WO2016151751A1 - Air conditioner - Google Patents

Abstract

An air conditioner is characterized by being provided with a pair of blowers (4), and a heat exchanger (3) disposed so as to surround an inner space (50) formed at the lower portion of the blowers (4), which serves as the upstream side of the blowers (4). The heat exchanger (3) comprises a pair of halves (30a, 30b) that are shaped symmetrically to one another. Each of the halves (30a, 30b) has, in the following order, a first heat exchanging section (3a), a second heat exchanging section (3b), a third heat exchanging section (3c), and a fourth heat exchanging section (3d) that successively extend while partially curving so as to surround a blower (4). The air conditioner is further characterized by being provided with an outdoor unit (90) that includes the heat exchanger (3), in which the pair of halves (30a, 30b) are joined via the fourth heat exchanging sections (3d).

Description

Air conditioner

The present invention relates to an air conditioner.

Conventionally, as an outdoor unit of an air conditioner, there is a blower on the front side of the outdoor unit, and heat exchange is performed between the remaining part of the front face except for a mounting plate to which the blower is attached, both side faces of the outdoor unit, and the back face. A device in which a container is arranged is known (for example, see Patent Document 1). According to this outdoor unit, a large heat exchange surface of the heat exchanger can be secured, so that the outdoor unit can be made compact.
Moreover, as an outdoor unit, what has a pair of air blower on the upper surface of an outdoor unit, and has arrange | positioned the heat exchanger in the front surface, both side surface, and back surface of an outdoor unit is known (for example, refer patent document 2). . Incidentally, the heat exchanger of this outdoor unit is joined so that the opening sides of a pair of halves having a substantially U shape face each other in a plan view when the heat exchanger is viewed from the blower side. . According to this outdoor unit, it is possible to secure a larger heat exchange surface of the outdoor heat exchanger than the outdoor unit in which the blower is attached to the front.

Japanese Patent Laid-Open No. 07-120012 Japanese Patent No. 3710874

However, in an outdoor unit having a blower on the front surface (for example, see Patent Document 1), the air blown out from the blower passes through a heat exchanger disposed on the same front surface as the mounting plate of the blower and enters the outdoor unit again. Sucked. That is, since the air after heat exchange is again taken into the outdoor unit, the heat exchange performance of the heat exchanger decreases. Moreover, in this outdoor unit, the outside air that has passed through the heat exchanger disposed in the front is reversed from the flow in the outdoor unit after the heat exchange, and blown out from the front fan. Therefore, the energy saving performance of the outdoor unit is hindered by the ventilation resistance in the outdoor unit during reversal.

Also, in an outdoor unit having a pair of blowers on the upper surface of the outdoor unit (see, for example, Patent Document 2), air flows generated by the two blowers in the outdoor unit are likely to interfere with each other. When the air flow interferes in the outdoor unit, the blowing performance of the blower is degraded. This hinders the energy saving performance of the outdoor unit.

In addition, at the joint between the halves of the outdoor unit that are substantially U-shaped, the end portions of the heat exchanger face each other. Generally, a pipe such as a flow divider is arranged at a portion where the ends of the heat exchanger face each other. Therefore, an extra space that hinders downsizing of the outdoor unit is formed around the end of the heat exchanger.
Therefore, in an air conditioner, what has the outdoor unit which is excellent in energy-saving performance and can achieve compactness is desired.

Therefore, an object of the present invention is to provide an air conditioner including an outdoor unit that is excellent in energy saving performance and can achieve downsizing.

The air conditioner of the present invention that has solved the above problems includes a pair of fans arranged side by side, and a heat exchanger arranged so as to surround an inner space formed on the lower side on the upstream side of the fan. The heat exchanger has a pair of symmetrical halves arranged to correspond to each of the pair of fans, each of the halves viewed from the corresponding fan side A first heat exchanging portion, a second heat exchanging portion, a third heat exchanging portion, and a fourth heat exchanging portion that extend continuously while partially bending so as to surround the blower in plan view are arranged in this order. And an outdoor unit having the heat exchanger in which the pair of half bodies are joined via the fourth heat exchange portions.

According to the present invention, it is possible to provide an air conditioner including an outdoor unit that is excellent in energy saving performance and can achieve downsizing.

It is composition explanatory drawing of the air conditioner which concerns on embodiment of this invention. It is a whole perspective view of the outdoor unit which constitutes the air harmony machine concerning the embodiment of the present invention. It is the schematic which shows the internal structure of the outdoor unit of FIG. It is a top view which shows typically the mode of the outdoor unit seen from upper direction. It is a whole perspective view of the outdoor heat exchanger which comprises the outdoor unit of FIG. It is a schematic diagram which shows the flow of the air in the inner side space of the outdoor heat exchanger at the time of the drive of a fan. It is a top view of the outdoor unit which shows the area | region where the external air which passed the outdoor heat exchanger is discharged | emitted by the outdoor air blower at a comparatively short distance. It is a top view of the outdoor unit which shows the 1st example of arrangement | positioning of the four-way valve and the accumulator in the inner side space of an outdoor unit. It is a top view of the outdoor unit which shows the 2nd example of arrangement | positioning of the four-way valve and the accumulator in the inner side space of an outdoor unit. It is a top view of the outdoor unit which shows the eccentric example of the propeller fan of an outdoor air blower. It is a longitudinal cross-sectional view in the central axis of the front-back direction of an outdoor heat exchanger, (a) is operation | movement explanatory drawing of the outdoor unit at the time of decentering the central axis of a propeller fan, (b) is a central axis of a propeller fan It is operation | movement explanatory drawing of the outdoor unit when not decentering. (A) is a top view which shows typically a mode that the outdoor air blower was seen from the upper direction of an outdoor unit, (b) is XII-XII sectional drawing of (a). It is a top view of the outdoor unit for demonstrating the modification of the 1st heat exchange part in an outdoor heat exchanger. It is a top view of the outdoor unit for demonstrating the modification of the 4th heat exchange part in an outdoor heat exchanger.

Next, embodiments of the present invention will be described in detail with reference to the drawings as appropriate.
The air conditioner of the present invention is characterized by including an outdoor unit having an outdoor heat exchanger in which halves, which are four-sided heat exchangers described later, are joined. The outdoor heat exchanger corresponds to a “heat exchanger” in the claims (the same applies hereinafter).
Below, after explaining the whole structure of an air conditioner, the outdoor unit which comprises this air conditioner is demonstrated.

<Overall configuration of air conditioner>
FIG. 1 is a configuration explanatory diagram of an air conditioner 100 according to the present embodiment.
As shown in FIG. 1, the air conditioner 100 includes an indoor unit 91 and an outdoor unit 90, and the indoor unit 91 and the outdoor unit 90 are connected via a pipe 10. Incidentally, in the air conditioner 100 according to the present embodiment, two indoor units 91 are connected in parallel by the pipe 10. In the air conditioner 100 according to the present embodiment, it is assumed that the indoor units 91 are individually arranged in the two rooms, but the present invention is not limited to this. The indoor unit 91 can be one or three or more. When the number of indoor units 91 is 3 or more, each indoor unit 91 is connected in parallel by the pipe 10.

The indoor unit 91 includes an indoor heat exchanger 7 and an indoor expansion valve 8.
The outdoor unit 90 includes a compressor 1, a four-way valve 2, an outdoor expansion valve 6, an outdoor heat exchanger 3, and an accumulator 5.
In FIG. 1, reference numeral 4 is an outdoor fan that sends outside air to the outdoor heat exchanger 3, and reference numeral 9 is an indoor fan that sends indoor air to the indoor heat exchanger 7. The outdoor blower 4 corresponds to a “blower” in the claims. Reference numerals 15 and 16 are pipe connection portions for connecting the pipe 10 to the outdoor unit 90. The pipe connecting portions 15 and 16 are provided on the left side of the service space 31a (see FIG. 6).

