CN213808155U

CN213808155U - Fan device and air condensing units

Info

Publication number: CN213808155U
Application number: CN202022252785.5U
Authority: CN
Inventors: 陈维涛; 李跃飞; 王其桢; 刘乃桐; 余东东
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; Guangdong Midea HVAC Equipment Co Ltd
Priority date: 2020-10-10
Filing date: 2020-10-10
Publication date: 2021-07-27
Anticipated expiration: 2030-10-10

Abstract

The application relates to the technical field of air conditioners and discloses a fan device and an air conditioner outdoor unit. This fan device includes: the first wind wheel and the second wind wheel are axially arranged at intervals; the first wind wheel and the second wind wheel are respectively provided with a plurality of 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. Through the mode, the noise can be reduced.

Description

Fan device and air condensing units

Technical Field

The application relates to the technical field of air conditioners, in particular to a fan device and an air conditioner outdoor unit.

Background

Air conditioners, i.e., Air conditioners (Air conditioners), generally refer to devices that manually adjust and control parameters such as temperature and humidity of ambient Air inside a building or structure. An air conditioning system generally comprises an indoor unit and an outdoor unit, and the indoor unit and the outdoor unit cooperate to adjust and control parameters of ambient air, such as temperature, humidity and the like.

However, the conventional fan device applied to the outdoor unit of the air conditioner generates a serious beat noise when the wind wheel of the fan device operates, and also has a serious harmonic noise.

Content of application

In view of this, the present disclosure provides a fan device and an outdoor unit of an air conditioner, which can reduce noise.

In order to solve the technical problem, the application adopts a technical scheme that: a fan apparatus is provided. This fan device includes: the first wind wheel and the second wind wheel are axially arranged at intervals; the first wind wheel and the second wind wheel are respectively provided with a plurality of 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.

In an embodiment of the 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 diameter of the first wind turbine and the diameter of the second wind turbine are both greater than or equal to a first threshold value, and the greater of the number of blades of the first wind turbine and the number of blades of the second wind turbine is greater than or equal to a second threshold value; or the diameter of the first wind wheel and the diameter of the second wind wheel are both smaller than a first threshold value, and the larger value of the number of the blades of the first wind wheel and the number of the blades of the second wind wheel is smaller than or equal to a third threshold value; wherein the second threshold is greater than the third threshold.

In an embodiment of the present application, the first threshold value ranges from 450mm to 800mm, the second threshold value is 9, and the third threshold value is 7.

In an embodiment of this application, one side that first wind wheel deviates from the second wind wheel is the air inlet side, and one side that the second wind wheel deviates from first wind wheel is the air outlet side, and the blade quantity of first wind wheel is greater than the blade quantity of second wind wheel.

In an embodiment of the application, one side of the first wind wheel departing from the second wind wheel is an air inlet side, one side of the second wind wheel departing from the first wind wheel is an air outlet side, and the number n of the blades of the first wind wheel is₁The number n of blades of the second wind wheel₂Has the following relationship: | h x n₁-s*n₂|≥2，h,s∈(1,2,3)。

In one embodiment of the present application, the number of blades of the first rotor and the number of blades of the second rotor are positively correlated with the respective diameters.

In one embodiment of the present application, the number of blades of the first rotor and the number of blades of the second rotor are both 5 to 15.

In an embodiment of the application, the direction of rotation of the first rotor and the direction of rotation of the second rotor are the same or opposite.

In an embodiment of the application, the fan device further includes a guide vane, the guide vane has a plurality of blades, and the guide vane is axially spaced from the first wind wheel and the second wind wheel respectively.

In an embodiment of the present application, the number of blades of the first wind turbine, the number of blades of the second wind turbine, and the number of blades of the guide vane are prime numbers to each other.

In an embodiment of the present application, the number of blades n of the first wind wheel₁The number n of blades of the second wind wheel₂Number n of vanes₃Has the following relationship: n is₁≤n₂、n₂≤n₃≤2n₁Or n is₂≤n₁、n₁≤n₃≤2n₂。

In an embodiment of the present application, the number of blades of the guide vane is 6 to 17.

In an embodiment of this application, the stator is located one side that first wind wheel deviates from the second wind wheel, and the blade bending direction of stator is opposite with the blade bending direction of first wind wheel, and wherein one side that first wind wheel deviates from the second wind wheel is the air inlet side, and one side that the second wind wheel deviates from first wind wheel is the air-out side.

In an embodiment of this application, the stator is located one side that the second wind wheel deviates from first wind wheel, and the blade bending direction of stator is opposite with the blade bending direction of second wind wheel, and wherein one side that first wind wheel deviates from the second wind wheel is the air inlet side, and one side that the second wind wheel deviates from first wind wheel is the air-out side.

In order to solve the above technical problem, the present application adopts another technical solution: provided is an outdoor unit of an air conditioner. The outdoor unit of the air conditioner includes a heat exchanger and a fan unit as set forth in the above embodiments for guiding an air flow through the heat exchanger.

The beneficial effect of this application is: be different from prior art, this application provides a fan device and air condensing units. The fan device comprises a first wind wheel and a second wind wheel which are axially arranged at intervals. 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 mutually. Therefore, the risk that the first wind wheel and the second wind wheel generate beat vibration noise in the operation process can be reduced, and meanwhile, partial harmonic noise can be reduced or eliminated, so that the noise generated by the fan device in the working process can be reduced.

Drawings

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

Fig. 1 is a schematic structural diagram 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 diagram of a first embodiment of a first and second rotor of the present application;

FIG. 5 is a schematic view of an embodiment of a fan assembly of the present application in comparison with a conventional single axial flow wind wheel for achieving different static pressures;

FIG. 6 is a schematic diagram of an embodiment of a fan assembly of the present application compared to a conventional single axial flow wind wheel to achieve different wind rates;

FIG. 7 is a schematic view of an embodiment of the fan assembly of the present application in comparison with a conventional single axial flow wind wheel for achieving noise at different wind volumes;

figure 8 is a schematic structural view of an embodiment of a first wind rotor according to the present application;

figure 9 is a schematic diagram of the structure of an embodiment of a second wind rotor according to the present application;

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

FIG. 11 is a schematic diagram of an embodiment of the present invention comparing the noise level at different frequencies with a conventional single axial flow rotor;

FIG. 12 is a schematic diagram of the construction of a second embodiment of the first and second wind turbines of the present application;

FIG. 13 is a schematic structural view of a first embodiment of a fan assembly according to the present application;

FIG. 14 is a schematic structural view of a second embodiment of a fan assembly according to the present application;

FIG. 15 is a schematic view of an embodiment of the present application showing noise variance at different positions of a first rotor within a nacelle;

FIG. 16 is a schematic view of an embodiment of the present application showing noise variation when a second rotor is in a different position within the nacelle;

FIG. 17 is a schematic view of an embodiment of the present disclosure;

FIG. 18 is a schematic structural view of a third embodiment of a fan assembly according to the present application;

FIG. 19 is a schematic structural view of a fourth embodiment of a fan assembly according to the present application;

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

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

fig. 22 is a schematic sectional view of the outdoor unit of fig. 21 taken along the direction a-a;

fig. 23 is a schematic sectional view of the outdoor unit of fig. 21 taken along the direction B-B.

