Centrifugal wind wheel, centrifugal fan and air purification equipment

Abstract

The utility model discloses a centrifugal wind wheel, a centrifugal fan and air purification equipment, and belongs to the technical field of ventilation machinery. The centrifugal wind wheel comprises a blade set, a rear disc and a front disc, the rear disc and the front disc are oppositely arranged, the rear disc sinks towards the blade set, the front disc comprises an annular fixing structure and a first extending part, and the ratio of the width of the first extending part in the radial direction of the centrifugal wind wheel to the outer diameter of the blade set is larger than or equal to 0.03 and smaller than or equal to 0.05. Thus, the first extending part is additionally arranged on the rear edge of the side, close to the air outlet, of the front disc, the static pressure of the centrifugal fan can be increased, meanwhile, the situation that airflow output by the air outlet of the centrifugal wind wheel flows back from a gap channel between the front disc and the fan shell can be reduced, and the efficiency of the centrifugal fan is improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to a ventilation machinery technical field, especially a centrifugal fan wheel, centrifugal fan and air purifier. BACKGROUND

[0002] With the development of ventilation machinery technology, the requirement for ventilation equipment is higher and higher. At present, in order to ensure the gas conveying capacity of the ventilation system, centrifugal fan is usually used to provide flowing gas for the ventilation system, and the centrifugal fan has high gas conveying capacity and is a relatively ideal ventilation structure. For example, the air purification equipment comprises filter screen structure and centrifugal fan structure, and the centrifugal fan provides stable airflow and pressure output, so that the air can uniformly pass through the filter screen structure, thereby improving the purification efficiency.

[0003] At present, the centrifugal fan usually comprises a centrifugal fan wheel, a fan shell and a driving assembly, and the centrifugal fan wheel has a plurality of blade sets formed by fan blades. In the operation process of the centrifugal fan, the blade sets rotating at high speed by centrifugal force can accelerate and change the flow direction of the gas, so that the kinetic energy is converted into potential energy, thereby extracting and pushing the air through the filter screen structure.

[0004] However, the air outlet of the existing centrifugal fan wheel is prone to airflow separation, which reduces the efficiency of the centrifugal fan. UTILITY MODEL CONTENT

[0005] The utility model embodiment provides a centrifugal fan wheel, centrifugal fan and air purification equipment. The problem that the air outlet of the centrifugal fan wheel in the prior art is prone to airflow separation, which reduces the efficiency of the centrifugal fan, can be solved, and the technical scheme is as follows:

[0006] According to an aspect of the utility model, a centrifugal fan wheel is provided, which comprises:

[0007] A blade set, a rear disc and a front disc arranged oppositely;

[0008] The blade set is located between the rear disc and the front disc, and an air outlet is formed between the rear disc and the front disc;

[0009] The rear disc is recessed towards the blade set and is fixedly connected to one end of the blade set, and the diameter of the rear disc is equal to the outer diameter of the blade set;

[0010] The front disc comprises an annular fixed structure and a first extension, the annular fixed structure is fixedly connected to the other end of the blade set, the annular fixed structure has an air inlet, and the first extension extends away from the blade set in a direction away from the air inlet and surrounds the blade set;

[0011] The ratio of the width of the first extension part in the radial direction of the centrifugal fan wheel to the outer diameter of the blade set is greater than or equal to 0.03 and less than or equal to 0.05.

[0012] Optionally, the ratio of the inner diameter of the blade set to the outer diameter of the blade set ranges from 0.5 to 0.55.

[0013] Optionally, the blade set includes a plurality of fan blades, the inlet angle of the fan blade near the air inlet side ranges from 28° to 35°, and the outlet angle of the fan blade near the air outlet side ranges from 30° to 35°.

[0014] Optionally, the fan blade has a first end surface and oppositely arranged suction surface and pressure surface, the suction surface is located on the side of the pressure surface close to the axis of the centrifugal fan wheel; the pressure surface is a convex surface of the fan blade, and the suction surface is a concave surface of the fan blade.

[0015] The first end surface is located on the side of the suction surface and the pressure surface close to the front disc, and the first end surface is connected to one end of the suction surface and one end of the pressure surface, respectively.

[0016] The first end surface is inclined towards the pressure surface, and the included angle between the first end surface and the pressure surface ranges from 30° to 45°.

[0017] Optionally, the first air outlet angle of the rear disc near the air outlet side is greater than or equal to the second air outlet angle of the front disc near the air outlet side.

[0018] The first air outlet angle ranges from 45° to 55°, and the second air outlet angle ranges from 45° to 55°.

