Centrifugal fan, centrifugal fan and air purification equipment

Abstract

The present application discloses a centrifugal wind wheel, a centrifugal fan and an air purification device, which belong to the technical field of ventilation machinery. The centrifugal wind wheel includes: a blade group, a rear disc and a front disc arranged oppositely, wherein the rear disc is recessed toward the blade group, and the front disc includes an annular fixing structure and a first extension portion, and the ratio of the width of the first extension portion in the radial direction of the centrifugal wind wheel to the outer diameter of the blade group is greater than or equal to 0.03, and less than or equal to 0.05. In this way, by adding the first extension portion to the trailing edge of the front disc on the side close to the air outlet, the static pressure of the centrifugal fan can be increased, and at the same time, the airflow output from the air outlet of the centrifugal wind wheel can be reduced from flowing back through the gap channel between the front disc and the fan housing, thereby improving the efficiency of the centrifugal fan.

Description

Technical Field

[0001] The present application relates to the technical field of ventilation machinery, and in particular to a centrifugal fan, a centrifugal blower and an air purifier. Background Art

[0002] With the development of ventilation machinery technology, the requirements for ventilation equipment are getting higher and higher. At present, in order to ensure the gas delivery capacity of the ventilation system, centrifugal fans are usually used to provide flowing gas for the ventilation system. Centrifugal fans have efficient gas delivery capabilities and are ideal ventilation structures. For example, air purification equipment includes filter structures and centrifugal fans. Centrifugal fans provide stable airflow and pressure output to ensure that air can pass through the filter structure evenly, thereby improving purification efficiency.

[0003] At present, centrifugal fans usually include structures such as a centrifugal wind wheel, a fan housing and a drive assembly. The centrifugal wind wheel has a blade group formed by multiple wind wheel blades. During the operation of the centrifugal fan, the centrifugal high-speed rotating blade group can accelerate the gas and change the flow direction, so that kinetic energy is converted into potential energy, thereby drawing air and pushing it through the filter structure.

[0004] However, the air flow separation phenomenon is more likely to occur at the air outlet of the existing centrifugal fan, resulting in low efficiency of the centrifugal fan. Summary of the invention

[0005] The embodiment of the present application provides a centrifugal wind wheel, a centrifugal fan and an air purification device. It can solve the problem that the air flow separation is easy to occur at the air outlet of the centrifugal wind wheel in the prior art, resulting in low efficiency of the centrifugal fan. The technical solution is as follows:

[0006] According to one aspect of the present application, a centrifugal wind wheel is provided, comprising:

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

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

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

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

[0011] Wherein, a ratio of a width of the first extension portion in the radial direction of the centrifugal wind wheel to an outer diameter of the blade assembly 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 assembly to the outer diameter of the blade assembly is in the range of 0.5 to 0.55.

[0013] Optionally, the blade group includes a plurality of wind rotor blades, an inlet angle of the wind rotor blades close to the air inlet is in a range of 28° to 35°, and an outlet angle of the wind rotor blades close to the air outlet is in a range of 30° to 35°.

[0014] Optionally, the wind rotor blade has a first end surface and a suction surface and a pressure surface arranged opposite to each other, the suction surface is located on a side of the pressure surface close to the axis of the centrifugal wind rotor; the pressure surface is a convex surface of the wind rotor blade, and the suction surface is a concave surface of the wind rotor blade;

[0015] The first end surface is located on a side of the suction surface and the pressure surface close to the front disk, 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 an inclined surface and is inclined toward the pressure surface. The angle between the first end surface and the pressure surface is in the range of 30° to 45°.

[0017] Optionally, a first air outlet angle of the rear disc close to the air outlet is greater than or equal to a second air outlet angle of the front disc close to the air outlet;

[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 channel portion and an annular second extending portion;

[0020] The first air channel portion is fixedly connected to the plurality of blades;

[0021] The second extension portion extends from the inner edge of the first air channel portion in a direction away from the rear disk, and the second extension portion surrounds the air inlet.

