Blower and outdoor unit of air conditioner comprising same

Abstract

Provided are a blower, capable of suppressing noise occurring in a stator while significantly improving blowing efficiency, and an outdoor unit using the same. The present disclosure comprises: a bell mouth part spaced apart at a predetermined distance in the radial direction with respect to an outer circumferential end of a propeller fan; and a diffuser part installed on the downstream side of the bell mouth part, and having a flow path area which is enlarged from the upstream side toward the downstream side with a larger magnification rate than the magnification rate of the flow path area in the downstream end of the bell mouth part; and a stator part having a plurality of stators, wherein the stator part is arranged within the diffuser part.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

This application FIG. 1 isFIG. 3

Here, C is a coefficient in the range of 1.03≤C≤1.5, and more preferably in the range of 1.06≤C≤1.12.

According to equation (1), the strength of the container-shaped molded object 73 is secured, an installation space may be maximally used, influence of an adjacent blower 7 is significantly reduced, noise due to maximizing a diameter of the propeller fan may be reduced, etc.

Meanwhile, as illustrated in

Hereinafter, an operation and an effect of the outdoor unit 600 configured as described above will be described.

As illustrated in FIGS. 1 and 2, although the heat exchanger 6 is not disposed in the front of the casing 5, the heat exchanger 6 is disposed at a side of the casing 5, and thus more air is suctioned when the blower 7 is operated. In addition, since electric elements and the like disposed inside the casing 5 also have air resistance, in the present embodiment, a larger amount of air is introduced through an inlet (the bell mouth 82) of the blower 7 from front and rear portions of the bell mouth 82 where the number of elements which can serve as air resistance are few. As a result, in the diffuser part 9, an air flow rate is maximized in the front and rear portions and the air flow rate is minimized in both side portions.

As described above, since a diffuser angle θ at the front and rear portions of the diffuser part 9 is set to as large a value as possible in the range in which a turbulent current does not occur (here, a maximum of 35°) even though an air flow rate increases in the front and rear portions of the diffuser part 9, a viscosity loss due to the turbulent current is suppressed and thus a pressure restoring effect at this portion may be maximized.

In addition, when the diffuser angles θ at the front and rear portions are the same while the air flow rate at both side portions of the diffuser part 9 is decreased, because the diffuser angle θ enlarges such that the air flow becomes unstable and a loss occurs.

In contrast, according to the present embodiment, since the diffuser angle θ at this portion is set to a small value (a minimum of 3°), the above-described unstable air flow may be suppressed and a pressure restoring effect due to the diffuser part 9 at this portion may also be maximized.

That is, in the diffuser part 9 according to the present embodiment, since a loss due to an unstable air current such as a dispersion of the suction flow rate is suppressed as much as possible, a pressure restoring effect is maximized, and a blowing efficiency may be dramatically increased.

In addition, since the maximizing of the pressure restoring effect denotes that a flow rate in the diffuser part 9 is decreased, a blowing noise reduction may also be obtained.

In addition, in the present embodiment, since the blowers 7 are installed in series and the diffuser angles θ at adjacent portions are set to be small values, an angle of an air current discharged therefrom becomes approximately vertical, Interference of the air currents exhausted from both of the blower 7 may be suppressed, and thus low noise blowing at high efficiency may be possible.

Because the above-described D_ratio is set to 0.9 or less, a bending process of the top panel 51 is certainly possible at a position at which the outlet opening of the diffuser part 9 is closest to an edge of a top panel surface plate part 511, and thus the bent part 512 may be formed. Meanwhile, since D_ratio is set to 0.6 or more, an equalization of a change ratio of the outlet opening of the diffuser part outlet (a change ratio of the diffuser angle θ along a circumferential direction) of the diffuser part defined by D_ratio, an equalization of a flow change by reducing the change and improvement of noise performance may be obtained. In addition, a configuration related to this may also be applied to the top panel 51 having a rectangular shape as seen from the axis of rotation C.

Next, a modified example of the first embodiment will be described.

