Impeller assembly and blowing equipment

Abstract

The invention discloses an impeller assembly and blowing equipment, and relates to the technical field of blowing equipment, the impeller assembly comprises an impeller assembly and at least one dynamic balance adjusting assembly, and the impeller assembly comprises a driving shaft and fan blades fixedly arranged on the driving shaft; the dynamic balance adjusting assembly comprises a fixed part and a rotating part, the fixed part is fixedly arranged on the driving shaft, the rotating part is rotationally arranged on the fixed part in a sleeving mode and can rotate around the driving shaft, damping force exists between the rotating part and the fixed part, and the mass center of the rotating part deviates from the rotating center of the driving shaft; when the driving shaft moves at variable speed, the angular speed of the rotating part changes under the action of damping force, the angular speed change lags behind the angular speed change of the driving shaft, and when the driving shaft rotates at constant speed, the rotating part overcomes the damping force under the driving of the centrifugal force of the rotating part and moves to the balance compensation position of the movable impeller assembly relative to the fixed part. In the application, the vibration of the blowing equipment can be effectively inhibited, and the operation stability and the structural durability are improved.

Description

Technical Field

[0001] This invention relates to the field of blower technology, and particularly to an impeller assembly and blower. Background Technology

[0002] In traditional fan systems, such as ordinary fans, the structure typically consists of a central column placed on the ground with the fan head at the top. This results in a relatively high center of gravity. When the fan blades at the top of the fan head rotate under the drive of the motor, the high center of gravity can cause a significant initial imbalance within the fan head itself, leading to vibration during operation. For some adjustable fan products, such as those with variable pitch blades, the rotating components contain multiple moving parts. The imbalance vector is not only constrained by manufacturing and assembly precision but also dynamically changes with the pitch adjustment, further complicating the dynamic balancing problem.

[0003] In related technologies, traditional blower equipment mostly uses integral fan blades. Due to the limitations of the molding process, the dynamic balance characteristics are difficult to control precisely, and it is difficult to cope with the initial imbalance caused by the high center of gravity. For adjustable fan blades such as variable pitch, the traditional fixed mass correction method cannot adapt to their dynamically changing working conditions, resulting in the equipment facing significant vibration challenges in different working states. Summary of the Invention

[0004] The main objective of this invention is to provide an impeller assembly and a blower device, which aims to solve the vibration problem caused by the dynamic imbalance of rotating parts in the blower device.

[0005] To achieve the above objectives, the present invention proposes an impeller assembly, which includes:

[0006] An impeller assembly, including a drive shaft and fan blades disposed on the drive shaft; At least one dynamic balance adjustment component includes a fixed component and a rotating component. The fixed component is fixedly disposed on the drive shaft. The rotating component is rotatably sleeved on the fixed component and can rotate around the drive shaft. There is a damping force between the rotating component and the fixed component. The center of mass of the rotating component is offset from the rotation center of the drive shaft. When the drive shaft moves at a variable speed, the angular velocity of the rotating component changes under the action of the damping force, and its angular velocity change lags behind the angular velocity change of the drive shaft. When the drive shaft rotates at a constant speed, the rotating component overcomes the damping force under its own centrifugal force and moves relative to the fixed component to the dynamic balance compensation position of the impeller assembly.

[0007] In one embodiment, the rotating member includes: The sleeve body is rotatably fitted onto the fixing member and has a damping force between it and the fixing member; and A counterweight is fixedly mounted on the sleeve, and the center of mass of the counterweight is offset from the rotation center of the drive shaft.

[0008] In one embodiment, a damping structure is provided between the fixing member and the sleeve; The damping structure includes a viscous medium filling the contact interface between the two and / or a rolling element disposed between the two.

[0009] In one embodiment, the counterweight is integrally formed; or The counterweight includes a fixed bracket and a counterweight part, wherein the fixed bracket is disposed on the sleeve body; and the counterweight part is detachably disposed on the fixed bracket.