Detailed Description

In order to make the objects, technical solutions and advantages of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the embodiments of the present application, and it is obvious that the described embodiments are some but not all of the embodiments of the present application. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application. The embodiments described below and the features of the embodiments can be combined with each other without conflict.

Whole machine structure

Air conditioners, i.e., Air conditioners (Air conditioners), generally refer to devices that manually adjust and control parameters such as temperature and humidity of ambient Air inside a building or structure. An air conditioning system generally comprises an indoor unit and an outdoor unit, wherein the indoor unit and the outdoor unit are matched to adjust and control parameters such as temperature and humidity of ambient air, and the specific adjustment and control mechanism belongs to the understanding scope of the technicians in the field, and is not described herein again. The embodiment of the application mainly aims at the air conditioner outdoor unit for explanation.

Referring to fig. 1 to 3, fig. 1 is a schematic structural view of an air conditioner outdoor unit according to an embodiment of the present invention, fig. 2 is a schematic structural view of an explosion structure of the air conditioner outdoor unit shown in fig. 1, and fig. 3 is a schematic structural view of a cross section of the air conditioner outdoor unit shown in fig. 1.

In one embodiment, the outdoor unit of an air conditioner includes a casing 10. The casing 10 serves as a basic component of the outdoor unit, and plays a role of supporting and protecting other components of the outdoor unit.

The outdoor unit of the air conditioner further includes a fan unit 20 and a heat exchanger 30, the heat exchanger 30 is disposed in the casing 10, and the fan unit 20 is installed in the casing 10. The shell 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 shell 10 through the vent hole 11 and to exchange heat through the heat exchanger 30.

In an embodiment, the fan device 20 may be an axial fan or the like, i.e. for guiding the air flow along the axial direction of the fan device 20. Axial flow fans are widely used in home and abroad household appliances, such as air conditioners, refrigerators, electric fans, microwave ovens, and the like. The efficiency, air quantity and noise of the fan are the main performance indexes. The high efficiency and low noise of axial flow fans have been the main research direction in the industry.

Specifically, the fan device 20 includes a plurality of axially spaced wind wheels, i.e., the plurality of wind wheels are coaxially disposed, as shown in fig. 2 and 3. The plurality of wind wheels of the fan device 20 are driven to rotate around respective axial directions, so that air in the surrounding environment is driven to flow to form an air flow, and specifically, the external air flow is guided to enter the shell 10 through the ventilation hole 11 and passes through the heat exchanger 30 for heat exchange.

Further, the axial flow fan device 20 may include two axially spaced apart 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, i.e. their central axes coincide. 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 also opposite to the bending direction of the blades of the second wind wheel 22, so that the rotation direction of the airflow generated by the first wind wheel 21 is opposite to the rotation direction of the airflow generated by the second wind wheel 22 (but the flow direction of the airflow generated by the first wind wheel 21 is the same as the flow direction of the airflow generated by the second wind wheel 22), and the rotation directions can mutually offset the circumferential rotation speed components of the airflow generated by the opposite side, so that the airflow flows along the axial direction of the fan device 20 as far as possible, and further the airflow flowing along the axial direction of the fan device 20, namely the axial airflow, is formed in a matching manner.

For example, as shown in FIG. 4, the leading edge profile δ of the blades (to be explained in detail below) of the first wind wheel 21₁And leading edge profile δ of the blades of the second rotor 22₂The orthographic projection of the leading edge profile is approximately in linear symmetry, wherein the orthographic projection of the leading edge profile is a vertical 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 leading edge profile delta of the blades of the first rotor 21₁And leading edge profile δ of the blades of the second rotor 22₂The intersection point of the orthographic projection and the axis point. Trailing edge profile λ of the blades of the first wind wheel 21₁The blade begins to bend in the opposite direction at 75-95% of the radius along the blade span direction, and the trailing edge profile line lambda of the blade of the second wind wheel 22₂And the blades start to bend in opposite directions at 75-95% of the radius along the blade extension direction, and arc-shaped gaps beta are formed, so that the blade efficiency is improved, and the interference noise between the first wind wheel 21 and the second wind wheel 22 is reduced. Leading edge profile δ of the blades of the first rotor 21₁With the profile δ of the leading edge of the blades of the second rotor 22₂Respectively form two tangent lines gamma, and the two tangent lines gamma are respectively connected with the respective leading edge molded lines (delta)₁、δ₂) The tangent lines are tangent, the included angle theta of the two tangent lines gamma is gradually increased along the blade span direction theta, theta is larger than or equal to 60 degrees from the position of 0.6 time of the radius of the blade, and theta close to the outermost edge blade tip position is 90 degrees.

Because the axial flow fan provides air volume circulation for the air conditioner outdoor unit to realize heat exchange, the air volume is closely related to the performance of the air conditioner outdoor unit. However, the problem of noise increase is faced with increasing the air volume, and the aerodynamic noise of the axial flow fan is still one of the main noise sources of the outdoor unit of the air conditioner, and mainly comprises the rotation noise caused by the rotation of the blades and the vortex noise. The improvement of the structure of the axial flow fan is needed to reduce the working noise of the outdoor unit of the air conditioner while ensuring the air volume.

The existing air-conditioning outdoor unit adopting a single axial flow wind wheel is particularly an air-conditioning outdoor unit in a top air outlet mode. The air outlet flow of the single axial flow wind wheel has a large part of rotation speed component along the circumferential direction, and the static pressure efficiency is low. In addition, the existing air conditioner outdoor unit adopts a fan system with a single axial flow wind wheel, so that the pressure resistance is poor, and the generated wind pressure is low. When the air conditioning system is in a heating condition, frost is easily formed on a heat exchanger of the air conditioning outdoor unit to block the heat exchanger, so that the air supply resistance of the air conditioning outdoor unit is increased, the air volume attenuation is large, and the performance of the air conditioning system is affected.

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

The performance of the fan device composed of the first wind wheel and the second wind wheel in the embodiment of the application is compared with the performance of the traditional single axial flow wind wheel as follows:

fig. 5 shows a comparison of static pressures of the fan device according to the embodiment of the present application and a conventional single axial flow wind wheel when different wind volumes are achieved. It can be seen that the static pressure of the fan device in the embodiment of the present application is obviously higher than that of the traditional single axial flow wind wheel when the same air volume is achieved, which means that the fan device in the embodiment of the present application has lower noise when the same air volume is achieved.

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 wheel when different wind volumes are achieved. It can be seen that, under the condition of achieving the same air volume, the power of the fan device in the embodiment of the application is lower, which means that the power required to be input by the fan device in the embodiment of the application is lower, and the operation cost of heat exchange is favorably reduced, and meanwhile, the noise generated by the operation of the fan device in the embodiment of the application is also lower.

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

In an embodiment, please refer to fig. 3, a side of the first wind wheel 21 away from the second wind wheel 22 is an air inlet side, a side of the second wind wheel 22 away from the first wind wheel 21 is an air outlet side, and the air flow generated by the rotation of the first wind wheel 21 and the second wind wheel 22 passes through the first wind wheel 21 and the second wind wheel 22 from the air inlet side and is then output from the air outlet side.