First, it is preferable that a diffuser angle be changed and an additional shape different from a circle be formed according to a shape of a downstream end opening of the diffuser part or, for example, a distribution of a suction flow rate. Since the distribution of the suction flow rate depends on at least an arrangement of internal apparatuses, it is preferable that, for example, a diffuser angle of the inclined surface positioned at a position at which the bell mouth parts are not vertically overlapped be set to be greater than the diffuser angle of the inclined surface positioned at a portion at which the internal apparatuses and the bell mouth part are vertically overlapped. Specifically, as illustrated in FIG. 4 FIGS. 4A, 4B, and 4C, a downstream end opening 9a of the diffuser part may have a shape such as a rectangular shape with rounded corners (see FIG. 4A), an oval shape (see FIG. 4B) or the like. In addition, for instance, when the downstream end opening 9a has the rectangular shape with rounded corners, a case in which the diffuser angle θ is maximized at the corners may occur. As described above, the air flow rate does not need to be a maximum at a position at which the diffuser angle θ is the maximum.

In the embodiment, although the diffuser angle θ smoothly and continuously varies along the circumferential direction so as to suppress an occurrence of turbulence and the like as much as possible, the diffuser angle θ may also vary discontinuously. In this case, as illustrated in FIG. 4C, the downstream end opening 9a has a shape with angles at discontinuous positions.

Although, the diffuser angle θ is set to 35° as a maximum and 3° as a minimum in the embodiment, it is not limited thereto. For example, the maximum value may also be less than 35°, and the minimum value may also be more than 3°. Particularly, the diffuser angle θ of a side of an adjacent blower is preferably in the range of 3°≤θ≤7°.

The diffuser angle θ may be formed to be smoothly changed step-by-step or continuously toward a downstream side as seen from a cross-section parallel to an axis of rotation. In this case, an enlargement rate of the flow path of the diffuser part increases toward the downstream side.

In the embodiment, although a height of the downstream end of the propeller fan 71 and a height of an upstream end of the diffuser part 9 are matched when seen from a direction perpendicular to the axis of rotation C as illustrated in FIG. 3 FIG. 3B, this may also be changed. Specifically, as illustrated in FIG. 5, when H denotes a value of an outer circumferential end of the propeller fan 71 along a shaft, and Z denotes a distance between the upstream end of the diffuser part 9 and the downstream end of the propeller fan 71 along the shaft, it is preferable that Z be in the range of H±20%. When set as described above, since a vortex discharged from the propeller fan smoothly decreases in speed and spreads along the inclined surface 91 of the diffuser part 9, a larger pressure restoring effect may be obtained.

A shape of the bell mouth duct is not limited to a cylindrical shape, and when the outer circumferential end of the propeller fan does not have a vertical shape, for example, the shape may be a partial cone shape corresponding thereto, or a noise prevention blade may be installed at the diffuser part. Such an example will be described in detail in a second embodiment.

The blower may not be limited to the outdoor unit, and may be used for various uses. For example, the blower may also be used for a blower having a ventilation fan or a blower connected to a duct for ventilation.

In addition, the blower is not limited to air and may obtain the same effect by being applied to a gas.

Second Embodiment

Next, a second embodiment of the present disclosure will be described. A blower 100 according to the present embodiment is formed by a resin injection mold, as illustrated in FIGS. 6 and 9, and includes a container-shaped molded object 1 formed in a substantially cylindrical shape and a molded blade part 2 in which a stator part 2F provided with a plurality of noise prevention blades 22 having a substantially flat rectangular parallelepiped shape is formed at a central circular portion. As illustrated in FIG. 6, the molded blade part 2 is assembled in the container-shaped molded object 1, and then the stator part 2F may be disposed at a predetermined position in the container-shaped molded object 1. In addition, a fan guide FG is installed at a downstream side of the molded blade part 2 to cover the stator part 2F.

As illustrated in FIGS. 6 and 9, the container-shaped molded object 1 is integrally formed with a bell mouth part 11 which is disposed to be spaced a predetermined distance from an outer circumferential end of the propeller fan FN in a radius direction, and a diffuser part 12 which is installed at a downstream side of the bell mouth part 11 and wherein a flow path extends from an upstream side toward a downstream side.

As illustrated in FIG. 6, the bell mouth part 11 has portions having a circular lateral cross-section, and includes a bell mouth provided to have an open upstream side in a cone shape, and a bell mouth duct installed so that its diameter is increased from a portion facing an uppermost stream portion of the propeller fan FN. In addition, an inner circumferential surface of the bell mouth part 11 and an outer circumferential end of the propeller fan FN maintain constant tip clearance when seen from any radius directions.