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

[0023] The second air channel portion is fixedly connected to the plurality of blades;

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

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

[0026] According to another aspect of the present application, a centrifugal fan is provided, comprising a fan housing, a centrifugal fan wheel and a drive assembly, wherein the centrifugal fan wheel and the drive assembly are installed in the fan housing, the drive assembly is connected to the centrifugal fan wheel, and the centrifugal fan wheel comprises any of the centrifugal fan wheels described above.

[0027] According to another aspect of the present application, an air purification device is also provided, which includes a device housing, a filter structure and a centrifugal fan, the centrifugal fan and the filter structure are both installed in the device housing, and the centrifugal fan includes the above-mentioned centrifugal fan.

[0028] The beneficial effects brought by the technical solution provided by the embodiment of the present application include at least:

[0029] A centrifugal fan wheel is provided, which includes a blade group, a rear disk and a front disk arranged opposite to each other, wherein the rear disk is recessed toward the blade group, the front disk includes an annular fixing structure and a first extension portion, and the ratio of the width of the first extension portion in the radial direction of the centrifugal fan wheel to the outer diameter of the blade group is greater than or equal to 0.03 and less than or equal to 0.05. In this way, by adding the first extension portion to the trailing edge of the front disk on the side close to the air outlet, the static pressure of the centrifugal fan can be increased, and at the same time, the airflow output from the air outlet of the centrifugal fan wheel can be reduced from flowing back through the gap channel between the front disk and the fan housing, thereby improving the efficiency of the centrifugal fan. The problem that the airflow separation is more likely to occur at the air outlet of the centrifugal fan wheel in the prior art, resulting in low efficiency of the centrifugal fan, can be solved. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0031] Figure 1 is a structural schematic diagram of a centrifugal wind wheel provided in an embodiment of the present application;

[0032] Figure 2 yes Figure 1 A schematic structural diagram of a centrifugal wind wheel from another perspective is shown;

[0033] Figure 3 yes Figure 2 The schematic diagram of the cross-sectional structure of the centrifugal wind wheel along the position A1-A2 shown;

[0034] Figure 4yes Figure 1 A schematic structural diagram of a centrifugal wind wheel from another perspective is shown;

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

[0036] Figure 6 yes Figure 1 A schematic structural diagram of a centrifugal wind wheel from another perspective is shown;

[0037] Figure 7 It is a schematic diagram of the structure of another centrifugal fan;

[0038] Figure 8 yes Figure 2 The schematic diagram of the cross-sectional structure of the centrifugal wind wheel along the position B1-B2 shown;

[0039] Fig. 9 yes Figure 1 A schematic structural diagram of a centrifugal wind wheel from another perspective is shown;

[0040] Fig.10 It is a structural schematic diagram of an air purification device provided in an embodiment of the present application;

[0041] Fig.11 yes Fig.10 A schematic cross-sectional structure diagram of an air purification device shown;

[0042] Fig.12 It is a simulation schematic diagram provided in an embodiment of the present application. DETAILED DESCRIPTION

[0043] In order to make the objectives, technical solutions and advantages of the present application clearer, the implementation methods of the present application will be further described in detail below with reference to the accompanying drawings.

[0044] Although the present application can be easily presented as embodiments of different forms, only some of the specific embodiments are shown in the drawings and described in detail in this specification. It should be understood that this description should be regarded as an exemplary description of the principles of the present application and is not intended to limit the present application to that described herein.

[0045] Thus, a feature indicated in this specification will be used to illustrate one of the features of an embodiment of the application, rather than implying that each embodiment of the application must have the described features. In addition, it should be noted that this specification describes many features. Although some features can be combined together to illustrate possible system designs, these features can also be used for other combinations that are not explicitly described. Thus, unless otherwise stated, the described combinations are not intended to be limiting.

