CN117889497A

CN117889497A - Air conditioner outdoor unit

Info

Publication number: CN117889497A
Application number: CN202410054986.4A
Authority: CN
Inventors: 陈维涛; 王其桢; 李跃飞; 刘乃桐; 余东东; 冯镜辉
Original assignee: Midea Group Co Ltd; GD Midea Heating and Ventilating Equipment Co Ltd
Current assignee: Midea Group Co Ltd; GD Midea Heating and Ventilating Equipment Co Ltd
Priority date: 2020-10-10
Filing date: 2020-10-10
Publication date: 2024-04-16
Also published as: CN114320959B; CN114320959A

Abstract

The application discloses an air condensing units includes: a housing having a vent hole; the fan device and the heat exchanger are arranged in the shell, and the fan device is arranged on the shell and is positioned above the heat exchanger; the fan device comprises a first wind wheel and a second wind wheel which are axially arranged at intervals, wherein one side of the first wind wheel, which is away from the second wind wheel, is an air inlet side, one side of the second wind wheel, which is away from the first wind wheel, is an air outlet side, the rotation directions of the first wind wheel and the second wind wheel are opposite to the bending direction of the blades, and the number of the blades of the first wind wheel and the number of the blades of the second wind wheel are prime numbers; the support is arranged on the shell and positioned at least one of the air inlet side, the air outlet side and between the first wind wheel and the second wind wheel, and the distance between the support and the first wind wheel and the distance between the support and the second wind wheel are all larger than or equal to a first distance threshold. The air conditioner outdoor unit can increase the air output and reduce noise.

Description

Air conditioner outdoor unit

Technical Field

The present disclosure relates to the field of air conditioning technologies, and in particular, to an air conditioning outdoor unit.

Background

An Air Conditioner (Air Conditioner) is a device for adjusting and controlling parameters such as temperature and humidity of Air in a building or a structure by using manual means. The air conditioning system is generally composed of an indoor unit and an outdoor unit, and the indoor unit and the outdoor unit are matched to complete the adjustment and control of parameters such as temperature, humidity and the like of ambient air.

The air volume of the air conditioner outdoor unit is closely related to the performance of the air conditioner outdoor unit, and the air outlet volume is often increased by increasing the number of fans in the prior art. However, the air volume of the air conditioner outdoor unit increases, and the noise thereof tends to increase.

Content of the application

In view of this, the technical problem that this application mainly solves is to provide an air condensing units, can reduce the production of noise when increasing the air output.

In order to solve the technical problems, one technical scheme adopted by the application is as follows: provided is an air conditioner outdoor unit including: the shell is provided with a vent hole, a fan device and a heat exchanger, the fan device is arranged in the shell, the heat exchanger is arranged in the shell, the fan device is positioned above the heat exchanger, and the fan device is used for guiding external air flow to enter the shell through the vent hole and pass through the heat exchanger to exchange heat; one side that fan unit is close to the heat exchanger is defined as the air inlet side, and one side that fan unit kept away from the heat exchanger is defined as the air-out side, and fan unit drive air current after the heat exchanger flows out the air-out side from the air inlet side, and fan unit includes: the wind power generation device comprises a first wind wheel and a second wind wheel, wherein the first wind wheel and the second wind wheel are axially arranged at intervals, one side of the first wind wheel, which is away from the second wind wheel, is an air inlet side, one side of the second wind wheel, which is away from the first wind wheel, is an air outlet side, the rotation directions of the first wind wheel and the second wind wheel are opposite, the bending directions of blades of the first wind wheel and the bending directions of blades of the second wind wheel are also opposite, and the number of blades of the first wind wheel and the number of blades of the second wind wheel are prime numbers; the support is arranged on the shell and is positioned at least one of the air inlet side, the air outlet side and between the first wind wheel and the second wind wheel, and the distance between the support and the first wind wheel and the distance between the support and the second wind wheel are both larger than or equal to a first distance threshold value.

In an embodiment of the present application, the difference between the number of blades of the first rotor and the number of blades of the second rotor is 2.

In an embodiment of the present application, the number of blades of the second rotor is smaller than the number of blades of the first rotor.

In an embodiment of the present application, the number of blades n1 of the first rotor and the number of blades n2 of the second rotor have the following relationship: and h is 1-s is 2 is more than or equal to 2, h, s is E (1, 2, 3).

In an embodiment of the present application, the diameter of the first wind wheel is larger than the diameter of the second wind wheel.

In an embodiment of the present application, the diameter D1 of the first wind wheel and the diameter D2 of the second wind wheel have the following relationship: 1.01D2D 1 is less than or equal to 1.03D2.

In an embodiment of the present application, a distance between the first wind wheel and the second wind wheel is greater than or equal to 20mm.

In an embodiment of the present application, the fan device further includes a guide cover, and the guide cover includes a main body portion, and the main body portion is sleeved on the outer circumferences of the first wind wheel and the second wind wheel.

In an embodiment of the present application, a distance S1 between an end of the first wind wheel located at the air intake side and an end of the main body portion located at the air intake side has the following relationship with a length H1 of the first wind wheel in an axial direction: S1/H1 is more than or equal to 0.4 and less than or equal to 0.7.

In one embodiment of the present application, S1/h1=0.55.

In an embodiment of the present application, a distance S2 between an end of the second wind wheel facing away from the first wind wheel and an end of the main body portion facing away from the first wind wheel has the following relationship with a length H2 of the second wind wheel in an axial direction: S2/H2 is more than or equal to 0 and less than or equal to 0.25.

In one embodiment of the present application, S2/h2=0.

In an embodiment of the present application, the diameter D1 of the first wind wheel has the following relationship with the inner diameter D3 of the main body portion: 5mm < (D3-D1)/2 <20mm.

In one embodiment of the present application, (D3-D1)/2=10 mm.

In an embodiment of the present application, the diameter D1 of the first wind wheel has the following relationship with the inner diameter D3 of the main body portion: 0.008D1 is less than or equal to D3-D1 is less than or equal to 0.016D1.

In one embodiment of the present application, the housing has a mounting base, and the pod is mounted on the mounting base; the length H3 of the air guide sleeve and the mounting seat in the axial direction of the air guide sleeve and the length H4 of the first wind wheel and the second wind wheel in the axial direction have the following relation: 0.68H3 and 0.75H3 are H4 and H2.

In an embodiment of the present application, the air guide sleeve further includes a tapered portion disposed at one end of the main body portion near the first wind wheel, and a cross-sectional area of each position of the tapered portion in an axial direction thereof gradually decreases in a direction near the main body portion; the length H1 of the first wind wheel in the axial direction and the length H5 of the tapered portion in the axial direction have the following relationship: 0.25H1 is less than or equal to H5 and is less than or equal to 0.4H1.

In an embodiment of the present application, the length H6 of the main body portion in the axial direction and the length H7 of the pod in the axial direction have the following relationship: 0.75H7 is less than or equal to H6 and is less than or equal to 0.8H7.

In an embodiment of the present application, the fan units comprise at least two groups, and central axes of the respective fan units are parallel to each other and do not coincide.

The beneficial effects of this application are: different from the prior art, this application provides an air condensing units, and adjustable off-premises station includes casing, fan device, heat exchanger and support. Through the arrangement of the first wind wheel and the second wind wheel, compared with a single wind wheel, the air conditioner outdoor unit increases the air output under the condition of certain input power. When the air quantity is required to be fixed, the first wind wheel and the second wind wheel can have lower rotating speeds, so that the pneumatic noise generated when the wind wheels operate can be reduced. Meanwhile, the rotating directions of the first wind wheel and the second wind wheel are opposite, and the bending directions of the blades of the first wind wheel and the bending directions of the blades of the second wind wheel are also opposite, so that the rotating directions of the air flow generated by the first wind wheel and the air flow generated by the second wind wheel are opposite, and the rotating directions of the air flow generated by the first wind wheel and the air flow generated by the second wind wheel can offset each other, thereby being beneficial to reducing noise. In addition, the number of the blades of the first wind wheel and the number of the blades of the second wind wheel are prime numbers, so that beat vibration abnormal sound generated when the first wind wheel and the second wind wheel operate can be reduced, part of harmonic noise can be reduced or eliminated, and further noise reduction is facilitated.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the application and together with the description, serve to explain the principles of the application. Furthermore, these drawings and the written description are not intended to limit the scope of the inventive concepts in any way, but rather to illustrate the inventive concepts to those skilled in the art by reference to specific embodiments.

Fig. 1 is a schematic structural view of an embodiment of an outdoor unit of an air conditioner according to the present application;

fig. 2 is an exploded view of the outdoor unit of the air conditioner shown in fig. 1;

fig. 3 is a schematic cross-sectional view of the outdoor unit of the air conditioner shown in fig. 1;

FIG. 4 is a schematic view of the first embodiment of the first wind wheel and the second wind wheel of the present application;

FIG. 5 is a schematic diagram of an embodiment of a fan apparatus of the present application in comparison with a conventional single-axis wind turbine in which static pressure is achieved at different wind volumes;

FIG. 6 is a schematic diagram of an embodiment of a fan apparatus of the present application in comparison to a conventional single-axis wind turbine power at different wind volumes;

FIG. 7 is a schematic diagram of an embodiment of a fan apparatus of the present application in comparison to a conventional single-axis wind turbine in terms of noise at different wind volumes;

FIG. 8 is a schematic view of an embodiment of a first wind wheel of the present application;

FIG. 9 is a schematic view of an embodiment of a second wind wheel of the present application;

FIG. 10 is a schematic view of an embodiment of a pod of the present application;

FIG. 11 is a schematic diagram of an embodiment of a fan apparatus of the present application in comparison to a conventional single-axis flow wind turbine with noise levels at different frequencies;

FIG. 12 is a schematic view of a second embodiment of the first and second wind turbines of the present disclosure;

FIG. 13 is a schematic view of a first embodiment of a fan apparatus of the present application;

FIG. 14 is a schematic view of a second embodiment of a fan apparatus of the present application;

FIG. 15 is a schematic view of an embodiment of the noise variance of the first wind wheel of the present application at different locations within the pod;

FIG. 16 is a schematic view of an embodiment of the noise variance of the second rotor of the present application at different locations within the pod;

FIG. 17 is a schematic view of an embodiment of a pod and mount of the present application;

FIG. 18 is a schematic view of a third embodiment of a fan apparatus of the present application;

FIG. 19 is a schematic view of a fourth embodiment of a fan apparatus of the present application;

FIG. 20 is a schematic view of a fifth embodiment of a fan apparatus of the present application;

fig. 21 is a schematic structural view of another embodiment of an outdoor unit of an air conditioner according to the present application;

Fig. 22 is a schematic sectional view of the air conditioner outdoor unit A-A shown in fig. 21;

fig. 23 is a schematic sectional view of the air conditioner outdoor unit B-B shown in fig. 21.