As illustrated in FIG. 6, the diffuser part 12 is formed so that an upstream end connected to the bell mouth part 11 is formed to have a substantially circular lateral cross-section, and as illustrated FIGS. 7 and 8, is formed so that an opening end of a downstream side has an oval lateral cross-section. The diffuser part 12 is also formed to have a lateral cross-section between an upstream end and a downstream end, in which a lateral cross-sectional area increases from an upstream side toward a downstream side, and simultaneously, the upstream end and the downstream end are smoothly and continuously connected. In addition, in the container-shaped molded object 1, when seen from a shaft direction from the upstream side to the downstream side, an area enlargement rate of a flow path at an upstream side end of the diffuser part 12 is greater than that of a lower downstream side end of the bell mouth part 11, and as illustrated in FIG. 6, the diffuser part 12 is connected to the bell mouth part 11 in a bent state.

As illustrated in FIG. 7, a length of a downstream end of the diffuser part 12 along a major axis direction is defined as W and a length along a minor axis direction is defined as D, each length is set to satisfy 0.75<D/W<1 in the present embodiment. According to the above-described setting, a large change in a curvature of an inner circumferential surface of the diffuser part 12 due to a difference between a divergence angle a of a major axis side of the diffuser part 12 and that of a divergence angle a of a minor axis side of the diffuser part 12 does not occur, and thus it is easy to rectify a fluid flow.

In addition, an intersection point of the major and minor axes of the diffuser part 12 and center of the stator part 2F is disposed on an axis of rotation of the propeller fan FN.

In addition, as illustrated in FIGS. 9 and 10, a downstream side end of the diffuser part 12 is formed to be in contact with an outer circumferential end 2E of the stator part 2F when the molded blade part 2 is assembled at the container-shaped molded object 1, and the stator part 2F is disposed and fixed to a flow path in the diffuser part 12 after assembly. In addition, a large seating part 13, which has a flat plate shape widened in a flat surface perpendicular to a shaft, is formed at the downstream end of the diffuser part 12, and the downstream end of the diffuser part 12 is provided to be in contact with an installation flat plate part 25 which is formed at the molded blade part 2 and which will be described later.

As illustrated in FIGS. 9 and 10, the above-described structure is formed so that a plurality of concave parts 1B having a shape substantially the same as that of each connection part 23 of the stator part 2F, which will be described later, are formed to be parallel to each other along a circumferential direction. The concave part 1B causes an internal surface of the diffuser part 12 to be concave along a radius direction, and at the same time, a bottom surface thereof to be parallel to the shaft direction. Accordingly, a depth of the concave part 1B becomes deeper from a downstream side to an upstream side.

Here, in the bell mouth part 11 and the diffuser part 12, when a radius increase rate at a position from the upstream side to the downstream side along the shaft direction (a major axis radius and a minor axis radius) is compared, the radial increase rate of the diffuser part 12 is set to be bigger. That is, when seen in a longitudinal cross-section in FIG. 6, a surface forming the upstream side end of the diffuser part 12 is inclined with respect to a surface forming a downstream side end of the bell mouth part 11 to form a predetermined angle. In other words, as illustrated in FIG. 6, when seen in the longitudinal cross-section, a divergence angle α at a corner formed by the inner circumferential surface of the diffuser part 12 with respect to a virtual line extending from a downstream end of the bell mouth part 11 in the shaft direction is set to be in the range of 0°<α<18°, which is slightly different from that of the first embodiment. As illustrated in a simulation result in FIG. 11, as the divergence angle α is set to the above-described angle, fluid separation due to a reverse pressure gradient is suppressed at an inner peripheral surface of the diffuser part 12, and thus a static pressure rising effect may be easily obtained. It is also preferable that the angle α be in the range of 3°≤α≤35°.

In addition, from the viewpoint of functions of the bell mouth part 11 and the diffuser part 12, the bell mouth part 11 is for improving a fluid pressure near the propeller fan FN, and the diffuser part 12 is for increasing a pressure of a vortex from the propeller fan FN.

As illustrated in an outer peripheral surface of the container-shaped molded object 1 in FIG. 9, vertical ribs 15 extending along the shaft direction and lateral ribs 14 extending in the circumferential direction are formed to increase strength of the container-shaped molded object. A protrusion direction of the vertical rib 15 does not face a radius direction with respect to the shaft, and the protrusion direction is the same for each half thereof. That is, the container-shaped molded object 1 is provided to be molded by a mold that is divided in two as a front and a rear in a radius direction thereof, and thus the vertical rib 15 is formed in a dividing direction of the mold for each half thereof.

Next, the molded blade part 2 will be described.