In one embodiment, with continued reference to fig. 2 and 3, the fan device 20 further includes a driving assembly. Each wind wheel (including the first wind wheel 21 and the second wind wheel 22, etc.) of the fan device 20 is connected to the driving assembly, so that each wind wheel of the fan device 20 is driven to rotate by the driving assembly, and the airflow is guided to pass through the heat exchanger 30 for heat exchange.

Specifically, the driving assembly may include a motor 23 and the like. Moreover, 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, for the case that the fan 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 coaxially disposed transmission shafts, the two transmission shafts can rotate around respective central axes in opposite directions, and the rotation speeds of the two transmission shafts can also be set differently (the specific working principle belongs to the understanding range of those skilled in the art, and is not described herein again), as shown in fig. 2 and fig. 3. In this way, the first wind wheel 21 and the second wind wheel 22 are respectively in transmission connection with different transmission shafts, so that the first wind wheel 21 and the second wind wheel 22 can be driven to rotate in opposite directions by one motor 23, and the difference setting of the rotating speed of the first wind wheel 21 and the rotating speed of the second wind wheel 22 can also be realized.

Of course, in other embodiments of the present application, the driving assembly may also include a plurality of motors 23, and each wind wheel of the fan device 20 is in transmission connection with a different motor 23, so as to be driven by the different motors 23 for rotation, which is not limited herein.

Also, the respective rotors (including the first rotor 21 and the second rotor 22, etc.) of the fan apparatus 20 may be turned in the same direction. 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 around respective central shafts, 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 turbine of the present application, and fig. 9 is a schematic structural view of an embodiment of a second wind turbine of the present application.

In an embodiment, first wind rotor 21 includes a first wind rotor hub 211 and a number of first blades 212. First plurality of blades 212 are spaced circumferentially about first rotor hub 211. Specifically, the first wind turbine hub 211 is drivingly connected to a driving assembly (e.g., the motor 23 shown in fig. 2 and 3, etc.) such that the first wind turbine 21 is drivingly connected to the driving assembly, and the driving assembly drives the first wind turbine hub 211 to rotate, thereby rotating the first wind turbine 21, 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 arranged at intervals in the circumferential direction of the second wind turbine hub 221. Specifically, the second wind wheel hub 221 is in transmission connection with the 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 assembly 20 further includes a flow guide 24. The air guide sleeve 24 is sleeved on the periphery of the wind wheel of the fan device 20, for example, the periphery of the first wind wheel 21 and the second wind wheel 22, and plays a role in guiding the airflow generated by the operation of the wind wheel of the fan device 20, so as to guide the airflow to be output, and further generate the airflow flowing through the heat exchanger 30 for heat exchange.

Alternatively, the cross-sectional shape of the pod 24 (i.e., a cross-section taken in 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 oval, etc., i.e., the pod 24 is an oval pod 24. The air guide sleeve 24 in the form of the elliptical air guide sleeve 24 can enable a gap between the wind wheel and the air guide sleeve 24 to be in a non-axial symmetry form, so that blade tip leakage vortex is reduced, and the air guide sleeve 24 in the form of the elliptical air guide sleeve 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 section taken along a radial direction thereof.

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

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

In one embodiment, the air guide sleeve 24 includes a main body portion 241, and the main body portion 241 is sleeved on the outer peripheries of the first wind wheel 21 and the second wind wheel 22. In this case, the cross section (i.e., a section taken along the radial direction, the same applies hereinafter) of the main body portion 241 at each position in the axial direction thereof has the same area. Further, the body portion 241 takes the form of a straight cylinder.

Further, the nacelle 24 further includes a tapered portion 242 provided at an end of the main body portion 241 close to the first wind wheel 21, and a cross-sectional area of the tapered portion 242 at each position in the axial direction thereof is gradually reduced in a direction close to the main body portion 241. The nacelle 24 further includes a divergent portion 243 provided at an end of the main body portion 241 close to the second rotor 22, and a cross-sectional area of the divergent portion 243 at each position in the axial direction thereof is gradually reduced in a direction close to the main body portion 241.

That is, the tapered portion 242 and the diverging portion 243 are located at 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 be gradually reduced in a direction approaching the main body portion 241. Further, the central axes of the main body 241, the tapered portion 242, and the tapered portion 243 are overlapped.

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

In one embodiment, with continued reference to fig. 2 and 3, the fan device 20 further includes a bracket 25, and the bracket 25 is used for mounting and fixing a driving component of the fan device 20. The bracket 25 is fixed to the casing 10 of the outdoor unit (for example, to the mounting base 12 in the above embodiment), so as to fix the relative positions of the wind wheel and the driving assembly in the casing 10.

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

In an embodiment, please refer to fig. 2 and fig. 3, the fan device 20 further includes a mesh enclosure 26, the mesh enclosure 26 is disposed on the air outlet side, that is, the mesh enclosure 26 is disposed on a side of the second wind wheel 22 away from the first wind wheel 21. The mesh enclosure 26 allows the airflow generated by the first wind wheel 21 and the second wind wheel 22 to pass through, and can also play a certain shielding role, so that foreign matters are prevented from falling into the fan device 20 from the air outlet side to influence the normal work of the fan device 20.

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 from a hot fluid to a cold fluid, also referred to as a heat exchanger. In this embodiment, the heat exchanger 30 exchanges heat with the gas passing through the heat exchanger 30, and the blower device 20 operates to form a gas flow passing through the heat exchanger 30 at a faster rate, 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 are provided with larger surfaces to be in contact with the outside air, so that a larger heat exchange area is provided, and the heat exchange efficiency can be improved. The material of the heat exchange tube and the heat exchange fin is preferably a material having good heat conductivity, such as metal copper, and is not limited herein.

Optionally, the fin-type heat exchanger 30 (i.e., the heat exchanger 30 composed of the heat exchange tubes and the heat exchange fins) may be divided into air intake forms such as single-sided air intake, two-sided air intake, three-sided air intake, and four-sided air intake according to the air intake surface 31.

Specifically, for the outdoor unit of the air conditioner having four sides 13, the casing 10 of the outdoor unit of the air conditioner surrounds 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 intake forms of the heat exchanger 30 correspond to the number of the air intake surfaces 31 of the heat exchanger 30.

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

In one embodiment, with continued reference to fig. 2 and 3, the fan apparatus 20 further includes a guide vane 27, the guide vane 27 being axially spaced from the first and

second wind wheels

21 and 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, for example, when the guide vane 27 is arranged on the air inlet side, the guide vane 27 is used for providing prerotation for the incoming flow of the first wind wheel 21, that is, providing prerotation airflow, so as to rectify the complex incoming flow, so as to reduce energy loss and improve air volume; when the guide vane 27 is disposed on the air outlet side, the guide vane 27 is used for recovering the rotational speed component of the airflow passing through the second wind wheel 22, so that the airflow 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 explained in detail below.

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

It can be understood that the air-conditioning outdoor unit of the embodiment of the present application can 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 enables the multi-connected air-conditioning system of the air-conditioning outdoor unit of the embodiment of the present application to have a stronger pressure resistance, and can effectively solve the problem of high outdoor pressure drop during the installation process of the multi-connected air-conditioning system, which is not limited herein.

