrence of a dead water area (that is, a portion inefficient as a heat exchanger) can be suppressed, and the heat exchange efficiency in the front lower heat exchanger 22A can be improved. In this way, the heat exchange efficiency in the front lower heat exchanger 22A is improved by changing the orientation of the flat heat transfer tubes 34c and 34c, which are places where the ventilation resistance is high as it is, so as to reduce the ventilation resistance. As a result, the indoor unit 2 having improved performance of the indoor heat exchanger 8B can be realized.

By the way, as shown by the arrow A4 in FIG. 4, the wind flow here tends to face the longitudinal direction s2 of the front lower heat exchanger 22A. In particular, when the air is not supplied from the front of the indoor unit 2 due to the limitation of the shape of the housing 11 (see FIG. 2) of the indoor unit 2, the air is supplied only from the upper part of the indoor unit 2. In particular, the flow of air tends to be directed in the longitudinal direction s2 of the front lower heat exchanger 22A. Therefore, as shown in FIG. 4, in the front lower heat exchanger 22A, all the rows of the flat heat transfer tubes 34c in the outer row are configured to face the same direction.

As described above, in the second embodiment, all of the flat heat transfer tubes 34c in the same row are oriented in the same direction with respect to the longitudinal direction s2. According to this, in all of the adjacent flat heat transfer tubes 34c and 34c, the change in the angle of the wind direction from the front side of the front lower heat exchanger 22A toward the flat heat transfer tube 34c becomes small, so that the ventilation resistance can be reduced. As a result, the heat exchange efficiency in the front lower lower heat exchanger 22A can be further improved, and the indoor unit 2 with improved performance of the indoor heat exchanger 8B can be realized.

Further, when the angle θ30 is 90 degrees or more and the angle θ40 is less than 90 degrees, not only the ventilation resistance increases, but also a dead water area (see FIG. 3) is generated due to the change in the wind direction, and the heat exchange efficiency May cause a decrease in. Therefore, it is preferable that the angle θ30 is less than 90 degrees and the angle θ40 is 90 degrees or more. As a result, ventilation resistance can be reduced while suppressing the occurrence of dead water areas. As a result, the heat exchange efficiency of the front lower heat exchanger 22A can be improved, and as a result, the indoor unit 2 having improved performance of the indoor heat exchanger 8B can be realized.

In the second embodiment, the case where the directions of the flat heat transfer tubes 34c in all the rows of the front lower heat exchanger 22A are changed has been described as an example, but the flat transmission in the outer row of the rear heat exchanger 23 has been described as an example. The orientation of all rows of heat tubes 36a may be changed to reduce resistance from the direction of the wind passing in front of the rear heat exchanger 23 to the direction of the wind passing through the flat heat transfer tube 36a.

(Third Embodiment)
FIG. 5 is a cross-sectional view showing the air conditioner according to the third embodiment.
As shown in FIG. 5, the indoor unit 2 of the third embodiment includes an indoor heat exchanger 8C and a blower 10. The indoor heat exchanger 8C includes a front upper heat exchanger 21, a front lower heat exchanger 22, and a rear heat exchanger 23A. The rear heat exchanger 23A is composed of, for example, fins 33 and a flat tube group 36 made of the same material as the front upper heat exchanger 21A.

The flat tube group 36 is arranged in two rows by a plurality of flat heat transfer tubes 36a, 36b, 36c, 36d from the outside to the inside (the side of the blower 10) of the rear heat exchanger 23A (toward the air flow direction). It is composed of (multiple columns). That is, the flat tube group 36 has a windward flat tube 36A arranged on the side where air is introduced (air introduction side) and a leeward flat tube 36B arranged on the blower 10 side. The windward flat tube 36A is composed of a plurality of flat heat transfer tubes 36a and 36c arranged along the longitudinal direction s3 of the fin 33. The leeward side flat tube 36B is composed of a plurality of flat heat transfer tubes 36b and 36d arranged along the longitudinal direction s3 of the fin 33. The flat heat transfer tubes 36a, 36b, 36c, 36d are configured in the same manner as the flat heat transfer tubes 32a, 32b, 32c described above. The outer row of the rear heat exchanger 23A is composed of five flat heat transfer tubes 36a and four flat heat transfer tubes 36c. The inner row of the rear heat exchanger 23A (the row on the blower 10 side) is composed of six flat heat transfer tubes 36b and three flat heat transfer tubes 36d.