As illustrated in FIGS. 7 and 9, the molded blade part 2 includes a hub 21 formed at a central portion in a substantially flat cylindrical shape, a plurality of noise prevention blades 22 disposed at an outer peripheral surface of the hub 21 in an outer radial shape, the connection parts 23 extending from the outer circumferential end 2E of the noise prevention blade 22 to a downstream side in the shaft direction, link parts 24 which connect the connection parts 23 along the circumferential direction, and the installation flat plate part 25 in contact with the large seating part 13 having a flat plate shape. In addition, in FIG. 8, the noise prevention blade 22 is hatched to be seen easily even though it is not a cross-section.

As illustrated in FIGS. 8 and 9, the hub 21 includes three coaxial ring-shaped members each having a different diameter and a reinforcement rib structure which connects ring state members along a radial direction. That is, the hub 21 is formed in a hollow through which a fluid can pass, as well as formed to be capable of maintaining a predetermined strength. In addition, since the hub 21 is formed in the hollow, loads on inner circumferential ends of the plurality of noise prevention blades 22 is decreased, strength needed by the noise prevention blade 22 is decreased, and thus the thickness thereof may be formed as thinly as possible.

As illustrated in FIG. 8, the plurality of noise prevention blades 22 include the stator part 2F, an inner circumferential end 21 of the noise prevention blade 22 is connected to the outer peripheral surface of the hub 21, and the outer circumferential end 2E is formed to be in contact with an inner surface of the diffuser part 12. However, because the diffuser part 12, except for a connection part with the bell mouth part 11, is formed to have a lateral cross-section in an oval shape, shapes of the noise prevention blades 22 and lengths of strings of noise prevention blades are different from each other in a quarter of the oval. Accordingly, the connection part 23 also has a shape corresponding to a shape of the noise prevention blade 22.

As described above, since a length in a span direction or a shape of the noise prevention blade 22 is repeatedly changed every quarter when the noise prevention blades 22 are seen in turn from the circumferential direction in the stator part 2F, noise may be prevented from being generated in the noise prevention blade 22 with the same specific frequency. That is, by alternating frequencies having the highest peak in the noise prevention blades 22, a Blade Passage Frequency (BPF) noise level may be decreased. More specifically, as illustrated in a graph in FIG. 12, a blower 100 according to the present embodiment may decrease a noise level at each frequency, particularly low frequencies, when compared with a conventional technology.

In addition, as illustrated in FIG. 9, the noise prevention blade 22 is installed so that a convex surface 2C thereof faces an upstream side where the bell mouth part 11 and a fan motor exist, as well as a concave pressure surface 2P faces a downstream side where the downstream end of the diffuser part 12 exists. In addition, as illustrated in the top view of FIG. 8, predetermined gaps are defined between the adjacent noise prevention blades 22 so that leading edges 2L and following edges 2T do not overlap each other when seen from the shaft.

As illustrated in an enlarged perspective view of FIG. 10A, the connection part 23 includes a plate-shaped part 231 extending from an outer end of the noise prevention blade 22 toward the shaft, and an outer edge rib 232 protruding from an outer edge of the plate-shaped part 231 in the radius direction. The plate-shaped part 231 has an inner circumferential surface having a shape so that the inner circumferential surface of the plate-shaped part 231 matches an inner surface of the diffuser part 12 when the connection part 23 is engaged with the concave part 1B. In addition, the outer edge rib 232 is formed to have a height which increases from a downstream side to an upstream side.

As illustrated in FIG. 10A, the link part 24 has a partial ring state extending along a circumferential direction, and is formed to connect upstream side ends of the connection parts 23. That is, the upstream side end of the connection part 23 and the link part 24 are alternatively disposed along the circumferential direction and formed in a ring state as a whole.

Next, division lines L between the container-shaped molded object 1 and the molded blade part 2 of the blower 100 provided as described above will be described.

As illustrated with bold lines in FIG. 10A, each division line L of elements is formed to include at least a convex surface forming line L1 forming a convex surface 2C at the outer circumferential end 2E of the noise prevention blade 22. In the present embodiment, the division line L is defined by the convex surface forming line L1, a circumferential direction line L2 which defines a downstream end of the link part 24, and a shaft direction line L3 which is a downstream side of the outer edge rib 232 of the connection part 23 and extends from the convex surface forming line L1 to the circumferential direction line L2 along the shaft direction. In another words, as illustrated in FIG. 10B, the division line L between the container-shaped molded object 1 and the molded blade part 2 is formed in approximately a saw-toothed shape, and includes the convex surface forming line L1 forming the convex surface 2C at the outer circumferential end 2E of the noise prevention blade 22.

