A forward and reverse suction and blowing motor

Abstract

The application discloses a positive and negative rotation suction and blowing motor and relates to the technical field of motors. The positive and negative rotation suction and blowing motor comprises a motor body, a fan arranged on the motor body, a fan cover arranged on the fan, a first gas flow channel formed between the fan and the fan cover for gas flow, a first flow channel opening and a second flow channel opening respectively arranged at two ends of the first gas flow channel, a hub, and a plurality of fan blades arranged at the circumferential side of the hub. The fan blades are inclined towards the first flow channel opening along the radial direction of the hub. When the gas flows reversely along the direction from the second flow channel opening to the first flow channel opening, the fan blades inclined towards the first flow channel opening can apply a downward pressure to the reversely flowing gas, so that the wind pressure during the gas flow is increased, the wind volume and the wind speed during the gas flow are improved, and the cleaning effect of the reversely flowing gas on the dust on the fan blades is enhanced.

Description

Technical Field

[0001] This application relates to the field of motor technology, and in particular to a forward and reverse reverse suction and blowing motor. Background Technology

[0002] A fan motor is an electric motor used to create air circulation between the inside and outside of a device; it is commonly used in vacuum cleaners, hair dryers, and other similar devices.

[0003] Existing fan motors include a motor body and a fan mounted on the motor body. The fan has forward and reverse rotation functions. When the motor body drives the fan to rotate forward, the fan can guide the air to flow in the forward direction, and the forward-flowing air can perform operations such as dust suction or blowing. When the motor body drives the fan to rotate in the reverse direction, the fan can guide the air to flow in the reverse direction, and the reverse-flowing air can clean the dust accumulated on the leading edge of the fan blades.

[0004] The inventors believe that although the aforementioned fan motor can achieve the function of blowing air in the opposite direction, due to the conventional vertical structure design between the fan blades and the hub, the air pressure is relatively small when the air flows in the opposite direction, resulting in a small air volume and air speed, which cannot effectively and thoroughly clean the dust on the leading edge of the fan blades. Summary of the Invention

[0005] In order to overcome the shortcomings of the prior art, this application provides a forward and reverse suction and blowing motor that can enhance the cleaning effect of reverse gas on dust.

[0006] The forward and reverse reversible suction and blowing motor provided in this application adopts the following technical solution:

[0007] A forward and reverse suction and blowing motor includes a motor body, a fan disposed on the motor body, and a shroud covering the fan. A first gas flow channel for gas flow is formed between the fan and the shroud. The first gas flow channel has a first flow channel opening and a second flow channel opening at its two ends. The fan includes a hub and a plurality of fan blades spaced apart on the periphery of the hub. The fan blades are inclined along the radial direction of the hub toward the first flow channel opening.

[0008] By adopting the above technical solution, when the gas flows in the opposite direction from the second flow channel to the first flow channel, the fan blades tilted towards the first flow channel can apply downward pressure to the gas flowing in the opposite direction, thereby increasing the wind pressure, increasing the air volume and wind speed, and enhancing the cleaning effect of the reverse-flowing gas on the dust on the fan blades.

[0009] Preferably, the first gas flow channel includes a plurality of flow channel grooves formed between each pair of adjacent fan blades, the openings of the flow channel grooves being inclined radially toward the first flow channel opening along the hub.

[0010] By adopting the above technical solution, when the gas flows in the opposite direction from the second flow channel opening to the first flow channel opening, the flow channel groove inclined towards the first flow channel opening can apply downward pressure to the gas flowing in the opposite direction through its groove wall, thereby increasing the wind pressure when the gas flows, increasing the air volume and wind speed when the gas flows, and enhancing the cleaning effect of the reverse flowing gas on the dust on the fan blades.

[0011] Preferably, the taper of the hub satisfies: arctan((r2-r1) / H1)∈[0°,30°], where r1 is the radius of the end of the hub near the first flow channel opening, r2 is the radius of the end of the hub near the second flow channel opening, and H1 is the axial height of the hub; the taper of the fan satisfies: arctan((d2-d1) / H2)∈[0°,20°], where d1 is the radius of the end of the fan near the first flow channel opening, d2 is the radius of the end of the fan near the second flow channel opening, and H2 is the axial height of the fan.