[0019] Optionally, the annular fixing structure includes an annular first air duct part and an annular second extension part.

[0020] The first air duct part is fixedly connected to the plurality of blades.

[0021] The second extension part extends away from the rear disc from the inner edge of the first air duct part, and the second extension part surrounds the air inlet.

[0022] Optionally, the rear disc includes a mounting part and an annular second air duct part.

[0023] The second air duct part is fixedly connected to the plurality of blades.

[0024] The mounting part is connected to the inner edge of the second air duct part, and the mounting part is used to connect a driving assembly.

[0025] Optionally, the number of wind wheel blades in the blade set is 9 or 11.

[0026] According to another aspect of the present application, a centrifugal fan is provided, which comprises a fan shell, a centrifugal wind wheel and a driving assembly, the centrifugal wind wheel and the driving assembly being installed in the fan shell, the driving assembly being connected with the centrifugal wind wheel, and the centrifugal wind wheel comprising any one of the centrifugal wind wheels described above.

[0027] According to another aspect of the present application, an air purification device is provided, which comprises a device shell, a filter screen structure and a centrifugal fan, the centrifugal fan and the filter screen structure being installed in the device shell, and the centrifugal fan comprising the centrifugal fan described above.

[0028] The technical scheme provided by the present application has at least the following beneficial effects:

[0029] Provided is a centrifugal wind wheel comprising a blade set, a rear disc and a front disc arranged oppositely, wherein the rear disc is recessed towards the blade set, the front disc comprises an annular fixing structure and a first extension, and the ratio of the width of the first extension in the radial direction of the centrifugal wind wheel to the outer diameter of the blade set is greater than or equal to 0.03 and less than or equal to 0.05. In this way, by adding the first extension to the trailing edge of the side of the front disc close to the air outlet, the static pressure of the centrifugal fan can be improved, and at the same time, the backflow of the airflow output from the air outlet of the centrifugal wind wheel through the gap channel between the front disc and the fan shell can be reduced, thereby improving the efficiency of the centrifugal fan. The phenomenon of airflow separation at the air outlet of the centrifugal wind wheel in the prior art can be solved, and the problem of low efficiency of the centrifugal fan can be solved. BRIEF DESCRIPTION OF DRAWINGS

[0030] In order to more clearly illustrate the technical scheme in the embodiments of the present application, the drawings needed in the embodiment description will be briefly introduced as follows. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can be obtained by those skilled in the art without creative effort on the basis of these drawings.

[0031] Figure 1 is a structural schematic view of a centrifugal wind wheel provided by the present application;

[0032] Figure 2 is Figure 1 is a structural schematic view of another perspective of the centrifugal wind wheel shown in

[0033] Figure 3 is Figure 2 is a sectional structural schematic view of the centrifugal wind wheel along the A1-A2 position shown in

[0034] Figure 4 is a structural schematic view of another perspective of the centrifugal fan wheel shown in FIG. Figure 1

[0035] Figure 5 is a gas flow direction schematic view of a centrifugal fan provided by an embodiment of the present application;

[0036] Figure 6 is a structural schematic view of another perspective of the centrifugal fan wheel shown in FIG. Figure 1

[0037] Figure 7 is a structural schematic view of another centrifugal fan;

[0038] Figure 8 is a cross-sectional structural schematic view of the centrifugal fan wheel along the B1-B2 position shown in FIG. Figure 2

[0039] Figure 9 is a structural schematic view of another perspective of the centrifugal fan wheel shown in FIG. Figure 1

[0040] Figure 10 is a structural schematic view of an air purification device provided by an embodiment of the present application;

[0041] Figure 11 is a cross-sectional structural schematic view of the air purification device shown in FIG. Figure 10

[0042] Figure 12 is a simulation schematic view provided by an embodiment of the present application. DETAILED DESCRIPTION

[0043] In order to make the purpose, technical scheme and advantages of the present application more clear, the following will make further detailed description to the embodiments of the present application in combination with the drawings.

[0044] Although the present application can be easily embodied in different forms of embodiments, only some specific embodiments are shown in the drawings and will be described in detail in the present specification, and it can be understood that the present specification should be considered as a demonstrative description of the principles of the present application, and is not intended to limit the present application to that described herein.

[0045] ​​​​​Thus, one feature that is described in the specification can be used to explain one embodiment of the application, and is not necessarily intended to be used to explain every embodiment of the application. Moreover, it should be noted that the specification describes many features that are described in combination with one another. These features can be used in other combinations, and the specification is intended to cover all of these and any other possible combinations.