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

[0047] Please refer to Figure 1 , Figure 2 and Figure 3 , Figure 1 is a schematic structural diagram of a centrifugal wind wheel 10 provided in an embodiment of the present application. Figure 2 Figure 1 The schematic structural diagram of the centrifugal wind wheel 10 from another perspective is shown. Figure 3 yes Figure 2 The cross-sectional structure diagram of the centrifugal wind wheel 10 along the position A1-A2 is shown. Figure 4 yes Figure 1 The centrifugal wind wheel 10 is shown as a structural schematic diagram from another perspective; the centrifugal wind wheel 10 may include: a blade group 11, a rear disk 12 and a front disk 13 arranged opposite to each other. The blade group 11 may include a plurality of wind wheel blades 111 of the same shape, and the plurality of wind wheel blades 111 are arranged around the axis of the centrifugal wind wheel 10. The wind wheel blades 111 may be in a curved shape, and the wind wheel blades 111 are used to inhale the airflow from the axial direction by rotation, and use the centrifugal force to accelerate the airflow and discharge it in the radial direction or in a direction close to the radial direction, thereby generating a pressure difference and airflow.

[0048] The blade group 11 is located between the rear disk 12 and the front disk 13, and an air outlet is formed between the rear disk 12 and the front disk 13. The edge of the rear disk 12 away from the axis of the centrifugal wind wheel 10 and the edge of the front disk 13 away from the axis of the centrifugal wind wheel 10 can form a ring-shaped air outlet.

[0049] The rear disc 12 is recessed toward the blade group 11 and is fixedly connected to one end of the blade group 11. The diameter of the rear disc 12 is equal to the outer diameter of the blade group 11. The rear disc 12 can be in a "bowl" shape, and the central area of ​​the rear disc 12 can be recessed toward the blade group 11 along the axial direction of the centrifugal wind wheel 10. In this way, the rear disc 12 can change the flow path of the gas inside the wind wheel and play a guiding role, so that it can more smoothly turn 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 airflow more concentrated and orderly discharged, enter the upward axial channel, reduce the airflow turning loss, and leave enough space for the motor installation; the recessed rear disc 12 can improve the pressure distribution inside the centrifugal wind wheel 10, so that the gas can be accelerated and discharged more evenly under the action of centrifugal force, thereby improving the pressure performance and efficiency of the centrifugal fan 20. In addition, the concave rear disk 12 can also enhance the structural strength and stability of the rear disk 12 . At least a portion of the rear disk 12 can be arc-shaped to reduce stress concentration during rotation and improve the mechanical strength and durability of the centrifugal wind wheel 10 .

[0050] The front disc 13 may be in a "horn" shape, and the diameter of the front disc 13 gradually increases in the direction close to the rear disc 12. For example, please refer to Figure 5 , Figure 5 It is a schematic diagram of the gas flow direction of a centrifugal fan 20 provided in an embodiment of the present application. The centrifugal fan 20 may include a fan housing 21 and a centrifugal fan wheel 10 in the embodiment of the present application. The air outlet of the centrifugal fan 20 is arranged on the fan housing 21. The air outlet of the centrifugal fan 20 may be located on the side of the rear disk 12 of the centrifugal fan wheel 10 away from the front disk 13. The centrifugal fan 20 can be used in air purification equipment (such as an air purifier). The flow direction of the airflow generated by the centrifugal fan wheel 10 in the air duct of the air purification equipment is axial-radial-axial. In this way, through the rear disk 12 and the front disk 13 of the above-mentioned shape, the gas flow direction can be guided so that the gas can be more smoothly turned from axial to radial and then to axial, that is, the gas flow direction output from the air outlet of the centrifugal wind wheel 10 can have an acute angle with the axial direction of the centrifugal wind wheel 10, thereby reducing the retention and turbulence of the airflow at the air outlet of the centrifugal wind wheel 10, and making the airflow more concentrated and stable to flow from the air outlet of the centrifugal wind wheel 10 to the air outlet of the centrifugal fan 20.