[0012] By adopting the above technical solution, the taper of the hub and the fan can be matched with the forward and reverse rotation of the fan, ensuring that the forward and reverse rotation suction and blowing motor of this application can smoothly realize the functions of forward rotation suction and reverse rotation blowing.

[0013] Preferably, the fan blade has a blade root connected to the hub and a blade tip away from the hub. The blade tip has a first projection on the hub. The distance between the first projection and the blade root in the axial direction of the hub is A, and the distance between two adjacent fan blades is B, where 0.2 ≤ A / B ≤ 0.8.

[0014] By adopting the above technical solution, it is possible to prevent the tilted fan blades from completely blocking the flow channel groove and affecting the airflow.

[0015] Preferably, the plurality of blade tips have a disc line extending along the direction from the first flow channel opening to the second flow channel opening. The disc line has a first tangent at the end near the first flow channel opening, and the first tangent is parallel to the axis of the fan. The disc line also has a second tangent at the end near the second flow channel opening, and the angle between the second tangent and the axis of the fan is θ1, where θ1 ranges from 4 to 12°.

[0016] By adopting the above technical solution, the input velocity of the gas at the second flow channel opening can be greater than its output velocity at the first flow channel opening, thereby further increasing the air volume when the gas flows in reverse and enhancing the cleaning effect of the reverse-flowing gas on the dust on the fan blades.

[0017] Preferably, the hub side has a hub line extending along the direction from the first flow channel opening to the second flow channel opening, and the expression of the hub line in the plane coordinate system is: y=a*(x-r1). 2 +H1, where r1 is the radius of the end of the hub near the first flow channel opening, H1 is the axial height of the hub, and a is a coefficient.

[0018] By adopting the above technical solution, the hub line that satisfies the above expression can form a smooth parabolic shape, and the gas can flow smoothly along the smooth hub surface, further improving the air volume and wind speed, thereby further enhancing the cleaning effect of the reverse-flowing gas on the dust on the fan blades.

[0019] Preferably, the fan has a β angle, which is the angle between the relative speed and the circumferential speed of the fan when it rotates. The β angle includes a plurality of β1 angles formed on the hub line and a plurality of β2 angles formed on the disc line. The plurality of β1 angles first decrease and then increase along the direction from the first flow channel opening to the second flow channel opening. The first β1 angle near the first flow channel opening is larger than the last β1 angle near the second flow channel opening. The plurality of β2 angles first decrease and then increase along the direction from the first flow channel opening to the second flow channel opening. The first β2 angle near the first flow channel opening is smaller than the last β2 angle near the second flow channel opening, and β1min > β2max.

[0020] By adopting the above technical solution, on the one hand, by designing the angles β1 and β2 to first decrease and then increase along the direction from the first flow channel opening to the second flow channel opening, the wind speed of the gas in the first gas flow channel can be effectively increased; on the other hand, the design of β1min>β2max can reduce the flow loss of the gas in the first gas flow channel and increase the air volume of the gas in the first gas flow channel.

[0021] Preferably, the fan has a wrap angle W, which is a circumferential angle formed between the first flow channel opening and the second flow channel opening when the fan rotates. It includes a first wrap angle W1 formed by the hub line and a second wrap angle W2 formed by the disc line, wherein 140°≤W2<W1≤180° and W1-W2≥10°.

[0022] By adopting the above technical solution, on the one hand, by limiting the parameters of the first wrap angle and the second wrap angle, it is possible to prevent the first wrap angle and the second wrap angle from being too large or too small, thus affecting the flow process of gas in the first gas flow channel; on the other hand, the design of W1-W2≥10° allows for a certain angle difference between the hub line and the disc line, preventing gas loss due to lateral flow.

[0023] Preferably, the fan blade has a leading edge near the first flow channel opening and a trailing edge near the second flow channel opening. The leading edge has a leading edge line extending from one end to the other, and the angle between the leading edge line and the radial plane of the fan is θ2, with the angle range of 5~30°. The trailing edge has a trailing edge line extending from one end to the other, and the angle between the trailing edge line and the radial plane of the fan is θ3, with the angle range of 40~60°.