Blade number relationship of first wind wheel and second wind wheel

With continued reference to fig. 2 and 3, the fan device 20 of the above embodiment including the first wind wheel 21 and the second wind wheel 22 will be described as an example.

In one embodiment, the number of blades of the first rotor 21 and the number of blades of the second rotor 22 are prime numbers to each other. Therefore, beat vibration noise generated when the first wind wheel 21 and the second wind wheel 22 operate can be reduced, and part of harmonic noise can be reduced or eliminated, so as to further reduce noise.

Referring to fig. 11, fig. 11 shows a comparison of noise levels of the fan device 20 of the present embodiment and a conventional single axial flow wind wheel under different frequencies. It can be seen that the fan apparatus 20 of the present embodiment has less noise at the same frequency. The reason is that the air flow generates obvious noise when passing through the traditional single axial flow wind wheel, and the number of the blades of the first wind wheel 21 and the number of the blades of the second wind wheel 22 are reasonably matched, so that the noise can be effectively reduced.

In one embodiment, the firstThe difference between the number of blades of the rotor 21 and the number of blades of the second rotor 22 is 2. In particular, the number n of blades of the first wind wheel 21₁Number n of blades of second wind wheel 22₂Has the following relationship: n is₁＞n₂、n₁＝n₂+2, or n₁＜n₂、n₂＝n₁+2。

According to the basic theoretical analysis of aerodynamic noise and the practical engineering experience, when the number of blades of the adjacent wind wheels (i.e., the first wind wheel 21 and the second wind wheel 22) which are axially connected in series satisfies the above relationship, the noise value generated by the mutual interference between the two wind wheels is low, which is beneficial to reducing the aerodynamic noise of the fan device 20.

Particularly, the wake of the first wind wheel 21 acts on the leading edge of the second wind wheel 22 (the edge close to the first wind wheel 21) to generate noise, so that the noise caused by the second wind wheel 22 is greater than the noise caused by the first wind wheel 21, and the number of the blades of the second wind wheel 22 is ensured to be less than that of the blades of the first wind wheel 21 in design, which is beneficial to reducing the noise caused by the second wind wheel 22, and is further beneficial to reducing the overall noise of the fan device 20.

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

For example, the value range of the first threshold is 450mm to 800mm, preferably 600mm, and the like; the second threshold is preferably 9, etc.; the third threshold value 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 greater than or equal to 600mm, n₁＝9、n₂7 or n₁＝7、n₂9, 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, n₁＝7、n₂5 or n₁＝5、n₂7, etc.

Through the mode, the problem that when the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 are small and the number of the blades of the first wind wheel 21 and the number of the blades of the second wind wheel 22 are large, the consistency of the first wind wheel 21 and the second wind wheel 22 is too large, and the performance of the first wind wheel 21 and the performance of the second wind wheel 22 are reduced can be avoided, and meanwhile, the problem that when the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 are large and the number of the blades of the first wind wheel 21 and the number of the blades of the second wind wheel 22 are small, the performance of the first wind wheel 21 and the performance of the second wind wheel 22 cannot be fully exerted can be avoided.

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

It should be noted that 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 the first wind wheel and the second wind wheel satisfies the above relationship.

In one embodiment, tip leakage vortices are one of the main sources of aerodynamic noise of the rotor, meaning that the second rotor 22 is the main source of noise, considering the presence of tip leakage vortices (i.e., vortices generated outside the tip of the second rotor 22) of the second rotor 22. Therefore, the number of blades of the first wind wheel 21 is preferably larger than that of the second wind wheel 22 on the premise of ensuring the performance of the fan device 20. Therefore, the number of the blades of the second wind wheel 22 is small, 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 air volume, air outlet efficiency and the like) of the fan device 20, the number of the blades of the first wind wheel 21 is large, so that the performance of the fan device 20 can meet the requirements.

In an alternative embodiment, the number of blades n of the first wind wheel 21₁Number n of blades of second wind wheel 22₂Has the following relationship: | h x n₁-s*n₂And | ≧ 2, h, s ∈ (1,2, 3). Thus, can protectThe noise caused by the mutual interference of the first wind wheel 21 and the second wind wheel 22 is guaranteed to be maintained at the lowest level, and the beat vibration phenomenon can be avoided as much as possible.

In one embodiment, the number of blades of the first wind rotor 21 and the number of blades of the second wind rotor 22 are positively correlated with the respective diameters. Specifically, the larger the diameter of the first wind rotor 21 is, the larger the number of blades of the first wind rotor 21 is, and the larger the diameter of the second wind rotor 22 is, the larger the number of blades of the second wind rotor 22 is.

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

Diameter relationship of first and second rotors

The fan device 20 in the above embodiment is explained as including the first wind wheel 21 and the second wind wheel 22.

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

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

The tip leakage vortex is one of the main sources of aerodynamic noise of the wind wheel, and considering the existence of the tip leakage vortex of the second wind wheel 22, 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 the part of the first wind wheel 21, the part of which the wind sweeping area is larger than that of the second wind wheel 22, can apply work to the airflow, eliminate or weaken the tip leakage vortex of the second wind wheel 22, and can further reduce the aerodynamic noise. Specifically, the airflow provided by the portion of the first wind wheel 21 with the wind area larger than that of 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, so as to achieve the noise reduction effect.

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 21₁Diameter D of second wind wheel 22₂Has the following relationship: 1.01D₂≤D₁≤1.03D₂. In this way, the aerodynamic noise can be further reduced.

Of course, if considering the problem of matching the performance of the first rotor 21 and the second rotor 22, the diameter of the first rotor 21 is preferably equal to the diameter of the second rotor 22, as shown in fig. 14. When the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 are set differently, the wind wheel with a smaller diameter is a bottleneck of the performance of the fan device 20, and is limited by the performance of the wind wheel with a smaller diameter, and the performance of the wind wheel with a larger diameter cannot be fully exerted, so that the cost of the fan device 20 is increased, and the burden of the whole system is 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 tip leakage vortex of the second wind wheel 22 cannot be eliminated or weakened by the first wind wheel 21, 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-rotational airflow to 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-rotational airflow to the second wind wheel 22.

Optionally, the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 are both 560mm to 850 mm. In this way, the first wind wheel 21 and the second wind wheel 22 can generate sufficient air volume, so that the outdoor unit of the air conditioner according to the embodiment of the present application can achieve the required heat exchange efficiency.

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

With continued reference to fig. 8 and 9, the fan device 20 of the above embodiment including the first wind wheel 21 and the second wind wheel 22 will be described as an example.

In an embodiment, the diameter D of the first wind wheel 21₁Diameter D of first rotor hub 211₁₁Has the following relationship: 2 is less than or equal to D₁/D₁₁4.5 percent or less, as shown in figure 8. Diameter D of second wind wheel 22₂Diameter D of second rotor hub 221₂₁Has the following relationship: 2 is less than or equal to D₂/D₂₁4.5 percent or less as shown in figure 9.

Through the mode, the size relation between the first wind wheel 21 and the first wind wheel hub 211 and the size relation between the second wind wheel 22 and the second wind wheel hub 221 can be reasonably configured, the first wind wheel 21 and the second wind wheel 22 are guaranteed, the mounting strength is sufficient, meanwhile, the airflow channel can be increased, and the ventilation air volume is greatly increased.