The major axis direction x4 of the flat heat transfer tube 36a is different from the direction of the major axis direction x4a of the flat heat transfer tube 36c. Further, the long axis direction x4 of the flat heat transfer tube 36b is different from the direction of the long axis direction x4b of the flat heat transfer tube 36d. Further, the flat heat transfer tube 36a and the flat heat transfer tube 36b have the same major axis directions x4. As described above, the angle θ70 of the leeward flat tube 36A (flat heat transfer tube 36c) and the angle θ80 of the leeward flat tube 36B (flat heat transfer tube 36d) in the rear heat exchanger 23A are different. Further, in the rear heat exchanger 23A, when the direction of gravity is 0 degree, the angle θ80 of the flat heat transfer tube 36d of the leeward flat tube 36B is set larger than the angle θ70 of the flat heat transfer tube 36c of the windward flat tube 36A. ing. The angle θ70 means an angle formed by the gravity direction G and the longitudinal direction x4a of the flat heat transfer tube 36c. Further, the angle θ80 means an angle formed by the gravity direction G and the longitudinal direction x4b of the flat heat transfer tube 36d. Specifically, the angle θ30 of the leeward flat pipe 34A is set to less than 45 degrees, and the angle θ80 of the leeward flat pipe 34B is set to 45 degrees or more.

The flat heat transfer tubes 36a are located in the outer row of the rear heat exchanger 23A and are arranged side by side along the longitudinal direction s3 of the fins 35. The flat heat transfer tubes 36c are located in the outer row of the rear heat exchanger 23A and are arranged side by side along the longitudinal direction s3 of the fins 35. The flat heat transfer tube 36a is arranged above the rear heat exchanger 23A, and the flat heat transfer tube 36c is arranged below the rear heat exchanger 23A. Further, the flat heat transfer tube 36c is located between the back nose portion 14b and the flow path wall surface 14c. The intervals between the adjacent flat heat transfer tubes 36a are formed equally, and the intervals between the adjacent flat heat transfer tubes 36c are formed equally. The intervals between the flat heat transfer tubes 36a and 36c are not necessarily limited to equal intervals.

The flat heat transfer tubes 36b are located in a row inside the rear heat exchanger 23A (on the blower 10 side), and are arranged side by side along the longitudinal direction s3 of the fins 35. The flat heat transfer tubes 36d are located in a row inside the rear heat exchanger 23A (on the blower 10 side), and are arranged side by side along the longitudinal direction s3 of the fins 35. The flat heat transfer tube 36b is arranged above the rear heat exchanger 23A, and the flat heat transfer tube 36d is arranged below the rear heat exchanger 23A. Further, the flat heat transfer tube 36d is located between the back nose portion 14b and the flow path wall surface 14c. The intervals between the adjacent flat heat transfer tubes 36b are formed equally, and the intervals between the adjacent flat heat transfer tubes 36d are formed equally. The intervals between the flat heat transfer tubes 36b and 36d are not necessarily limited to equal intervals.

Further, the flat heat transfer tube 36a faces a direction in which the long axis direction x4 of the flat heat transfer tube 36a is orthogonal to the longitudinal direction s3 of the fin 35. Further, when the direction of gravity is 0 degree, the angle θ50 of the flat heat transfer tube 36a is set to 45 degrees. The angle θ50 is not limited to 45 degrees, and may be less than 45 degrees. Further, the flat heat transfer tube 36c has a different direction from the flat heat transfer tube 36a, and is oriented in a direction of reducing the ventilation resistance as compared with the case where the flat heat transfer tube 36a is arranged.

Further, the flat heat transfer tube 36b faces a direction in which the long axis direction x4 of the flat heat transfer tube 36b is orthogonal to the longitudinal direction s3 of the fin 35. Further, when the direction of gravity is 0 degree, the angle θ60 of the flat heat transfer tube 36b is set to 45 degrees. The angle θ60 is not limited to 45 degrees and may be less than 45 degrees. Further, the flat heat transfer tube 36d has a different orientation from the flat heat transfer tube 36b, and faces a direction of reducing the ventilation resistance as compared with the case where the flat heat transfer tube 36b is arranged.