This air conditioner 100 switches the four-way valve 2 so that the indoor heat exchanger 7 is used as an evaporator and the outdoor heat exchanger 3 is used as a condenser, and the indoor heat exchanger 7 is used as a condenser and outdoor heat exchange. This is a heat pump type that performs heating operation using the vessel 3 as an evaporator. The switching state of the four-way valve 2 shown in FIG. 1 is that during cooling operation. Further, in FIG. 1, the solid line arrow X indicates the refrigerant circulation direction during the cooling operation, and the broken line arrow Y indicates the refrigerant circulation direction during the heating operation.

For example, in the air conditioner 100 during the cooling operation, the high-temperature and high-pressure refrigerant compressed by the compressor 1 passes through the four-way valve 2 and flows into the outdoor heat exchanger 3 and dissipates heat by heat exchange with air. Condensed. Thereafter, the refrigerant undergoes isenthalpy expansion by the outdoor expansion valve 6 and becomes a gas-liquid two-phase flow in which a gas refrigerant and a liquid refrigerant are mixed at a low temperature and a low pressure. This gas-liquid two-phase flow of the refrigerant flows into the pipe 10 via the pipe connecting portion 15. Thereafter, the refrigerant flows into the indoor heat exchanger 7 through the indoor expansion valve 8 in each indoor unit 91.

At this time, the indoor expansion valve 8 adjusts the flow rate of the refrigerant flowing into the indoor heat exchanger 7. Then, the liquid refrigerant in the indoor heat exchanger 7 is vaporized into a gas refrigerant by an endothermic action from the air. That is, when the liquid refrigerant is vaporized, the indoor heat exchanger 7 cools the surrounding air, so that the air conditioner 100 exhibits a cooling function. Subsequently, the refrigerant that has exited each indoor heat exchanger 7 flows into the pipe 10. Thereafter, the refrigerant returns to the compressor 1 via the pipe connection portion 15 and the accumulator 5. The refrigerant that has returned to the compressor 1 is compressed to high temperature and pressure again, and circulates through the four-way valve 2, the outdoor heat exchanger 3, the indoor expansion valve 8, and the indoor heat exchanger 7. That is, a refrigeration cycle is configured by repeating this circulation.

<Outdoor unit>
Next, the outdoor unit 90 will be described in more detail.
FIG. 2 is an overall perspective view of the outdoor unit 90 constituting the air conditioner 100 (see FIG. 1) according to the present embodiment. In addition, the front-back, up-down, left-right directions in the outdoor unit 90 in this embodiment are based on the front-back, up-down, left-right directions shown in FIG. 2 when the outdoor unit 90 is installed.

As shown in FIG. 2, the outdoor unit 90 has a substantially rectangular parallelepiped outer shape.
The outdoor unit 90 is disposed on the base member 12 inside the four support frames 11, the base member 12 having a rectangular shape in plan view, the four support frames 11 standing at the four corners of the base member 12, respectively. The outdoor heat exchanger 3 and the outdoor blower 4 disposed above the outdoor heat exchanger 3 are provided.

The support frame 11 has an L shape in a sectional view (see FIG. 4), and is arranged so that the outer corner portion of the L shape corresponds to the corner portion of the base member 12.
Although not shown, the outdoor heat exchanger 3 is arranged in a plurality so that heat radiation fins made of elongated rectangular plates extending in the vertical direction are stacked in the outer peripheral direction of the outdoor unit 90, and penetrates the plurality of heat radiation fins. A plurality of refrigerant tubes are provided so as to be connected.

Such an outdoor heat exchanger 3 is exposed on four side surfaces of the substantially rectangular parallelepiped outdoor unit 90. The outdoor heat exchanger 3 forms a substantially cylindrical body having an inner space 50 (see FIG. 3) in cooperation with a panel 31 (also referred to as a service panel) disposed on the front surface of the outdoor unit 90. .
The outdoor heat exchanger 3 will be described in detail later.

The outdoor unit 90 of this embodiment includes a pair of outdoor fans 4a and 4b.
The outdoor blower 4 is disposed above the outdoor heat exchanger 3. The outdoor blower 4 is configured to discharge air from the inner space 50 (see FIG. 3) formed inside the outdoor heat exchanger 3, that is, upstream of the outdoor blower 4 to the outside of the outdoor unit 90 by driving. Has been. The driven outdoor blower 4 sucks outside air into the outdoor unit 90 from between the heat radiation fins (not shown) of the outdoor heat exchanger 3 exposed on the four side surfaces of the outdoor unit 90, and this sucked air is sucked into the outdoor unit 90. Send out.

These outdoor fans 4a and 4b are arranged side by side. In the following description, when the two outdoor fans 4a and 4b are not particularly distinguished, they are simply referred to as outdoor fans 4. In FIG. 2, reference numeral 13 is a top plate disposed on the outdoor heat exchanger 3, and reference numeral 44 is a casing disposed on the top plate 13 so as to surround the periphery of the outdoor fan 4. The code | symbol 41a is a propeller fan which comprises the outdoor air blower 4a, and the code | symbol 41b is a propeller fan which comprises the outdoor air blower 4b. When the two propeller fans 41a and 41b are not particularly distinguished, they are simply referred to as propeller fans 41.

FIG. 3 is a schematic diagram showing the internal structure of the outdoor unit 90 of FIG. FIG. 4 is a plan view showing the internal structure of the outdoor unit 90 viewed from the outdoor fan 4 side. In FIG. 3, the compressor 1 is indicated by a broken line. In FIG. 4, the description of the casing 44 (see FIG. 2) and the top plate 13 (see FIG. 2) is omitted for the convenience of drawing. In FIG. 4, the outdoor blower 4 is indicated by a two-dot chain line circle equal to the outer diameter of the propeller fan 41. Moreover, in FIG. 4, the compressor 1 is shown with the broken line.

As shown in FIG. 3, the outdoor blower 4 includes a propeller fan 41, a motor 42 that rotates the propeller fan 41, and a bell mouth 43 that covers the periphery of the propeller fan 41. Incidentally, as will be described later, it is assumed that the propeller fans 41a and 41b (see FIG. 6) in the present embodiment rotate counterclockwise (counterclockwise) in a top view.

As shown in FIG. 3, the bell mouth 43 is a substantially cylindrical body. Specifically, the bell mouth 43 is formed in a substantially cylindrical shape having a reduced diameter portion that gradually decreases in diameter from the lower portion toward the upper portion on the inner space 50 side.
Although not shown, the top plate 13 to be disposed between the bell mouth 43 and the outdoor heat exchanger 3 is formed with a circular opening having an outer diameter substantially equal to the inner diameter of the lower portion of the bell mouth 43. . The inner space 50 communicates with the inner side of the bell mouth 43 through the circular opening.

Further, a motor support frame (not shown) is spanned in the radial direction of the circular opening. The motor 42 is supported by this motor support frame (not shown).
In FIG. 3, reference numeral 32 denotes a machine room housing disposed inside the outdoor heat exchanger 3 and closer to the front of the base member 12, that is, on the rear surface side of the panel 31. Incidentally, the panel 31 forms a wall surface that partitions the inner space 50 on the opposite side of the joining pillar 40 described later with the inner space 50 interposed therebetween.

In the machine room (not shown) formed inside the machine room housing 32, the compressor 1 and the outdoor expansion valve 6 (see FIG. 1) are arranged. The machine room housing 32 in the present embodiment is disposed so as to be close to the rear surface of the panel 31.

As described later, the outdoor unit 90 of the present embodiment is assumed to have two compressors 1 arranged in a horizontal direction in the machine room housing 32 (see FIG. 8). However, the outdoor unit 90 may be configured to have one compressor 1.

Numeral 33 is an electric box superimposed on the machine room housing 32, and numeral 35 is a radiator attached to the electric box 33. Incidentally, the electric box 33 is provided with a control device for overall control of the air conditioner 100 (see FIG. 1). The electric box 33 is disposed so as to be close to the rear surface of the panel 31.