[0046] In the embodiments shown in the drawings, the indications of directions, such as up, down, left, right, front, and back, are used to explain the structure and movement of various elements of the application, and are not absolute but relative. These indications are appropriate when the elements are in the positions shown in the drawings. If the positions of the elements change, the indications of the directions change accordingly.

[0047] Please refer to Figure 1 , Figure 2 and Figure 3 , Figure 1 is a structural schematic view of a centrifugal fan 10 provided by an embodiment of the application, Figure 2 Figure 1 is a structural schematic view of another view of the centrifugal fan 10, Figure 3 is Figure 2 is a sectional structural schematic view of the centrifugal fan 10 along the position of A1-A2, Figure 4 is Figure 1 is a structural schematic view of another view of the centrifugal fan 10; the centrifugal fan 10 can include a blade group 11, a rear disc 12 and a front disc 13 arranged oppositely. The blade group 11 can include a plurality of fan blades 111 with the same shape, and the plurality of fan blades 111 are arranged around the axis of the centrifugal fan 10. The fan blade 111 can be in a curved shape, and the fan blade 111 is used to suck air flow from the axial direction by rotation, and accelerate the air flow by centrifugal force and discharge the air flow in the radial direction or the direction close to the radial direction, so as to generate pressure difference and air flow.

[0048] The blade group 11 is located between the rear disc 12 and the front disc 13, and the rear disc 12 and the front disc 13 form an air outlet. The edge of the rear disc 12 away from the axis of the centrifugal fan 10 and the edge of the front disc 13 away from the axis of the centrifugal fan 10 can enclose the annular air outlet.

[0049] The rear disc 12 is recessed towards the blade set 11 and is fixedly connected to one end of the blade set 11, and the diameter of the rear disc 12 is equal to the outer diameter of the blade set 11. The rear disc 12 can be in the shape of a "bowl", and the central region of the rear disc 12 can be recessed along the axial direction of the centrifugal fan 10 towards the blade set 11. In this way, the rear disc 12 can change the flow path of the gas inside the fan, and play a guiding role to make the gas flow more smoothly from the axial direction to the radial direction or a direction close to the radial direction; and the recessed rear disc 12 can make the gas flow more concentrated and orderly discharged into the upward axial passage, reduce the gas flow turning loss, and at the same time, leave enough space for the motor installation; the recess of the rear disc 12 can improve the pressure distribution inside the centrifugal fan 10, so that the gas is accelerated and discharged more uniformly under the action of the centrifugal force, thereby improving the pressure performance and efficiency of the centrifugal fan 20. In addition, the recessed rear disc 12 can also enhance the structural strength and stability of the rear disc 12, and at least part of the rear disc 12 can be in the shape of a circular arc to reduce stress concentration during rotation and improve the mechanical strength and durability of the centrifugal fan 10.

[0050] The front disc 13 can be in the shape of a "bell", and the diameter of the front disc 13 gradually increases along the direction close to the rear disc 12. For example, please refer to Figure 5 , Figure 5 is a schematic diagram of the gas flow direction of a centrifugal fan 20 provided by an embodiment of the utility model, the centrifugal fan 20 can include a fan shell 21 and the centrifugal fan 10 in the embodiment of the utility model, and the air outlet of the centrifugal fan 20 is arranged on the fan shell 21. The air outlet of the centrifugal fan 20 can be located on the side of the rear disc 12 of the centrifugal fan 10 away from the front disc 13. The centrifugal fan 20 can be applied in an air purification device (such as an air purifier), and the flow direction of the gas flow generated by the centrifugal fan 10 in the air duct of the air purification device is axial-radial-axial. In this way, through the rear disc 12 and the front disc 13 with the above shape, the gas flow direction can be guided, so that the gas can flow more smoothly from the axial direction to the radial direction and then to the axial direction, that is, the gas flow direction output by the air outlet of the centrifugal fan 10 can have an acute angle with the axial direction of the centrifugal fan 10, so that the gas flow can be more concentrated and stable from the air outlet of the centrifugal fan 10 to the air outlet of the centrifugal fan 20.