As described above, since the blower 100 according to the present embodiment has a complex structure in which the diffuser part 12 is formed at the downstream side of the bell mouth part 11 and the stator part 2F in which the shape of the noise prevention blade 22 is formed at an inner surface of the bell mouth part 11 is disposed in the diffuser part, a restoring pressure of fluid increases compared to a conventional technology, and thus the blowing efficiency may be significantly improved.

In addition, because the diffuser part 12 is installed at the downstream side of the bell mouth part 11, the downstream end of the diffuser part 12 is formed in the oval shape, and the noise prevention blade 22 is installed in the radial shape therein, first, speed of fluid which flows from the downstream end of the diffuser part 12 is decreased, and thus an entire noise level may be decreased. In addition, because lengths along the span direction or the shapes of the noise prevention blades are not the same and have a tiny difference between them and the vortex coming out from the propeller fan FN and the interference state of the noise prevention blade 22 are different from each other, noise intensively generated at a specific frequency may also be prevented. From that, blowing performance may be significantly improved and a noise level may also be decreased.

In addition, since the container-shaped molded object 1 is divided by the division line L, and the blower 100 includes the molded blade part 2, the noise prevention blades 22 of the diffuser part 12 and the stator part 2F are formed separately. Accordingly, the diffuser part 12 which has the complex shape for improving the blowing efficiency described above, has an enlarged flow path varying from the circular shape to the oval shape and a form in which the noise prevention blade 22 of the stator part 2F is formed up to the outer circumferential end 2E, and thus priority is given to such a complex structure while preventing manufacturability from being decreased.

More specifically, for example, when the outer circumferential end 2E of the noise prevention blade 22 is integrally injection-molded with the other members, only the outer circumferential end 2E is perpendicularly molded with respect to the shaft to be easily separated from the mold, and thus priority has been given to the manufacturability while blowing efficiency is sacrificed. In contrast to the above description, in the present embodiment, since each element is divided by the division line L, consideration of mold separation in the conventional technology may not be needed, and blowing efficiency may be improved by installing the convex surface 2C and the pressure surface 2P formed to be inclined toward the outer circumferential end 2E. In addition, since as illustrated in a top view illustrating the blower 100 in FIG. 9, the noise prevention blades 22 do not overlap when seen from the shaft, and as illustrated in FIG. 10A, the outer edge rib 232 is only formed at the outer edge part of the connection part 23, and because the upstream side is formed to be open, the molded blade part 2 may be easily molded by a mold divided along the shaft direction.

As described above, because molding property of the noise prevention blade 22 for the container-shaped molded object 1 is not needed, the shape of the bell mouth part 11 which expands from the substantially circular shape to the oval shape may also be molded by a simple mold. In addition, since a direction of the vertical rib 15 may be arranged by a half surface, the container-shaped molded object 1 may be molded by a mold divided into two along a radius direction, and thus manufacturability may be improved.

In addition, since the bell mouth part 11 and the diffuser part 12 are not separately formed, but are integrally formed as the container-shaped molded object 1, the blower 100 includes only two elements of the container-shaped molded object 1 and the molded blade part 2, and thus blowing efficiency is improved as well as the number of elements may also be decreased.

In addition, the other embodiments will be described.

As illustrated in FIG. 13, a cover member 25 having a top surface in a dome-shaped curved surface to cover a downstream side (a top surface side) of a hub 21 may be installed to prevent a blower 100 from being damaged by being in contact with a bell mouth part 11 when snow is accumulated on a central portion of a propeller fan FN and a rotation shaft is shaken. In addition, the cover member 25 may be provided to be separable from the hub 21 so that cost is easily decreased by omitting the present structure in areas snow does not fall.

In the above-described embodiment, although the stator part 2F is formed by installing the noise prevention blade 22 into the diffuser part 12 in a radial shape, for instance, the plurality of noise prevention blades 22 having a shape expanding straight along a long or minor axis may be installed. Such a structure may improve blowing efficiency and also suppress a noise from being intensively increased at a specific frequency by varying lengths of the noise prevention blades 22. Although the downstream end of the diffuser part 12 has an oval shape, for instance, the downstream end may have a polygonal shape close to a circle or oval. In this case, it is preferable that a central point of the downstream end of the diffuser part 12 be disposed on the rotation shaft line of the propeller fan FN.