Further, diameter D of first rotor hub 211₁₁Diameter D of second rotor hub 221₂₁Has the following relationship: d₂₁≤D₁₁And 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 easily form a vortex, so that the air volume and the fan efficiency are adversely affected.

The relationship between the thickness of the first rotor, the thickness of the second rotor, and the spacing of the first rotor from the second rotor

In one embodiment, continuing to refer to fig. 14, the first rotor 21 has a length H in the axial direction₁(i.e., the thickness of first rotor 21), the length H of second rotor 22 in the axial direction₂(i.e., the thickness of second rotor 22) and the spacing S of first rotor 21 from second rotor 22₀(i.e., the distance of first rotor wheel 21 and second rotor wheel 22 in the axial direction, which is parallel to the central axis of first rotor wheel 21 and second rotor wheel 22) has the following relationship: s₀<(H₁+H₂)/2. In this way, it can be avoided that the performance of the fan device 20 is affected by an excessively large 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 20 mm. This is to consider error factors such as flow-induced vibration and machining assembly of the first and

second wind wheels

21 and 22 during rotation, so as to ensure that the first and

second wind wheels

21 and 22 do not contact excessively during rotation, and reduce noise generated by mutual interference between the first and

second wind wheels

21 and 22.

In one embodiment, continuing to refer to fig. 14, the end of the first rotor 21 facing away from the second rotor 22 is spaced from the end of the second rotor 22 facing away from the first rotor 21 by a distance of 260mm to 360 mm. That is, the sum of the total thickness of the first rotor 21 and the second rotor 22 and the distance therebetween (i.e., the above-mentioned H)₁、H₂、S₀The sum of the three) is 260mm to 360 mm. According to practical engineering experience, the first rotor 21 and the second rotor 22, as arranged, can be well adapted to models of 12 and below.

In one embodiment, continuing with figure 14, the diameter of the first rotor 21 is equal to the diameter of the second rotor 22 so that the performance of the first and

second rotors

21, 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 direction₁Length H in the axial direction of second wind wheel 22₂Has the following relationship: h₁≤H₂≤1.2H₁Or 0.75H₂≤H₁≤H₂。

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 matched. Moreover, one of the main functions of the first wind wheel 21 is to provide the pre-rotation airflow for the second wind wheel 22, and the design that the length of the first wind wheel 21 in the axial direction is smaller than that of the second wind wheel 22 in the axial direction is to properly weaken the pressure rise effect of the first wind wheel 21 and highlight the pre-rotation 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 ratio of the first wind wheel 21 to the pressure-rise distribution ratio of the second wind wheel 22 is 1:1, it corresponds to the case where 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; and when the pressure-rise distribution rate of the first wind wheel 21 is low and the pressure-rise distribution rate 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 in the axial direction corresponds to.

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 40 mm. Therefore, the first wind wheel 21 and the second wind wheel 22 are prevented from excessively contacting in the rotating process while the distance between the first wind wheel 21 and the second wind wheel 22 is prevented from being excessively large, and noise generated by mutual interference between the first wind wheel 21 and the second wind wheel 22 is reduced.

Relationship of Fan device to air guide shroud

With continued reference to fig. 14, the fan device 20 of the above embodiment including the first wind wheel 21 and the second wind wheel 22 will be described as an example.

In an embodiment, portions of the first wind wheel 21 are disposed within the main body portion 241 of the nacelle 24, and at least portions of the second wind wheel 22 are disposed within the main body portion 241 of the nacelle 24. That is, the first wind wheel 21 is only partially disposed in the main body portion 241, and the second wind wheel 22 may be only partially disposed in the main body portion 241, or the second wind wheel 22 may be entirely disposed in the main body portion 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 side₁Length H in the axial direction from the first rotor 21₁Has the following relationship: s is more than or equal to 0.4₁/H₁Less than or equal to 0.7, which is favorable for 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 duct 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. Figure 15 showsShow S₁/H₁E (0,1) and the noise variation detected by the detection point. It can be seen that S₁And H₁The ratios of (A) to (B) are all varied in noise and all appear to be increased in noise except for 0.55, so that S is preferred in this embodiment₁/H₁The fan device 20 of the present embodiment is made to have as little noise as possible, i.e., 0.55.

Optionally based on S₁/H₁Case 0.55, in an exemplary embodiment, H₁＝126mm，S₁69.3mm, which is not limited herein.

In one 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 241 facing away from the first wind wheel 21₂Length H in the axial direction of second wind wheel 22₂Has the following relationship: s is more than or equal to 0₂/H₂Less than or equal to 0.25, which is favorable for reducing noise.

It should be noted that, by adjusting the position of the second wind wheel 22 in the nacelle 24, the flow field of the wind channel in the nacelle 24 can be improved, and the coupling noise between the blades of the second wind wheel 22 and the nacelle 24 can be reduced. FIG. 16 shows S₂/H₂And taking the noise variation detected by the detection point when different values are obtained. In addition, in fig. 16, when the second wind wheel 22 is only partially disposed in the main body portion 241, the distance between one end of the second wind wheel 22 away from the first wind wheel 21 and one end of the main body portion 241 away from the first wind wheel 21 is a positive value; when the second wind wheel 22 is completely arranged in the main body part 241, the distance between one end of the second wind wheel 22 departing from the first wind wheel 21 and one end of the main body part 241 departing from the first wind wheel 21 is a negative value, specifically S₂/H₂∈(-0.5,0.5)。

It can be seen that S₂And H₂The ratio of (A) is other than 0, and the noise changes in different degrees and the noise is increased, so the embodiment is preferably S₂/H ₂0, the fan device 20 of the present embodiment is made to have as little noise as possible.

Optionally based on S₂/H₂The case of 0, in an exemplary embodiment,H₂＝126mm，S₂the distance between the end of the second wind wheel 22 away from the first wind wheel 21 and the end of the main body 241 away from the first wind wheel 21 is zero, which is not limited herein.

In one 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 241 facing away from the first wind wheel 21₂Length H in the axial direction from the divergent portion 243_kHas the following relationship: s₂≤H_k。

According to the 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 pneumatic performance of the fan device 20. Specifically, the distance between the end of the second wind wheel 22 away from the first wind wheel 21 and the end of the main body part 241 away from the first wind wheel 21 and the axial length of the divergent part 243 satisfy the above relations, so that the air flow of the second wind wheel 22 can be ensured to be subjected to the drainage effect of the air guide sleeve 24, and the air quantity and the fan efficiency can be improved. If the above-mentioned S₂＞H_kPart of the airflow passing through the second wind wheel 22 cannot be guided by the air guide sleeve 24, and air dispersion occurs, which affects the air volume and the fan efficiency.

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 properties 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 21₁And the inner diameter D of the main body part 241₃Has the following relationship: 5mm<(D₃-D₁)/2<20 mm. In this way, the inner diameter of the main body portion 241 of the air guide sleeve 24 is set, which is beneficial to reducing tip leakage vortexes 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 at the same rotation speed.