The length of the electric box 33 in the front-rear direction is shorter than the length of the machine room housing 32 in the front-rear direction.
Due to the difference in length in the front-rear direction, a step is formed from the upper electric box 33 to the lower machine chamber housing 32. That is, the rear surface of the machine room housing 32 protrudes rearward from the rear surface of the electric box 33.
Further, the electrical box 33 is shorter than the machine room housing 32 in the left and right widths. That is, the cross sectional area of the electric box 33 is set to be smaller than the cross sectional area of the machine room housing 32.

In addition, the electric box 33 in the present embodiment is disposed so as to overlap the machine room housing 32 as described above. However, the arrangement position of the electric box 33 in the vertical direction is not limited to this, and is set between the upper end of the outdoor heat exchanger 3 and the upper end of the machine room housing 32, preferably the upper end of the compressor 1. can do.

As shown in FIG. 3, the heat radiator 35 is attached to the side surface of the electric box facing the central portion of the inner space 50, that is, the rear surface of the electric box 33. The vertical mounting position of the radiator 35 is set such that the vertical center position P1 of the radiator 35 is higher than the vertical center position P2 of the electrical box 33.

As shown in FIG. 4, the radiator 35 attached to the rear surface of the electric box 33 includes a plurality of radiating fins. The radiator 35 is erected on the rear surface of the electric box 33 such that the longitudinal direction of the plurality of radiating fins is along the vertical direction, and is arranged so that the plate surfaces of the plurality of radiating fins face the left-right direction of the outdoor unit 90. ing.

(Outdoor heat exchanger)
Next, the outdoor heat exchanger 3 constituting the outdoor unit 90 will be described in more detail.
As shown in FIG. 4, as described above, the outdoor heat exchanger 3 is formed integrally with the panel 31 provided at the center of the front surface of the outdoor unit 90 (front surface, the same applies hereinafter) to form a substantially cylindrical body. Yes.
This outdoor heat exchanger 3 is configured by integrally joining a left half 30a and a right half 30b.

The left half 30a and the right half 30b are provided so as to correspond to the left and right outdoor fans 4a and 4b.
The left half 30a and the right half 30b are formed symmetrically. Specifically, the left half 30a and the right half 30b are formed to be line-symmetric with respect to the central axis 60 of the outdoor unit 90 extending in the front-rear direction of the outdoor unit 90 in plan view.

Each of the left half 30a and the right half 30b extends continuously while partially bending so as to surround each of the outdoor fans 4a and 4b when viewed from the corresponding outdoor fan 4a and 4b. Yes. In other words, each of the left half 30a and the right half 30b has one end disposed on the front side, and is disposed along the outer periphery of the outdoor unit 90 to the front, side, and back.

Specifically, the left half 30a includes a first heat exchange unit 3a disposed on the front surface of the outdoor unit 90, a second heat exchange unit 3b disposed on the left side surface of the outdoor unit 90, and the outdoor unit 90. It has the 3rd heat exchange part 3c arrange | positioned at a back surface, and the 4th heat exchange part 3d arrange | positioned so as to oppose the 2nd heat exchange part 3b. And the 1st heat exchanging part 3a to the 4th heat exchanging part 3d are continuing in the clockwise direction centering on left outdoor fan 4a. The first heat exchanging part 3a to the fourth heat exchanging part 3d are bent so as to form an inner angle of 90 degrees with each other through an R part having a predetermined curvature.

The right half 30b is disposed on the first heat exchange unit 3a disposed on the front surface of the outdoor unit 90, the second heat exchange unit 3b disposed on the right side surface of the outdoor unit 90, and the rear surface of the outdoor unit 90. The third heat exchanging part 3c and the fourth heat exchanging part 3d arranged so as to face the second heat exchanging part 3b are provided. And the 1st heat exchange part 3a to the 4th heat exchange part 3d are continuing counterclockwise centering on the outdoor fan 4a of the right side. The first heat exchanging part 3a to the fourth heat exchanging part 3d are bent so as to form an inner angle of 90 degrees with each other through an R part having a predetermined curvature.

That is, in each of the left half 30a and the right half 30b, the first heat exchange part 3a and the third heat exchange part 3c face each other in the front, rear, left and right with the outdoor fans 4a and 4b as the center, and the second heat The exchange part 3b and the fourth heat exchange part 3d are opposed to each other. Therefore, each of the left half 30a and the right half 30b is a four-sided heat exchanger having the first heat exchanger 3a to the fourth heat exchanger 3d.

In such left half body 30a and right half body 30b, the length in the left-right direction of the first heat exchange unit 3a is shorter than the length in the left-right direction of the third heat exchange unit 3c.
Therefore, an opening is formed between the end of the first heat exchange part 3a in the left half 30a and the end of the first heat exchange 3a in the right half 30b. This opening constitutes a service space 31a described later of the outdoor unit 90. The panel 31 is attached to the service space 31a.

The length in the front-rear direction of the fourth heat exchange part 3d is shorter than the length in the front-rear direction of the second heat exchange part 3b.
Therefore, a predetermined interval is ensured between the end of the fourth heat exchange part 3d in the left half 30a and the right half 30b and the panel 31. By securing this distance, the space surrounded by the left half 30a and the space surrounded by the right half 30b are integrated to form the inner space 50 described above.

It is desirable that the end of the first heat exchanging part 3a and the end of the fourth heat exchanging part 3d are arranged outside the outer diameters of the propeller fans 41a and 41b as will be described later.
Incidentally, the end portion of the first heat exchange unit 3a in the present embodiment is disposed on the outer side in the left-right direction with respect to the respective rotation centers Ax of the propeller fans 41a and 41b.

In addition, in the outdoor heat exchanger 3 shown in FIG. 4, the outer edge part of the outdoor heat exchanger 3 and the propeller fans 41a and 41b has overlapped partially by planar view seen from the outdoor air blower 4 side. However, the propeller fans 41 a and 41 b may be configured to be disposed inside the outdoor heat exchanger 3.

The fourth heat exchange portions 3d of the left half 30a and the right half 30b face each other, and form parallel portions with each other in the vicinity of the ends. A gap 39 is formed between the facing portions of the fourth heat exchange portion 3d.
The gap 39 is a plan view of the outdoor heat exchanger 3 viewed from the outdoor fan 4 side, and the width of the gap 39 (the left-right width in FIG. 4) is gradually narrowed from the back side to the front side of the outdoor unit 90. It has become.
The width W1 of the gap 39 at the end of the fourth heat exchange part 3d is the narrowest.

In the outdoor heat exchanger 3, the fourth heat exchange part 3d in the left half 30a and the fourth heat exchange part 3d in the right half 30b are joined via a substantially U-shaped joining pillar 40 in a sectional view. Has been. The joining pillar 40 corresponds to a “joining member” in the claims.

FIG. 5 is an overall perspective view of the outdoor heat exchanger 3 constituting the outdoor unit 90.
As shown in FIG. 5, the joining pillar 40 extends in the vertical direction between the fourth heat exchange part 3d in the left half 30a and the fourth heat exchange part 3d in the right half 30b. .
The joining pillar 40 is formed such that the gap 39 is formed between the fourth heat exchanging part 3d in the left half 30a and the fourth heat exchanging part 3d in the right half 30b, while the left half 30a and the right half 30a are formed. The body 30b is integrally connected.

In FIG. 5, the code | symbol 38 is a side plate long in the up-down direction connected to the edge part of the 1st heat exchange part 3a. The side plate 38 covers a folded portion (not shown) of the refrigerant pipe formed at the end of the first heat exchange unit 3a. The lower end of the side plate 38 is fixed to the base member 12 (see FIG. 4), and the upper end of the side plate 38 is fixed to the top plate 13 (see FIG. 3).
Moreover, the code | symbol 3b is a 2nd heat exchange part, the code | symbol 3c is a 3rd heat exchange part, and the code | symbol 3d is a 4th heat exchange part. Reference numeral 21 is a branch pipe, and reference numeral 37 is a connecting pipe that connects the branch pipe 21 and a refrigerant pipe (not shown) of the outdoor heat exchanger 3.