[0051] For example, please refer to Figures 1 to 6 , Figure 6 Figure 1Another structural schematic view of the centrifugal fan wheel 10 from another perspective is shown; the front disc 13 can include an annular fixing structure 131 and a first extension 132, the annular fixing structure 131 is fixedly connected with the other end of the blade set 11, the annular fixing structure 131 has an air inlet, the first extension 132 extends from one end of the annular fixing structure 131 away from the air inlet to a direction away from the blade set 11, and the first extension 132 surrounds the blade set 11. Wherein, the ratio of the width of the first extension 132 in the radial direction of the centrifugal fan wheel 10 to the outer diameter of the blade set 11 is greater than or equal to 0.03 and less than or equal to 0.05. For example, the ratio of the width L1 of the first extension 132 in the radial direction of the centrifugal fan wheel 10 to the outer diameter D2 of the blade set 11 is 0.03, 0.04 or 0.05. In the embodiment of the utility model, by additionally setting the first extension 132 on the trailing edge of the front disc 13 close to the air outlet, the static pressure of the centrifugal fan 20 can be improved, and at the same time, the backflow of the airflow output from the air outlet of the centrifugal fan wheel 10 through the gap channel between the front disc 13 and the fan shell 21 can be reduced, thereby improving the efficiency of the centrifugal fan 20.

[0052] Please refer to Figure 7 , Figure 7 is another structural schematic view of the centrifugal fan 20, Figure 7 In the centrifugal fan 20 in the embodiment of the utility model, the outer diameter of the front disc 13 is equal to the outer diameter of the blade set 11, that is, the first extension 132 is not arranged on the trailing edge of the front disc 13. As shown by the black arrow in Figure 7 When the airflow flows out from the air outlet of the centrifugal fan wheel 10, part of the airflow will backflow through the gap channel between the front disc 13 and the fan shell 21, causing airflow separation and reducing the efficiency of the centrifugal fan 20.

[0053] In the embodiment of the utility model, the first extension 132 is arranged on the front disc 13, and the width of the first extension 132 satisfies the following relationship:

[0054] 0.03D2≤L1≤0.05D2;

[0055] Wherein, L1 is the width of the first extension 132 in the radial direction of the centrifugal fan wheel 10, and D2 is the outer diameter of the blade set 11. Compared with the centrifugal fan wheel 10 in Figure 7 The first extension 132 in the centrifugal fan wheel 10 in the embodiment of the utility model can guide the airflow to enter the fan shell 21 more smoothly and flow to the air outlet of the centrifugal fan 20, reduce the airflow separation and turbulence at the air outlet of the centrifugal fan wheel 10, and also reduce the sudden expansion or diffusion of the airflow at the outlet of the fan wheel, thereby reducing the noise and energy loss.

[0056] And, the outer edge of the rear disc 12 does not extend outward, which is conducive to the gas flowing to the air outlet of the centrifugal fan 20, and can improve the air volume and reduce the noise.

[0057] In summary, the utility model disc embodiment provides a kind of centrifugal fan wheel 10 comprising blade group 11, oppositely arranged rear disc 12 and front disc 13, wherein rear disc 12 is recessed towards blade group 11, and front disc 13 includes annular fixed structure 131 and first extension 132, the ratio of the width of first extension 132 in the radial direction of centrifugal fan wheel 10 to the outer diameter of blade group 11 is greater than or equal to 0.03 and less than or equal to 0.05.Such, by additionally providing first extension 132 on the trailing edge of the side of front disc 13 close to air outlet, the static pressure of centrifugal fan 20 can be improved, and the backflow of airflow output from the gap passage between front disc 13 and fan housing 21 can be reduced, thereby improving the efficiency of centrifugal fan 20.The phenomenon that airflow separation is more likely to occur at the air outlet of the centrifugal fan wheel 10 in the prior art can be solved, and the problem of low efficiency of centrifugal fan 20 can be solved.

[0058] Please refer to Figure 8 , Figure 8 is Figure 2 The cross-sectional structure diagram of centrifugal fan wheel 10 along B1-B2 position is shown, and in an alternative embodiment, blade group 11 includes a plurality of fan blades 111, the cross section of the plurality of fan blades 111 is arc-shaped, and the ratio of inner diameter D1 of blade group 11 to outer diameter D2 of blade group 11 ranges from 0.5 to 0.55.The range of inlet angle β1 of fan blade 111 close to air inlet side is 28°-35°, and the range of outlet angle β2 of fan blade 111 close to air outlet side is 30°-35°.For example, the ratio of inner diameter D1 of blade group 11 to outer diameter D2 of blade group 11 ranges from 0.5, 0.51, 0.52, 0.53, 0.54 or 0.55, the inlet angle β1 of fan blade 111 close to air inlet side is 28°, 29°, 30°, 32°, 33° or 35°, and the outlet angle β2 of fan blade 111 close to air outlet side ranges from 30°, 31°, 32°, 33°, 34° or 35°.