Detailed Description

For the purposes of making the objects, technical solutions and advantages of the present application more apparent, the technical solutions in the embodiments of the present application will be clearly and completely described in the following in conjunction with the embodiments of the present application, and it is apparent that the described embodiments are some, but not all, embodiments of the present application. All other embodiments, which can be made by one of ordinary skill in the art without undue burden from the present disclosure, are within the scope of the present disclosure. The following embodiments and features of the embodiments may be combined with each other without conflict.

Complete machine structure

An Air Conditioner (Air Conditioner) is a device for adjusting and controlling parameters such as temperature and humidity of Air in a building or a structure by using manual means. The air conditioning system generally comprises an indoor unit and an outdoor unit, and the indoor unit and the outdoor unit cooperate to complete the adjustment and control of parameters such as temperature, humidity and the like of the ambient air, and the specific mechanism of the adjustment and control belongs to the understanding scope of those skilled in the art, and will not be described herein. The embodiment of the application is mainly described with respect to an air conditioner outdoor unit.

Referring to fig. 1 to 3, fig. 1 is a schematic structural diagram of an embodiment of an air conditioner outdoor unit according to the present application, fig. 2 is an exploded structural diagram of the air conditioner outdoor unit shown in fig. 1, and fig. 3 is a schematic sectional structural diagram of the air conditioner outdoor unit shown in fig. 1.

In one embodiment, the outdoor unit of the air conditioner includes a housing 10. The casing 10 serves as a basic component of the air conditioner outdoor unit, and serves to carry and protect other components of the air conditioner outdoor unit.

The outdoor unit further includes a fan device 20 and a heat exchanger 30, the heat exchanger 30 is disposed in the housing 10, and the fan device 20 is mounted to the housing 10. The casing 10 is provided with a vent hole 11, the vent hole 11 is arranged corresponding to the heat exchanger 30, and the fan device 20 is used for guiding external air flow to enter the casing 10 through the vent hole 11 and pass through the heat exchanger 30 to exchange heat.

In an embodiment, the fan apparatus 20 may be an axial flow fan or the like, i.e. for guiding the airflow in the axial direction of the fan apparatus 20. The axial flow fan is widely applied to home appliance industries such as air conditioners, refrigerators, electric fans, microwave ovens and the like at home and abroad. Fan efficiency, air volume, noise are the main performance indexes. The high efficiency and low noise of the axial flow fan are the main research directions in the industry.

Specifically, the fan apparatus 20 includes a plurality of wind wheels disposed at axial intervals, that is, the plurality of wind wheels are coaxially disposed, as shown in fig. 2 and 3. The wind wheels of the fan device 20 are driven to rotate around the respective axial directions, so that air in the surrounding environment is driven to flow to form air flow, and the outside air flow is specifically guided to enter the shell 10 through the vent hole 11 and pass through the heat exchanger 30 to exchange heat.

Further, the axial flow fan apparatus 20 may include two axially spaced wind wheels, i.e., a first wind wheel 21 and a second wind wheel 22, as shown in fig. 2 and 3. Further, the first wind wheel 21 and the second wind wheel 22 are coaxially arranged, that is, the central axes of the two are coincident. The rotation direction of the first wind wheel 21 is opposite to the rotation direction of the second wind wheel 22, and the bending direction of the blades of the first wind wheel 21 is opposite to the bending direction of the blades of the second wind wheel 22, so that the rotation direction of the air flow generated by the first wind wheel 21 is opposite to the rotation direction of the air flow generated by the second wind wheel 22 (but the flow direction of the air flow generated by the first wind wheel 21 is the same as the flow direction of the air flow generated by the second wind wheel 22), and the rotation speed components of the air flow generated by the opposite directions in the circumferential direction can be mutually offset, so that the air flow flows along the axial direction of the fan device 20 as far as possible, and then the air flow flowing along the axial direction of the fan device 20, namely the axial air flow, is formed in a matching way.

For example, as shown in fig. 4, a leading edge profile δ of a blade (to be described in detail later) of the first wind wheel 21 ₁ And the leading edge profile delta of the blades of the second rotor 22 ₂ Is substantially linear symmetric, wherein the orthographic projection of the leading edge profile is the orthographic projection of the leading edge profile on a plane perpendicular to the axial direction of the first wind wheel 21 and the second wind wheel 22. The symmetry line alpha is the firstLeading edge profile delta of a blade of a wind wheel 21 ₁ And the leading edge profile delta of the blades of the second rotor 22 ₂ A line connecting the intersection point of the orthographic projection of (c) and the axial center point. Trailing edge profile lambda of the blades of the first rotor 21 ₁ The trailing edge profile lambda of the blades of the second rotor 22 starts to curve in the opposite direction at 75-95% of the radius in the spanwise direction ₂ Also, the blades are bent in the opposite directions at 75-95% of the radius along the span direction, and an arc gap beta is formed, so as to improve the efficiency of the blades and reduce the interference noise between the first wind wheel 21 and the second wind wheel 22. Leading edge profile delta of the blade passing through the first rotor 21 ₁ Is aligned with the leading edge profile delta of the blades of the second rotor 22 ₂ Form two tangent lines gamma respectively at the intersection point of the orthographic projection of (a) and the two tangent lines gamma respectively form a curve (delta) with the respective front edge line ₁ 、δ ₂ ) The included angle theta of the two tangent lines gamma gradually increases along the leaf spreading direction theta, and the included angle theta is larger than or equal to 60 degrees from the position of the radius of the blade which is 0.6 times, and the included angle theta near the position of the blade tip at the outermost edge is 90 degrees.

Because the axial flow fan provides air quantity circulation for the air conditioner outdoor unit to realize heat exchange, the air quantity is closely related to the performance of the air conditioner outdoor unit. However, the problem of noise increase is faced when the air quantity is increased, and the pneumatic noise of the axial flow fan is still one of the main noise sources of the air conditioner outdoor unit, and the main components of the pneumatic noise are rotation noise and vortex noise caused by rotation of blades. There is a great need for improvement of the structure of the axial fan to reduce the working noise of the air conditioner while guaranteeing the air quantity of the air conditioner outdoor unit.

The prior air conditioner outdoor unit adopting the single-axial flow wind wheel, in particular to an air conditioner outdoor unit adopting an top-outlet mode. The outlet air flow of the single-shaft flow wind wheel has a large part of rotation speed components along the circumferential direction, and the static pressure efficiency is lower. In addition, the existing air conditioner outdoor unit adopts a fan system with a single-axis flow wind wheel, so that the compression resistance is poor, and the generated wind pressure is low. When the air conditioning system is under the heating working condition, the heat exchanger of the air conditioning outdoor unit is easy to frost and block, so that the air supply resistance of the air conditioning outdoor unit is increased, and the air quantity is greatly attenuated to influence the performance of the air conditioning system.

Compared with the conventional single axial flow wind wheel, the design of the first wind wheel 21 and the second wind wheel 22 in the fan device 20 of the present embodiment is that the rotation direction of the first wind wheel 21 is opposite to the rotation direction of the second wind wheel 22, and the rotation direction of the air flow generated by the first wind wheel 21 is opposite to the rotation direction of the air flow generated by the second wind wheel 22, so that the air flow flows along the axial direction of the fan device 20 as much as possible, and the air volume can be improved, specifically, the total air pressure of the first wind wheel 21 and the second wind wheel 22 is greater than twice the air pressure of the single axial flow wind wheel. Therefore, under the condition that the air quantity requirement is fixed, the rotating speeds of the first wind wheel 21 and the second wind wheel 22 are allowed to have lower rotating speeds, so that the aerodynamic noise of the wind wheels during operation is reduced; in addition, under the condition of certain input power, the first wind wheel 21 and the second wind wheel 22 can have larger air output, have higher air output efficiency, and are favorable for improving heat exchange efficiency. In addition, the design of the first wind wheel 21 and the second wind wheel 22 has better compression resistance compared with the single-shaft flow wind wheel, and the compression resistance of the unit can be improved.

The following compares the performance of a fan device formed by the first wind wheel and the second wind wheel in the embodiment of the present application with the performance of a traditional single-axis flow wind wheel:

Fig. 5 shows a comparison of static pressure of the fan device according to the embodiment of the present application with that of a conventional single axial flow wind wheel under different air volumes. It can be seen that, under the condition of reaching the same air quantity, the static pressure of the fan device in the embodiment of the application is obviously higher than that of the traditional single axial flow wind wheel, which means that the fan device in the embodiment of the application has lower noise under the condition of reaching the same air quantity.

Fig. 6 shows a comparison of the power of the fan device according to the embodiment of the present application with that of a conventional single axial flow wind turbine when different air volumes are achieved. It can be seen that under the condition that the same air quantity is achieved, the fan device of the embodiment of the application is lower in power, which means that the fan device of the embodiment of the application is lower in required input power, and is beneficial to reducing the running cost of heat exchange, and meanwhile noise generated by the operation of the fan device of the embodiment of the application is also lower.

Fig. 7 shows the noise of the fan device according to the embodiment of the present application compared with that of a conventional single axial flow wind wheel under different air volumes. It can be seen that the fan device of the embodiment of the application has lower noise when the same air volume is achieved.

In an embodiment, referring to fig. 3, a side of the first wind wheel 21 facing away from the second wind wheel 22 is an air inlet side, a side of the second wind wheel 22 facing away from the first wind wheel 21 is an air outlet side, and air flows generated by rotation of the first wind wheel 21 and the second wind wheel 22 sequentially pass through the first wind wheel 21 and the second wind wheel 22 from the air inlet side and then are output from the air outlet side.

In one embodiment, with continued reference to fig. 2 and 3, the fan apparatus 20 further includes a drive assembly. The wind wheels (including the first wind wheel 21, the second wind wheel 22, etc.) of the fan device 20 are connected with a driving assembly, so that the driving assembly drives the wind wheels of the fan device 20 to rotate, and then the air flow is guided to pass through the heat exchanger 30 for heat exchange.