As shown in FIG. 4, the minimum width W1 of the gap 39 on the end side of the fourth heat exchanging portion 3d is obtained when the distance from the side surface of the outdoor unit 90 to the outer side surface of the second heat exchanging portion 3b is W2. It is desirable to set the distance larger than twice the distance W2.
The joining pillar 40 closes an opening formed between the end of the fourth heat exchange part 3d in the left half 30a and the end of the fourth heat exchange 3d in the right half 30b. The outside air is prevented from entering the inner space 50 through the opening.

Incidentally, the lower end of the joining pillar 40 is fixed to the base member 12 (see FIG. 4), and the upper end of the joining pillar 40 is fixed to the top plate 13 (see FIG. 3).
The service space 31a is secured between the end of the first heat exchanging part 3a in the left half 30a and the end of the first heat exchanging part 3a in the right half 30b.

The service space 31a is an access opening to the inner space 50, and for example, allows access to devices arranged in the inner space 50.
A panel 31 (see FIG. 2) is detachably attached to the service space 31a so as to close the service space 31a.

As shown in FIG. 4, the refrigerant branch pipe 21 is connected to the front end of the fourth heat exchanging section 3 d via the connecting pipe 37 as described above.
The branch pipe 21 connected to one fourth heat exchange part 3d of the pair of fourth heat exchange parts 3d, 3d is opposite to the other fourth heat exchange part 3d aligned with the fourth heat exchange part 3d. Placed in.
That is, the branch pipe 21 attached to the left half 30a is arranged at a position shifted to the left from the position of the fourth heat exchange part 3d of the left half 30a. The connecting pipe 37 connected to the refrigerant pipe (not shown) at the end of the fourth heat exchanging portion 3d extends forward from the end of the fourth heat exchanging portion 3d and then reverses clockwise. It is connected to the branch pipe 21 (by changing the extending direction by 180 ° so as to bend to the left side).

Further, the branch pipe 21 attached to the right half 30b is arranged at a position shifted to the right from the position of the fourth heat exchange part 3d of the right half 30b. Then, the connecting pipe 37 connected to the refrigerant pipe (not shown) at the end of the fourth heat exchanging part 3d extends forward from the end of the fourth heat exchanging part 3d and then reverses counterclockwise. It is connected to the branch pipe 21 (by changing the extending direction by 180 ° so as to be bent to the right).

Each end portion of the first heat exchanging portion 3a in the left half body 30a and the right half body 30b is disposed outside the rotation radius (outer diameter) of the propeller fans 41a and 41b.
Further, the fourth heat exchanging part 3d in the left half 30a and the right half 30b has an end extending from the back side to the front side of the outdoor unit 90, and the rotation radius (outer diameter) of the propeller fans 41a and 41b. It is arranged outside.

Further, the length L1 from the rear end of the outdoor heat exchanger 3 to the end (front end) of the fourth heat exchange part 3d is the length from the rear end of the outdoor heat exchanger 3 to the front end of the outdoor heat exchanger 3. It is desirable that it is not more than half of L2 (L1 ≦ L2 / 2).
In addition, when the distance from the rear end of the outdoor heat exchanger 3 to the rotation center Ax of the propeller fan 41 is L3, it is desirable to set the distances L1 and L3 so that the distance L1 <the distance L3. It is more desirable to set the distance L1 to be larger than half of the distance L3.

<Operation effect of air conditioner>
Next, the effect which the air conditioner 100 provided with the above outdoor unit 90 show | plays is demonstrated.
In the air conditioner 100 of this embodiment, each of the left half 30a and the right half 30b constituting the outdoor heat exchanger 3 includes a first heat exchange unit 3a, a second heat exchange unit 3b, and a third heat exchange unit. 3c and the 4th heat exchange part 3d. Accordingly, each of the left half 30a and the right half 30b takes outside air into the inner space 50 from the four directions of front, rear, left and right.

Therefore, according to the outdoor unit 90, unlike the conventional outdoor unit (see, for example, Patent Document 1), outside air is taken into the inner space 50 via the outdoor heat exchanger 3 arranged in four directions, front, rear, left, and right. It is done.
Therefore, according to this outdoor unit 90, compared with the conventional outdoor unit (for example, refer patent document 1), the wind speed distribution of the circumferential direction of the propeller fan 41 is made more uniform, and ventilation performance can be improved further. it can.

Further, according to the outdoor unit 90, the first heat exchange unit 3a, the second heat exchange unit 3b, the third heat exchange unit 3c, and the fourth heat exchange unit 3d are arranged along the outer periphery of the outdoor unit 90. Therefore, the inner space 50 can be used effectively, and the increase in the size of the outdoor unit 90 is suppressed.

Moreover, according to this outdoor unit 90, since the heat transfer performance of the outdoor heat exchanger 3 can be improved and the ventilation resistance can be reduced without increasing the size of the outdoor unit 90, it is excellent in energy saving performance and compact. It is possible to provide the air conditioner 100 that can achieve the above.

Moreover, the outdoor heat exchanger 3 in this embodiment differs from what the edge parts of the conventional half body oppose (for example, refer patent document 2) toward the front side from the back side of the outdoor unit 90. The extending end portions of the fourth heat exchange section 3d of the left half body 30a and the right half body 30b do not face each other but face each other in the parallel direction (see FIG. 4).

In the case where the ends of the conventional halves face each other, it is necessary to secure an extra space between the halves in order to avoid interference between the pipes extending from each end.
On the other hand, in the outdoor heat exchanger 3 in the present embodiment, the end portions of the fourth heat exchanging portion 3d face each other in the parallel direction (see FIG. 4), and therefore the connecting pipe extending from the end portion. 37 do not interfere with each other. Therefore, it is not necessary to secure an extra space between the left half 30a and the right half 30b, and the left half 30a and the right half 30b can be arranged close to each other.
Therefore, according to the outdoor unit 90 of the present embodiment, it is possible to achieve downsizing.
Moreover, according to the outdoor unit 90 of the present embodiment, the degree of freedom in structural design around the end of the fourth heat exchange unit 3d is also increased.

Moreover, since the outdoor heat exchanger 3 of this embodiment has the 4th heat exchange part 3d extended | stretched from the back side to the front side, it is outdoor heat rather than the conventional outdoor unit (for example, refer patent document 2). An even larger heat exchange surface of the exchanger 3 can be secured. Moreover, since the 4th heat exchange part 3d has in both the left half 30a and the right half 30b, the increase effect of a heat exchange surface is doubled. Therefore, this outdoor unit 90 is excellent in energy saving performance.

Moreover, according to the outdoor unit 90 in the present embodiment, the outside air is supplied to the fourth heat exchange unit 3d of the left half 30a and the right half 30b through the gap 39 (see FIG. 4). That is, in the conventional outdoor unit (for example, refer to Patent Document 2), unlike the extra space formed between the end portions of the half bodies, the gap 39 in the present embodiment has the outdoor heat exchanger 3 ( It can be effectively used as an outside air supply path for the fourth heat exchange section 3d). Therefore, the outdoor unit 90 of this embodiment can increase the heat exchange surface of the outdoor heat exchanger 3 without enlarging the external dimension of the outdoor unit 90. Therefore, this outdoor unit 90 is excellent in energy saving performance and can achieve downsizing.

Next, FIG. 6 referred to is a schematic diagram showing the air flow in the inner space 50 of the outdoor heat exchanger 3 when the propeller fans 41a and 41b are driven.
In a conventional outdoor unit (for example, see Patent Document 2), a swirl flow is generated in the same direction as the rotation direction of the blower on the outside air suction side. Therefore, assuming that both of the propeller fans provided in the pair of halves rotate counterclockwise when viewed from above, each propeller fan rotates on the upstream side of each propeller fan (inside the outdoor heat exchanger). A counterclockwise swirling flow is generated depending on the direction.