[0059] Please refer to Figure 3 The ratio between the diameter d1 of air inlet and the outer diameter D2 of blade group 11 ranges from 0.75 to 0.85, for example, the ratio between the diameter d1 of air inlet and the outer diameter D2 of blade group 11 is 0.75, 0.78, 0.80, 0.82 or 0.85.

[0060] Wherein, the inlet angle β1 refers to the included angle between the tangent of the inlet of the wind wheel blade 111 and the direction of the relative velocity of the inlet, and the inlet angle β1 is used to determine the angle of the airflow entering the impeller, and a smaller angle can be selected to reduce the impact loss. The outlet angle β2 refers to the included angle between the tangent of the outlet of the wind wheel blade 111 and the direction of the relative velocity of the outlet. The outlet angle β2 is used to determine the angle of the airflow leaving the impeller, and a larger angle can be selected to increase the pressure.

[0061] In the embodiments of the utility model, the shape and arrangement direction of the plurality of wind wheel blades 111 are the same, so as to improve the stability of the centrifugal wind wheel 10, and the specification of the wind wheel blade 111 is set in the above range, so that the area expansion of the impeller flow passage is more reasonable, the pressure is fully expanded, the airflow can flow better in the impeller flow passage, the separation loss and friction loss in the impeller flow passage are reduced, and the fan efficiency is improved; at the same time, the boundary layer separation of the suction surface m2 of the wind wheel blade 111 is slowed down, the boundary layer vortex shedding noise is weakened, which is conducive to reducing the noise of the centrifugal wind wheel 10 in the running process, and can also effectively reduce the air volume loss of the centrifugal wind wheel 10, improve the flow and pressure of the centrifugal wind wheel 10.

[0062] Wherein, the impeller flow passage is the space between any adjacent two wind wheel blades 111, the suction surface m2 of the wind wheel blade 111 refers to the leeward surface of the wind wheel blade 111, the pressure surface m3 of the wind wheel blade 111 refers to the windward surface of the wind wheel blade 111, the pressure of the suction surface m2 of the wind wheel blade 111 is less than the pressure of the pressure surface m3 of the wind wheel blade 111, and the pressure difference between the pressure surface m3 and the suction surface m2 causes the wind wheel blade 111 to generate lift, thereby realizing the rotary motion of the wind wheel blade 111.

[0063] In an exemplary embodiment, during the rotation of the centrifugal wind wheel 10, a negative pressure can be formed in the inside of the centrifugal wind wheel 10, and air enters the blade set 11 from the air inlet and between any adjacent two wind wheel blades 111. Since the wind wheel blade 111 is curved, the airflow path can be optimized, so that the airflow can flow more smoothly when passing through the wind wheel blade 111, reducing turbulence and energy loss; by setting the inlet angle and outlet angle of the plurality of wind wheel blades 111 in the above range, the airflow can be more easily discharged from the air outlet.

[0064] Experiments show that when the outlet angle and the inlet angle are less than the above range, the small inlet angle will cause the gas flow to be unable to effectively adhere to the surface of the blade when entering the centrifugal fan 10, increasing the flow loss, and the small inlet angle will limit the gas flow rate, causing the fan flow to be insufficient. The small outlet angle will reduce the centrifugal force of the gas flow, causing the outlet pressure of the centrifugal fan 10 to be insufficient, and the small outlet angle will also limit the exhaust capacity of the gas flow, causing the flow of the centrifugal fan 10 to decrease, thereby causing the efficiency of the centrifugal fan 10 to be low. When the outlet angle and the inlet angle are greater than the above range, the impact of the gas flow on the leading edge of the blade may be intensified, causing additional energy loss, and the large outlet angle will cause the gas flow to separate at the outlet of the blade, increasing the flow loss, thereby reducing the overall efficiency of the fan. In actual application, the skilled person can select according to the size of the gas flow rate and the specific working condition to avoid being too small or too large to ensure the high efficiency and stable operation of the fan.