Specifically, the drive assembly may include a motor 23 or the like. In addition, each wind wheel of the fan device 20 may be driven by a different motor 23, or some wind wheels may share the same motor 23 for driving. Preferably, in the case where the wind turbine device 20 includes the first wind wheel 21 and the second wind wheel 22 in the above embodiment, the first wind wheel 21 and the second wind wheel 22 share the same motor 23, specifically, the motor 23 has two transmission shafts coaxially disposed, the two transmission shafts can reversely rotate around respective central axes, and the rotation speeds of the two transmission shafts can also be differently disposed (specific working principles are within the understanding scope of those skilled in the art and will not be described herein), as shown in fig. 2 and 3. In this way, the first wind wheel 21 and the second wind wheel 22 are respectively connected with different transmission shafts in a transmission manner, so that the first wind wheel 21 and the second wind wheel 22 can be driven to reversely rotate by one motor 23, and the differential setting of the rotating speed of the first wind wheel 21 and the rotating speed of the second wind wheel 22 can be realized.

Of course, in other embodiments of the present application, the driving assembly may also include a plurality of motors 23, where each wind wheel of the fan apparatus 20 is in driving connection with a different motor 23, and is further driven to rotate by a different motor 23, which is not limited herein.

The steering of the respective wind wheels (including the first wind wheel 21 and the second wind wheel 22, etc.) of the fan device 20 may be the same. For example, the motor 23 shared by the first wind wheel 21 and the second wind wheel 22 has two transmission shafts rotating in the same direction about respective central axes, so that the first wind wheel 21 and the second wind wheel 22 rotate in the same direction, which is not limited herein.

Referring to fig. 8 and 9, fig. 8 is a schematic structural view of an embodiment of a first wind wheel of the present application, and fig. 9 is a schematic structural view of an embodiment of a second wind wheel of the present application.

In an embodiment, the first wind rotor 21 comprises a first rotor hub 211 and a number of first blades 212. The plurality of first blades 212 are disposed at intervals along the circumferential direction of the first wind wheel hub 211. Specifically, the first wind wheel hub 211 is in driving connection with a driving assembly (such as the motor 23 shown in fig. 2 and 3, etc.), so that the first wind wheel 21 is in driving connection with the driving assembly, and the driving assembly drives the first wind wheel hub 211 to rotate, so that the first wind wheel 21 rotates, as shown in fig. 8.

The second rotor 22 comprises a second rotor hub 221 and a number of second blades 222. The plurality of second blades 222 are disposed at intervals along the circumference of the second wind wheel hub 221. Specifically, the second wind wheel hub 221 is in transmission connection with a driving assembly, so that the second wind wheel 22 is in transmission connection with the driving assembly, and the driving assembly drives the second wind wheel hub 221 to rotate, so that the second wind wheel 22 rotates, as shown in fig. 9.

In one embodiment, with continued reference to fig. 2 and 3, the fan apparatus 20 further includes a pod 24. The air guide sleeve 24 is sleeved on the periphery of the wind wheel of the fan device 20, for example, the peripheries of the first wind wheel 21 and the second wind wheel 22, and plays a role in guiding air flow generated by the wind wheel operation of the fan device 20, and is used for guiding air flow output, so that air flow flowing through the heat exchanger 30 is generated for heat exchange.

Alternatively, the cross-section of the pod 24 (i.e., a cross-section taken along a direction perpendicular to the direction in which the pod 24 extends) may be circular, etc., i.e., the pod 24 is a circular pod 24; the cross-sectional shape of the pod 24 may also be elliptical, i.e., the pod 24 is an elliptical pod 24. The flow guide cover 24 in the form of the elliptical flow guide cover 24 can enable gaps between the wind wheel and the flow guide cover 24 to be in a non-axial symmetrical mode, so that the leakage vortex of the blade tips is reduced, and the flow guide cover 24 in the form of the elliptical flow guide cover 24 can effectively convert dynamic pressure into static pressure so as to further reduce noise. Here, the cross section of the pod 24 is a cross section taken along the radial direction thereof.

Further, the casing 10 of the air conditioner outdoor unit has a mounting base 12, and the air guide cover 24 is mounted on the mounting base 12 and is further fixed to the casing 10 of the air conditioner outdoor unit.

Referring to fig. 2, 3 and 10, fig. 10 is a schematic structural diagram of an embodiment of a pod of the present application.

In an embodiment, the nacelle 24 includes a main body 241, and the main body 241 is sleeved on the outer peripheries of the first wind wheel 21 and the second wind wheel 22. Wherein the cross-sectional area (i.e., the cross-section taken in the radial direction, the same applies hereinafter) of the main body portion 241 at each position in the axial direction thereof is the same. Further, the body portion 241 takes the form of a straight cylinder.

Further, the nacelle 24 further includes a tapered portion 242 provided at one end of the main body portion 241 near the first wind wheel 21, and the cross-sectional area of each position of the tapered portion 242 in the axial direction thereof gradually decreases in the direction approaching the main body portion 241. The pod 24 further includes a diverging portion 243 provided at one end of the main body portion 241 near the second wind wheel 22, and the cross-sectional area of each position of the diverging portion 243 in the axial direction thereof gradually decreases in a direction approaching the main body portion 241.

That is, the tapered portion 242 and the diverging portion 243 are located on opposite sides of the main body portion 241, respectively, and the cross-sectional areas of the tapered portion 242 and the diverging portion 243 each appear to gradually decrease in a direction approaching the main body portion 241. Further, the central axes of the main body 241, the tapered portion 242, and the diverging portion 243 are arranged in a superposed manner.

Of course, in other embodiments of the present application, the pod 24 may include only the main body 241 and the tapered portion 242, or include only the main body 241 and the diverging portion 243, or include only the main body 241, which is not limited herein.

In one embodiment, with continued reference to fig. 2 and 3, the fan apparatus 20 further includes a bracket 25, the bracket 25 being configured to mount a drive assembly for securing the fan apparatus 20. The bracket 25 is fixed to the housing 10 of the outdoor unit of the air conditioner (for example, to the mount 12 in the above embodiment), thereby fixing the relative positions of the wind wheel and the driving assembly in the housing 10.

Alternatively, the cross-sectional shape of the bracket 25 may be square, circular, elliptical, etc., without limitation.

In an embodiment, referring to fig. 2 and 3, the fan apparatus 20 further includes a mesh enclosure 26, where the mesh enclosure 26 is disposed on the air outlet side, that is, the mesh enclosure 26 is disposed on the side of the second wind wheel 22 facing away from the first wind wheel 21. The mesh enclosure 26 allows the air flow generated by the first wind wheel 21 and the second wind wheel 22 to pass through, and can play a certain shielding role at the same time, so that foreign matters are prevented from falling into the fan device 20 from the air outlet side to influence the normal operation of the fan device 20, and the like.

In one embodiment, with continued reference to fig. 2 and 3, the heat exchanger 30 is a device that transfers a portion of the heat of a hot fluid to a cold fluid, also known as a heat exchanger. In this embodiment, the heat exchanger 30 exchanges heat with the gas passing through the heat exchanger 30, and the fan device 20 works to form an air flow passing through the heat exchanger 30 at a faster speed, which helps to improve the heat exchange efficiency.

Specifically, the heat exchanger 30 is generally composed of heat exchange tubes and heat exchange fins. The refrigerant filled in the heat exchange tube exchanges heat with the outside through the heat exchange tube and the heat exchange fins, and the heat exchange tube and the heat exchange fins have larger surfaces to contact with the outside air, namely, larger heat exchange area is provided, so that the heat exchange efficiency can be improved. The heat exchange tube and the heat exchange fin are preferably made of a material having good heat conductive properties, for example, copper metal, etc., and are not limited thereto.

Optionally, the fin-type heat exchanger 30 (i.e. the heat exchanger 30 comprising the heat exchange tubes and the heat exchange fins) may be divided into a single-sided air intake mode, a double-sided air intake mode, a three-sided air intake mode, a four-sided air intake mode, and the like according to the condition of the air intake surface 31.

Specifically, for the air conditioner outdoor unit having four sides 13, the casing 10 of the air conditioner outdoor unit is enclosed to form a quadrangular prism having four sides 13, wherein one air inlet surface 31 of the heat exchanger 30 is disposed corresponding to one side 13 of the casing 10, as shown in fig. 2. The various air inlet forms of the heat exchanger 30 correspond to the number of air inlet surfaces 31 of the heat exchanger 30.

For example, a single-sided inlet type heat exchanger 30 means that the heat exchanger 30 is arranged in correspondence with one side 13 of the housing 10, i.e. has only one inlet side 31, e.g. an I-type heat exchanger or the like; the heat exchanger 30 in the form of two-sided air intake means that the heat exchanger 30 is arranged in correspondence of the two sides 13 of the housing 10, i.e. has two air intake sides 31, such as a V-shaped heat exchanger or the like; the three-sided air-intake type heat exchanger 30 means that the heat exchanger 30 is disposed corresponding to the three side surfaces 13 of the housing 10, i.e., has three air intake surfaces 31, such as a U-shaped heat exchanger, etc.; the heat exchanger 30 in the form of four-sided air intake means that the heat exchanger 30 is arranged in correspondence with the four sides 13 of the housing 10, i.e. has four air intake surfaces 31, such as e.g. a G-type heat exchanger, a mouth-type heat exchanger, etc.

In an embodiment, with continued reference to fig. 2 and 3, the fan apparatus 20 further includes guide vanes 27, the guide vanes 27 being axially spaced from the first wind wheel 21 and the second wind wheel 22, respectively. Further, the guide vane 27, the first wind wheel 21 and the second wind wheel 22 are coaxially arranged, that is, the central axes of the guide vane 27, the first wind wheel 21 and the second wind wheel 22 coincide.

The guide vane 27 has different functions according to the position of the guide vane 27, for example, when the guide vane 27 is arranged on the air inlet side, the guide vane 27 is used for providing pre-rotation for the incoming flow of the first wind wheel 21, namely providing pre-rotation airflow, so that the complicated incoming flow is rectified, the energy loss is reduced, and the air quantity is improved; when the guide vane 27 is disposed at the air outlet side, the guide vane 27 is used for recovering the rotational velocity component of the air flow passing through the second wind wheel 22, so that the air flow is blown out along the axial direction of the fan device 20 as much as possible, which is beneficial to improving the static pressure and the air volume, and further improving the efficiency of the fan device 20. As will be described in detail below.

Specifically, the vane 27 includes a vane hub 271 and a plurality of vane blades 272, the plurality of vane blades 272 being disposed at intervals along the circumferential direction of the vane hub 271, as shown in fig. 2.

It can be appreciated that the air conditioning outdoor unit of the embodiment of the present application may be applied to a multi-connected air conditioning system, and the design of the first wind wheel 21 and the second wind wheel 22 in the embodiment of the present application makes the multi-connected air conditioning system applying the air conditioning outdoor unit of the embodiment of the present application have a stronger compression resistance, and can effectively solve the problem of high external pressure drop in the installation process of the multi-connected air conditioning system, which is not limited herein.