[0051] Please refer to Figures 1 to 6 , Figure 6 Figure 1The schematic diagram of the structure of the centrifugal wind wheel 10 from another perspective is shown; the front disk 13 may include an annular fixing structure 131 and a first extension portion 132, the annular fixing structure 131 is fixedly connected to the other end of the blade group 11, the annular fixing structure 131 has an air inlet, the first extension portion 132 extends from the end of the annular fixing structure 131 away from the air inlet in a direction away from the blade group 11, and the first extension portion 132 surrounds the blade group 11. The ratio of the width of the first extension portion 132 in the radial direction of the centrifugal wind wheel 10 to the outer diameter of the blade group 11 is greater than or equal to 0.03 and less than or equal to 0.05. Exemplarily, the ratio of the width L1 of the first extension portion 132 in the radial direction of the centrifugal wind wheel 10 to the outer diameter D2 of the blade group 11 is 0.03, 0.04 or 0.05. In the embodiment of the present application, by adding a first extension portion 132 to the rear edge of the front disk 13 on the side close to the air outlet, the static pressure of the centrifugal fan 20 can be increased, and at the same time, the airflow output from the air outlet of the centrifugal wind wheel 10 can be reduced from flowing back through the gap channel between the front disk 13 and the fan housing 21, thereby improving the efficiency of the centrifugal fan 20.

[0052] Please refer to Figure 7 , Figure 7 is a schematic diagram of the structure of another centrifugal fan 20, Figure 7 In the centrifugal fan 20, the outer diameter of the front disc 13 is equal to the outer diameter of the blade assembly 11, that is, the first extension portion 132 is not provided at the rear edge of the front disc 13. Figure 7 As shown by the black arrow in the figure, after the airflow flows out from the air outlet of the centrifugal fan wheel 10, part of the airflow will flow back from the gap channel between the front disk 13 and the fan housing 21, resulting in airflow separation and reducing the efficiency of the centrifugal fan 20.

[0053] In the embodiment of the present application, the first extension portion 132 is provided on the front plate 13, and the width of the first extension portion 132 satisfies the following relationship:

[0054] 0.03D2≤L1≤0.05D2;

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

[0056] Furthermore, in the embodiment of the present application, the outer edge of the rear disk 12 does not extend outward, which is beneficial for the gas to flow to the air outlet of the centrifugal fan 20, thereby increasing the air volume and reducing noise.

[0057] In summary, the embodiment of the present application provides a centrifugal fan 10 including a blade group 11, a rear disc 12 and a front disc 13 arranged opposite to each other, wherein the rear disc 12 is recessed toward the blade group 11, and the front disc 13 includes an annular fixing structure 131 and a first extension portion 132, and the ratio of the width of the first extension portion 132 in the radial direction of the centrifugal fan 10 to the outer diameter of the blade group 11 is greater than or equal to 0.03 and less than or equal to 0.05. In this way, by adding the first extension portion 132 to the rear edge of the side of the front disc 13 close to the air outlet, the static pressure of the centrifugal fan 20 can be increased, and at the same time, the airflow output from the air outlet of the centrifugal fan 10 can be reduced from flowing back through the gap channel between the front disc 13 and the fan housing 21, thereby improving the efficiency of the centrifugal fan 20. It can solve the problem that the airflow separation is more likely to occur at the air outlet of the centrifugal fan 10 in the prior art, resulting in the low efficiency of the centrifugal fan 20.

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

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

[0060] Among them, the inlet angle β1 refers to the angle between the tangent line at the inlet of the wind rotor blade 111 and the relative velocity direction of the inlet. The inlet angle β1 is used to determine the angle at which the airflow enters the impeller. A smaller angle can be selected to reduce impact loss. The outlet angle β2 refers to the angle between the tangent line at the outlet of the wind rotor blade 111 and the relative velocity direction of the outlet. The outlet angle β2 is used to determine the angle at which the airflow leaves the impeller. A larger angle can be selected to increase the pressure.