As a result, in the adjacent region between the two counterclockwise swirling flows, that is, in the central portion in the left-right direction of the inner space, the swirling flows interfere with each other because they flow in opposite directions. Therefore, in the conventional outdoor unit (for example, refer to Patent Document 2), the interference between the swirling flows is a factor that reduces the blowing performance of the blower.

On the other hand, in the outdoor unit 90 of the present embodiment, as shown in FIG. 6, the outside air passes through the fourth heat exchange unit 3d through a gap 39 formed on the back side of the outdoor heat exchanger 3.
The outside air that has passed through the fourth heat exchanging portion 3d of the right half 30b generates a rightward air flow FR on the upstream side of the right propeller fan 41b (the inner space 50 of the outdoor heat exchanger 3). The air flow FR is changed so that the swirling flow that flows toward the lower side of the sheet of FIG.

Also, the outside air that has passed through the fourth heat exchanging portion 3d of the left half 30a generates a leftward air flow FL on the upstream side of the left propeller fan 41a (the inner space 50 of the outdoor heat exchanger 3). This air flow FL changes the swirl flow that flows toward the upper side of the sheet of FIG. 6 at the center in the left-right direction of the inner space 50 so as to flow to the left.

This suppresses the interference of airflow induced by the left and right propeller fans 41a and 41b. Therefore, in the outdoor unit 90, the energy saving performance of the propeller fans 41a and 41b can be improved by suppressing the interference of the airflow.

Further, as shown in FIG. 6, a distance T is secured between the outflow surfaces of the air flows FR and FL in the pair of fourth heat exchange portions 3d and 3d. And by ensuring this distance T, a predetermined distance will be ensured between the center part of the inner side space 50 prescribed | regulated between the propeller fans 41a and 41b, and the said outflow surface. . That is, interference in the central portion of the inner space 50 due to the air flows FR and FL is also reduced.

Further, as shown in FIG. 6, in this outdoor unit 90, the amount of air flowing into the inner space 50 from the back side is larger than the amount of air flowing into the inner space 50 from the front side where the panel 31 is located. That is, the air that has flowed into the inner space 50 from the back side of the outdoor heat exchanger 3 flows toward the panel 31 side. Therefore, the interference of the air flow in the central portion of the inner space 50 is more reliably reduced.

In the outdoor unit 90, as described above, the minimum width W1 of the gap 39 on the end side of the fourth heat exchange unit 3d is from the side surface of the outdoor unit 90 to the outer side surface of the second heat exchange unit 3b. When the distance is W2, it is desirable to set it to be larger than twice the distance W2 (see FIG. 4).
According to such an outdoor unit 90, the gap 39 can be sufficiently secured, and the heat exchange performance in the fourth heat exchange unit 3d can be further improved.

In the outdoor unit 90, as described above, the length L1 from the rear end of the outdoor heat exchanger 3 to the end (front end) of the fourth heat exchange unit 3d is the rear end of the outdoor heat exchanger 3. It is desirable that it is not more than half of the length L2 from the front end of the outdoor heat exchanger 3 (L1 ≦ L2 / 2).

For example, assuming that a plurality of outdoor units 90 are installed side by side in the left-right direction, it is conceivable that outside air is preferentially taken into the inner space 50 of each outdoor unit 90 from the back side.
Therefore, it is desirable to allow the outside air to efficiently pass through also in the fourth heat exchange unit 3d.
On the other hand, according to the outdoor unit 90 in which the distances L1 and L2 are defined as described above, the outside air can be passed efficiently even in the fourth heat exchange unit 3d. Thereby, since the outside air can be effectively taken into the inner space 50, the outdoor unit 90 is further excellent in energy saving performance.

Further, in the outdoor unit 90, as described above, when the distance from the rear end of the outdoor heat exchanger 3 to the rotation center Ax of the propeller fan 41 is L3, the distance L1 <the distance L3 is satisfied. It is desirable to set the distances L1 and L3. It is more desirable to set the distance L1 to be larger than half of the distance L3.

As described above, according to the outdoor unit 90 that defines the distances L1 and L3, the flow of outside air that passes through the fourth heat exchanging portion 3d and moves toward the inner space 50 is not interfered with the flow of air in the vicinity of the panel 31. Therefore, this outdoor unit 90 can maintain the ventilation performance by the propeller fans 41a and 41b well, and can improve the heat exchange performance in the fourth heat exchange section 3d. Further, by setting the distance L1 to be larger than half of the distance L3, the heat exchange performance in the fourth heat exchange part 3d can be improved, and the interference between the air flows in the central part of the inner space 50 is effective. Can be suppressed.

This outdoor unit 90 can further improve the blowing performance and the heat exchange performance even when the propeller fans 41a and 41b are brought close to each other by arranging the fourth heat exchange section 3d as described above. it can.

In the outdoor unit 90, as described above, the end of the first heat exchanging unit 3a and the end of the fourth heat exchanging unit 3d are larger than the rotation radius (outer diameter) of the propeller fans 41a and 41b. Arranged outside. Thereby, the ventilation resistance by the propeller fans 41a and 41b with respect to the edge part of the 1st heat exchange part 3a and the edge part of the 4th heat exchange part 3d is relieved. Thereby, since the propeller fans 41a and 41b and the outdoor heat exchanger 3 can be arranged closer to each other in the vertical direction, the outdoor unit 90 can be made compact.

In the outdoor unit 90, as described above, the branch pipe 21 connected to one of the pair of fourth heat exchange units 3d, 3d is connected to the fourth heat exchange unit. It is arrange | positioned on the opposite side of the other 4th heat exchange part 3d along with 3d.

According to such an outdoor unit 90, for example, compared to a configuration in which the branch pipe 21 is arranged in front of the end of the fourth heat exchange unit 3d, the outdoor unit 90 is secured in front of the end of the fourth heat exchange unit 3d. The inner space 50 increases. Therefore, the 4th heat exchange part 3d can extend the length of the 4th heat exchange part 3d further ahead according to the increase in the inside space 50.
Thereby, since the heat exchange surface of the outdoor heat exchanger 3 increases, the outdoor unit 90 can further improve energy saving performance.
Further, for example, since the branch pipe 21 is not arranged in front of the end of the fourth heat exchange part 3d, there is a margin in the arrangement space of the joining pillar 40 that connects the ends of the fourth heat exchange part 3d. Thereby, the freedom degree of the structural design around the edge part of the 4th heat exchange part 3d expands.

In addition, at the position shifted laterally from the end of the fourth heat exchanging part 3d where the branch pipe 21 is arranged as described above, the air flow is larger than that in front of the end of the fourth heat exchanging part 3d. Get faster.
Therefore, according to this outdoor unit 90, the branch pipe 21 itself exposed to this fast air flow is utilized as a heat exchanger.

When the branch pipes 21a and 21b are to function as heat exchangers themselves, the outside air that has passed through the outdoor heat exchanger 3 is discharged to the propeller fans 41a and 41b at a relatively short distance. It is desirable to be arranged on the passage route of some outside air.

FIG. 7 is a plan view of the outdoor unit 90 illustrating the regions 51a and 51b in which the outdoor air that has passed through the outdoor heat exchanger 3 is discharged by the outdoor blower 4 ( propeller fans 41a and 41b) at a relatively short distance. .
As shown in FIG. 7, the regions 51 a and 51 b are defined by a region surrounded by the outdoor heat exchanger 3 and a line segment connecting the end of the outdoor heat exchanger 3 and the rotation center of the propeller fans 41 a and 41 b. Is done.
The branch pipes 21a and 21b arranged in the regions 51a and 51b can function as a heat exchanger.

As mentioned above, although this embodiment was described, this invention is not limited to the said embodiment, It can implement with a various form.
(Example of arrangement of cycle components)
The four-way valve 2 and the accumulator 5 (see FIG. 1) in the outdoor unit 90 of the air conditioner 100 (see FIG. 1) of the present invention can be arranged at the next position in the inner space 50.
FIG. 8 is a plan view of the outdoor unit 90 showing a first arrangement example of the four-way valve 2 and the accumulator 5 in the inner space 50 of the outdoor unit 90. FIG. 9 is a plan view of the outdoor unit 90 showing a second arrangement example of the four-way valve 2 and the accumulator 5 in the inner space 50 of the outdoor unit 90.