By the way, as shown in Comparative Example 1 of FIG. 3, there is a wall (flow path wall surface 14c) on the back side of the indoor heat exchanger 200. As a result, the flow path of the air outside the indoor heat exchanger 200 is restricted, and further, the presence of the back nose portion 14b for generating the air flow by the blower 10 (throughflow fan) also causes the air on the blower 10 side. Easy to be restricted. The rear heat exchanger 23 of the indoor heat exchanger 200 shown in FIG. 3 includes a plurality of flat heat transfer tubes 36a and 36b, and all the flat heat transfer tubes 36a and 36b are orthogonal to the longitudinal direction s3 of the fins 35. Is facing. Therefore, as shown by the white arrows A230 and A260 in FIG. 3, the wind direction is almost opposite before and after entering the rear heat exchanger 23, so that the air flows into and flows out into the rear heat exchanger 23. In the meantime, the direction of the air flow changes significantly.

Temporarily, the angle formed by the wind direction (arrow A230) before flowing into the rear heat exchanger 23 and the wind direction (arrow A240) when passing through the flat heat transfer tube 36a in the outer row of the rear heat exchanger 23 (arrow A240). The changing angle) is θ100. Further, the wind direction (arrow A240) when passing through the flat heat transfer tube 36a in the outer row of the rear heat exchanger 23 and the flat heat transfer tube 36b on the side of the blower 10 of the rear heat exchanger 23. Let θ200 be the angle (changing angle) formed by the wind direction (arrow A250). Further, the angle (changing angle) formed by the wind direction (arrow A250) when passing through the flat heat transfer tube 36b on the side of the blower 10 and the wind direction (arrow A260) after flowing out from the rear heat exchanger 23 is θ300. And. At this time, the angle θ100 ≈90 degrees, the angle θ200≈0 degrees, and the angle θ300≈90 degrees. Here, by changing the direction of the flat heat transfer tubes 36a in the outer row of the rear heat exchanger 23, the angle θ100 can be reduced, but the angle θ200 increases. Further, the angle θ300 does not change even if the direction of the flat heat transfer tubes 36a in the outer row of the rear heat exchanger 23 is changed.

Therefore, in such a case, not only the direction of the flat heat transfer tubes 36a in the outer row of the rear heat exchanger 23 is changed, but also the direction of the flat heat transfer tubes 36b in the row on the blower 10 side is changed to air. The angle formed by the direction of the flow can be reduced, and the ventilation resistance can be reduced.

That is, as shown in FIG. 5, the angle θ70 of the windward flat tube 36A (flat heat transfer tube 36c) in the rear heat exchanger 23A and the angle θ80 of the leeward flat tube 36B (flat heat transfer tube 36d) are different. .. Further, when the direction of gravity is set to 0 degrees, the angle θ80 of the flat heat transfer tube 36d of the leeward flat tube 36B is made larger than the angle θ70 of the flat heat transfer tube 36c of the leeward flat tube 36A. Specifically, the angle θ70 of the leeward flat pipe 34A is set to less than 45 degrees, and the angle θ80 of the leeward flat pipe 34B is set to 45 degrees or more.

As a result, it is possible to reduce the ventilation resistance when going from the wind direction (arrow A7) to the wind direction (arrow A8). Further, it is possible to reduce the ventilation resistance when going from the wind direction (arrow A9) to the wind direction (arrow A10). Therefore, the heat exchange efficiency in the rear-front heat exchanger 23A can be further improved, and as a result, the indoor unit 2 with improved performance of the indoor heat exchanger 8C can be realized.

In the third embodiment, the flat heat transfer tubes 36c are oriented in the same direction, but the flat heat transfer tubes 36c may be oriented in different directions (the same applies to the flat heat transfer tubes 36d).

FIG. 6 is a cross-sectional view showing an air conditioner according to Comparative Example 2.
The indoor heat exchanger 300 shown as a comparative example in FIG. 6 is configured so that the flat heat transfer tubes 340 in the outer row of the front lower heat exchanger 22 face in the horizontal direction (substantially horizontal direction). By the way, in the case where the flat heat transfer tube 340 having such an orientation is provided, when the air conditioner 100 (see FIG. 1) is operated for cooling, condensed water is generated on the upper portion (flat portion) of the flat heat transfer tube 340. It becomes easy to collect. If the condensed water is likely to be accumulated, water droplets are likely to be discharged from the air outlet 11c of the indoor unit during the cooling operation, which causes so-called "water skipping".