[0061] In the embodiment of the present application, the shapes and arrangement directions of the multiple wind wheel blades 111 are the same to improve the stability of the centrifugal wind wheel 10, and the specifications of the wind wheel blades 111 are set within the above-mentioned range, so that the area expansion of the impeller flow channel can be more reasonable and the pressure expansion can be sufficient, so that the airflow can flow better in the impeller flow channel, reducing the separation loss and friction loss in the impeller flow channel, and improving the efficiency of the fan; at the same time, the boundary layer separation of the suction surface m2 of the wind wheel blade 111 can be slowed down, and the boundary layer vortex shedding noise can be weakened, which is beneficial to reducing the noise of the centrifugal wind wheel 10 during operation, and can also effectively reduce the air volume loss of the centrifugal wind wheel 10 and increase the flow and pressure of the centrifugal wind wheel 10.

[0062] Among them, the impeller flow channel is the space between any two adjacent wind rotor blades 111, the suction surface m2 of the wind rotor blade 111 refers to the leeward side of the wind rotor blade 111, and the pressure surface m3 of the wind rotor blade 111 refers to the windward side of the wind rotor blade 111. The pressure of the suction surface m2 of the wind rotor blade 111 is less than the pressure of the pressure surface m3 of the wind rotor blade 111. The pressure difference between the pressure surface m3 and the suction surface m2 causes the wind rotor blade 111 to generate lift, thereby realizing the rotational movement of the wind rotor blade 111.

[0063] In an exemplary embodiment, during the rotation of the centrifugal wind wheel 10, negative pressure can be formed inside the centrifugal wind wheel 10, and air enters from the air inlet into between any two adjacent wind wheel blades 111 in the blade group 11. Since the wind wheel blades 111 are curved, it can help optimize the airflow path, so that the airflow can flow more smoothly when passing through the wind wheel blades 111, reducing turbulence and energy loss; setting the inlet angle and outlet angle of the multiple wind wheel blades 111 within the above range can make the airflow easier to be discharged from the air outlet.

[0064] Through experiments, it is known that when the outlet angle and the inlet angle are less than the above range values, a too small inlet angle will cause the airflow to fail to effectively adhere to the blade surface when entering the centrifugal wind wheel 10, increasing the flow loss, and a too small inlet angle will limit the air intake of the airflow, resulting in insufficient fan flow; a too small outlet angle will reduce the centrifugal force of the airflow, resulting in insufficient outlet pressure of the centrifugal wind wheel 10, and a too small outlet angle will also limit the discharge capacity of the airflow, resulting in a reduction in the flow of the centrifugal wind wheel 10, thereby resulting in a lower efficiency of the centrifugal wind wheel 10. When the outlet angle and the inlet angle are greater than the above range values, the impact between the airflow and the leading edge of the blade may be aggravated, resulting in additional energy loss, and a too large outlet angle may cause the airflow to separate at the blade outlet, increasing flow loss, thereby reducing the overall efficiency of the fan. In actual application, technicians can make reasonable choices based on the amount of airflow and the specific working conditions to avoid being too small or too large to ensure efficient and stable operation of the fan.

[0065] Please refer to Figure 1 and Figure 3 , Figure 8 and Fig. 9 , Fig. 9 yes Figure 1 The structural schematic diagram of the centrifugal wind wheel from another perspective shown in the figure, in an optional embodiment, the wind wheel blade 111 may have a first end face m1 and a suction face m2 and a pressure face m3 which are arranged opposite to each other, the suction face m2 is located on the side of the pressure face m3 which is close to the axis of the centrifugal wind wheel 10; the pressure face m3 is the convex surface of the wind wheel blade 111, and the suction face m2 is the concave surface of the wind wheel blade 111; the first end face m1 is located on the side of the suction face m2 and the pressure face m3 which are close to the front disk 13, and the first end face m1 is respectively connected to one end of the suction face m2 and one end of the pressure face m3; wherein the first end face m1 is an inclined face and is inclined toward the pressure face m3, and the angle range α1 between the first end face m1 and the pressure face m3 is 30° to 45°. Exemplarily, the angle α1 between the first end face m1 and the pressure face m3 is 30°, 35°, 38°, 42° or 45°; in the embodiment of the present application, the extension direction of the pressure face m3 of the wind wheel blade 111 can be parallel to the axial direction of the centrifugal wind wheel 10, that is, the angle between the first end face m1 and the axis of the centrifugal wind wheel 10 ranges from 30° to 45°.