As shown in FIG. 8, in the first arrangement example, the machine room housing 32 that houses the pair of compressors 1 is arranged in the front center portion of the inner space 50. Further, the four-way valve 2 and the pipe connecting portions 15 and 16 are disposed in the inner space 50 corresponding to the left propeller fan 41a. The pipe connection parts 15 and 16 are arranged close to the left side of the machine room housing 32.
In the outdoor unit 90, the accumulator 5 is disposed in the inner space 50 corresponding to the right propeller fan 41b.

In such an outdoor unit 90, when an operator whose right hand is right faces the inner space 50 through the service space 31a, the right hand is used with respect to the pipe connection portions 15 and 16 disposed on the left side of the inner space 50. Easy maintenance.

Further, when the pipe connection portions 15 and 16 are accessed with the right hand via the service space 31a, even if the positions of the pipe connection portions 15 and 16 are shifted to the right side, the operator can move the pipe connection portions 15 and 16 to the pipe connection portions 15 and 16. It can be easily accessed.

When the positions of the pipe connecting portions 15 and 16 are shifted to the right as described above, the position of the front end of the left half 30a can also be shifted to the right. That is, the heat exchange surface of the outdoor heat exchanger 3 increases. Therefore, the outdoor unit 90 can improve energy saving performance.
Incidentally, it is desirable that the pipe connection part 16 is disposed closer to the four-way valve 2 than the pipe connection part 15. That is, the gas refrigerant that returns to the outdoor unit 90 during the cooling operation flows in this order to the pipe connection unit 16, the four-way valve 2, the accumulator 5, and the compressor 1, as shown in FIG. Therefore, in the outdoor unit 90 in which the pipe connection part 16 and the four-way valve 2 are close as described above, the pressure loss in the refrigerant flow path is reduced and the energy saving performance is improved.

In the outdoor unit 90, since the accumulator 5 is disposed in the inner space 50 corresponding to the right propeller fan 41b, the accumulator 5 is located on the left side with respect to the inner space 50 in which the four-way valve 2 and the pipe connecting portions 15 and 16 are disposed. This makes it easier to balance the weight.
Assuming that the operator with the dominant arm on the left performs maintenance, a configuration in which the four-way valve 2 and the pipe connecting portions 15 and 16 are disposed in the inner space 50 corresponding to the right propeller fan 41b is desirable.
That is, in the first arrangement example, it is desirable that both the four-way valve 2 and the pipe connection portions 15 and 16 are arranged in the inner space 50 corresponding to one of the left and right propeller fans 41a and 41b.

Moreover, the outdoor unit 90 in which the accumulator 5 is arranged in the right inner space 50 can also provide the following operational effects.
Returning to FIG. 6, on the rear side of the panel 31 of the outdoor unit 90, the flow in the right direction parallel to the panel 31 (not shown) generated by the left propeller fan 41a and the rear side generated by the right propeller fan 41b. The flow (not shown) toward the front panel 31 interferes.

Therefore, on the rear side of the panel 31, a large clockwise vortex FV is formed slightly to the left from the center of the inner space 50. Accordingly, when the blowing efficiency of both propeller fans 41a and 41b is compared, the blowing efficiency of the left propeller fan 41a is relatively suppressed.

Under such conditions, when the accumulator 5 that generates ventilation resistance is disposed in the inner space 50 corresponding to the right propeller fan 41b, the blowing efficiency of the left and right propeller fans 41a and 41b is balanced. Thereby, since this outdoor unit 90 can improve the ventilation efficiency as a whole, energy saving performance improves.

In addition, balance adjustment of the ventilation efficiency of propeller fan 41a, 41b can be performed also by changing the rotational speed of propeller fan 41a, 41b. In addition, the balance adjustment of the blowing efficiency can be performed by arranging a device that generates ventilation resistance in the inner space 50 and changing the rotation speed of the propeller fans 41a and 41b.

Moreover, as shown in FIG. 9, the outdoor unit 90 can also arrange | position the piping connection parts 15 and 16, the four-way valve 2, and the accumulator 5 in the inner side space on the same side.
According to such an outdoor unit 90, the length of the pipe connecting the four-way valve 2 and the accumulator 5 can be shortened. Thereby, the pressure loss in piping can be reduced and the outdoor unit 90 can further improve energy saving performance.

Further, since the low-pressure gas pipe having a large diameter, represented by the pipe connecting the four-way valve 2 and the accumulator 5, can be mainly concentrated in the left inner space 50, the right inner space 50 has a relatively small diameter on the liquid side. Will be mainly arranged. Therefore, even when the space for communicating the left and right inner spaces 50 is narrow, the piping can be relatively easily arranged, and the degree of freedom in designing the outdoor unit 90 can be improved.

The two compressors 1 are arranged in parallel along the panel 31. However, when the compressor 1 having a variable rotational speed and the compressor 1 having a constant rotational speed are used in combination, the compressor 1 having a variable rotational speed that tends to increase the operation time is disposed on the panel 31 side. You can also

(Eccentricity of propeller fan rotation center)
The rotation center of the propeller fans 41a and 41b in the outdoor unit 90 of the air conditioner 100 (see FIG. 1) of the present invention can be decentered with respect to the rotation center in the above embodiment.
FIG. 10 is a plan view of the outdoor unit 90 showing an example of eccentricity of the propeller fans 41a and 41b.
In FIG. 10, reference sign HA0 is a central axis in the left-right direction of the outdoor unit 90, and reference signs HA1 and HA2 are central axes in the left-right direction in the left half 30a and the right half 30b of the outdoor heat exchanger 3, respectively. , DA1 is the central axis of the outdoor unit 90 in the front-rear direction.

Each of the central axis FCa of the propeller fan 41a and the central axis FCb of the propeller fan 41b is eccentric to the HA0 side with respect to the central axis HA1 and the central axis HA2.
Each of the central axis FCa of the propeller fan 41a and the central axis FCb of the propeller fan 41b is eccentric to the panel 31 side with respect to the central axis DA1.

FIG. 11 is a longitudinal sectional view of the outdoor heat exchanger 3 in the longitudinal center axis DA1, and FIG. 11 (a) is an operation explanatory view of the outdoor unit 90 when the central axis FCa of the propeller fan 41a is eccentric. b) is an operation explanatory diagram of the outdoor unit 90 when the central axis FCa of the propeller fan 41a is not decentered.
As shown in FIG. 11B, in the outdoor unit 90 in which the center axis FCa is not decentered, outside air that has passed through the left half 30a flows near the center axis HA0 and then flows into the propeller fan 41a.

On the other hand, as shown in FIG. 11A, in the outdoor unit 90 in which the center axis FCa is eccentric, the outside air that has passed through the left half 30a is prevented from spreading to the center axis HA0, and the propeller fan 41a. Sucked into.
Therefore, in the outdoor unit 90 in which the center axis FCa is eccentric, the bending of the flow of the outside air is corrected and the blowing efficiency is improved.

Further, in the outdoor unit 90 in which the central axis FCa shown in FIG. 11A is eccentric, the velocity component of the outside air flowing in the horizontal direction relative to the propeller fan 41a is relatively reduced. Thereby, the outdoor unit 90 increases the speed component in the axial direction and improves the blowing efficiency.

Although not shown, even in the outdoor unit 90 in which the center axis FCa is eccentric to the panel 31 side, the bending of the outside air is suppressed in the vicinity of the panel 31, and the outside air is efficiently sucked into the propeller fan 41a.
That is, each of the central axis FCa of the propeller fan 41a and the central axis FCb of the propeller fan 41b is eccentric to the HA0 side with respect to the central axis HA1 and the central axis HA2, and is closer to the panel 31 side with respect to the central axis DA1. The ventilation efficiency of the eccentric outdoor unit 90 is most excellent.