Relationship between the number of blades of the first rotor and the second rotor

With continued reference to fig. 2 and 3, the following description will take the example in which the fan apparatus 20 includes the first wind wheel 21 and the second wind wheel 22.

In an embodiment, the number of blades of the first rotor 21 and the number of blades of the second rotor 22 are prime numbers with respect to each other. In this way, beat noise generated when the first wind wheel 21 and the second wind wheel 22 operate can be reduced, and meanwhile, part of harmonic noise can be reduced or eliminated, so that noise can be further reduced.

Referring to fig. 11, fig. 11 shows a comparison of the noise levels of the fan apparatus 20 of the present embodiment and the conventional single-axis wind turbine at different frequencies. It can be seen that the fan apparatus 20 of the present embodiment has less noise at the same frequency. This is because the airflow generates obvious noise when passing through the conventional single-axis airflow wind wheel, and the number of blades of the first wind wheel 21 and the number of blades of the second wind wheel 22 in this embodiment are reasonably matched, so that the noise level can be effectively reduced.

In an embodiment, the difference between the number of blades of the first rotor 21 and the number of blades of the second rotor 22 is 2. Specifically, the number of blades n of the first wind wheel 21 ₁ Number of blades n of the second rotor 22 ₂ Has the following relationship: n is n ₁ ＞n ₂ 、n ₁ ＝n ₂ +2, or n ₁ ＜n ₂ 、n ₂ ＝n ₁ +2。

According to the aerodynamic noise basic theory analysis and the actual engineering experience, when the number of blades of adjacent wind wheels (namely, the first wind wheel 21 and the second wind wheel 22) axially connected in series meets the above relation, the noise value generated by mutual interference between the two wind wheels is lower, which is beneficial to reducing the aerodynamic noise of the fan device 20.

Particularly, the wake flow of the first wind wheel 21 acts on the front edge (edge close to the first wind wheel 21) of the second wind wheel 22 to generate noise, so that the noise caused by the second wind wheel 22 is larger than the noise caused by the first wind wheel 21, the number of blades of the second wind wheel 22 is ensured to be smaller than that of the blades of the first wind wheel 21, the noise caused by the second wind wheel 22 is reduced, and the overall noise of the fan device 20 is reduced.

Further, when the diameter of the first wind wheel 21 (as shown by D in fig. 8 ₁ As shown, below) and the diameter of the second rotor 22 (as D in fig. 9) ₂ As shown, the same applies below) are each greater than or equal to the first threshold value, the greater of the number of blades of the first rotor 21 and the number of blades of the second rotor 22 is greater than or equal to the second threshold value; and when the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 are both smaller than the first threshold value, the larger value of the number of blades of the first wind wheel 21 and the number of blades of the second wind wheel 22 is smaller than or equal to the third threshold value. Wherein the second threshold is greater than the third threshold.

For example, the value of the first threshold value ranges from 450mm to 800mm, preferably 600mm, etc.; the second threshold value is preferably 9 or the like; the third threshold is preferably 7 or the like. For example, when the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 are both 600mm or more, n ₁ ＝9、n ₂ =7 or n ₁ ＝7、n ₂ =9, etc.; and when the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 are both smaller than 600mm, n ₁ ＝7、n ₂ =5 or n ₁ ＝5、n ₂ =7, etc.

By the above-mentioned mode, can avoid when the diameter of first wind wheel 21 and the diameter of second wind wheel 22 are less and the blade quantity of first wind wheel 21 and the blade quantity of second wind wheel 22 are more, lead to the consistence of first wind wheel 21 and second wind wheel 22 too big, and then lead to the problem that the performance of first wind wheel 21 and second wind wheel 22 reduces, can avoid simultaneously when the diameter of first wind wheel 21 and the diameter of second wind wheel 22 are great and the blade quantity of first wind wheel 21 and the blade quantity of second wind wheel 22 are less, lead to the problem that the performance of first wind wheel 21 and second wind wheel 22 can not obtain full play.

Fig. 12a shows a case where the number of blades of the first rotor 21 is 9 and the number of blades of the second rotor 22 is 7. Fig. 12b shows a case where the number of blades of the first rotor 21 is 7 and the number of blades of the second rotor 22 is 9. Fig. 12c shows a case where the number of blades of the first rotor 21 is 5 and the number of blades of the second rotor 22 is 7.

In this embodiment, the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 may be the same or different, and the number of blades of both may satisfy the above relationship.

In one embodiment, the existence of tip leakage vortex of the second wind wheel 22 (i.e. vortex generated on the outer side of the tip of the second wind wheel 22) is considered, and the tip leakage vortex is one of the main sources of aerodynamic noise of the wind wheel, which means that the second wind wheel 22 is a main noise source. The number of blades of the first rotor 21 is thus preferably greater than the number of blades of the second rotor 22, while ensuring the performance of the fan assembly 20. In this way, the number of the blades of the second wind wheel 22 is smaller, so that the aerodynamic noise caused by the second wind wheel 22 can be effectively reduced, and meanwhile, in order to ensure the performance (including the air quantity, the air outlet efficiency, etc.) of the fan device 20, the number of the blades of the first wind wheel 21 is larger, so that the performance of the fan device 20 can meet the requirement.

In an alternative embodiment, the number of blades n of the first rotor 21 ₁ Number of blades n of the second rotor 22 ₂ Has the following relationship: |h|n ₁ -s*n ₂ And the I is more than or equal to 2, h, s is E (1, 2, 3). In this way, the noise caused by the mutual interference of the first wind wheel 21 and the second wind wheel 22 can be kept at the minimum level, and the occurrence of the flapping phenomenon can be avoided as much as possible.

In an embodiment, the number of blades of the first rotor 21 and the number of blades of the second rotor 22 are each in positive correlation with their respective diameters. Specifically, the larger the diameter of the first wind wheel 21, the larger the number of blades of the first wind wheel 21, and the larger the diameter of the second wind wheel 22, the larger the number of blades of the second wind wheel 22.

Under the condition of a certain rotating speed, the larger the diameter of the wind wheel is, the more the number of blades is, and the larger the air quantity is. Therefore, the number of blades of the first wind wheel 21 and the number of blades of the second wind wheel 22 in this embodiment are in positive correlation with the respective diameters, respectively, so that the number of blades of the first wind wheel 21 and the number of blades of the second wind wheel 22 can be matched with the respective diameters to improve the performance of the first wind wheel 21 and the second wind wheel 22.

Diameter relation of first wind wheel and second wind wheel

The following description will be given by taking the example in which the fan apparatus 20 includes the first wind wheel 21 and the second wind wheel 22 in the above embodiment.

Referring to fig. 13 and 14, fig. 13 is a schematic structural view of a first embodiment of a fan apparatus according to the present application, and fig. 14 is a schematic structural view of a second embodiment of the fan apparatus according to the present application.

In one embodiment, the diameter of the first rotor 21 (see D in fig. 13 and 14 ₁ As shown below) is greater than or equal to the diameter of the second rotor 22 (see D in fig. 13 and 14) ₂ As shown, the following is the same).

The tip leakage vortex is one of main sources of aerodynamic noise of the wind wheel, and the existence of the tip leakage vortex of the second wind wheel 22 is considered, the diameter of the first wind wheel 21 is larger than that of the second wind wheel 22, as shown in fig. 13, so that a part of the first wind wheel 21 with a larger wind sweeping area than that of the second wind wheel 22 can apply work to airflow, the tip leakage vortex of the second wind wheel 22 is eliminated or weakened, and aerodynamic noise can be further reduced. Specifically, the airflow provided by the part of the first wind wheel 21 with the larger wind sweeping area than the second wind wheel 22 can blow the vortex outside the blade tip of the second wind wheel 22 away from the blade tip of the second wind wheel 22, thereby playing a role in noise reduction.

Further, the diameter of the first wind wheel 21 is larger than the diameter of the second wind wheel 22. Preferably, the diameter D of the first wind wheel 21 ₁ Diameter D of the second wind wheel 22 ₂ Has the following relationship: 1.01D ₂ ≤D ₁ ≤1.03D ₂ . In this way, the aerodynamic noise can be further reduced.

Of course, if the problem of matching the performance of the first wind wheel 21 and the second wind wheel 22 is considered, the diameter of the first wind wheel 21 is preferably equal to the diameter of the second wind wheel 22, as shown in fig. 14. Since the smaller diameter wind wheel is a bottleneck of the performance of the fan device 20 when the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 are set differently, the performance of the larger diameter wind wheel cannot be fully exerted due to the performance of the smaller diameter wind wheel, but the cost of the fan device 20 and the burden of the whole system are increased. Thus, in the above case, the diameter of the first wind wheel 21 is preferably equal to the diameter of the second wind wheel 22.

It should be noted that, if the diameter of the first wind wheel 21 is smaller than the diameter of the second wind wheel 22, the wind sweeping area of the first wind wheel 21 is smaller than the wind sweeping area of the second wind wheel 22, so that the first wind wheel 21 cannot eliminate or weaken the tip leakage vortex of the second wind wheel 22, which is not beneficial to reducing aerodynamic noise. Moreover, since one of the main functions of the first wind wheel 21 is to provide the pre-spinning air flow for the second wind wheel 22, the diameter of the first wind wheel 21 is smaller than that of the second wind wheel 22, which will affect the first wind wheel 21 to provide the pre-spinning air flow for the second wind wheel 22.

Alternatively, the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 are each 560mm to 850mm. In this way, the first wind wheel 21 and the second wind wheel 22 can generate enough air quantity, so that the air conditioner outdoor unit in the embodiment of the application achieves the required heat exchange efficiency.

Relation between diameters of the first wind wheel and the second wind wheel and diameters of respective hubs

With continued reference to fig. 8 and 9, the following description will take the example in which the fan apparatus 20 includes the first wind wheel 21 and the second wind wheel 22.

In one embodiment, the diameter D of the first rotor 21 ₁ Diameter D to first rotor hub 211 ₁₁ Has the following relationship: 2 is less than or equal to D ₁ /D ₁₁ And less than or equal to 4.5, as shown in figure 8. Diameter D of the second wind wheel 22 ₂ Diameter D of second rotor hub 221 ₂₁ Has the following relationship: 2 is less than or equal to D ₂ /D ₂₁ And 4.5, as shown in figure 9.

Through the above mode, the dimensional relationship between the first wind wheel 21 and the first wind wheel hub 211 and the dimensional relationship between the second wind wheel 22 and the second wind wheel hub 221 can be reasonably configured, which is beneficial to ensuring that the first wind wheel 21 and the second wind wheel 22 have enough installation strength, and meanwhile, the airflow channel can be increased, and the ventilation air quantity can be greatly increased.