Therefore, in the indoor heat exchanger 8A of the first embodiment, the orientation of the flat heat transfer tube 34a, in the indoor heat exchanger 8B of the second embodiment, the orientation of the flat heat transfer tube 34c, the indoor heat exchanger 8C of the third embodiment. Then, the direction of the flat heat transfer tube 34a is set so as not to face the horizontal direction (substantially horizontal direction). Further, not only the flat heat transfer tubes 34a and 34c, but also the directions of the flat heat transfer tubes 32a, 32b, 34b, 36a and 36b of the indoor heat exchanger 8A, and the flat heat transfer tubes 32a, 32b, 34b and 36a of the indoor heat exchanger 8B. It is preferable that the orientation of 36b and the orientation of the flat heat transfer tubes 32a, 32b, 34b, 36a, 36b, 36c, 36d of the indoor heat exchanger 8C do not face the horizontal direction (substantially horizontal direction), respectively. As a result, condensed water is less likely to accumulate in the flat heat transfer tubes 32a, 32b, 34a to 34c, 36a to 36d, and "water jumping" can be suppressed.

By the way, in FIG. 3, in the indoor heat exchanger 200 shown as a comparative example, the air flow at the portion where the front upper heat exchanger 21 and the front lower heat exchanger 22 are combined is shown by the white arrow A270, and the front upper heat is shown. The air flow at the site where the exchanger 21 and the rear heat exchanger 23 are combined is shown by the white arrow A280. Ventilation resistance is small at the parts indicated by arrows A270 and A280, so if the air flow is concentrated here, the amount of air flowing to the indoor heat exchanger 200 at other parts will decrease, and the performance of the indoor heat exchanger 200 will decrease. May decrease. Therefore, in the fourth embodiment and the fifth embodiment, the direction of a part of the flat heat transfer tube in the portion where the air flow is likely to be concentrated is set so as to obstruct the air flow. It prevents the flow from concentrating and improves the performance as a heat exchanger.

(Fourth Embodiment)
FIG. 7 is a cross-sectional view showing the air conditioner according to the fourth embodiment.
As shown in FIG. 7, the indoor unit 2 of the fourth embodiment includes an indoor heat exchanger 8D and a blower 10. The indoor heat exchanger 8D includes a front upper heat exchanger 21B, a front lower heat exchanger 22B, and a rear heat exchanger 23.

The front upper heat exchanger 21B is composed of fins 31 (plurality of fins) and a flat tube group 32. That is, the flat tube group 32 has a windward flat tube 32A arranged on the side where air is introduced (air introduction side) and a leeward flat tube 32B arranged on the blower 10 side. The windward flat tube 32A is composed of a plurality of flat heat transfer tubes 32a and 32d arranged along the longitudinal direction s1 of the fin 31. The leeward side flat tube 32B is composed of a plurality of flat heat transfer tubes 32b arranged along the longitudinal direction s1 of the fin 31.

The plurality of flat heat transfer tubes 32a and 32d are arranged side by side in the longitudinal direction s1 of the fins 31. The direction of the flat heat transfer tube 32a in the major axis direction x1 is a direction orthogonal to the longitudinal direction s1. The orientation of the flat heat transfer tube 32d in the major axis direction x5 is different from the direction of the flat heat transfer tube 32a, and the ventilation resistance is higher than when the flat heat transfer tube 32a is arranged (see the flat heat transfer tube 32a1 shown by the broken line). It is facing the direction of raising. In other words, the flat heat transfer tube 32d is configured to approach the direction orthogonal to the air flow (arrow A270, see FIG. 3).

The front lower heat exchanger 22B is composed of fins 33 (plurality of fins) and a heat transfer tube group 34. That is, the flat tube group 34 has a windward flat tube 34A arranged on the side where air is introduced (air introduction side) and a leeward flat tube 34B arranged on the blower 10 side. The windward flat tube 34A is composed of a plurality of flat heat transfer tubes 34a and 34d arranged along the longitudinal direction s2 of the fin 33. The leeward side flat tube 34B is composed of a plurality of flat heat transfer tubes 34b arranged along the longitudinal direction s2 of the fins 33.