[0024] By adopting the above technical solution, the angles of the leading edge and the trailing edge can be matched with the forward and reverse rotation of the fan, ensuring that the forward and reverse rotation suction and blowing motor of this application can smoothly realize the functions of forward rotation suction and reverse rotation blowing. At the same time, the larger trailing edge angle can increase the input speed of the gas at the trailing edge, thereby increasing the wind speed when the gas flows in the reverse direction and enhancing the cleaning effect of the reverse flow gas on the dust on the fan blades.

[0025] Preferably, the forward and reverse suction and blowing motor further includes a fixed impeller disposed between the fan and the motor body, and a wheel cover disposed on the fixed impeller. A second gas flow channel for gas flow is formed between the fixed impeller and the wheel cover. A plurality of impeller ribs are provided at intervals on the circumferential side of the fixed impeller. The plurality of impeller ribs have a second projection on the radial plane of the fixed impeller. The length of the second projection is L1, and the distance between two adjacent second projections is L2, wherein 1 / 5L1≤L2≤1 / 2L1.

[0026] By adopting the above technical solution, when the gas flows in the second gas flow channel, the gap between two adjacent impeller ribs can provide a straight passage space for the gas, allowing some gas to pass directly through the straight passage space. This can increase the air volume and wind speed when the gas flows in reverse, and enhance the cleaning effect of the reverse-flowing gas on the dust on the fan blades.

[0027] In summary, the present invention has at least one of the following beneficial technical effects:

[0028] When the gas flows in the opposite direction from the second flow channel opening to the first flow channel opening, the fan blades tilted towards the first flow channel opening can apply downward pressure to the gas flowing in the opposite direction, thereby increasing the wind pressure, increasing the air volume and wind speed, and enhancing the cleaning effect of the reverse-flowing gas on the dust on the fan blades. Attached Figure Description

[0029] Figure 1 This is a schematic diagram of the axial cross-section of the forward and reverse reversible suction and blowing motor in the embodiments of this application;

[0030] Figure 2 This is a schematic outline of the fan in the embodiments of this application. Figure 1 ;

[0031] Figure 3 This is a schematic diagram of the axial cross-section of the fan in an embodiment of this application;

[0032] Figure 4 This is a linear relationship diagram between the ratio of A / B in the embodiments of this application and the airflow volume when the fan rotates in the opposite direction;

[0033] Figure 5 This is a schematic outline of the fan in the embodiments of this application. Figure 2 ;

[0034] Figure 6 This is a linear relationship diagram between the angle θ1 in the embodiments of this application and the vacuum degree when the fan rotates in the forward direction and the airflow volume when the fan rotates in the reverse direction;

[0035] Figure 7 This is a schematic outline of the fan in the embodiments of this application. Figure 3 ;

[0036] Figure 8 This is a triangular schematic diagram of the relative speed and circumferential speed of the fan in the embodiments of this application when it rotates;

[0037] Figure 9 This is a simulation line drawing of the fan β angle in the embodiments of this application;

[0038] Figure 10 This is a simulation line drawing of the fan wrap angle in the embodiments of this application;

[0039] Figure 11 This is a linear relationship diagram between the second wrap angle in this application embodiment and the vacuum degree when the fan rotates in the forward direction and the airflow volume when the fan rotates in the reverse direction;

[0040] Figure 12 This is a linear relationship diagram between the angle θ2 and the ratio of A / B in the embodiments of this application;

[0041] Figure 13 This is a top view of the fixed impeller in an embodiment of this application.