Further, diameter D of first rotor hub 211 ₁₁ Diameter D of second rotor hub 221 ₂₁ Has the following characteristicsRelationship: d (D) ₂₁ ≤D ₁₁ The air quantity and the fan efficiency are improved. If the diameter of the first wind wheel hub 211 is smaller than that of the second wind wheel hub 221, the second wind wheel hub 221 will block the airflow passing through the first wind wheel 21, and form vortex easily, so as to have adverse effects on the airflow and fan efficiency.

Relation between thickness of first wind wheel, thickness of second wind wheel and spacing of first wind wheel and second wind wheel

In one embodiment, with continued reference to fig. 14, the length H of the first rotor 21 in the axial direction ₁ (i.e., the thickness of the first rotor 21), the length H of the second rotor 22 in the axial direction ₂ (i.e., the thickness of the second rotor 22) and the spacing S between the first rotor 21 and the second rotor 22 ₀ (i.e., the distance between the first wind wheel 21 and the second wind wheel 22 in the axial direction parallel to the central axes of the first wind wheel 21 and the second wind wheel 22) has the following relationship: s is S ₀ <(H ₁ +H ₂ )/2. In this way, the performance of the fan device 20 can be prevented from being affected by the excessive distance between the first wind wheel 21 and the second wind wheel 22.

Further, the distance between the first wind wheel 21 and the second wind wheel 22 is preferably greater than or equal to 20mm. This is to consider the flow induced vibration of the first wind wheel 21 and the second wind wheel 22 in the rotation process and the error factors such as processing and assembling, so as to ensure that the first wind wheel 21 and the second wind wheel 22 do not excessively contact in the rotation process, and reduce the noise generated by the mutual interference between the first wind wheel 21 and the second wind wheel 22.

In an embodiment, with continued reference to fig. 14, the distance between the end of the first wind wheel 21 facing away from the second wind wheel 22 and the end of the second wind wheel 22 facing away from the first wind wheel 21 is 260mm to 360mm. That is, the sum of the total thickness of the first wind wheel 21 and the second wind wheel 22 and the distance therebetween (i.e., H as described above ₁ 、H ₂ 、S ₀ The sum of the three) is 260mm to 360mm. According to practical engineering experience, the first wind wheel 21 and the second wind wheel 22 can be well applied to 12 pieces and below Model.

In an embodiment, with continued reference to fig. 14, the diameter of the first wind wheel 21 is equal to the diameter of the second wind wheel 22, such that the performance of the first wind wheel 21 and the second wind wheel 22 can be matched to each other.

Further, the length of the first wind wheel 21 in the axial direction is preferably smaller than or equal to the length of the second wind wheel 22 in the axial direction. Specifically, the length H of the first wind wheel 21 in the axial direction ₁ Length H in axial direction with second wind wheel 22 ₂ Has the following relationship: h ₁ ≤H ₂ ≤1.2H ₁ Or 0.75H ₂ ≤H ₁ ≤H ₂ 。

The length of the first wind wheel 21 in the axial direction is equal to the length of the second wind wheel 22 in the axial direction, so that the performances of the first wind wheel 21 and the second wind wheel 22 can be further ensured to be matched with each other. In addition, since one of the main functions of the first wind wheel 21 is to provide the pre-spinning air flow for the second wind wheel 22, the length of the first wind wheel 21 in the axial direction is smaller than that of the second wind wheel 22, so as to properly weaken the pressure rising effect of the first wind wheel 21 and highlight the pre-spinning effect of the first wind wheel 21.

And, the length of the first wind wheel 21 in the axial direction and the length of the second wind wheel 22 in the axial direction can adjust the pressure rise distribution of the first wind wheel 21 and the second wind wheel 22. The ratio of the pressure rise distribution ratio of the first wind wheel 21 to the pressure rise distribution ratio of the second wind wheel 22 is 3:5 to 1:1. It can be understood that when the ratio of the pressure rise distribution rate of the first wind wheel 21 to the pressure rise distribution rate of the second wind wheel 22 is 1:1, the axial length of the first wind wheel 21 is equal to the axial length of the second wind wheel 22; and when the pressure rise distribution ratio of the first wind wheel 21 is low and the pressure rise distribution ratio of the second wind wheel 22 is high, the situation that the length of the first wind wheel 21 in the axial direction is smaller than that of the second wind wheel 22 is corresponding.

Further, when the diameter of the first wind wheel 21 is equal to the diameter of the second wind wheel 22, the distance between the first wind wheel 21 and the second wind wheel 22 is preferably 20mm to 40mm. In this way, the excessive distance between the first wind wheel 21 and the second wind wheel 22 can be avoided, the first wind wheel 21 and the second wind wheel 22 are ensured not to excessively contact in the rotation process, and noise generated by mutual interference between the first wind wheel 21 and the second wind wheel 22 is reduced.

Relationship between fan device and air guide sleeve

With continued reference to fig. 14, the following description will take the example in which the blower device 20 includes the first wind wheel 21 and the second wind wheel 22.

In an embodiment, a portion of the first wind wheel 21 is disposed within the main body portion 241 of the pod 24, and at least a portion of the second wind wheel 22 is disposed within the main body portion 241 of the pod 24. That is, the first wind wheel 21 is only partially disposed in the main body 241, and the second wind wheel 22 may be only partially disposed in the main body 241, or the second wind wheel 22 may be entirely disposed in the main body 241.

In one embodiment, the distance S between the end of the first wind wheel 21 on the air inlet side and the end of the main body 241 on the air inlet side ₁ Length H in axial direction with first wind wheel 21 ₁ Has the following relationship: s is more than or equal to 0.4 ₁ /H ₁ Less than or equal to 0.7, which is beneficial to reducing noise.

It should be noted that, by adjusting the position of the first wind wheel 21 in the air guide sleeve 24, the flow field of the air channel in the air guide sleeve 24 can be improved, and the coupling noise between the blades of the first wind wheel 21 and the air guide sleeve 24 can be reduced. FIG. 15 shows S ₁ /H ₁ E (0, 1), the noise variation amount detected by the detection point. As can be seen, S ₁ And H is ₁ The ratio of (2) is other than 0.55, and the noise variation is different and the noise increase is shown, so that the embodiment is preferably S ₁ /H ₁ =0.55, so that the fan device 20 of the present embodiment has as little noise as possible.

Optionally based on S ₁ /H ₁ In the case of =0.55, in an exemplary embodiment, H ₁ ＝126mm，S ₁ =69.3 mm, not limited herein.

In an embodiment, the distance S between the end of the second wind wheel 22 facing away from the first wind wheel 21 and the end of the main body portion 241 facing away from the first wind wheel 21 ₂ Length H in axial direction with second wind wheel 22 ₂ Has the following relationship: s is more than or equal to 0 ₂ /H ₂ Less than or equal to 0.25, which is beneficial to reducing noise.

It should be noted that, by adjusting the position of the second wind wheel 22 in the air guide sleeve 24, the flow field of the air channel in the air guide sleeve 24 can be improved, and the coupling noise between the blades of the second wind wheel 22 and the air guide sleeve 24 can be reduced. FIG. 16 shows S ₂ /H ₂ And taking the noise variation detected by the detection point when different values are taken. In fig. 16, when the second wind wheel 22 is only partially disposed in the main body 241, the distance between the end of the second wind wheel 22 facing away from the first wind wheel 21 and the end of the main body 241 facing away from the first wind wheel 21 is positive; with the distance between the end of the second wind wheel 22 facing away from the first wind wheel 21 and the end of the main body portion 241 facing away from the first wind wheel 21 being negative when the second wind wheel 22 is fully disposed in the main body portion 241, specifically S ₂ /H ₂ ∈(-0.5,0.5)。

As can be seen, S ₂ And H is ₂ The ratio of (2) is other than 0, and the noise variation is different and the noise increase is shown, so that the embodiment is preferably S ₂ /H ₂ =0, so that the fan apparatus 20 of the present embodiment has as little noise as possible.

Optionally based on S ₂ /H ₂ In the case of =0, in an exemplary embodiment, H ₂ ＝126mm，S ₂ =0mm, i.e. the distance between the end of the second wind wheel 22 facing away from the first wind wheel 21 and the end of the main body portion 241 facing away from the first wind wheel 21 is zero, which is not limited herein.

In an embodiment, the distance S between the end of the second wind wheel 22 facing away from the first wind wheel 21 and the end of the main body portion 241 facing away from the first wind wheel 21 ₂ Length H in axial direction with diverging section 243 _k Has the following relationship: s is S ₂ ≤H _k 。

According to practical engineering experience, the above relation can greatly improve the diffusion effect of the outlet air quantity of the fan device 20, and is beneficial to enhancing the aerodynamic performance of the fan device 20. Specifically, the distance between the end of the second wind wheel 22 facing away from the first wind wheel 21 and the end of the main body portion 241 facing away from the first wind wheel 21 satisfies the above relationship with the length of the diverging portion 243 in the axial direction, so that the air passing through the second wind wheel 22 can be ensuredThe flow can receive the drainage effect of the air guide sleeve 24, which is beneficial to improving the air quantity and the fan efficiency. If the above S ₂ ＞H _k Part of the airflow passing through the second wind wheel 22 cannot receive the drainage effect of the air guide sleeve 24, so that scattered wind can occur, and the wind quantity and the fan efficiency are affected.

In an embodiment, the diameter of the first wind wheel 21 is equal to the diameter of the second wind wheel 22, as shown in fig. 14, so that the performance of the first wind wheel 21 and the second wind wheel 22 can be matched to each other.

Further, the diameter D of the first wind wheel 21 ₁ An inner diameter D with the main body 241 ₃ Has the following relationship: 5mm of<(D ₃ -D ₁ )/2<20mm. In this way, the inner diameter of the main body 241 of the air guide sleeve 24 is set, which is favorable for reducing the tip leakage vortex of the first wind wheel 21 and the second wind wheel 22, so as to achieve the effects of larger air volume and smaller noise under the same rotation speed.

Further, the diameter D of the first wind wheel 21 ₁ An inner diameter D with the main body 241 ₃ Has the following relationship: 8mm of<(D ₃ -D ₁ )/2<12mm. Preferably, (D) ₃ -D ₁ ) 2=10mm. In this way, the tip leakage vortex of the first wind wheel 21 and the second wind wheel 22 can be reduced to the maximum extent, thereby improving the wind volume to the maximum extent and reducing noise.