The plurality of flat heat transfer tubes 34a and 34d are arranged side by side in the longitudinal direction s2 of the fins 33. The direction of the flat heat transfer tube 34a in the major axis direction x3 is a direction orthogonal to the longitudinal direction s2. The orientation of the flat heat transfer tube 32d in the major axis direction x6 is different from the direction of the flat heat transfer tube 34a, and the ventilation resistance is higher than that in the case where the flat heat transfer tube 34a is arranged (see the flat heat transfer tube 34a1 shown by the broken line). It is facing the direction of raising. In other words, the flat heat transfer tube 34d is configured to approach the direction orthogonal to the air flow (arrow A270, see FIG. 3).

In this way, the angle θ91 of the flat heat transfer tube 32d of the windward flat tube 32A and the angle θ10 of the flat heat transfer tube 32b of the leeward flat tube 32B at the boundary between the front upper heat exchanger 21B and the front lower heat exchanger 22B It's different. Further, the angle θ92 of the flat heat transfer tube 34d of the windward flat tube 34A and the angle θ40 of the flat heat transfer tube 34b of the leeward flat tube 34B at the boundary between the front upper heat exchanger 21B and the front lower heat exchanger 22B are different. There is. Further, when the gravity direction G is 0 degree, the angle θ10 of the flat heat transfer tube 32b of the leeward flat tube 32B is larger than the angle θ91 of the flat heat transfer tube 32d of the windward flat tube 32A. Further, the angle θ91 of the windward flat tube 32A (flat heat transfer tube 32d) is less than 45 degrees, and the angle of the leeward flat tube 32B (flat heat transfer tube 32b) is 45 degrees or more. Further, when the gravity direction G is 0 degrees, the angle θ40 of the flat heat transfer tube 34b of the leeward flat tube 34B is larger than the angle θ92 of the flat heat transfer tube 34d of the leeward flat tube 34A. Further, the angle θ92 of the windward flat tube 34A (flat heat transfer tube 34d) is less than 45 degrees, and the angle of the leeward flat tube 34B (flat heat transfer tube 34b) is 45 degrees or more.

According to the fourth embodiment, the ventilation resistance is low as it is, and the heat exchange efficiency is low at the boundary between the bent portion (combination portion) of the front upper heat exchanger 21B and the front lower heat exchanger 22B. The directions of the heat transfer tubes 32d and 34d are changed so that the ventilation resistance increases. As a result, it is possible to suppress a decrease in heat exchange efficiency in the front upper heat exchanger 21B and the front lower heat exchanger 22B, and as a result, it is possible to realize an indoor unit 2 having improved performance of the indoor heat exchanger 8D.

(Fifth Embodiment)
FIG. 8 is a cross-sectional view showing the air conditioner according to the fifth embodiment.
As shown in FIG. 8, the indoor unit 2 of the fifth embodiment includes an indoor heat exchanger 8E and a blower 10. The indoor heat exchanger 8E includes a front upper heat exchanger 21C, a front lower heat exchanger 22, and a rear heat exchanger 23B. The front upper heat exchanger 21C is composed of, for example, fins 31 and flat tube group 32 made of the same material as the front upper heat exchanger 21A.

The front upper heat exchanger 21C is composed of fins 31 (plurality of fins) and a flat tube group 32. That is, the flat tube group 32 has a windward flat tube 32A arranged on the side where air is introduced (air introduction side) and a leeward flat tube 32B arranged on the blower 10 side. The windward flat tube 32A is composed of a plurality of flat heat transfer tubes 32a arranged along the longitudinal direction s1 of the fin 31. The leeward side flat tube 32B is composed of a plurality of flat heat transfer tubes 32b, 32e arranged along the longitudinal direction s1 of the fin 31.

Further, the front upper heat exchanger 21C has fins 31 (plurality of fins) and a plurality of flat heat transfer tubes 32a ..., 32b ..., 32e from the outside of the front upper heat exchanger 21C. It is composed of two rows toward the inside (blower 10 side). The flat heat transfer tubes 32b and 32e are arranged side by side in the longitudinal direction s1 of the fins 31. The orientation of the flat heat transfer tubes 32a and 32b in the major axis direction x1 is a direction orthogonal to the longitudinal direction s1. The orientation of the flat heat transfer tube 32e in the major axis direction x7 is different from the orientation of the flat heat transfer tube 32b, and the ventilation resistance is higher than that in the case where the flat heat transfer tube 32b is arranged (see the flat heat transfer tube 32b1 shown by the virtual line). It is facing the direction of increasing. In other words, it points in a direction orthogonal to the air flow shown by arrow A280 in FIG.