Various modifications or embodiments except for the above-described embodiments may be combined without departing from the purposes of the present.

Claims

1. An outdoor unit for an air conditioner, comprising:

a first fan having coupled to a first rotation shaft;

a second fan having coupled to a second rotation shaft that is parallel to the first rotation shaft;

a casing surrounding the first fan and the second fan in a vertical direction;

a first bell mouth part and a second bell mouth part, each of the first bell mouth part and the second bell mouth part to guide air introduced into the first fan and the second fan, respectively, while the first fan and the second fan respectively discharge the air, each of the first bell mouth part and the second bell mouth part having a downstream end and being spaced apart from outer circumferential ends of the first fan and the second fan, respectively;

a first diffuser part obliquely extending from the downstream end of the first bell mouth part to guide the air discharged from the first fan, the first diffuser part having a first inner circumferential surface inclined at first inclination angles with respect to the first rotation shaft, the first inclination angles varied along a circumferential direction of the first fan;, the first diffuser part forming a first opening at a downstream end of the first inner circumferential surface;

a second diffuser part obliquely extending from the downstream end of the second bell mouth part to guide the air discharged from the second fan, the second diffuser part having a second inner circumferential surface inclined at second inclination angles with respect to the second rotation shaft, the second inclination angles varied along a circumferential direction of the second fan, the second diffuser part forming a second opening at a downstream end of the second inner circumferential surface;

wherein when a length of a major axis of the first opening is W and a length of a minor axis of the first opening is D, lengths of the first opening is set to satisfy 0.75<D/W<1, and

wherein when a length of a major axis of the second opening is W and a length of a minor axis of the second opening is D, lengths of the second opening is set to satisfy 0.75<D/W<1;

wherein:

the first diffuser part and the second diffuser part are disposed inside the casing in the vertical direction,

a portion ofthe first inner circumferential surface of the first diffuser part at a minor axis of the first diffuser part and a portion of the second inner circumferential surface of the second diffuser part at a minor axis of the second diffuser part are adjacent to each other,

the portion ofthe first inner circumferential surface of the first diffuser part at the minor axis of the first diffuser part is inclined at at least one first inclination angle from among the first inclination angles of the first diffuser part,

the portion ofthe second inner circumferential surface of the second diffuser part at the minor axis of the second diffuser part is inclined at at least one second inclination angle from among the second inclination angles of the second diffuser part,

the at least one first inclination angle from among the first inclination angles of the first diffuser part is smaller than at least one other first inclination angle from among the first inclination angles of the first diffuser part, and

the at least one second inclination angle from among the second inclination angles of the second diffuser part is smaller than at least one other second inclination angle from among the second inclination angles of the second diffuser part, and

a downstream end of the first diffuser part and a downstream end of the second diffuser part are surrounded by four side walls of the casing.

2. The outdoor unit according to claim 1, wherein:

the first diffuser part includes a first opening formed at a downstream end of the first inner circumferential surface;

the second diffuser part includes a second opening formed at a downstream end of the second inner circumferential surfaces; and

the first opening and the second opening are formed to be opposite to each other.

3. The outdoor unit according to claim 2 1, wherein each of the first inclination angles (θ) and the second inclination angles (θ) are each provided in a range of 3°≤θ≤35°.

4. The outdoor unit according to claim 2 1, wherein:

a length of the first inner circumferential surface of the first diffuser part defined as a length between an upstream end and the downstream end of the first diffuser part increases as the inclination angle of the first diffuser part increases; and

a length of the second inner circumferential surface of the second diffuser part defined as a length between an upstream end and the downstream end of the second diffuser part increases as the inclination angle of the second diffuser part increases.

5. The outdoor unit according to claim 2 1, wherein:

the rotation shaft of the first fan is disposed at a center of the first opening; and

the rotation shaft of the second fan is disposed at a center of the second opening.

6. The outdoor unit according to claim 2, wherein when a length of a major axis of the first opening is W and a length of a minor axis of the first opening is D, the lengths of the first and second openings are set to satisfy 0.75<D/W<1.

7. The outdoor unit according to claim 1, wherein:

the first diffuser part includes a first opening formed at a downstream end of the first inner circumferential surface; and

the first opening is provided in an oval shape.

8. The outdoor unit according to claim 1, wherein:

the first diffuser part includes a first opening formed at a downstream end of the first inner circumferential surface; and

the first opening is provided in a polygonal shape having at least three corners.