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

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

[0068] In the embodiment of the present application, the rear disk 12 has a first disk surface facing the front disk 13, and the edge area of ​​the first disk surface close to the air outlet is an arc surface. The first air outlet angle θ1 is the angle between the extension direction of the tangent at the edge of the first disk surface away from the axis and the radial direction of the centrifugal wind wheel 10; the first extension portion 132 of the front disk 13 has a second disk surface facing the rear disk 12, and the second disk surface is an inclined surface. The second air outlet angle θ2 of the front disk 13 is the angle between the extension direction of the second disk surface and the radial direction of the centrifugal wind wheel 10.

[0069] Please refer to Figure 2 In an optional embodiment, the annular fixed structure 131 may include an annular first air channel portion 1311 and an annular second extension portion 1312; the first air channel portion 1311 is fixedly connected to a plurality of blades; the second extension portion 1312 extends from the inner edge of the first air channel portion 1311 in a direction away from the rear disc 12, and the second extension portion 1312 forms an air inlet. The second extension portion 1312 may be cylindrical, and the second extension portion 1312 may make the airflow more uniform before entering the centrifugal wind wheel 10, reduce turbulence and separation at the air inlet end, improve flow stability, and guide the airflow to enter the centrifugal wind wheel 10 at a more appropriate angle to reduce the impact of the airflow with the leading edge of the blades, reduce energy loss, thereby reducing flow loss, reducing noise, and enhancing the operating stability of the centrifugal wind wheel 10.

[0070] Please refer to Figure 3 In an optional embodiment, the rear disc 12 may include a mounting portion 121 and an annular second air channel portion 122; the second air channel portion 122 is fixedly connected to the plurality of blades; the mounting portion 121 is connected to the inner edge of the second air channel portion 122, and the mounting portion 121 is used to connect the drive assembly 22. The mounting portion 121 may be connected to the drive shaft of the drive assembly 22, so that the mounting portion 121 is driven to rotate through the drive assembly 22, thereby driving the centrifugal wind wheel 10 to rotate. The second air channel portion 122 may be arc-shaped, which may improve the stability of the airflow.

[0071] In an optional embodiment, the number of wind rotor blades 111 in the blade group 11 is 9 or 11. If the number of wind rotor blades 111 is small, the impeller flow channel is more likely to be incomplete, and airflow separation is likely to occur, resulting in increased losses; if the number of wind rotor blades 111 is too large, the impeller flow channel becomes narrower, the airflow is seriously blocked, and the impact loss and friction loss increase. If an even number of blades is arranged, the wind rotor blades 111 are symmetrically arranged, which can easily lead to the destruction of the balance of the wind rotor blades 111 themselves, and the wind rotor blades 111 are more likely to resonate when running at high speed, and even the wind rotor blades 111 may suffer fatigue fracture. Therefore, the number of blades in the wind rotor blade 111 group 11 is 9 or 11, which can optimize the airflow distribution between two adjacent wind rotor 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 present application provides a centrifugal fan 10 including a blade group 11, a rear disc 12 and a front disc 13 arranged opposite to each other, wherein the rear disc 12 is recessed toward the blade group 11, and the front disc 13 includes an annular fixing structure 131 and a first extension portion 132, and the ratio of the width of the first extension portion 132 in the radial direction of the centrifugal fan 10 to the outer diameter of the blade group 11 is greater than or equal to 0.03 and less than or equal to 0.05. In this way, by adding the first extension portion 132 to the rear edge of the side of the front disc 13 close to the air outlet, the static pressure of the centrifugal fan 20 can be increased, and at the same time, the airflow output from the air outlet of the centrifugal fan 10 can be reduced from flowing back through the gap channel between the front disc 13 and the fan housing 21, thereby improving the efficiency of the centrifugal fan 20. It can solve the problem that the airflow separation is more likely to occur at the air outlet of the centrifugal fan 10 in the prior art, resulting in the low efficiency of the centrifugal fan 20.