That is, the flat heat transfer tube 32e is first rotated with reference to the flat heat transfer tube 32b so as to increase the ventilation resistance as shown by the flat heat transfer tube 32b1 in the broken line, and is further shown by the flat heat transfer tube 32b2 in the broken line. As shown above, it was moved in parallel so that the ventilation resistance was further increased.

The rear heat exchanger 23B is composed of fins 35 (plurality of fins) and a flat tube group 36. That is, the flat tube group 36 has a windward flat tube 36A arranged on the side where air is introduced (air introduction side) and a leeward flat tube 36B arranged on the blower 10 side. The windward flat tube 36A is composed of a plurality of flat heat transfer tubes 36a arranged along the longitudinal direction s3 of the fins 35. The leeward side flat tube 36B is composed of a plurality of flat heat transfer tubes 36b, 36e arranged along the longitudinal direction s3 of the fin 35.

Further, the rear heat exchanger 23B has fins 35 (plurality of fins) and a plurality of flat heat transfer tubes 36a ..., 36b ..., 36e, and is provided from the outside of the rear front heat exchanger 23B. It is composed of two rows toward the inside (blower 10 side). The flat heat transfer tubes 36a are arranged side by side in the longitudinal direction s3 of the fins 33. The directions of the flat heat transfer tubes 36a and 36b in the major axis direction x4 are oriented orthogonal to the longitudinal direction s3. The orientation of the flat heat transfer tube 36e in the major axis direction x8 is different from the orientation of the flat heat transfer tubes 36a and 36b, and ventilation is greater than when it is assumed that the flat heat transfer tube 36b is arranged (see the flat heat transfer tube 36b1 shown by the broken line). It is facing the direction of increasing resistance. In other words, it points in a direction orthogonal to the air flow shown by arrow A280 in FIG.

Like the flat heat transfer tube 32e, the flat heat transfer tube 36e is rotated with respect to the flat heat transfer tube 36b so as to increase the ventilation resistance as shown by the flat heat transfer tube 36b1 in the broken line, and is further flattened in the broken line. As shown by the heat transfer tube 36b2, the heat transfer tubes are moved in parallel so as to further increase the ventilation resistance.

According to the fifth embodiment, the flat heat transfer tube at the upper end at the boundary of the combination portion between the front upper heat exchanger 21C and the rear heat exchanger 23B, which is a place where the ventilation resistance is low and the heat exchange efficiency is low as it is. The directions (rotation and translation) of 32e and 34g are changed so as to increase the ventilation resistance. As a result, it is possible to suppress a decrease in heat exchange efficiency at the combination portion of the front side upper heat exchanger 21C and the rear side heat exchanger 23B, and as a result, the indoor unit 2 with improved performance of the indoor heat exchanger 8E. Can be realized.

The present invention is not limited to the above-described embodiment, and includes various modifications. For example, in the first to fifth embodiments, as the indoor heat exchangers 8A to 8E, the directions of some of the flat heat transfer tubes 32a and 32b are orthogonal to the longitudinal direction s1 of the fins 31, and some of the flat heat transfer tubes 34a. , 34b was set to be orthogonal to the longitudinal direction s2 of the fin 33, and some flat heat transfer tubes 36a, 36b were set to be orthogonal to the fin 35 in the longitudinal direction s3. It may deviate from orthogonality as long as the effect of the invention is exhibited.

Further, in the first to fifth embodiments described above, the indoor heat exchangers 8A to 8E have been described by taking as an example a flat heat transfer tube composed of two rows, but one row may be used. There may be three or more rows.

Further, the indoor heat exchangers 8A to 8C of the plurality of embodiments of the first to third embodiments may be combined and configured. Further, the first to third embodiments may be combined with the fourth and fifth embodiments.

Further, in the first to fifth embodiments, the case where the front upper heat exchanger and the front lower heat exchanger are configured as separate bodies has been described as an example, but they are integrally formed in a boomerang shape (dogleg shape). It may be configured. Further, the front upper heat exchanger and the rear heat exchanger may be integrated.

Further, as the blower 10, although the once-through fan is taken as an example, another type of blower such as a propeller fan may be used.

Further, in the first to fifth embodiments, the case where the front upper heat exchanger and the rear heat exchanger do not overlap in the vertical direction has been described as an example, but for example, after the front upper heat exchanger 21 The end 31d and the upper end 35a of the rear heat exchanger 23 may be linearly contacted and overlapped.