[0065] Please refer to Figure 1 and Figure 3 、 Figure 8 and Figure 9 , Figure 9 is Figure 1 another perspective view of the centrifugal fan, in an alternative embodiment, the fan blade 111 can have a first end surface m1 and an oppositely arranged suction surface m2 and pressure surface m3, the suction surface m2 is located on the side of the pressure surface m3 close to the axis of the centrifugal fan 10; the pressure surface m3 is the convex surface of the fan blade 111, and the suction surface m2 is the concave surface of the fan blade 111; the first end surface m1 is located on the side of the suction surface m2 and the pressure surface m3 close to the front disc 13, and the first end surface m1 is connected with one end of the suction surface m2 and one end of the pressure surface m3 respectively; wherein the first end surface m1 is inclined, and inclined towards the pressure surface m3, the included angle range α1 between the first end surface m1 and the pressure surface m3 is 30°-45°. Exemplarily, the included angle α1 between the first end surface m1 and the pressure surface m3 is 30°, 35°, 38°, 42° or 45°; in the embodiment of the utility model, the extension direction of the pressure surface m3 of the fan blade 111 can be parallel to the axial direction of the centrifugal fan 10, that is, the included angle range between the first end surface m1 and the axis of the centrifugal fan 10 is 30°-45°.

[0066] In this way, by setting the inclined first end surface m1 at the end of the fan blade 111, the gas flow separation phenomenon at the leading edge of the fan blade 111 can be reduced, the gas flow entering the impeller flow passage is more stable, the turbulence intensity is weakened, and the noise during the operation of the centrifugal fan 10 can be reduced. That is, the first end surface m1 arranged obliquely can be used to adapt to the angle and direction of gas flow, and at the same time, when the gas contacts the fan blade 111, the collision force generated when the gas contacts can be divided, thereby reducing the gas turbulence caused by the collision.

[0067] Please refer to Figure 2 In an alternative embodiment, the first air outlet angle θ1 of the rear disc 12 near the air outlet side can be greater than or equal to the second air outlet angle θ2 of the front disc 13 near the air outlet side; the first air outlet angle θ1 can range from 45° to 55°. Since the airflow generated by the centrifugal fan 10 flows in the axial-radial-axial direction in the air duct of the air purification device 30, the first air outlet angle θ1 being greater than or equal to the second air outlet angle θ2 can effectively increase the turning radius from the radial to the axial direction, and the greater the turning radius, the smaller the flow loss, which is conducive to improving the air volume of the entire machine and the purification capacity of the air purifier.

[0068] In the embodiment of the present application, the rear disc 12 has a first disc surface facing the front disc 13, and the edge region of the first disc surface near the air outlet is arc-shaped; the first air outlet angle θ1 is the included angle between the extension direction of the tangent line of the edge of the first disc surface away from the axis and the radial direction of the centrifugal fan 10; the first extension part 132 of the front disc 13 has a second disc surface facing the rear disc 12, and the second disc surface is inclined; the second air outlet angle θ2 of the front disc 13 is the included angle between the extension direction of the second disc surface and the radial direction of the centrifugal fan 10.

[0069] Please refer to Figure 2 In an alternative embodiment, the annular fixing structure 131 can include an annular first air duct part 1311 and an annular second extension part 1312; the first air duct part 1311 is fixedly connected with the plurality of blades; the second extension part 1312 extends away from the rear disc 12 from the inner edge of the first air duct part 1311, and the second extension part 1312 surrounds the air inlet. The second extension part 1312 can be cylindrical, and the second extension part 1312 can make the airflow more uniform before entering the centrifugal fan 10, reduce turbulence and separation at the air inlet end, improve flow stability, and also guide the airflow to enter the centrifugal fan 10 at a more appropriate angle to reduce the impact of the airflow on the leading edge of the blades and reduce energy loss, thereby reducing flow loss, reducing noise, and enhancing the operating stability of the centrifugal fan 10.

[0070] Please refer to Figure 3 In an alternative embodiment, the rear disc 12 can include a mounting part 121 and an annular second air duct part 122; the second air duct part 122 is fixedly connected with the plurality of blades; the mounting part 121 is connected with the inner edge of the second air duct part 122, and the mounting part 121 is used to connect the driving assembly 22. The mounting part 121 can be connected with the driving shaft of the driving assembly 22 to drive the mounting part 121 to rotate by the driving assembly 22, thereby driving the centrifugal fan 10 to rotate. The second air duct part 122 can be arc-shaped, which can improve the stability of the airflow.

[0071] In an alternative embodiment, the number of wind turbine blades 111 in the blade group 11 is 9 or 11. If the number of wind turbine blades 111 is small, the impeller flow passage is prone to be under-filled, which can easily cause airflow separation and result in increased loss. If the number of wind turbine blades 111 is too large, the impeller flow passage becomes narrow, airflow blockage is serious, and impact loss and friction loss increase. If an even number of blades is arranged, the wind turbine blades 111 are symmetrically arranged, which can easily cause the balance of the wind turbine blades 111 to be destroyed, and the wind turbine blades 111 are more prone to resonance at high speed, and even fatigue fracture of the wind turbine blades 111. Therefore, the number of blades in the blade group 11 is 9 or 11, which can optimize the airflow distribution between two adjacent wind turbine blades 111, reduce the collision between airflows and the formation of turbulence, and thus improve the overall efficiency.