[0042] Marked in the attached diagram:

[0043] 1. Motor body; 2. Fan; 2a. Hub; 2b. Fan blade; 2b1. Blade root; 2b2. Blade tip; 2b3. Leading edge; 2b4. Trailing edge; 2b5. First projection; 3. Fan cover; 4. First gas flow channel; 4a. First flow channel opening; 4b. Second flow channel opening; 4c. Flow channel groove; 5. Impeller line; 6. First tangent; 7. Axis line; 8. Second tangent; 9. Hub line; 10. Leading edge line; 11. Trailing edge line; 12. Fixed impeller; 13. Impeller cover; 14. Second gas flow channel; 15. Impeller ribs; 16. Second projection; 17. Rotating shaft; 18. Vertical ribs; 19. Fan cover line. Detailed Implementation

[0044] The following is in conjunction with the appendix Figure 1-13 The present invention will be described in further detail below.

[0045] In the description of this invention, it should be understood that the orientation descriptions, such as up, down, front, back, left, right, etc., are based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting this invention.

[0046] See Figure 1 As shown, a forward and reverse suction and blowing motor is shown, including a motor body 1, a fan 2 disposed on the motor body 1, and a fan cover 3 disposed on the fan 2. The fan 2 is rotatably connected to the motor body 1, and the fan cover 3 is fixedly connected to the motor body 1.

[0047] The motor body 1 has a rotating shaft 17 coaxially mounted on it, and the fan 2 is coaxially sleeved on the end of the rotating shaft 17. The motor body 1 can drive the rotating shaft 17 to rotate. The fan 2 includes a hub 2a coaxially mounted on the rotating shaft 17 and a plurality of fan blades 2b spaced apart on the periphery of the hub 2a. A first gas flow channel 4 for gas flow is formed between the fan 2 and the fan cover 3. The first gas flow channel 4 has a first flow channel opening 4a and a second flow channel opening 4b at both ends.

[0048] The forward and reverse suction and blowing motor of this application has a suction state and a blowing state. When the fan 2 rotates in the forward direction, the suction and blowing motor is in the suction state, and the gas flows in the forward direction from the first flow channel 4a to the second flow channel 4b. At this time, the suction and blowing motor can complete the dust suction operation. When the fan 2 rotates in the reverse direction, the suction and blowing motor is in the blowing state, and the gas flows in the reverse direction from the second flow channel 4b to the first flow channel 4a. During the reverse flow, the gas can clean the dust in the first gas flow channel 4, thereby effectively eliminating the dust accumulated on the fan blades 2b of the fan 2.

[0049] In this embodiment, the fan blade 2b is inclined radially toward the first flow channel opening 4a along the hub 2a. Furthermore, the first gas flow channel 4 includes a plurality of flow channel grooves 4c formed between each pair of adjacent fan blades 2b, and the openings of the flow channel grooves 4c are inclined radially toward the first flow channel opening 4a along the hub 2a.

[0050] In this way, when the gas flows in the opposite direction from the second flow channel 4b to the first flow channel 4a, the fan blade 2b and the flow channel groove 4c, which are inclined towards the first flow channel 4a, can apply downward pressure to the gas flowing in the opposite direction, thereby increasing the wind pressure, increasing the air volume and wind speed, and enhancing the cleaning effect of the gas flowing in the opposite direction on the dust on the fan blade 2b.

[0051] In this embodiment, combined with Figure 1-2 As shown, the taper of hub 2a satisfies: arctan((r2-r1) / H1)∈[0°,30°], where r1 is the radius of the end of hub 2a near the first flow channel opening 4a, r2 is the radius of the end of hub 2a near the second flow channel opening 4b, and H1 is the axial height of hub 2a; the taper of fan 2 satisfies: arctan((d2-d1) / H2)∈[0°,20°], where d1 is the radius of the end of fan 2 near the first flow channel opening 4a, d2 is the radius of the end of fan 2 near the second flow channel opening 4b, and H2 is the axial height of fan 2. According to simulation results, the tapers of hub 2a and fan 2 that satisfy the above relationships can match the forward and reverse rotation conditions of fan 2, ensuring that the forward and reverse rotation suction and blowing motor of this application can smoothly realize the functions of forward rotation suction and reverse rotation blowing.