In an alternative embodiment, the diameter D of the first wind wheel 21 ₁ An inner diameter D with the main body 241 ₃ Has the following relationship: 0.008D ₁ ≤D ₃ -D ₁ ≤0.016D ₁ . In this way, the inner diameter of the main body 241 of the air guide sleeve 24 is set, which is favorable for reducing the tip leakage vortex of the first wind wheel 21 and the second wind wheel 22, so as to achieve the effects of larger air volume and smaller noise under the same rotation speed.

Fan device, air guide sleeve and mounting seat relation

Referring to fig. 14 and 17, fig. 17 is a schematic structural view of an embodiment of a pod and mount of the present application.

In one embodiment, the length H of the pod 24 and mount 12 in the axial direction of the pod 24 ₃ (as shown in fig. 17) and the length H of the first wind wheel 21 and the second wind wheel 22 in the axial direction ₄ (as shown in fig. 14) has the following relationship: 0.68H ₃ ≤H ₄ ≤0.75H ₃ . Wherein the length H of the first wind wheel 21 and the second wind wheel 22 in the axial direction ₄ It should be understood that the sum of the length of the first wind wheel 21 in the axial direction, the length of the second wind wheel 22 in the axial direction, and the distance between the first wind wheel 21 and the second wind wheel 22.

By the above mode, the lengths of the air guide sleeve 24 and the mounting seat 12 in the axial direction of the air guide sleeve 24 can be matched with the lengths of the first wind wheel 21 and the second wind wheel 22 in the axial direction, so that the purpose of inhibiting the tip leakage vortex of the first wind wheel 21 and the second wind wheel 22 can be achieved, and the air quantity is improved and the noise is reduced.

In one embodiment, the length H of the first wind wheel 21 in the axial direction ₁ Length H in axial direction with tapered portion 242 ₅ Has the following relationship: 0.25H ₁ ≤H ₅ ≤0.4H ₁ . Through the above manner, the length of the air guide sleeve 24 in the axial direction can be matched with the length of the first wind wheel 21 in the axial direction, so that the purpose of inhibiting the tip leakage vortex of the first wind wheel 21 can be achieved, and meanwhile, the air inlet area of the fan device 20 is allowed to be increased to the greatest extent, and further, the air quantity is improved and noise is reduced.

In one embodiment, the length H of the body portion 241 in the axial direction ₆ Length H in axial direction with the pod 24 ₇ Has the following relationship: 0.75H ₇ ≤H ₆ ≤0.8H ₇ . In this way, the proportional relationship between the length of the main body 241 of the air guide sleeve 24 in the axial direction and the length of the entire air guide sleeve 24 in the axial direction can be reasonably set, so that the length parameters of each part of the air guide sleeve 24 in the axial direction can be more reasonably matched with the length parameters of the first wind wheel 21 and the second wind wheel 22 in the axial direction, which is more beneficial to inhibiting the tip leakage vortex of the first wind wheel 21 and the second wind wheel 22, further improving the air quantity and reducing the noise.

Relationship between the first wind wheel, the second wind wheel and the guide vane in the axial direction

Referring to fig. 18 and 19, fig. 18 is a schematic structural view of a third embodiment of a fan apparatus according to the present application, and fig. 19 is a schematic structural view of a fourth embodiment of the fan apparatus according to the present application.

In one embodiment, the length H of the first wind wheel 21 in the axial direction ₁ Length H of the second wind wheel 22 in the axial direction ₂ Length H of guide vane 27 in axial direction ₈ Has the following relationship: 0.25 (H) ₁ +H ₂ )≤H ₈ ≤0.75(H ₁ +H ₂ ). And, the distance S between the guide vane 27 and the adjacent first wind wheel 21 or second wind wheel 22 ₃ Length H of first wind wheel 21 in axial direction ₁ And the length H of the second wind wheel 22 in the axial direction ₂ Has the following relationship: 0.05 (H) ₁ +H ₂ )≤S ₃ ≤0.25(H ₁ +H ₂ )。

Specifically, when the guide vanes 27 are provided on the air intake side, i.e., the guide vanes 27 are provided on the side of the first wind wheel 21 facing away from the second wind wheel 22, as shown in fig. 18. Distance S between guide vane 27 and adjacent first wind wheel 21 ₃ Length H of first wind wheel 21 in axial direction ₁ And the length H of the second wind wheel 22 in the axial direction ₂ Has the following relationship: 0.05 (H) ₁ +H ₂ )≤S ₃ ≤0.25(H ₁ +H ₂ ). The bending direction of the blades of the guide vanes 27 is opposite to that of the blades of the first wind wheel 21, and the guide vanes 27 are used for providing pre-rotation for the incoming flow of the first wind wheel 21, namely providing pre-rotation airflow, so that the complicated incoming flow is rectified, energy loss is reduced, and the wind quantity is improved.

Further, for the case that the fan device 20 is provided with the guide vane 27, the end part of the guide vane 27 far away from the first wind wheel 21 can be flush with the end part of the main body part 241 of the guide cover 24 close to the first wind wheel 21, so that the entering airflow can not only receive the rectifying action of the guide vane 27, but also receive the drainage action of the guide cover 24.

When the guide vane 27 is arranged on the air outlet side, that is, the guide vane 27 is arranged on the second wind wheel 22 and faces away from the first wind wheelOne side of the wind wheel 21 is shown in fig. 19. Spacing S of guide vanes 27 from adjacent second wind wheel 22 ₃ Length H of first wind wheel 21 in axial direction ₁ And the length H of the second wind wheel 22 in the axial direction ₂ Has the following relationship: 0.05 (H) ₁ +H ₂ )≤S ₃ ≤0.25(H ₁ +H ₂ ). The second wind wheel 22 can recover most of the rotational velocity component of the air flow passing through the first wind wheel 21 along the circumferential direction through the rotational direction different from that of the first wind wheel 21, so that the air flow is blown out along the axial direction of the fan device 20 as much as possible, which is beneficial to improving the static pressure and the air quantity, and further improving the efficiency of the fan device 20. Meanwhile, the guide vanes 27 are additionally arranged on the air outlet side, the bending direction of the blades of the guide vanes 27 is opposite to that of the blades of the second wind wheel 22, so that the rotating speed component of the air flow passing through the second wind wheel 22 along the circumferential direction is further recovered through the guide vanes 27, the air flow is further blown out along the axial direction of the fan device 20 as much as possible, static pressure and air quantity are further facilitated to be improved, and the efficiency of the fan device 20 is further improved.

Further, for the case that the fan device 20 is provided with the guide vane 27, the end portion of the guide vane 27 far away from the second wind wheel 22 may be flush with the end portion of the main body portion 241 of the guide cover 24 close to the second wind wheel 22, so that the airflow passing through the second wind wheel 22 can receive both the rectifying action of the guide vane 27 and the drainage action of the guide cover 24.

The bending direction of the blades of the first rotor 21, the bending direction of the blades of the second rotor 22, and the bending direction of the blades of the guide vanes 27 are specifically represented by the bending tendency of the blades of the three in the respective circumferential directions.

Of course, the guide vanes 27 can be disposed on the air inlet side and the air outlet side, and the guide vanes 27 at corresponding positions have corresponding effects, and will not be described herein.

Relationship between first wind wheel hub, second wind wheel hub and guide vane hub

In an embodiment, with continued reference to FIG. 19, the diameter of the vane hub 271 is smaller than the diameter of the first rotor hub 211 and the diameter of the second rotor hub 221.

Specifically, the diameter D of the vane hub 271 ₈₁ Diameter D of the first rotor hub 211 ₁₁ And diameter D of second rotor hub 221 ₂₁ Has the following relationship: 0<D ₈₁ ≤0.95D ₁₁ ，0<D ₈₁ ≤0.95D ₂₁ . Preferably, the diameter D of the vane hub 271 ₈₁ Diameter D of the first rotor hub 211 ₁₁ And diameter D of second rotor hub 221 ₂₁ Has the following relationship: 0.7D ₁₁ ≤D ₈₁ ≤0.9D ₁₁ ，0.7D ₂₁ ≤D ₈₁ ≤0.9D ₂₁ . In this way, the guide vane 27 is beneficial to ensuring enough installation structural strength, and meanwhile, enough flow passage can be reserved, so that air quantity loss is reduced. In addition, the diameter of the vane hub 271 is smaller than the diameters of the first wind wheel hub 211 and the second wind wheel hub 221, so that the phenomenon that the air flow impacts the vane hub 271 to generate vortex can be relieved.

Blade number relation among first wind wheel, second wind wheel and guide vane

In an embodiment, the number of blades of the first rotor 21, the number of blades of the second rotor 22, and the number of blades of the guide vanes 27 are prime numbers of each other. For example, the number of blades of the first wind wheel 21 is 9, the number of blades of the second wind wheel 22 is 7, the number of blades of the guide vanes 27 is 11, etc.

In this way, since the number of blades of the guide vane 27 is related to the lifting effect of the fan device 20, by the design that the number of blades of the first wind wheel 21, the number of blades of the second wind wheel 22 and the number of blades of the guide vane 27 are prime, the number of blades of the first wind wheel 21, the number of blades of the second wind wheel 22 and the number of blades of the guide vane 27 can be mutually matched, so that the fan device 20 achieves the optimal lifting effect.

In an embodiment, the number of blades n of the first rotor 21 ₁ Number of blades n of the second rotor 22 ₂ GuideNumber of leaves n of leaves 27 ₃ Has the following relationship: n is n ₁ ≤n ₂ 、n ₂ ≤n ₃ ≤2n ₁ Or n ₂ ≤n ₁ 、n ₁ ≤n ₃ ≤2n ₂ . According to practical engineering experience, the number of the blades of the guide vanes 27, the number of the blades of the first wind wheel 21 and the number of the blades of the second wind wheel 22 meet the above relation, so that the guide vanes 27 can be ensured to have enough consistency to ensure that the guide vanes 27 have good rectifying and pressurizing effects, the number of new noise sources introduced can be limited, and the total noise value of the fan device 20 can be effectively controlled.

Preferably, the number of blades n of the first rotor 21 ₁ Number of blades n of the second rotor 22 ₂ Number of blades n of guide vane 27 ₃ Has the following relationship: n is n ₂ ≤n ₁ 、n ₁ ≤n ₃ ≤2n ₂ . In this way, since the first wind wheel 21 is relatively close to the air inlet side and the second wind wheel 22 is relatively close to the air outlet side, and the second wind wheel 22 is considered to be a main source of aerodynamic noise, the number of blades of the second wind wheel 22 is smaller than that of the first wind wheel 21, which means that the number of blades of the second wind wheel 22 is relatively smaller, so that noise caused by rotation of the second wind wheel 22 is reduced; meanwhile, for the case that the number of blades of the first wind wheel 21 is equal to that of the second wind wheel 22, the performance of the first wind wheel 21 can be matched with that of the second wind wheel 22, so that the performance of the first wind wheel 21 and the second wind wheel 22 can be exerted to the maximum extent and the cost of the fan device 20 can be reduced. In addition, the number of blades of the guide vanes 27 can improve the pressure rise effect to the maximum extent as described above, which is further advantageous for improving the performance of the fan apparatus 20.