[0073] Please refer to Figure 5 The embodiment of the present application further provides a centrifugal fan 20, which includes a fan housing 21, a centrifugal fan wheel 10 and a drive assembly 22. The centrifugal fan wheel 10 and the drive assembly 22 are installed in the fan housing 21. The drive assembly 22 is connected to the centrifugal fan wheel 10. The centrifugal fan wheel 10 includes the centrifugal fan wheel 10 in any of the above embodiments. The drive assembly 22 may include a motor 221 and a motor cover 222.

[0074] Please refer to Fig.10 and Fig.11 , Fig.10 is a schematic diagram of the structure of an air purification device 30 provided in an embodiment of the present application. Fig.11 yes Fig.10The cross-sectional structural schematic diagram of the air purification device 30 shown in the figure, the embodiment of the present application also provides an air purification device 30, the air purification device 30 may include a device housing 31, a filter structure 32 and a centrifugal fan 20, the centrifugal fan 20 and the filter structure 32 are both installed in the device housing 31, and the centrifugal fan 20 includes the centrifugal fan 20 in the above embodiment. The device housing 31 may have an air inlet grille 311 and an air outlet grille 312. Under the drive of the centrifugal fan 20, the outside air enters the device housing from the air inlet grille 311, passes through the filter structure 32, and then flows through the filter structure 32, enters the centrifugal wind wheel 10 through the collector, and then the airflow is transported to the air outlet grille 312 through the centrifugal wind wheel 10 to achieve air purification.

[0075] Please refer to Fig.12 and Table 1, Fig.12 is a simulation schematic diagram provided in an embodiment of the present application, Fig.12 , a schematic diagram of simulation results of a centrifugal fan 20 in the related art before optimization and a schematic diagram of simulation results of the centrifugal fan 20 in the embodiment of the present application are shown, and the schematic diagram of simulation results of the centrifugal fan 20 in the embodiment of the present application includes a pressure cloud diagram, a velocity cloud diagram and a velocity vector diagram. Table 1 is a performance comparison table of a centrifugal fan 20 in the related art and a centrifugal fan 20 in the embodiment of the present application, the centrifugal fan wheel 10 in the centrifugal fan 20 in the related art and the centrifugal fan wheel 10 in the embodiment of the present application have the first extension part 132 and other structures.

[0076] Table 1

[0077]

[0078] from Fig.11 As can be seen from Table 1, compared with the centrifugal fan 20 in the related art, the centrifugal fan in the embodiment of the present application can reduce the speed by 90 rpm and the shaft power by more than 3 W at the same air volume, and the total pressure efficiency and static pressure efficiency of the centrifugal fan are increased by 1% and 3.1% respectively, and the maximum broadband noise is reduced by 2.6 dB.

[0079] Specifically, it can be seen from the pressure cloud diagram that the centrifugal wind wheel in the embodiment of the present application has a more stable and increasing pressure gradient change in the impeller flow channel without obvious mutation, while the pressure gradient change of the centrifugal wind wheel in the related technology is unstable, which will cause unstable airflow in the impeller flow channel.

[0080] It can be seen from the velocity cloud diagram and the velocity vector diagram that for the centrifugal fan in the embodiment of the present application, the airflow velocity gradually decreases from the inlet to the outlet of the impeller flow channel, and the axial velocity distribution is more uniform, while for the centrifugal fan in the related technology, there is a large mutation in the airflow velocity from the inlet to the outlet of the impeller flow channel, there are local low-speed areas, and there is obvious airflow separation on the trailing edge suction surface m2. Compared with the prior art, the centrifugal fan in the present application has better performance.