[0052] In this embodiment, combined with Figure 3 As shown, the fan blade 2b has a blade root 2b1 connected to the hub 2a and a blade tip 2b2 away from the hub 2a. The blade tip 2b2 has a first projection 2b5 on the hub 2a. The distance between the first projection 2b5 and the blade root 2b1 in the axial direction of the hub 2a is A. The distance between two adjacent fan blades 2b is B. This B is the width of the flow channel groove 4c. A and B satisfy 0.2≤A / B≤0.8. This can prevent the tilted fan blade from completely blocking the flow channel groove 4c and affecting the airflow.

[0053] Combination Figure 4 As shown in the figure, the simulation experiment relationship between the A / B ratio and the air volume when the gas flows in reverse is illustrated. According to the simulation results, the air volume is optimal when the A / B ratio is between 0.2 and 0.8.

[0054] In this embodiment, combined with Figure 1 and Figure 5As shown, there are multiple blade tips 2b2 with a disc line 5 extending along the direction from the first flow channel opening 4a to the second flow channel opening 4b. The disc line 5 has a first tangent 6 at the end near the first flow channel opening 4a, which is parallel to the axis 7 of the fan 2. The disc line 5 has a second tangent 8 at the end near the second flow channel opening 4b, and the angle between the second tangent 8 and the axis 7 of the fan 2 is θ1, which has a range of 4~12°.

[0055] When the gas flows in reverse, its input velocity at the second flow channel inlet 4b can be greater than its output velocity at the first flow channel inlet 4a, thereby further increasing the airflow during reverse flow and enhancing the cleaning effect of the reverse-flowing gas on the dust on the fan blade 2b. Combined with... Figure 6 As shown, the linear relationship between angle θ1 and the vacuum level when fan 2 rotates forward and the airflow when fan 2 rotates in reverse is illustrated. According to the simulation results, when angle θ1 is between 4 and 12°, both the vacuum level when fan 2 rotates forward and the airflow when fan 2 rotates in reverse are relatively high. If the value of θ1 is less than 4°, the vacuum level when fan 2 rotates forward is too low, and the dust suction function cannot be effectively achieved. If the value of θ1 is greater than 12°, the airflow when fan 2 rotates in reverse is too low, and the dust on the fan blade 2b cannot be effectively cleaned.

[0056] Furthermore, in combination Figure 1 and Figure 7 As shown, the wheel line 5 adopts a Bézier curve design, and correspondingly, the hood line 19 on the inner wall of the hood 3 also adopts a Bézier curve design. Designing both the wheel line 5 and the hood line 19 on the inner wall of the hood 3 as Bézier curves effectively ensures the airtightness of the suction motor during forward and reverse rotation. The hood line 19 on the inner wall of the hood 3 is obtained by offsetting the wheel line 5 by a distance δ, where δ ranges from 0.1 to 1.0 mm. According to simulation results, when δ is within this range, the suction motor exhibits the best airtightness during forward and reverse rotation.

[0057] In this embodiment, combined again Figure 2 As shown, the hub 2a has a hub line 9 extending along the direction from the first flow channel opening 4a to the second flow channel opening 4b. The expression of the hub line 9 in the plane coordinate system is: y = a*(x-r1)² + H1, where r1 is the radius of the end of the hub 2a closest to the first flow channel opening 4a, H1 is the axial height of the hub 2a, and a is a mathematical coefficient. The hub line 9, which satisfies the above expression, can form a smooth parabolic shape, allowing gas to flow smoothly along the smooth surface of the hub 2a, further increasing the airflow and velocity, thereby further enhancing the cleaning effect of the reverse-flowing gas on the dust on the fan blade 2b.

[0058] In this embodiment, fan 2 has a β angle. Combined with Figure 8 As shown, angle β is the angle between the relative velocity ω and the circumferential velocity u of fan 2 when it rotates. The relative velocity ω and the circumferential velocity u of fan 2 can be combined to form the absolute velocity c. The specific definitions and principles of the relative velocity ω, circumferential velocity u, absolute velocity c, and angle β of fan 2 are existing technologies and will not be elaborated here.