[0072] In summary, the embodiment of the utility model provides a kind of centrifugal fan 10 comprising blade group 11, relatively arranged rear disc 12 and front disc 13, wherein rear disc 12 is recessed towards blade group 11, and front disc 13 includes annular fixed structure 131 and first extension 132, the ratio of the width of first extension 132 in the radial direction of centrifugal fan 10 to the outer diameter of blade group 11 is greater than or equal to 0.03 and less than or equal to 0.05. In this way, by additionally providing first extension 132 on the trailing edge of the side of front disc 13 close to the air outlet, the static pressure of centrifugal fan 20 can be improved, and the backflow of airflow output from the air outlet of centrifugal fan 10 through the gap channel between front disc 13 and fan housing 21 can be reduced, thereby improving the efficiency of centrifugal fan 20. The problem of airflow separation at the air outlet of centrifugal fan 10 in the prior art, which leads to low efficiency of centrifugal fan 20, can be solved.

[0073] Please refer to Figure 5 The embodiment of the utility model further provides a kind of centrifugal fan 20, centrifugal fan 20 includes fan housing 21, centrifugal fan 10 and drive assembly 22, centrifugal fan 10 and drive assembly 22 are installed in fan housing 21, drive assembly 22 is connected with centrifugal fan 10, and centrifugal fan 10 includes the centrifugal fan 10 in any embodiment described above. Drive assembly 22 can include motor 221 and motor cover 222.

[0074] Please refer to Figure 10 And Figure 11 , Figure 10 It is the structure diagram of air purification equipment 30 provided by the embodiment of the utility model, Figure 11 It is Figure 10The cross-sectional structure schematic diagram of the air purification equipment 30 is shown, and the air purification equipment 30 can include an equipment shell 31, a filter screen structure 32 and a centrifugal fan 20, the centrifugal fan 20 and the filter screen structure 32 are both installed in the equipment shell 31, and the centrifugal fan 20 includes the centrifugal fan 20 in the above-mentioned embodiment. The equipment shell 31 can have an air inlet grille 311 and an air outlet grille 312, under the driving of the centrifugal fan 20, the air from the outside enters the equipment shell from the air inlet grille 311, passes through the filter screen structure 32, and then passes through the filter screen structure 32, enters the centrifugal impeller 10 through the flow collector, and then the air flow is delivered to the air outlet grille 312 through the centrifugal impeller 10, so that the air purification is realized.

[0075] Please refer to Figure 12 and Table 1, Figure 12 is a simulation schematic diagram provided by the utility model embodiment, Figure 12 The simulation result schematic diagram of the centrifugal fan 20 in the prior art before optimization and the simulation result schematic diagram of the centrifugal fan 20 in the utility model embodiment are shown in the figure, and the simulation result schematic diagram includes a pressure cloud chart, a velocity cloud chart and a velocity vector chart. Table 1 is a performance comparison table of the centrifugal fan 20 in the prior art and the centrifugal fan 20 in the utility model embodiment, and the centrifugal impeller 10 in the centrifugal fan 20 in the prior art has the first extension 132 and other structures in the centrifugal impeller 10 in the utility model embodiment.

[0076] Table 1

[0077]

[0078] From Figure 11 And from Table 1, compared with the centrifugal fan 20 in the prior art, the centrifugal fan in the utility model embodiment can reduce the rotating speed by 90 rpm, reduce the shaft power by more than 3W, increase the centrifugal fan total pressure efficiency and static pressure efficiency by 1% and 3.1% respectively, and reduce the maximum wideband noise by 2.6dB under the same air volume.

[0079] Specifically, from the pressure cloud chart, it can be seen that the pressure gradient change in the impeller flow passage of the centrifugal impeller in the utility model embodiment is more stable and increases, and there is no obvious mutation, while the pressure gradient change of the centrifugal impeller in the prior art is unstable, which can cause the airflow in the impeller flow passage to flow unstably.