In one embodiment, the number of blades of the guide vanes 27 is 6 to 17. In this way, the production costs of the fan device and the performance of the guide vanes 27 can be optimized.

Relative position relation of first wind wheel, second wind wheel and bracket

In an embodiment, the support 25 is provided at least one of a side of the first wind wheel 21 facing away from the second wind wheel 22, a side of the second wind wheel 22 facing away from the first wind wheel 21, and between the first wind wheel 21 and the second wind wheel 22. Fig. 2 and 3 show that the bracket 25 is disposed on the side of the first wind wheel 21 facing away from the second wind wheel 22, and the other arrangement manners described above are within the understanding scope of those skilled in the art, and will not be described herein.

Specifically, when the first wind wheel 21 and the second wind wheel 22 are driven by the same motor 23, the motor 23 common to the first wind wheel 21 and the second wind wheel 22 is mounted on the bracket 25. At this time, the bracket 25 may be disposed on a side of the first wind wheel 21 facing away from the second wind wheel 22, or on a side of the second wind wheel 22 facing away from the first wind wheel 21. Fig. 2 and 3 show that the support 25 is provided on the side of the first wind wheel 21 facing away from the second wind wheel 22.

When the first wind wheel 21 and the second wind wheel 22 are driven by different motors 23, the motors 23 connected with the first wind wheel 21 and the motors 23 connected with the second wind wheel 22 are respectively arranged on different brackets 25. Also, the bracket 25 corresponding to the first wind wheel 21 may be disposed on any one of two sides of the first wind wheel 21 facing and facing away from the second wind wheel 22, and the bracket 25 corresponding to the second wind wheel 22 may be disposed on any one of two sides of the second wind wheel 22 facing and facing away from the first wind wheel 21.

In an exemplary embodiment, the motor 23 connected to the first wind wheel 21 is disposed on a side of the first wind wheel 21 facing away from the second wind wheel 22, the corresponding bracket 25 is also disposed on a side of the first wind wheel 21 facing away from the second wind wheel 22, and the motor 23 connected to the second wind wheel 22 is disposed on a side of the second wind wheel 22 facing away from the first wind wheel 21, and the corresponding bracket 25 is also disposed on a side of the second wind wheel 22 facing away from the first wind wheel 21.

In another exemplary embodiment, the motor 23 to which the first wind wheel 21 is connected is provided on the side of the first wind wheel 21 facing the second wind wheel 22, the corresponding bracket 25 is also provided on the side of the first wind wheel 21 facing the second wind wheel 22, and the motor 23 to which the second wind wheel 22 is connected is provided on the side of the second wind wheel 22 facing the first wind wheel 21, and the corresponding bracket 25 is also provided on the side of the second wind wheel 22 facing the first wind wheel 21.

It should be noted that, in the embodiment of the present application, the first wind wheel 21 and the second wind wheel 22 are preferably driven by the same motor 23, that is, the first wind wheel 21 and the second wind wheel 22 share the same motor 23.

In an embodiment, the larger the distance between the support 25 and the first wind wheel 21 and the second wind wheel 22, the more the influence of the support 25 on the first wind wheel 21 and the second wind wheel 22 can be avoided, and the influence of the support 25 on the flow condition of the air flow generated by the first wind wheel 21 and the second wind wheel 22 can be avoided as much as possible.

Specifically, the distance between the bracket 25 and the first wind wheel 21 and the distance between the bracket 25 and the second wind wheel 22 are both greater than or equal to the first distance threshold. That is, when the bracket 25 is disposed on a side of the first wind wheel 21 facing away from the second wind wheel 22, the distance between the bracket 25 and the first wind wheel 21 is greater than or equal to the first distance threshold; when the bracket 25 is arranged on one side of the second wind wheel 22 facing away from the first wind wheel 21, the distance between the bracket 25 and the second wind wheel 22 is larger than or equal to a first distance threshold; when the bracket 25 is disposed between the first wind wheel 21 and the second wind wheel 22, the distance between the bracket 25 and the first wind wheel 21 and the distance between the bracket 25 and the second wind wheel 22 are both greater than or equal to the first distance threshold.

By the above mode, the bracket 25 has enough distance with the first wind wheel 21 and the second wind wheel 22, so that the interference of the bracket 25 on the flow condition of the air flow generated by the first wind wheel 21 and the second wind wheel 22 can be avoided as much as possible, the influence of the bracket 25 on the first wind wheel 21 and the second wind wheel 22 is avoided, and further the performance of the first wind wheel 21 and the second wind wheel 22 can be well guaranteed.

Further, the first distance threshold is preferably 15mm or the like. In this way, the interference of the bracket 25 to the flow conditions of the air flows generated by the first wind wheel 21 and the second wind wheel 22 can be avoided to the maximum extent, and further the full play of the performances of the first wind wheel 21 and the second wind wheel 22 can be ensured to the maximum extent.

In an embodiment, the portions of the first wind wheel 21 and the second wind wheel 22 closest to the support 25 are the tip portions of both. Specifically, the distance between the stand 25 and the tip of the blade of the first wind wheel 21 and the distance between the stand 25 and the tip of the blade of the second wind wheel 22 are both greater than or equal to the second distance threshold. Wherein the second distance threshold is greater than the first distance threshold.

By the above mode, the bracket 25 is further provided with enough distance from the first wind wheel 21 and the second wind wheel 22, so that the interference of the bracket 25 on the flow condition of the air flow generated by the first wind wheel 21 and the second wind wheel 22 is further avoided, the influence of the bracket 25 on the first wind wheel 21 and the second wind wheel 22 is avoided, and the performance of the first wind wheel 21 and the second wind wheel 22 is further ensured to be well exerted.

Further, the second distance threshold is preferably 20mm or the like. In this way, the interference of the bracket 25 to the flow conditions of the air flows generated by the first wind wheel 21 and the second wind wheel 22 can be avoided to the maximum extent, and further the full play of the performances of the first wind wheel 21 and the second wind wheel 22 can be ensured to the maximum extent.

In an embodiment, referring to fig. 2 and 3, a mesh enclosure 26 is disposed on a side of the second wind wheel 22 facing away from the first wind wheel 21, i.e. the mesh enclosure 26 is disposed on the wind outlet side. And, the distance between the second wind wheel 22 and the mesh enclosure 26 is greater than or equal to the third distance threshold. In this way, a sufficient distance is provided between the second wind wheel 22 and the mesh enclosure 26, so that the interference of the mesh enclosure 26 on the flow conditions of the air flows generated by the first wind wheel 21 and the second wind wheel 22 can be avoided as much as possible, the influence of the mesh enclosure 26 on the first wind wheel 21 and the second wind wheel 22 is avoided, and further the performance of the first wind wheel 21 and the second wind wheel 22 can be ensured to be well exerted.

Further, the third distance threshold is preferably 20mm or the like. In this way, the interference of the mesh enclosure 26 to the flow conditions of the air flows generated by the first wind wheel 21 and the second wind wheel 22 can be avoided to the maximum extent, and further the full play of the performances of the first wind wheel 21 and the second wind wheel 22 can be ensured to the maximum extent.

Multiple groups of fan devices are coaxially arranged

Referring to fig. 20, fig. 20 is a schematic structural diagram of a fifth embodiment of a fan apparatus according to the present application.

In one embodiment, the outdoor unit of the air conditioner includes at least two fan units 20, and each fan unit 20 is coaxially disposed, that is, central axes of the fan units 20 are coincident with each other. Further, each fan apparatus 20 may include a first wind wheel 21 and a second wind wheel 22 spaced along a respective central axis as in the previous embodiments.

Through the above mode, at least two fan units 20 are overlapped on the same axial direction, so that the air quantity and the air outlet efficiency of the air conditioner outdoor unit can be effectively improved, the heat exchange efficiency of the air conditioner outdoor unit can be further effectively improved, the air pressure can be greatly increased, and the high static pressure requirement of special occasions can be met.

Further, the diameters of the first wind wheel 21 and the second wind wheel 22 of each fan device 20 are equal. Specifically, the diameters of the first wind wheels 21 of the same fan device 20 are equal to the diameters of the second wind wheels 22, the diameters of the first wind wheels 21 of different fan devices 20 are equal, and the diameters of the second wind wheels 22 of different fan devices 20 are equal. In this way, the wind wheels of each fan device 20 are arranged with the same diameter, so that the optimal fan efficiency can be ensured.

For example, with continued reference to fig. 20, the at least two fan units 20 include a first fan unit 201 and a second fan unit 202, and the first fan unit 201 and the second fan unit 202 include a first wind wheel 21 and a second wind wheel 22, respectively. Specifically, the diameters of the first wind wheel 21 and the second wind wheel 22 of the first fan device 201 and the second fan device 202 are equal, the diameters of the first wind wheel hub 211 and the second wind wheel hub 221 of the first fan device 201 and the second fan device 202 are equal, the rotation directions of the first wind wheel 21 and the second wind wheel 22 of the first fan device 201 are opposite, the rotation directions of the first wind wheel 21 and the second wind wheel 22 of the second fan device 202 are opposite, and the rotation directions of the first wind wheel 21 of the first fan device 201 and the second wind wheel 202 are the same or opposite.

In addition, the first fan device 201 and the second fan device 202 may share a nacelle 24, that is, the first wind wheel 21 and the second wind wheel 22 of the first fan device 201 and the second fan device 202 are both disposed in the same nacelle 24.

Multiple fan units arranged in a coplanar manner

Referring to fig. 21 to 23, fig. 21 is a schematic structural view of another embodiment of an outdoor unit of an air conditioner according to the present invention, fig. 22 is a schematic structural view of a cross section of the outdoor unit of an air conditioner in A-A direction shown in fig. 21, and fig. 23 is a schematic structural view of a cross section of the outdoor unit of an air conditioner in a B-B direction shown in fig. 21.

In one embodiment, the outdoor unit of the air conditioner includes at least two fan units 20, and the central axes of the fan units 20 are parallel to each other and do not coincide with each other. Further, the fan units 20 are on the same plane. Further, each fan unit 20 may include a first wind wheel 21 and a second wind wheel 22 spaced along the respective central axes as in the above embodiments.