[0059] Combination Figure 9 As shown, the β angle of this application includes a plurality of β1 angles formed on the hub line 9 and a plurality of β2 angles formed on the disc line 5. The plurality of β1 angles first decrease and then increase along the direction from the first flow channel opening 4a to the second flow channel opening 4b. The first β1 angle near the first flow channel opening 4a is larger than the last β1 angle near the second flow channel opening 4b. The plurality of β2 angles first decrease and then increase along the direction from the first flow channel opening 4a to the second flow channel opening 4b. The first β2 angle near the first flow channel opening 4a is smaller than the last β2 angle near the second flow channel opening 4b, and β1min > β2max.

[0060] Based on the above design, on the one hand, by designing the angles β1 and β2 to first decrease and then increase along the direction from the first flow channel opening 4a to the second flow channel opening 4b, the wind speed of the gas in the first gas flow channel 4 can be effectively increased; on the other hand, according to the simulation results, the design of β1min>β2max can reduce the flow loss of the gas in the first gas flow channel 4 and increase the air volume of the gas in the first gas flow channel 4.

[0061] In this embodiment, the fan 2 has a wrap angle W, which is the circumferential angle formed between the first flow channel opening 4a and the second flow channel opening 4b when the fan 2 rotates. The specific definition and principle of this wrap angle W are existing technologies and will not be elaborated here. Figure 10 As shown, the wrap angle W includes a first wrap angle W1 formed by the hub line 9 and a second wrap angle W2 formed by the disc line 5, wherein 140°≤W2<W1≤180° and W1-W2≥10°.

[0062] Based on the above design, on the one hand, by limiting the parameters of the first wrap angle W1 and the second wrap angle W2, it is possible to prevent the first wrap angle W1 and the second wrap angle W2 from being too large or too small, thus affecting the flow process of gas in the first gas flow channel 4; on the other hand, the design of W1-W2≥10° allows for a certain angle difference between the hub line 9 and the disc line 5, preventing gas loss due to lateral flow.

[0063] Combination Figure 11As shown, the linear relationship between the second wrap angle W2 and the vacuum level when fan 2 rotates forward and the airflow volume when fan 2 rotates in reverse is illustrated. According to simulation results, the value of angle W2 is positively correlated with the airflow volume when fan 2 rotates in reverse and negatively correlated with the vacuum level when fan 2 rotates forward. Therefore, when 140°≤W2≤180°, both the vacuum level when fan 2 rotates forward and the airflow volume when fan 2 rotates in reverse are optimal.

[0064] In this embodiment, combined with Figure 3 and Figure 5 As shown, the fan blade 2b has a leading edge 2b3 near the first flow channel opening 4a and a trailing edge 2b4 near the second flow channel opening 4b. The leading edge 2b3 has a leading edge line 10 extending from one end to the other. The angle between the leading edge line 10 and the radial plane of the fan 2 is θ2, and the angle range of θ2 is 5~30°.

[0065] The trailing edge 2b4 has a trailing edge line 11 extending from one end to the other, and the angle between the trailing edge line 11 and the radial plane of the fan 2 is θ3, with the angle range of θ3 being 40~60°. According to simulation results, the above-mentioned angle range of the leading edge 2b3 and the trailing edge 2b4 can match the forward and reverse rotation conditions of the fan 2, ensuring that the forward and reverse rotation suction and blowing motor of this application can smoothly realize the functions of forward rotation suction and reverse rotation blowing; at the same time, the larger angle θ3 can increase the input speed of the gas at the trailing edge 2b4, thereby increasing the wind speed when the gas flows in the reverse direction and enhancing the cleaning effect of the reverse flow gas on the dust on the fan blade 2b.

[0066] Combination Figure 12 As shown, the linear relationship between angle θ2 and the ratio of A / B is illustrated. According to simulation results, when the angle θ2 is in the range of 5~30°, the ratio of A / B can be between 0.2 and 0.8, at which point the airflow is optimal for reverse gas flow.