Further, in the outdoor unit 90 in which the fourth heat exchange unit 3d extends from the back side to the front side, the airflow in the left-right direction generated by the propeller fans 41a and 41b is blocked on the back side of the outdoor unit 90.
Therefore, the airflow to the front center part of the outdoor unit 90 becomes remarkable. Therefore, the blowing efficiency can be improved by decentering the central axes FCa and FCb of the propeller fans 41a and 41b toward the panel 31 and decentering toward the central axis HA0.

Further, in the outdoor unit 90 in which the central axes FCa and FCb of the propeller fans 41a and 41b are eccentric to the panel 31 side and the central axis HA0 side, the propeller fans 41a and 41b are separated from the outdoor heat exchanger 3. Thereby, the bending of the airflow when the outside air that has passed through the outdoor heat exchanger 3 flows upward is suppressed. Thereby, the outdoor unit 90 can improve the air blowing efficiency more effectively. Moreover, in this outdoor unit 90, since the bending of the airflow at the time of flowing upward is suppressed, the air path loss of the inner space 50 is also reduced.

Further, the end of the first heat exchanging portion 3a is disposed on the outer side in the left-right direction with respect to the rotation centers Ax of the propeller fans 41a and 41b (see FIG. 4). Therefore, even if the central axes FCa and FCb of the propeller fans 41a and 41b are eccentric to the panel side, the blowing resistance by the propeller fans 41a and 41b with respect to the end of the first heat exchange unit 3a is alleviated.

Moreover, the 4th heat exchange part 3d is extended | stretched toward the front side from the back side (refer FIG. 4). Therefore, even if the central axes FCa and FCb of the propeller fans 41a and 41b are decentered toward the central axis HA0, the fourth heat exchange part 3d functions as a partition wall. Airflow interference is mitigated. According to this outdoor unit 90, for example, unlike the case where a partition plate or the like is separately provided in the vicinity of the central axis HA0 of the outdoor unit 90, it is possible to achieve excellent air blowing performance and compactness.

Further, the eccentric amounts of the central axes FCa and FCb of the propeller fans 41a and 41b can be different from each other.
As shown in FIG. 10, the eccentric amount of the central axis FCb of the right propeller fan 41b is larger than the eccentric amount of the central axis FCa of the left propeller fan 41a.

By the way, when the rotation direction of the propeller fans 41a and 41b is set to be counterclockwise (counterclockwise) as described above, the rear side of the panel 31 is slightly leftward from the center of the inner space 50 as shown in FIG. A large clockwise vortex FV is formed. As a result, the left propeller fan 41a has a relatively low blowing efficiency.
Therefore, the vortex FV is less likely to occur by relatively increasing the amount of eccentricity of the central axis FCb of the right propeller fan 41b. Thereby, as for the outdoor unit 90, the ventilation efficiency as a whole improves, and energy saving performance is improved.

Note that the relative eccentricity of the central axes FCa and FCb of the propeller fans 41a and 41b can also be different in the front-rear direction.
Further, it is sufficient that at least one of the central axes FCa and FCb is eccentric to the panel 31 side and / or the central axis HA0 side, and the other is not eccentric. Moreover, if one side is eccentric to the panel 31 side and / or the central axis HA0 side, the other side can also be configured to be eccentric to the back side and / or the side surface side of the outdoor unit 90.

(Velmouth variant)
FIG. 12A is a plan view schematically showing a state in which the outdoor blower 4 is viewed from above the outdoor unit 90, and FIG. 12B is a cross-sectional view taken along the line XII-XII in FIG. In addition, in Fig.12 (a), the left half 30a and the right half 30b of the outdoor heat exchanger 3 are shown with the hidden line (broken line).

As shown in FIGS. 12A and 12B, the rotation center of the propeller fans 41a and 41b of the outdoor unit 90 is decentered toward the center of the outdoor unit 90, so that the left and right bell mouths 43 are also shifted toward the center. is doing. Thereby, the left and right bell mouths 43 are fused with each other on the adjacent side, and a part of the partition wall 43a between the bell mouths 43 is shared.
Incidentally, the bell mouth 43 is not fused with the casing 44 outside the bell mouth 43 in the left-right direction.

Although not shown, when the outer diameters of the propeller fans 41a and 41b are increased to improve the blowing performance of the outdoor blower 4, the bell mouth 43 that is expanded in accordance with the increased size is fused on the adjacent side. It can also be. In this case, the bell mouth 43 and the casing 44 may be fused on the outside of the bell mouth 43.

(Modification of the first heat exchange unit)
FIG. 13 is a plan view of the outdoor unit 90 for explaining a modification of the first heat exchange unit 3a in the outdoor heat exchanger 3. FIG.
As shown in FIG. 13, the first heat exchanging part 3 a is a first heat exchanging part 3 a extending from one end side of the second heat exchanging part 3 b arranged on the side surface of the outdoor unit 90 toward the front side of the outdoor unit 90. Is larger than 90 degrees. Specifically, the internal angle formed by the first heat exchange unit 3a and the second heat exchange unit 3b is set to 120 degrees.

That is, in the outdoor unit 90 (refer FIG. 4) of the said embodiment, it arrange | positions so that the 1st heat exchange part 3a may follow the front edge of the outdoor unit 90, in other words, in parallel with the 3rd heat exchange part 3c. Yes. On the other hand, the first heat exchange unit 3a shown in FIG. 13 extends in a shortcut manner from the front side to the side surface side of the outdoor unit 90 and is connected to the second heat exchange unit 3b, in other words, the third heat exchange unit 3a. It arrange | positions so that it may incline with respect to the heat exchange part 3c.

4th heat exchange part 3d is comprised similarly to the outdoor unit 90 (refer FIG. 4) in the said embodiment.

According to the outdoor unit 90 shown in FIG. 13 as described above, since the internal angle formed by the first heat exchange unit 3a and the second heat exchange unit 3b is set to be larger than 90 degrees, the outdoor heat exchanger 3 is folded. The manufacturing process is facilitated when manufacturing by bending. This is particularly advantageous when reducing the size of the outdoor heat exchanger 3 in order to reduce the size of the outdoor unit 90.

Further, according to the outdoor unit 90 shown in FIG. 13, as described above, the first heat exchanging part 3 a extends as a shortcut from the front side to the side surface side of the outdoor unit 90, so the first heat exchanging part 3 a A distance can be provided between the support frame 11 and the support frame 11.
Therefore, an air flow can be efficiently guided between the support frame 11 and the first heat exchange unit 3a, and the heat exchange performance of the first heat exchange unit 3a can be further enhanced.

Further, according to the outdoor unit 90 shown in FIG. 13, when the plurality of outdoor units 90 are installed adjacent to each other, the distance between the first heat exchange units 3a arranged between the adjacent outdoor units 90 is as shown in FIG. 4 is wider than the outdoor unit 90 shown in FIG. Therefore, the amount of air supplied to the first heat exchange unit 3a increases. Therefore, according to the outdoor unit 90 shown in FIG. 13, when the plurality of outdoor units 90 are installed adjacent to each other, the arrangement interval between the outdoor units 90 can be reduced. The floor area required for construction is reduced.

(Modification of the fourth heat exchange part)
FIG. 14 is a plan view of the outdoor unit 90 for describing a modification of the fourth heat exchange unit 3d in the outdoor heat exchanger 3. FIG.
As shown in FIG. 14, in this outdoor unit 90, the internal angle formed by the fourth heat exchange unit 3d with respect to the third heat exchange unit 3c extending along the back surface of the outdoor unit 90 is greater than 90 degrees. . Specifically, the internal angle formed by the third heat exchange unit 3c and the fourth heat exchange unit 3d is set to 120 degrees. The 1st heat exchange part 3a and the 2nd heat exchange part 3b are comprised similarly to the outdoor unit 90 shown in FIG.