In this embodiment, the central axes of the fan devices 20 are parallel to each other and do not overlap, and each fan device 20 is disposed corresponding to a different portion of the heat exchanger 30, so as to generate an air flow passing through a portion of each corresponding heat exchanger 30, thereby implementing heat exchange of a portion of each corresponding heat exchanger 30.

The air volume of each fan device 20 is matched with the heat exchange area of the corresponding heat exchanger 30 (for the fin type heat exchanger 30, the heat exchange area is the sum of the surface areas of the heat exchange tube and the heat exchange fin), so that the heat exchange efficiency of the air conditioner outdoor unit is ensured as much as possible. Specifically, the diameter of the first wind wheel 21 of each fan device 20 (D in fig. 22 ₁ As shown, below) and the diameter of the second rotor 22 (as shown at D in fig. 22) ₂ As shown, the following is true) is positively correlated with the heat exchange area of the respective corresponding heat exchanger 30 portion. That is, the larger the heat exchange area of the portion of each fan unit 20 corresponding to the heat exchanger 30, the larger the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 of each fan unit 20.

Further, the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 of each fan device 20 are in direct proportion to the heat exchange area of the corresponding heat exchanger 30. In this way, the air volume of each fan device 20 can be maximally ensured to match the heat exchange area of the corresponding heat exchanger 30, so that the heat exchange efficiency of the air conditioner outdoor unit can be maximally ensured.

In an embodiment, the at least two sets of fan units 20 include a first fan unit 201 and a second fan unit 202, and the first fan unit 201 and the second fan unit 202 include a first wind wheel 21 and a second wind wheel 22, respectively, as shown in fig. 22. The heat exchange area of the portion of the heat exchanger 30 corresponding to the first fan device 201 is larger than the heat exchange area of the portion of the heat exchanger 30 corresponding to the second fan device 202, and the sum of the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 of the first fan device 201 is larger than the sum of the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 of the second fan device 202.

In this way, the heat exchange area of the portion of the first fan device 201 corresponding to the heat exchanger 30 is larger, which means that the air volume required by the first fan device 201 is larger, so that the sum of the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 is larger, and the heat exchange area of the portion of the corresponding heat exchanger 30 is matched; the smaller heat exchange area of the portion of the second fan device 202 corresponding to the heat exchanger 30 means that the air volume required by the second fan device 202 is smaller, so that the sum of the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 is smaller, and the heat exchange area of the portion of the second fan device 202 corresponding to the heat exchanger 30 is also matched.

For example, as shown in fig. 22 and 23, the heat exchanger 30 is a G-type heat exchanger 30, the portion of the heat exchanger 30 corresponding to the first fan device 201 has three air inlet surfaces 31, and the portion of the heat exchanger 30 corresponding to the second fan device 202 has only two air inlet surfaces 31, so that the heat exchange area of the portion of the heat exchanger 30 corresponding to the first fan device 201 is larger than the heat exchange area of the portion of the heat exchanger 30 corresponding to the second fan device 202, i.e. the air volume required by the first fan device 201 is larger than the air volume required by the second fan device 202. At this time, the first fan device 201 employs the first wind wheel 21 and the second wind wheel 22 having larger diameters, and the second fan device 202 employs the first wind wheel 21 and the second wind wheel 22 having smaller diameters.

The above-mentioned case where the sum of the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 of the first fan device 201 is larger than the sum of the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 of the second fan device 202 specifically includes the following cases:

in an embodiment, the diameter of the first wind wheel 21 of the first fan device 201 is larger than the diameter of the first wind wheel 21 of the second fan device 202, and the diameter of the second wind wheel 22 of the first fan device 201 is larger than the diameter of the second wind wheel 22 of the second fan device 202.

In an alternative embodiment, the diameter of the first wind wheel 21 of the first fan unit 201 is larger than the diameter of the first wind wheel 21 of the second fan unit 202, and the diameter of the second wind wheel 22 of the first fan unit 201 is smaller than the diameter of the second wind wheel 22 of the second fan unit 202.

In another alternative embodiment, the diameter of the first wind wheel 21 of the first fan unit 201 is smaller than the diameter of the first wind wheel 21 of the second fan unit 202, and the diameter of the second wind wheel 22 of the first fan unit 201 is larger than the diameter of the second wind wheel 22 of the second fan unit 202.

In an embodiment, with continued reference to fig. 22, the at least two sets of fan units 20 include a first fan unit 201 and a second fan unit 202, where the first fan unit 201 and the second fan unit 202 include a first wind wheel 21 and a second wind wheel 22, respectively. The heat exchange area of the portion of the heat exchanger 30 corresponding to the first fan device 201 is equal to the heat exchange area of the portion of the heat exchanger 30 corresponding to the second fan device 202, the diameter of the first wind wheel 21 of the first fan device 201 is equal to the diameter of the first wind wheel 21 of the second fan device 202, and the diameter of the second wind wheel 22 of the first fan device 201 is equal to the diameter of the second wind wheel 22 of the second fan device 202.

In this embodiment, the central axes of at least two sets of fan units 20 are parallel to each other and do not overlap, and each fan unit 20 includes a first wind wheel 21 and a second wind wheel 22 disposed at intervals along the respective central axes. Compared with the situation that the single-stage wind wheels are arranged in a coplanar manner, the embodiment has higher fan efficiency, larger wind pressure and wind quantity, and the low-frequency beat noise generated by coupling when the single-stage wind wheels are arranged in a coplanar manner can be avoided between at least two groups of fan devices 20 in the embodiment, so that the embodiment has smaller noise.

It should be noted that "pitch", "distance", and the like referred to in the embodiments of the present application preferably refer to a minimum pitch, a minimum distance in an axial direction between different elements, portions.

In addition, in the present application, unless explicitly stated and limited otherwise, the terms "connected," "stacked," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art as the case may be.

Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present application, and not for limiting the same; although the present application has been described in detail with reference to the foregoing embodiments, it should be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the corresponding technical solutions from the scope of the technical solutions of the embodiments of the present application.

Claims

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

a housing having a vent hole,

the fan device is arranged in the shell, the heat exchanger is arranged in the shell, the fan device is positioned above the heat exchanger, and the fan device is used for guiding external air flow to enter the shell through the vent hole and pass through the heat exchanger to exchange heat;

one side of the fan device, which is close to the heat exchanger, is defined as an air inlet side, one side of the fan device, which is far away from the heat exchanger, is defined as an air outlet side, and air flow which is driven by the fan device to pass through the heat exchanger flows out of the air outlet side from the air inlet side, wherein the fan device comprises:

The wind power generation device comprises a first wind wheel and a second wind wheel, wherein the first wind wheel and the second wind wheel are axially arranged at intervals, one side of the first wind wheel, which faces away from the second wind wheel, is the air inlet side, one side of the second wind wheel, which faces away from the first wind wheel, is the air outlet side, the rotation directions of the first wind wheel and the second wind wheel are opposite, the bending directions of blades of the first wind wheel and the bending directions of blades of the second wind wheel are also opposite, and the number of blades of the first wind wheel and the number of blades of the second wind wheel are prime numbers;

the support is arranged on the shell and positioned at least one of the air inlet side, the air outlet side and between the first wind wheel and the second wind wheel, and the distance between the support and the first wind wheel and the distance between the support and the second wind wheel are both larger than or equal to a first distance threshold.

2. The outdoor unit of claim 1, wherein a difference between the number of blades of the first rotor and the number of blades of the second rotor is 2.

3. The outdoor unit of claim 1, wherein the number of blades of the second rotor is less than the number of blades of the first rotor.

4. The outdoor unit of claim 1, wherein the number of blades n1 of the first rotor and the number of blades n2 of the second rotor have the following relationship:

|h*n1-s*n2|≥2,h,s∈(1,2,3)。

5. the outdoor unit of claim 1, wherein the diameter of the first wind wheel is greater than the diameter of the second wind wheel.

6. The outdoor unit of claim 5, wherein the diameter D1 of the first wind wheel and the diameter D2 of the second wind wheel have the following relationship:

1.01D2≤D1≤1.03D2。

7. the outdoor unit of claim 1, wherein the first wind wheel is spaced from the second wind wheel by a distance greater than or equal to 20mm.

8. The outdoor unit of any one of claims 1-7, wherein the fan assembly further comprises a pod comprising a main body portion that is disposed around the first wind wheel and the second wind wheel.

9. The outdoor unit of claim 8, wherein a distance S1 between an end of the first wind wheel on the air intake side and an end of the main body on the air intake side has a relationship with a length H1 of the first wind wheel in an axial direction as follows:

0.4≤S1/H1≤0.7。

10. The outdoor unit of claim 9, wherein s1/h1=0.55.

11. The outdoor unit of claim 8, wherein a distance S2 between an end of the second wind wheel facing away from the first wind wheel and an end of the main body portion facing away from the first wind wheel has the following relationship with a length H2 of the second wind wheel in an axial direction:

0≤S2/H2≤0.25。

12. the outdoor unit of claim 11, wherein S2/h2=0.

13. The outdoor unit of claim 8, wherein the diameter D1 of the first wind wheel and the inner diameter D3 of the main body have the following relationship:

5mm<(D3-D1)/2<20mm。

14. the outdoor unit of claim 13, wherein (D3-D1)/2=10 mm.

15. The outdoor unit of claim 8, wherein the diameter D1 of the first wind wheel and the inner diameter D3 of the main body have the following relationship:

0.008D1≤D3-D1≤0.016D1。

16. the outdoor unit of claim 8, wherein the housing has a mounting base, and wherein the pod is mounted to the mounting base;

the length H3 of the air guide sleeve and the mounting seat in the axial direction of the air guide sleeve and the length H4 of the first wind wheel and the second wind wheel in the axial direction have the following relation:

0.68H3≤H4≤0.75H3。

17. The outdoor unit of claim 8, wherein the casing further comprises a tapered portion provided at one end of the main body portion near the first wind wheel, the tapered portion having a cross-sectional area gradually decreasing in a direction approaching the main body portion at each position in an axial direction thereof;

the length H1 of the first wind wheel in the axial direction and the length H5 of the tapered portion in the axial direction have the following relationship:

0.25H1≤H5≤0.4H1。

18. the outdoor unit of claim 8, wherein the length H6 of the main body in the axial direction and the length H7 of the cover in the axial direction have the following relationship:

0.75H7≤H6≤0.8H7。

19. the outdoor unit of any one of claims 1 to 7, wherein said fan units comprise at least two groups, and wherein the central axes of each of said fan units are parallel to each other and do not coincide with each other.