[0067] In this embodiment, combined with Figure 1 and Figure 13 As shown, the forward and reverse suction and blowing motor also includes a fixed impeller 12 disposed between the fan 2 and the motor body 1, a wheel cover 13 covering the fixed impeller 12, a rotating shaft 17 passing through the fixed impeller 12 and rotatably connected to the fixed impeller 12, a second gas flow channel 14 for gas flow is formed between the fixed impeller 12 and the wheel cover 13, the second gas flow channel 14 is connected to the first gas flow channel 4, a plurality of impeller ribs 15 are provided at intervals on the periphery of the fixed impeller 12, the plurality of impeller ribs 15 have a second projection 16 on the radial plane of the fixed impeller 12, the length of the second projection 16 is L1, the distance between two adjacent second projections 16 is L2, wherein 1 / 5L1≤L2≤1 / 2L1.

[0068] In this way, when the gas flows within the second gas flow channel 14, the gap between two adjacent impeller ribs 15 provides a direct passage for the gas, allowing some gas to pass directly through this space. This increases the airflow and velocity during reverse flow, enhancing the cleaning effect of the reverse-flowing gas on the dust on the fan blades 2b. According to simulation results, the optimal direct passage effect is achieved when the distance between L1 and L2 satisfies 1 / 5L1≤L2≤1 / 2L1.

[0069] In this embodiment, combined again Figure 1 As shown, the impeller 12 near the end of the fan 2 is provided with two concentric vertical ribs 18. The end of the hub 2a is accommodated between the two vertical ribs 18, and the height of the inner vertical rib 18 is greater than the height of the outer vertical rib 18. In this way, the two vertical ribs 18 and the end of the hub 2a form a wedge-shaped structure, which can prevent the gas from flowing back with the outside atmosphere at the end of the hub 2a, effectively improving the work capacity of the fan 2.

[0070] The implementation principle of the forward and reverse suction and blowing motor in this embodiment is as follows:

[0071] When the motor body 1 is connected to the power supply, the rotating shaft 17 drives the fan 2 to rotate in the forward direction. At this time, the suction motor is in the suction state. The gas enters the first gas flow channel 4 from the first flow channel port 4a, then enters the second gas flow channel 14 through the second flow channel port 4b, and finally exits from the rear end of the second gas flow channel 14.

[0072] The rotating shaft 17 drives the fan 2 to rotate in the opposite direction, and the suction and blowing motor is in the blowing state. The gas enters the second flow channel port 4b from the rear end of the second gas flow channel 14, then enters the first gas flow channel 4 through the second flow channel port 4b, and finally carries the dust out from the first flow channel port 4a.

[0073] The embodiments described herein are preferred embodiments of the present invention and are not intended to limit the scope of protection of the present invention. Therefore, all equivalent changes made in accordance with the structure, shape, and principle of the present invention should be covered within the scope of protection of the present invention.

Claims

1. A positive and negative rotation blowing and sucking motor, comprising a motor body (1), a fan (2) arranged on the motor body (1), a fan cover (3) arranged on the fan (2), a first gas flow channel (4) formed between the fan (2) and the fan cover (3) for gas flow, the first gas flow channel (4) having a first flow channel opening (4a) and a second flow channel opening (4b) at two ends respectively, and the fan (2) comprising a hub (2a) and a plurality of fan blades (2b) arranged at intervals on the circumferential side of the hub (2a), characterized in that: The fan blade (2b) is inclined along the radial direction of the hub (2a) towards the first flow passage opening (4a). The fan blade (2b) has a leading edge (2b3) near the first flow passage opening (4a) and a trailing edge (2b4) near the second flow passage opening (4b), the leading edge (2b3) has a leading edge line (10) extending along the direction from one end to the other end, the angle between the leading edge line (10) and the radial plane of the fan (2) is θ2, and the angle θ2 ranges from 5° to 30°; the trailing edge (2b4) has a trailing edge line (11) extending along the direction from one end to the other end, the angle between the trailing edge line (11) and the radial plane of the fan (2) is θ3, and the angle θ3 ranges from 40° to 60°.

2. A positive and negative rotation suction blower motor according to claim 1, characterized in that: The first gas flow passage (4) comprises a plurality of flow passage grooves (4c) respectively formed between every two adjacent fan blades (2b), and the groove opening of the flow passage groove (4c) is inclined along the radial direction of the hub (2a) towards the first flow passage opening (4a).