According to the outdoor unit 90 shown in FIG. 14 as described above, the fourth heat exchanging units 3d are not parallel to each other, so that the bending of the air flow taken into the inner space 50 from the back side of the outdoor unit 90 is suppressed. Therefore, according to this outdoor unit 90, ventilation efficiency improves and energy-saving performance is improved further.

Further, according to the outdoor unit 90 shown in FIG. 14, the fourth heat exchanging unit 3 d is inclined with respect to the back surface of the outdoor unit 90, so that the inner space 50 is increased between the fourth heat exchanging unit 3 d and the panel 31. Can be secured. Therefore, according to the outdoor unit 90, the degree of freedom in the layout of the device arrangement with respect to the inner space 50 is further increased. In particular, when the four-way valve 2 (see FIG. 1) and the accumulator 5 (see FIG. 1) are arranged separately in the inner space 50, the outdoor unit 90 can shorten the piping connecting them, thus saving Energy performance can also be improved.
In addition, in the outdoor unit 90 shown in FIG. 14, the 1st heat exchange part 3a and the 2nd heat exchange part 3b can also be arrange | positioned similarly to the outdoor unit 90 shown in FIG.

DESCRIPTION OF SYMBOLS 1 Compressor 2 Four-way valve 3 Outdoor heat exchanger 3a 1st heat exchange part 3b 2nd heat exchange part 3c 3rd heat exchange part 3d 4th heat exchange part 4 Outdoor fan 4a Outdoor fan 4b Outdoor fan 5 Accumulator 6 Outdoor expansion valve DESCRIPTION OF SYMBOLS 7 Indoor heat exchanger 8 Indoor expansion valve 10 Piping 11 Support frame 12 Base member 13 Top plate 15 Piping connection part 16 Piping connection part 21 Branch pipe 30a Left half body 30b Right half body 31 Panel 31a Service space 32 Machine room housing 33 Electricity Box 35 Radiator 37 Connecting pipe 38 Side plate 39 Gap 40 Joining pillar 41 Propeller fan 41a Propeller fan 41b Propeller fan 42 Motor 43 Bell mouth 44 Casing 50 Inner space 90 Outdoor unit 91 Indoor unit 100 Air conditioner

Claims (15)

1. A pair of fans arranged side by side;
   A heat exchanger disposed so as to surround an inner space formed on the lower side on the upstream side of the blower,
   The heat exchanger has a pair of halves symmetrical to each other and arranged to correspond to each of the pair of fans.
   Each of the halves extends continuously while partially bending so as to surround the blower in a plan view seen from the corresponding blower side, a first heat exchange part, a second heat exchange part, and a third It has a heat exchange part and a 4th heat exchange part in this order,
   An air conditioner comprising an outdoor unit having the heat exchanger in which a pair of the half bodies are joined via the fourth heat exchange units.
2. In the air conditioner according to claim 1,
   In a plan view of the heat exchanger seen from the blower side,
   The first heat exchange part and the third heat exchange part in the half are opposed to each other, and the second heat exchange part and the fourth heat exchange part are opposed to each other,
   The first heat exchange part side is defined as the front side of the heat exchanger, the third heat exchange part side is defined as the rear side of the heat exchanger, and the direction in which the second heat exchange parts face each other is the heat When it is defined as the width direction of the exchanger,
   The first heat exchange part is shorter than the third heat exchange part in the width direction,
   Between the ends of the first heat exchange part in each half, an opening facing the inner space is formed,
   An air conditioner, wherein a panel is detachably provided at the opening so as to close the opening.
3. In the air conditioner according to claim 2,
   The fourth heat exchange part is shorter than the second heat exchange part in the front-rear direction,
   A front end portion of the fourth heat exchange portion extending forward from the third heat exchange portion side faces the panel,
   A gap is formed between the fourth heat exchange parts of each half,
   An air conditioner provided between front ends of the fourth heat exchanging part, joining the halves and having a joining member separating the gap and the inner space.
4. In the air conditioner according to claim 3,
   The length L1 from the rear end of the heat exchanger to the front end of the fourth heat exchange unit is less than or equal to half the length L2 from the rear end of the heat exchanger to the front end of the heat exchanger (L1 ≦ L2 / 2), an air conditioner.
5. In the air conditioner according to claim 3,
   When the distance from the rear end of the heat exchanger to the rotation center of the propeller fan constituting the blower is L3, the length L1 from the rear end of the heat exchanger to the front end of the fourth heat exchange part is An air conditioner that is larger than half of the distance L3 and shorter than the distance L3 (L3 / 2 <L1 <L3).
6. In the air conditioner according to claim 3,
   The air conditioner characterized in that the end of the first heat exchanging part and the front end of the fourth heat exchanging part are arranged outside an outer diameter of a propeller fan constituting the blower.
7. In the air conditioner according to claim 3,
   The fourth heat exchange parts of the half are in parallel,
   A refrigerant branch pipe is connected to the front end of the fourth heat exchange section via a connecting pipe,
   The branch pipe connected to one of the pair of fourth heat exchange parts is arranged on the opposite side of the other fourth heat exchange part along with the fourth heat exchange part. ,
   The air conditioner characterized in that the branch pipe connected to the other fourth heat exchange part is disposed on the opposite side of the fourth heat exchange part along with the fourth heat exchange part.
8. In the air conditioner according to claim 3,
   The outdoor unit is a pipe to which a compressor constituting a refrigeration cycle, a four-way valve for changing a flow direction of refrigerant discharged from the compressor in the refrigeration cycle, and a refrigerant pipe connected to the indoor unit side are connected. A connecting portion,
   In the plan view of the half seen from the blower side,
   The air conditioner, wherein the four-way valve and the pipe connection portion are disposed in the inner space corresponding to one of the pair of blowers.
9. In the air conditioner according to claim 3,
   The outdoor unit has a refrigerant accumulator on the upstream side of the compressor of the cycle,
   In the plan view of the half seen from the blower side,
   The said accumulator is arrange | positioned in the said inner space corresponding to the said one air blower same as the said four-way valve and the said piping connection part, The air conditioner characterized by the above-mentioned.
10. The air conditioner according to claim 9,
    In a plan view of the half as viewed from the blower side, between the ends of the first heat exchange parts of each half, an opening facing the inner space is formed,
    A panel that closes the opening is disposed in the opening.
    The compressor is housed in a machine room arranged close to the panel,
    The air conditioner is characterized in that the pipe connection portion is disposed close to the machine room.
11. In the air conditioner according to claim 1,
    In a plan view of the half as viewed from the blower side, the rotation shafts of the propeller fans constituting the pair of blowers are decentered closer to the center of the inner space than the central axis of each half. Air conditioner.
12. The air conditioner according to claim 11,
    When the first heat exchanging part side is defined as the front side of the heat exchanger and the third heat exchanging part side is defined as the rear side of the heat exchanger, the half surface seen from the blower side The air conditioner characterized in that the rotation shafts of the propeller fans constituting the pair of blowers are decentered forward from the central axis of each half body.
13. The air conditioner according to claim 11,
    Each of the pair of blowers includes a propeller fan and a substantially cylindrical bell mouth arranged to surround the periphery of the propeller fan.
    The bell mouths are fused on the adjacent side and share a partition wall between the bell mouths.
14. The air conditioner according to claim 11,
    The air conditioner characterized in that the eccentric amounts of the rotation shafts of the pair of propeller fans with respect to the central axes of the half bodies are different from each other.
15. The air conditioner according to claim 11,
    When the first heat exchange unit side is defined on the front side of the outdoor unit and the third heat exchange unit side is defined on the back side of the outdoor unit, in a plan view of each blower viewed from above the blowers, When rotating each of the pair of propeller fans counterclockwise, the amount of eccentricity of the rotation shaft of the left propeller fan as viewed from the front of the pair of blowers is calculated as the amount of eccentricity of the rotation shaft of the right propeller fan. An air conditioner characterized by being smaller than the amount.

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