[0080] From the velocity nephogram and the velocity vector diagram can see, the centrifugal wind wheel in the utility model embodiment, the air flow gradually reduces from the impeller flow passage entrance to the exit speed, the axial velocity distribution is more uniform, and the centrifugal wind wheel in the related art has a big mutation from the impeller flow passage entrance to the exit speed, there is a low speed area locally, and the tail edge suction surface m2 has obvious air flow separation phenomenon, compared with the prior art, the centrifugal fan in the utility model has better performance.

[0081] It should be noted that in the drawings, the dimensions of the regions can be exaggerated for clarity. Also, it should be understood that when a component is referred to as being "on" another component, it can be directly on the other component or intervening components can also be present. In addition, it should be understood that when a component is referred to as being "under" another component, it can be directly under the other component or one or more intervening components can also be present. In addition, it should be understood that when a component is referred to as being "between" two components, it can be the only component between the two components or one or more intervening components can also be present. Like reference numerals refer to like elements throughout.

[0082] In the present utility model, the terms "first" and "second" are used only for descriptive purposes and not to connote or imply relative importance. The term "plurality" means two or more, unless otherwise expressly specified.

[0083] The above description is only optional embodiments of the present utility model and does not limit the present utility model, and any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model should be included.

Claims

1. A centrifugal fan wheel, characterized in that The centrifugal fan comprises: a blade group, a rear disc and a front disc arranged oppositely; the blade group is located between the rear disc and the front disc, and an air outlet is formed between the rear disc and the front disc; the rear disc is recessed towards the blade group and is fixedly connected to one end of the blade group, and the diameter of the rear disc is equal to the outer diameter of the blade group; the front disc comprises a ring-shaped fixed structure and a first extension, the ring-shaped fixed structure is fixedly connected to the other end of the blade group, the ring-shaped fixed structure has an air inlet, and the first extension extends away from the blade group from the end of the ring-shaped fixed structure away from the air inlet; wherein the ratio of the width of the first extension in the radial direction of the centrifugal fan to the outer diameter of the blade group is greater than or equal to 0.03 and less than or equal to 0.

05.

2. The centrifugal fan wheel according to claim 1, characterized in that The ratio of the inner diameter of the blade group to the outer diameter of the blade group ranges from 0.5 to 0.

55.

3. The centrifugal fan wheel of claim 1, wherein The blade group comprises a plurality of fan blades, the inlet angle of the fan blades on the side close to the air inlet ranges from 28° to 35°, and the outlet angle of the fan blades on the side close to the air outlet ranges from 30° to 35°.

4. The centrifugal fan wheel of claim 3, wherein The fan blade has a first end face and oppositely arranged suction surface and pressure surface, the suction surface is located on the side of the pressure surface close to the axis of the centrifugal fan; the pressure surface is a convex surface of the fan blade, and the suction surface is a concave surface of the fan blade; the first end face is located on the side of the suction surface and the pressure surface close to the front disc, and the first end face is connected to one end of the suction surface and one end of the pressure surface, respectively; wherein the first end face is inclined towards the pressure surface, and the included angle between the first end face and the pressure surface ranges from 30° to 45°.

5. The centrifugal fan wheel of claim 3, wherein The first air outlet angle of the rear disc on the side close to the air outlet is greater than or equal to the second air outlet angle of the front disc on the side close to the air outlet; the first air outlet angle ranges from 45° to 55°, and the second air outlet angle ranges from 45° to 55°.

6. The centrifugal fan wheel of claim 3 wherein, The ring-shaped fixed structure comprises a ring-shaped first air duct portion and a ring-shaped second extension; the first air duct portion is fixedly connected to the plurality of blades; the second extension extends away from the rear disc from the inner edge of the first air duct portion, and the second extension surrounds the air inlet.

7. The centrifugal fan wheel of claim 3 wherein, The rear disc comprises a mounting portion and a ring-shaped second air duct portion; the second air duct portion is fixedly connected to the plurality of blades; the mounting portion is connected to the inner edge of the second air duct portion, and the mounting portion is used for connecting a driving assembly.

8. The centrifugal fan wheel of claim 3 wherein, The number of fan blades in the blade group is 9 or 11.

9. A centrifugal fan characterized by The centrifugal fan comprises a fan shell, a centrifugal fan and a driving assembly, the centrifugal fan and the driving assembly are installed in the fan shell, the driving assembly is connected to the centrifugal fan, and the centrifugal fan comprises the centrifugal fan according to any one of claims 1 to 8.

10. An air cleaning apparatus, characterized by, The air purification device comprises a device shell, a filter screen structure and a centrifugal fan, the centrifugal fan and the filter screen structure are both installed in the device shell, and the centrifugal fan comprises the centrifugal fan in claim 9.

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