Further, the diameter D of the first wind wheel 21₁And the inner diameter D of the main body 241₃Has the following relationship: 8mm<(D₃-D₁)/2<12 mm. Preferably, (D)₃-D₁) 10 mm/2. In this way, tip let-off of the first rotor 21 and the second rotor 22 can be minimizedThe vortex is exposed, so that the air quantity is improved to the maximum extent and the noise is reduced.

In an alternative embodiment, the diameter D of the first wind wheel 21₁And the inner diameter D of the main body part 241₃Has the following relationship: 0.008D₁≤D₃-D₁≤0.016D₁. In this way, the inner diameter of the main body portion 241 of the air guide sleeve 24 is set, which is beneficial to reducing tip leakage vortexes 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 at the same rotation speed.

Relationship of fan device, air guide sleeve and mounting seat

Referring to fig. 14 and 17, fig. 17 is a schematic structural view of an embodiment of the air guide sleeve and the mounting seat of the present application.

In one embodiment, the length H of the nacelle 24 and the mount 12 in the axial direction of the nacelle 24₃(as shown in fig. 17) and the lengths H of the first rotor 21 and the second rotor 22 in the axial direction₄(as shown in FIG. 14) has the following relationship: 0.68H₃≤H₄≤0.75H₃. Wherein the first wind wheel 21 and the second wind wheel 22 have a length H in the axial direction₄It is to be understood as the sum of the length of the first rotor 21 in the axial direction, the length of the second rotor 22 in the axial direction and the distance between the first rotor 21 and the second rotor 22.

Through the mode, the length of the air guide sleeve 24 and the length of the mounting seat 12 in the axial direction of the air guide sleeve 24 can be matched with the length of the first wind wheel 21 and the second wind wheel 22 in the axial direction, the aim of restraining vortex leakage of the blade tips of the first wind wheel 21 and the second wind wheel 22 can be achieved, and therefore 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 direction₁And length H of the tapered portion 242 in the axial direction₅Has the following relationship: 0.25H₁≤H₅≤0.4H₁. In this way, 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, and the purpose of restraining the first wind can be achievedThe purpose of vortex leakage at the tip of the wheel 21 allows the air inlet area of the fan device 20 to be increased to the maximum extent, which is favorable for improving the air quantity and reducing the noise.

In one embodiment, the length H of the main body 241 in the axial direction₆Length H in axial direction with respect to the pod 24₇Has the following relationship: 0.75H₇≤H₆≤0.8H₇. In this way, the proportional relationship between the axial length of the main body portion 241 of the nacelle 24 and the axial length of the entire nacelle 24 can be reasonably set, so that the axial length parameters of each part of the nacelle 24 can be more reasonably matched with the axial length parameters of the first wind wheel 21 and the second wind wheel 22, 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 volume and reducing the noise.

The first wind wheel, the second wind wheel and the guide vane are axially related

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

In one embodiment, the length H of the first wind wheel 21 in the axial direction₁Length H of second wind wheel 22 in axial direction₂And the length H of the guide vane 27 in the axial direction₈Has the following relationship: 0.25 (H)₁+H₂)≤H₈≤0.75(H₁+H₂). And the distance S between the guide vane 27 and the adjacent first wind wheel 21 or second wind wheel 22₃Length H of first wind wheel 21 in axial direction₁And the length H of the second rotor 22 in the axial direction₂Has the following relationship: 0.05 (H)₁+H₂)≤S₃≤0.25(H₁+H₂)。

Specifically, when the guide vane 27 is provided on the air inlet side, that is, the guide vane 27 is provided on the side of the first wind wheel 21 facing away from the second wind wheel 22, as shown in fig. 18. Spacing S of guide vanes 27 from adjacent first wind wheels 21₃ First rotor 21 in axial directionLength H₁And the length H of the second rotor 22 in the axial direction₂Has the following relationship: 0.05 (H)₁+H₂)≤S₃≤0.25(H₁+H₂). The bending direction of the blades of the guide vane 27 is opposite to that of the blades of the first wind wheel 21, and the guide vane 27 is used for providing prerotation for the incoming flow of the first wind wheel 21, namely providing prerotation airflow, so that the complicated incoming flow is rectified, the energy loss is reduced, and the air volume is increased.

Further, in 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 first wind wheel 21 may be flush with the end portion of the main body portion 241 of the air guide sleeve 24 close to the first wind wheel 21, so that the entering airflow can receive both the rectifying effect of the guide vane 27 and the flow guiding effect of the air guide sleeve 24.

And when the stator 27 was located the air-out side, namely stator 27 was located the one side that second wind wheel 22 deviates from first wind wheel 21, as shown in fig. 19. Spacing S of guide vanes 27 from adjacent second wind rotor 22₃Length H of first wind wheel 21 in axial direction₁And the length H of the second rotor 22 in the axial direction₂Has the following relationship: 0.05 (H)₁+H₂)≤S₃≤0.25(H₁+H₂). The second wind wheel 22 can recover most of the rotation speed components of the airflow passing through the first wind wheel 21 along the circumferential direction through the rotation direction different from that of the first wind wheel 21, so that the airflow 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. Meanwhile, the guide vane 27 is added on the air outlet side, and the bending direction of the blade of the guide vane 27 is opposite to that of the blade of the second wind wheel 22, so that the rotating speed component of the airflow passing through the second wind wheel 22 along the circumferential direction is further recycled through the guide vane 27, the airflow is further blown out along the axial direction of the fan device 20 as far as possible, the static pressure and the air volume are further improved, and the efficiency of the fan device 20 is further improved.

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

It should be noted that the blade bending direction of the first wind wheel 21, the blade bending direction of the second wind wheel 22, and the blade bending direction of the guide vane 27 are embodied as the bending tendency of the three blades in the respective circumferential directions.

Of course, above-mentioned air inlet side and air-out side all can set up stator 27, and stator 27 that corresponds the position plays corresponding effect, just no longer describes here.

Relationship of first wind wheel hub, second wind wheel hub and guide wheel hub

In one embodiment, continuing with reference to fig. 19, the diameter of the impeller hub 271 is smaller than the diameter of the first wind turbine hub 211 and the diameter of the second wind turbine hub 221.

Specifically, diameter D of guide vane hub 271₈₁Respectively, diameter D of first rotor hub 211₁₁And diameter D of second rotor hub 221₂₁Has the following relationship: 0<D₈₁≤0.95D₁₁，0<D₈₁≤0.95D₂₁. Preferably, the diameter D of the guide vane hub 271₈₁Respectively, diameter D of first rotor hub 211₁₁And diameter D of second rotor hub 221₂₁Has the following relationship: 0.7D₁₁≤D₈₁≤0.9D₁₁，0.7D₂₁≤D₈₁≤0.9D₂₁. Therefore, the guide vane 27 has sufficient installation structural strength, and meanwhile, sufficient flow passage can be reserved, and air loss is reduced. Moreover, the diameter of the guide vane wheel hub 271 is smaller than the diameter of the first wind wheel hub 211 and the diameter of the second wind wheel hub 221, so that the phenomenon that the airflow impacts the guide vane wheel hub 271 to generate vortex can be relieved.

Blade number relation among the first wind wheel, the second wind wheel and the guide vanes

In one embodiment, the number of blades of the first wind turbine 21, the number of blades of the second wind turbine 22, and the number of blades of the guide vane 27 are prime numbers to each other. For example, the first wind turbine 21 has 9 blades, the second wind turbine 22 has 7 blades, the guide vane 27 has 11 blades, and so on.