2 Indoor unit (indoor unit of air conditioner)
8,8A, 8B, 8C, 8D, 8E Indoor heat exchanger (heat exchanger)
10 Blower 14b Back nose 21A, 21B, 21C Front upper heat exchanger 22A, 22B Front lower heat exchanger 23A, 23B Rear heat exchanger 32A, 34A, 36A Wind upper flat tube 32B, 34B, 36B Downwind flat tube 100 Air exchanger s1, s2, s3 Longitudinal direction x1, x2, x3, x3a, x4, x4a, x4b, x5, x6, x7, x8 Long axis direction

Claims (2)

A heat exchanger having a plurality of fins and a plurality of flat heat transfer tubes having a flat cross-sectional shape penetrating the plurality of fins.
A blower for discharging the heat-exchanged air in the heat exchanger to the outside of the housing is provided.
The heat exchangers are arranged on the front side of the blower so as to be inclined forward from the upper end to the lower end, and on the lower side of the front upper heat exchanger, from the upper end to the lower end. With a front lower heat exchanger, which is arranged to incline backwards,
The plurality of flat heat transfer tubes are arranged in a plurality of rows in the longitudinal direction of the fins, and are composed of a windward flat tube arranged on the air introduction side and a leeward flat tube arranged on the blower side. , The long axis direction of the flat heat transfer tube is arranged so as to face a direction orthogonal to the longitudinal direction of the fin.
The angle of a part of the windward flat tube at the boundary between the front upper heat exchanger and the front lower heat exchanger is different from the angle of the leeward flat tube.
When the gravity direction of the front upper heat exchanger is 0 degrees, the counterclockwise view of a part of the wind upper flat tube in the clockwise direction of the blower when the front upper heat exchanger is viewed from the front The angle θ10 in the counterclockwise direction in the right side view in the rotation axis direction of the leeward flat tube is larger than the angle θ91 in the clockwise direction.
The front lower heat exchanger is a clock in the right side view in the rotation axis direction of the blower when the front lower heat exchanger of a part of the wind upper flat tube is viewed from the front when the gravity direction is 0 degrees. The angle θ40 in the clockwise direction in the right side view in the rotation axis direction of the leeward flat tube is larger than the angle θ92 in the clockwise direction .
An air conditioner characterized in that the angle of a part of the windward flat tube in the front upper heat exchanger and the front lower heat exchanger is less than 45 degrees, and the angle of the leeward flat tube is 45 degrees or more. Indoor unit. A heat exchanger having a plurality of fins and a plurality of flat heat transfer tubes having a flat cross-sectional shape penetrating the plurality of fins.
A blower for discharging the heat-exchanged air in the heat exchanger to the outside of the housing is provided.
The heat exchangers are an upper front heat exchanger arranged so as to incline forward from the upper end to the lower end on the upper front side of the blower, and a rear upper heat exchanger on the rear side of the blower from the upper end to the lower end. With a rear heat exchanger located in,
The plurality of flat heat transfer tubes are arranged in a plurality of rows in the longitudinal direction of the fins, and are composed of a windward flat tube arranged on the air introduction side and a leeward flat tube arranged on the blower side. , The long axis direction of the flat heat transfer tube is arranged so as to face a direction orthogonal to the longitudinal direction of the fin.
The angle of a part of the leeward flat tube at the boundary between the front upper heat exchanger and the rear heat exchanger is different from the angle of the leeward flat tube.
When the gravity direction of the front upper heat exchanger is 0 degrees, the counterclockwise direction in the rotation axis direction right side view of the blower when the front upper heat exchanger of the wind upper flat tube is viewed from the front. The angle θ93 in the counterclockwise direction in the right side view in the rotation axis direction of a part of the leeward flat tube is larger than the angle θ10.
When the direction of gravity is 0 degrees, the rear heat exchanger is in the clockwise direction in the right side view in the rotation axis direction of the blower when the rear heat exchanger of the wind-up flat tube is viewed from the front . The angle θ94 in the clockwise direction in the right side view in the rotation axis direction of a part of the leeward flat tube is larger than the angle θ50.
An indoor unit of an air conditioner, characterized in that a part of the leeward flat tube of each of the front upper heat exchanger and the rear heat exchanger is arranged so as to move in a direction approaching each other.

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