3. A positive and reverse rotation suction blower motor as claimed in claim 1 wherein: The taper of the hub (2a) satisfies arctan((r2-r1) / H1)∈[0°,30°], wherein r1 is the radius of one end of the hub (2a) near the first flow passage opening (4a), r2 is the radius of one end of the hub (2a) near the second flow passage opening (4b), and H1 is the axial height of the hub (2a); the taper of the fan (2) satisfies arctan((d2-d1) / H2)∈[0°,20°], wherein d1 is the radius of one end of the fan (2) near the first flow passage opening (4a), d2 is the radius of one end of the fan (2) near the second flow passage opening (4b), and H2 is the axial height of the fan (2).

4. A positive-reverse rotation suction blower motor according to any one of claims 1-3, characterized in that: The fan blade (2b) has a blade root (2b1) connected to the hub (2a) and a blade tip (2b2) away from the hub (2a), the blade tip (2b2) has a first projection (2b5) on the hub (2a), the distance between the first projection (2b5) and the blade root (2b1) in the axial direction of the hub (2a) is A, the distance between two adjacent fan blades (2b) is B, and 0.2≤A / B≤0.

8.

5. A positive-reverse rotation suction blower motor according to claim 4, characterized in that: A plurality of blade tips (2b2) have a wheel disc line (5) extending along the direction from the first flow passage opening (4a) to the second flow passage opening (4b), one end of the wheel disc line (5) near the first flow passage opening (4a) has a first tangent line (6) parallel to the axial center line (7) of the fan (2); one end of the wheel disc line (5) near the second flow passage opening (4b) has a second tangent line (8), the angle between the second tangent line (8) and the axial center line (7) of the fan (2) is θ1, and the angle θ1 ranges from 4° to 12°.

6. A positive-reverse rotation suction blower motor according to claim 5, characterized in that: The hub (2a) side has a hub line (9) extending along the direction from the first flow port (4a) to the second flow port (4b), and the expression of the hub line (9) in the plane coordinate system is: y=a*(x-r1)2+H1, wherein r1 is the radius of the end of the hub (2a) close to the first flow port (4a), H1 is the axial height of the hub (2a), and a is a coefficient.

7. A positive-reverse rotation suction blower motor according to claim 6, characterized in that: The fan (2) has a β angle, which is the included angle between the relative velocity and the circumferential velocity when the fan (2) rotates, and includes a plurality of β1 angles formed on the hub line (9) and a plurality of β2 angles formed on the disc line (5). The plurality of β1 angles first decrease and then increase along the direction from the first flow port (4a) to the second flow port (4b), the first β1 angle close to the first flow port (4a) is greater than the last β1 angle close to the second flow port (4b), the plurality of β2 angles first decrease and then increase along the direction from the first flow port (4a) to the second flow port (4b), the first β2 angle close to the first flow port (4a) is less than the last β2 angle close to the second flow port (4b), and β1min>β2max.

8. A positive-reverse rotation suction blower motor according to claim 6, characterized in that: The fan (2) has a wrap angle W, which is the circumferential angle formed between the first flow port (4a) and the second flow port (4b) when the fan (2) rotates, and includes a first wrap angle W1 formed by the hub line (9) and a second wrap angle W2 formed by the disc line (5), wherein 140°≤W2 9. A positive-reverse rotation suction blower motor according to any one of claims 1-3, characterized in that: The forward-reverse suction blowing motor further comprises a stationary impeller (12) arranged between the fan (2) and the motor body (1), and a wheel cover (13) arranged on the stationary impeller (12), and a second gas flow channel (14) for gas flow is formed between the stationary impeller (12) and the wheel cover (13). A plurality of impeller ribs (15) are arranged at intervals on the peripheral side of the stationary impeller (12), and the plurality of impeller ribs (15) have a second projection (16) on the radial plane of the stationary impeller (12), the length of the second projection (16) is L1, and the distance between adjacent two second projections (16) is L2, wherein 1 / 5L1≤L2≤1 / 2L1.

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