9. The outdoor unit according to claim 1, wherein the at least one first inclination angle (α) from among the first inclination angles of the first diffuser part and the at least one second inclination angle (α) from among the first inclination angles of the second diffuser part are each provided in a range of 3°≤α≤7°.

10. The outdoor unit according to claim 1, further comprising wherein:

a casing includingthe four side walls of the casing include:

a first surface wall extending in a direction the first and second fans are disposed and to cover one side of the first fan and one side of the second fan,

a second surface wall configured to cover the other side of the first fan and the other side of the second fan while disposed parallel to the first surface wall,

a third surface wall configured to cover the first fan while disposed between the first surface wall and the second surface wall, and

a fourth surface wall configured to cover the second fan while disposed parallel to the third surface wall; and

at least one heat exchanger disposed between the casing and the first and second fans and formed along the third surface wall, the first surface wall, and the fourth surface wall.

11. The outdoor unit according to claim 10, wherein the heat exchanger formed along the third surface wall, the first surface wall, and the fourth surface is also formed along at least a portion of wall extends toward the second surface wall.

12. The outdoor unit according to claim 10, wherein the first inclination angles of the first diffuser part and the second inclination angles of the second diffuser part respectively have maximum values when the first diffuser part and the second diffuser part respectively face the first surface wall and the second surface wall.

13. The outdoor unit according to claim 10, wherein the first inclination angles of the first diffuser part and the second inclination angles of the second diffuser parts each have minimum values when the first diffuser part and the second diffuser part respectively face the third surface walland the fourth surface wall.

14. An outdoor unit for an air conditioner, comprising:

a pair of fans each having a rotation shaft provided vertically;

a casing including four surfaces walls that extend verticallywhile covering vertical sides of the pair of fans;

a pair of fans, each coupled to a respective rotation shaft provided vertically and disposed inside the casing in a vertical direction;

a heat exchanger disposed between the casing and the pair of fans and extended along at least three surfaces walls of the four surfaces walls;

a pair of bell mouth parts respectively provided for the pair of fans and disposed to be spaced apart from outer circumferential ends of each of the pair of fans, each bell mouth of the pair of bell mouth parts configured to guide air introduced into a respective fan of the pair of fans while the pair of fans discharge the air, the pair of bell mouth parts respectively having downstream ends; and

a pair of diffuser parts respectively disposed at downstream ends of the pair of bell mouth parts and obliquely extending in directions toward which the air is to be discharged, to guide the air discharged from the pair of fans, and the pair of diffuser parts including a pair of inner circumferential surfaces, respectively;

a pair of openings are respectively formed at downstream ends of the pair of inner circumferential surfaces and each of the pair of openings has a shape corresponding to each other;

wherein when a length of a major axis of the pair of openings is W and a length of a minor axis of the pair of openings is D, the lengths of the pair of openings are set to satisfy 0.75<D/W<1;

wherein

the pair of diffuser parts are disposed inside the casing in the vertical direction,

downstream ends of the pair of diffuser parts are surrounded by the four walls of the casing,

the inner circumferential surface of each of the pair of diffuser parts have an inner circumferential surface is inclined at an inclination angle that are is varied along circumferential directions direction of a respective diffuser part of the pair of diffuser parts with respect to respective rotation shaft of the rotation shafts of the pair of fans, and

the inclination angle of the respective diffuser part has a minimum value at first portions of the inner circumferential surfaces where the pair of diffuser parts are adjacent to each other at respective minor axes of the pair of diffuser parts.

15. The outdoor unit according to claim 14, wherein at the first portions of each of the inner circumferential surfaces at the respective minor axes of the pair of diffuser parts, the inclination angle (θ) of the respective diffuser part of the pair of diffuser parts is provided in a range of 3°≤θ≤7°.

16. The outdoor unit according to claim 14, wherein the inclination angle (θ) of the respective diffuser part of the pair of diffuser parts is provided in a range of 3°≤θ≤35°.

17. The outdoor unit according to claim 14, wherein:

a pair of openings is respectively formed at downstream ends of the pair of inner circumferential surfaces; and

each of the pair of openings has a shape corresponding to each other.

18. The outdoor unit according to claim 17 14, wherein each opening of the pair of openings is provided in an oval shape.

19. The outdoor unit according to claim 17, wherein each opening of the pair of openings are provided in a polygonal shape having at least three corners.