In this way, because the blade quantity of stator 27 is related to the pressure lift effect of fan device 20, the blade quantity of first wind wheel 21, the blade quantity of second wind wheel 22 and the blade quantity of stator 27 are designed to be prime numbers mutually through this embodiment, so that the blade quantity of first wind wheel 21, the blade quantity of second wind wheel 22 and the blade quantity of stator 27 match each other, and fan device 20 achieves the best pressure lift effect.

In one embodiment, the number of blades n of the first wind wheel 21₁Number n of blades of second wind wheel 22₂Number n of vanes 27₃Has the following relationship: n is₁≤n₂、n₂≤n₃≤2n₁Or n is₂≤n₁、n₁≤n₃≤2n₂. According to practical engineering experience, the number of the blades of the guide vane 27, the number of the blades of the first wind wheel 21 and the number of the blades of the second wind wheel 22 satisfy the relationship, so that the guide vane 27 can be guaranteed to have enough consistency, the guide vane 27 can be guaranteed to have good rectifying and pressurizing effects, the number of introduced new noise sources 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 wind wheel 21₁Number n of blades of second wind wheel 22₂Number n of vanes 27₃Has the following relationship: n is₂≤n₁、n₁≤n₃≤2n₂. In this way, because 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 considering that the second wind wheel 22 is a main source of aerodynamic noise, the number of the blades of the second wind wheel 22 is smaller than that of the first wind wheel 21, which means that the number of the blades of the second wind wheel 22 is relatively small, and is beneficial to reducing noise caused by rotation of the second wind wheel 22; at the same time, for the first wind wheel 21The number of the blades of the first wind wheel 21 is equal to that of the blades of the second wind wheel 22, so that the performance of the first wind wheel 21 can be matched with that of the second wind wheel 22, 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 the vanes of the guide vane 27 is as shown above, which can improve the pressure rise lifting effect to the maximum extent, and further contributes to improving the performance of the fan device 20.

In one embodiment, the number of blades of the vane 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 between the first wind wheel, the second wind wheel and the bracket

In an embodiment, the bracket 25 is provided at least one of a side of the first rotor wheel 21 facing away from the second rotor wheel 22, a side of the second rotor wheel 22 facing away from the first rotor wheel 21, and between the first rotor wheel 21 and the second rotor wheel 22. Fig. 2 and 3 show that the bracket 25 is disposed on a side of the first wind wheel 21 away from the second wind wheel 22, and the above-mentioned other arrangement modes belong to the understanding scope of those skilled in the art, and are not described herein again.

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. In this case, 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 bracket 25 is arranged on the side of the first rotor 21 facing away from the second rotor 22.

When the first wind wheel 21 and the second wind wheel 22 are driven by different motors 23, the motor 23 connected with the first wind wheel 21 and the motor 23 connected with the second wind wheel 22 are respectively mounted on different brackets 25. Moreover, the bracket 25 corresponding to the first wind wheel 21 can be arranged on any one of two sides of the first wind wheel 21 facing and departing from the second wind wheel 22, and the bracket 25 corresponding to the second wind wheel 22 can be arranged on any one of two sides of the second wind wheel 22 facing and departing 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 departing from the second wind wheel 22, the corresponding bracket 25 is also disposed on a side of the first wind wheel 21 departing from the second wind wheel 22, the motor 23 connected to the second wind wheel 22 is disposed on a side of the second wind wheel 22 departing from the first wind wheel 21, and the corresponding bracket 25 is also disposed on a side of the second wind wheel 22 departing from the first wind wheel 21.

In another exemplary embodiment, the motor 23 connected to the first wind wheel 21 is disposed on a side of the first wind wheel 21 facing the second wind wheel 22, the corresponding bracket 25 is also disposed on a side of the first wind wheel 21 facing the second wind wheel 22, the motor 23 connected to the second wind wheel 22 is disposed on a side of the second wind wheel 22 facing the first wind wheel 21, and the corresponding bracket 25 is also disposed on a 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, it is preferable that the first wind rotor 21 and the second wind rotor 22 are driven by the same motor 23, that is, the first wind rotor 21 and the second wind rotor 22 share the same motor 23.

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

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

Through the above manner, 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 flowing 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 the performance of the first wind wheel 21 and the second wind wheel 22 can be well exerted.

Further, the first distance threshold is preferably 15mm or the like. In this way, the interference of the bracket 25 on the flow condition of the airflow generated by the first wind wheel 21 and the second wind wheel 22 can be avoided to the maximum extent, and the performance of the first wind wheel 21 and the second wind wheel 22 can be ensured to the maximum extent.

In one embodiment, the portion of first rotor 21 and second rotor 22 closest to support 25 is the tip portion of both. Specifically, the distance between the support 25 and the tip of the blade of the first wind wheel 21 and the distance between the support 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.

Through the above manner, the bracket 25 is further spaced from the first wind wheel 21 and the second wind wheel 22 by a sufficient distance, so that the bracket 25 is further prevented from interfering with the flowing condition of the airflow generated by the first wind wheel 21 and the second wind wheel 22, the bracket 25 is prevented from influencing the first wind wheel 21 and the second wind wheel 22, 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 on the flow condition of the airflow generated by the first wind wheel 21 and the second wind wheel 22 can be avoided to the maximum extent, and the performance of the first wind wheel 21 and the second wind wheel 22 can be ensured to the maximum extent.

In an embodiment, please continue to refer to fig. 2 and fig. 3, a mesh enclosure 26 is disposed on a side of the second wind wheel 22 away from the first wind wheel 21, that is, the mesh enclosure 26 is disposed on the air 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. Therefore, the second wind wheel 22 and the mesh enclosure 26 have a sufficient distance therebetween, so that the mesh enclosure 26 can be prevented from interfering with the flow conditions of the air currents generated by the first wind wheel 21 and the second wind wheel 22 as much as possible, the mesh enclosure 26 is prevented from affecting the first wind wheel 21 and the second wind wheel 22, and the performance of the first wind wheel 21 and the performance of 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 on the flow condition of the air flow generated by the first wind wheel 21 and the second wind wheel 22 can be avoided to the maximum extent, and the performance of the first wind wheel 21 and the second wind wheel 22 can be ensured to the maximum extent.

The multiple fan units are coaxially arranged

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

In one embodiment, the outdoor unit of the air conditioner includes at least two sets of fan devices 20, and each fan device 20 is coaxially disposed, i.e. the central axes of the fan devices 20 coincide with each other. Further, each fan unit 20 may include a first wind wheel 21 and a second wind wheel 22 spaced along a central axis thereof, as described in the above embodiments.

In this way, at least two sets of fan devices 20 are arranged in the same axial direction in an overlapped mode, 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 effectively improved, meanwhile, the air pressure can be greatly increased, and the high static pressure requirement of special occasions can be met.

Further, the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 of each fan device 20 are equal. Specifically, the diameter of the first wind wheel 21 of the same fan device 20 is equal to the diameter of the second wind wheel 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 the fan devices 20 are arranged in the same diameter, so that the optimal fan efficiency can be ensured.