[0081] It should be noted that in the accompanying drawings, the size of the region may be exaggerated for clarity of illustration. It is also understood that when an element is referred to as being "on" another element, it may be directly on the other element, or there may be an intermediate element. In addition, it is understood that when an element is referred to as being "under" another element, it may be directly under the other element, or there may be more than one intermediate element. In addition, it is also understood that when an element is referred to as being "between" two elements, it may be the only layer between the two elements, or there may be more than one intermediate element. Similar reference numerals throughout the text indicate similar elements.

[0082] In the present application, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance. The term "plurality" refers to two or more than two, unless otherwise clearly defined.

[0083] The above description is only an optional embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present application should be included.

Claims

1. A centrifugal wind wheel, characterized in that: include: A blade assembly, a rear disc and a front disc arranged oppositely; The blade group is located between the rear disk and the front disk, and an air outlet is formed between the rear disk and the front disk; The rear disc is recessed toward the blade assembly and is fixedly connected to one end of the blade assembly, and the diameter of the rear disc is equal to the outer diameter of the blade assembly; The front disc comprises an annular fixing structure and a first extension portion, wherein the annular fixing structure is fixedly connected to the other end of the blade group, the annular fixing structure has an air inlet, and the first extension portion extends from one end of the annular fixing structure away from the air inlet in a direction away from the blade group, and the first extension portion surrounds the blade group; Wherein, a ratio of a width of the first extension portion in the radial direction of the centrifugal wind wheel to an outer diameter of the blade assembly is greater than or equal to 0.03 and less than or equal to 0.

05.

2. The centrifugal wind 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 is in the range of 0.5 to 0.

55.

3. The centrifugal wind wheel according to claim 1, characterized in that: The blade group includes a plurality of wind rotor blades, wherein the inlet angle of the wind rotor blades close to the air inlet is in the range of 28° to 35°, and the outlet angle of the wind rotor blades close to the air outlet is in the range of 30° to 35°.

4. The centrifugal wind wheel according to claim 3, characterized in that: The wind wheel blade has a first end surface and a suction surface and a pressure surface arranged opposite to each other, wherein the suction surface is located on a side of the pressure surface close to the axis of the centrifugal wind wheel; the pressure surface is a convex surface of the wind wheel blade, and the suction surface is a concave surface of the wind wheel blade; The first end surface is located on a side of the suction surface and the pressure surface close to the front disk, and the first end surface is connected to one end of the suction surface and one end of the pressure surface respectively; The first end surface is an inclined surface and is inclined toward the pressure surface. The angle between the first end surface and the pressure surface is in the range of 30° to 45°.

5. The centrifugal wind wheel according to claim 3, characterized in that: The first air outlet angle of the rear disc close to the air outlet is greater than or equal to the second air outlet angle of the front disc 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 wind wheel according to claim 3, characterized in that: The annular fixing structure includes an annular first air channel portion and an annular second extending portion; The first air channel portion is fixedly connected to the plurality of blades; The second extension portion extends from the inner edge of the first air channel portion in a direction away from the rear disk, and the second extension portion surrounds the air inlet.

7. The centrifugal wind wheel according to claim 3, characterized in that: The rear disc includes a mounting portion and an annular second air duct portion; The second air channel 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 to connect a driving component.

8. The centrifugal wind wheel according to claim 3, characterized in that: The number of the wind wheel blades in the blade group is 9 or 11.

9. A centrifugal fan, characterized in that: The centrifugal fan comprises a fan housing, a centrifugal fan wheel and a drive assembly, wherein the centrifugal fan wheel and the drive assembly are installed in the fan housing, the drive assembly is connected to the centrifugal fan wheel, and the centrifugal fan wheel comprises the centrifugal fan wheel described in any one of claims 1 to 8.

10. An air purification device, characterized in that: The air purification device comprises a device housing, a filter structure and a centrifugal fan. The centrifugal fan and the filter structure are both installed in the device housing. The centrifugal fan comprises the centrifugal fan described in claim 9.

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