20. The outdoor unit according to claim 17 14, further comprising a pair of stator parts, each stator of the pair of stator parts including a plurality of noise prevention blades,

wherein the pair of stator parts are respectively provided on the pair of inner circumferential surfaces.

21. An outdoor unit for an air conditioner, comprising:

a casing including four walls that extend vertically;

a pair of fans, each coupled to a respective rotation shaft provided vertically and disposed inside the casing in a vertical direction;

a heat exchanger extended along at least three walls of the four walls of the casing;

a pair of bell mouth parts respectively provided for the pair of fans and disposed to be spaced apart from outer circumferential ends of each of the pair of fans, each bell mouth of the pair of bell mouth parts configured to guide air introduced into a respective fan of the pair of fans while the pair of fans discharge the air, the pair of bell mouth parts respectively having downstream ends;

a pair of diffuser parts respectively disposed at downstream ends of the pair of bell mouth parts and obliquely extending in directions toward which the air is to be discharged, to guide the air discharged from the pair of fans and the pair of diffuser parts including a pair of inner circumferential surfaces, respectively, and

a pair of openings respectively formed at downstream ends of a pair of inner circumferential surfaces, each of the pair of openings has a shape corresponding to each other;

wherein when a length of a major axis of the pair of openings is W and a length of a minor axis of the pair of openings is D, the lengths of the pair of openings are set to satisfy 0.75<D/W<1;

wherein

the pair of diffuser parts are disposed inside the casing in the vertical direction,

the inner circumferential surface of each of the pair of diffuser parts is inclined at a diffuser angle that is varied along circumferential direction of a respective diffuser part of the pair of diffuser parts with respect to the respective rotation shaft of the rotation shafts of the pair of fans, and the inclination angle of the respective diffuser part has a minimum value at first portions of the inner circumferential surfaces where the pair of diffuser parts are adjacent to each other.

each of the pair of diffuser parts, in a major axis direction from a front to a rear, has a first diffuser angle,

each of the pair of diffuser parts, in a minor axis direction from one side to another side, has a second diffuser angle,

the second diffuser angle is smaller than the first diffuser angle, and

downstream ends of the pair of diffuser parts are surrounded by the four walls of the casing.

22. The outdoor unit according to claim 21, wherein the pair of diffuser parts is disposed inside the casing in a vertical direction.

23. The outdoor unit according to claim 21, wherein, for each of the diffuser parts, the second diffuser angle is a lowest diffuser angle among a plurality diffuser angles along circumferential directions of the diffuser part.

24. The outdoor unit according to claim 21, wherein the first diffuser angle is a highest diffuser angle among a plurality of diffuser angles along circumferential directions of the diffuser part.

25. The outdoor unit according to claim 23, wherein the second diffuser angle is provided in a range of 3°≤θ≤7°.

26. The outdoor unit according to claim 24, wherein the first diffuser angle is provided in a range of 3°≤θ≤35°.

27. The outdoor unit according to claim 21, wherein each opening of the pair of openings is provided in an oval shape.

28. The outdoor unit according to claim 1, wherein

a distance from a center of rotation of the first fan to a corner of the casing, formed by two side walls of the four side walls of the casing, is defined by L1+L2,

wherein L1 is a distance from the corner of the casing to an outer edge of the first diffuser part, L2 is a distance from the center of rotation of the first fan to the outer edge of the first diffuser part, and Dratio=L2/(L1+L2) satisfies 0.60≤Dratio≤0.95.

29. The outdoor unit according to claim 14, wherein

a distance from a center of rotation of a fan of the pair of fans to a corner of the casing, formed by two side walls of the four side walls of the casing, is defined by L1+L2,

wherein L1 is a distance from the corner of the casing to an outer edge of a diffuser part of the pair of diffusor parts, L2 is a distance from the center of rotation of the fan of the pair of fans to the outer edge of the diffuser part of the pair of diffuser parts, and Dratio=L2/(L1+L2) satisfies 0.60≤Dratio≤0.95.

30. The outdoor unit according to claim 21, wherein

a distance from a center of rotation of a fan of the pair of fans to a corner of the casing, formed by two side walls of the four side walls of the casing, is defined by L1+L2,

wherein L1 is a distance from the corner of the casing to an outer edge of a diffuser part of the pair of diffuser parts, L2 is a distance from the center of rotation of the fan of the pair of fans to the outer edge of the diffuser part of the pair of diffuser parts, and Dratio=L2/(L1+L2) satisfies 0.60≤Dratio≤0.95.