For example, continuing to refer to fig. 20, the at least two sets of fan devices 20 include a first fan device 201 and a second fan device 202, and the first fan device 201 and the second fan device 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 both 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 also both 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 first wind wheel 21 of the second fan device 202 may be the same or opposite.

Moreover, the first fan device 201 and the second fan device 202 may share one air guide sleeve 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 air guide sleeve 24.

Coplanar arrangement of multiple fan units

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 application, fig. 22 is a schematic sectional view of the outdoor unit of the air conditioner shown in fig. 21 in a direction a-a, and fig. 23 is a schematic sectional view of the outdoor unit of the air conditioner shown in fig. 21 in a direction B-B.

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

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

The air volume of each fan device 20 matches 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 tubes and the heat exchange fins), so that the heat exchange efficiency of the outdoor unit of the air conditioner is ensured as much as possible. Specifically, the diameter of the first wind wheel 21 of each fan unit 20 (D in fig. 22)₁Shown, the same below) and the diameter of the second rotor 22 (see D in fig. 22)₂As shown, the same below) is positively correlated with the heat exchange area of the respective corresponding heat exchanger 30 portion. That is to say, the larger the heat exchange area of the heat exchanger 30 portion corresponding to each fan device 20 is, the larger the diameter of the first wind wheel 21 and the diameter of the second wind wheel 22 of each fan device 20 are.

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, it can be ensured that the air volume of each fan device 20 matches the heat exchange area of the corresponding heat exchanger 30 portion to the maximum, and the heat exchange efficiency of the outdoor unit of the air conditioner is ensured to the maximum.

In an embodiment, the at least two sets of fan devices 20 include a first fan device 201 and a second fan device 202, and the first fan device 201 and the second fan device 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 heat exchanger 30 part corresponding to the first fan device 201 is larger than that of the heat exchanger 30 part 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 that 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 heat exchanger 30 part corresponding to the first fan device 201 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 heat exchanger 30 part corresponding to the first fan device is matched; the smaller heat exchange area of the heat exchanger 30 corresponding to the second fan device 202 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 heat exchanger 30 corresponding to the second fan device 202 is also matched.

For example, referring to 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, that is, 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 adopts the first wind wheel 21 and the second wind wheel 22 with larger diameters, and the second fan device 202 adopts the first wind wheel 21 and the second wind wheel 22 with smaller diameters.

The above case that 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 greater 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 has the following specific situations:

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 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 smaller than the diameter of the second wind wheel 22 of the second fan device 202.

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

It should be noted that, in the present embodiment, the central axes of at least two groups of fan devices 20 are parallel to each other and do not coincide with each other, and each fan device 20 includes a first wind wheel 21 and a second wind wheel 22 that are disposed at an interval along the respective central axis. Compared with the situation that a plurality of single-stage wind wheels are arranged in a coplanar manner, the fan device has higher fan efficiency, larger wind pressure and larger wind volume, and low-frequency beat vibration noise generated by coupling when the plurality of single-stage wind wheels are arranged in the coplanar manner can be avoided between at least two groups of fan devices 20 in the fan device, so that the fan device has lower noise.

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

In addition, in the present application, unless otherwise expressly specified or limited, the terms "connected," "stacked," and the like are to be construed broadly, e.g., as meaning permanently attached, removably attached, or integral to one another; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.

Finally, it should be noted that: the above embodiments are only used for illustrating the technical solutions 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 solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present application.

Claims

1. A fan apparatus, characterized in that the fan apparatus comprises:

the wind power generator 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;

the first wind wheel and the second wind wheel are respectively provided with a plurality of 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.

2. The fan apparatus of claim 1, wherein the difference between the number of blades of the first rotor and the number of blades of the second rotor is 2.

3. The fan apparatus of claim 2,

the diameter of the first wind wheel and the diameter of the second wind wheel are both larger than or equal to a first threshold value, and the larger value of the number of blades of the first wind wheel and the number of blades of the second wind wheel is larger than or equal to a second threshold value; or

The diameter of the first wind wheel and the diameter of the second wind wheel are both smaller than the first threshold value, and the larger value of the number of blades of the first wind wheel and the number of blades of the second wind wheel is smaller than or equal to a third threshold value;

wherein the second threshold is greater than the third threshold.

4. The fan apparatus according to claim 3, wherein the first threshold value ranges from 450mm to 800mm, the second threshold value is 9, and the third threshold value is 7.

5. The fan device according to any one of claims 1 to 4, wherein a side of the first wind wheel facing away from the second wind wheel is an air inlet side, a side of the second wind wheel facing away from the first wind wheel is an air outlet side, and the number of blades of the first wind wheel is greater than that of the second wind wheel.

6. The fan device according to any of claims 1 to 4, wherein a side of the first wind wheel facing away from the second wind wheel is an air inlet side, and a side of the second wind wheel facing away from the first wind wheel is an air outlet sideWind side, number n of blades of the first wind wheel₁The number n of blades of the second wind wheel₂Has the following relationship:

|h*n₁-s*n₂|≥2，h,s∈(1,2,3)。

7. the wind turbine arrangement of any of claims 1 to 4, wherein the number of blades of the first wind turbine and the number of blades of the second wind turbine are each positively correlated with their respective diameters.

8. The wind turbine arrangement of any of claims 1 to 4, wherein the number of blades of the first wind turbine and the number of blades of the second wind turbine are both 5 to 15.

9. The wind turbine arrangement of any of claims 1 to 4, wherein the direction of rotation of the first wind rotor and the direction of rotation of the second wind rotor are the same or opposite.

10. The fan device of claim 1, further comprising a guide vane having a plurality of blades, the guide vane axially spaced from the first and second wind wheels, respectively.

11. The fan device of claim 10, wherein the number of blades of the first wind wheel, the number of blades of the second wind wheel, and the number of blades of the vane are mutually prime.

12. The wind turbine arrangement of claim 10, wherein the first wind turbine has a number of blades n₁The number n of blades of the second wind wheel₂The number n of blades of the guide vane₃Has the following relationship:

n₁≤n₂、n₂≤n₃≤2n₁or is or

n₂≤n₁、n₁≤n₃≤2n₂。

13. The fan apparatus of any of claims 10 to 12, wherein the number of blades of the guide vane is from 6 to 17.

14. The fan device according to any one of claims 10 to 12, wherein the guide vane is disposed on a side of the first wind wheel facing away from the second wind wheel, a bending direction of the blade of the guide vane is opposite to a bending direction of the blade of the first wind wheel, wherein a side of the first wind wheel facing away from the second wind wheel is an air inlet side, and a side of the second wind wheel facing away from the first wind wheel is an air outlet side.

15. The fan device according to any one of claims 10 to 12, wherein the guide vane is disposed on a side of the second wind wheel facing away from the first wind wheel, a bending direction of the blade of the guide vane is opposite to a bending direction of the blade of the second wind wheel, wherein a side of the first wind wheel facing away from the second wind wheel is an air inlet side, and a side of the second wind wheel facing away from the first wind wheel is an air outlet side.

16. An outdoor unit of an air conditioner, comprising a heat exchanger and the fan apparatus of any one of claims 1 to 15, for guiding an air flow through the heat exchanger.