[0010] In one embodiment, the number of the dynamic balancing adjustment components is set to multiple, and the multiple dynamic balancing adjustment components are distributed at intervals along the axial direction of the drive shaft.

[0011] In one embodiment, the impeller assembly further includes: The fan blade holder is fixedly sleeved on the output shaft, and the fan blade is rotatably connected to the outer periphery of the fan blade holder.

[0012] The present invention also proposes an impeller assembly, the impeller assembly comprising: An impeller assembly, including a drive shaft and fan blades disposed on the drive shaft; At least one dynamic balance adjustment component includes a rotating member rotatably mounted on the drive shaft, a damping force between the rotating member and the drive shaft, and the center of mass of the rotating member being offset from the rotation center of the drive shaft. When the drive shaft moves at a variable speed, the angular velocity of the rotating component changes under the action of the damping force, and its angular velocity change lags behind the angular velocity change of the drive shaft. When the drive shaft rotates at a constant speed, the rotating component overcomes the damping force under its own centrifugal force and moves relative to the drive shaft to the dynamic balance compensation position of the impeller assembly.

[0013] The present invention also proposes a blower device, the blower device comprising: The impeller assembly as described in any one of claims 1 to 7; A drive assembly having opposite sides along the axial direction of the drive shaft, the drive shaft being disposed on one of the sides; and The mounting base is located on the other side of the drive assembly.

[0014] In one embodiment, the blower further includes: At least one elastic connector is connected between the drive assembly and the mounting base and is capable of elastic deformation between the two.

[0015] In one embodiment, the stiffness of the elastic connector in the axial direction of the drive shaft is less than its stiffness in the radial direction of the drive shaft.

[0016] In one embodiment, the mounting base is provided with a support portion at a position corresponding to the elastic connector, and the support portion extends along the axial direction of the drive shaft; The elastic connector includes: A sleeve, fitted onto the outside of the support portion and extending axially along the drive shaft, the sleeve being capable of elastic deformation in the axial direction of the drive shaft; and Multiple support blocks are fixedly disposed on the inner wall of the sleeve and in contact with the support portion; The sleeve is fixedly connected to the drive assembly.

[0017] In one embodiment, the support portion is disposed on one side of the drive assembly in the radial direction of the drive shaft; At least two of the support blocks are located on the line connecting the midpoint of the support portion and the rotation center of the drive shaft.

[0018] In one embodiment, one of the elastic connector and the mounting base is provided with a positioning protrusion, and the other is provided with a positioning groove; The positioning groove engages with the positioning protrusion so that at least two of the support blocks in the elastic connector are located on the line connecting the midpoint of the support portion and the rotation center of the drive shaft.

[0019] In one embodiment, at least a portion of the periphery of the sleeve is recessed to form a mounting groove for at least a portion of the drive assembly to be inserted.

[0020] In one embodiment, the driving component includes: A motor is located on one side of the mounting base along the axial direction of the drive shaft, and the rotor of the motor is drively connected to the drive shaft; and A mounting bracket is provided on the side of the motor away from the mounting base, and at least a portion of the mounting bracket is embedded in the mounting groove.

[0021] In one embodiment, the elastic connector further includes: A connecting portion is provided at one end of the sleeve away from the mounting base and covers the inner cavity of the sleeve. The connecting portion is provided with a through hole for fasteners to pass through. At least a portion of the connecting portion is located between the fastener and the mounting base.

[0022] In one embodiment, the other end of the sleeve abuts against the mounting base; The sleeve is provided with at least one opening to connect the inner cavity of the sleeve with the external environment.

[0023] In the technical solution of this application, a damping force is provided between the rotating component and the fixed component. This ensures that when the fixed component accelerates or decelerates with the drive shaft, the angular velocity change of the rotating component lags behind that of the fixed component, and then gradually approaches the angular velocity of the fixed component. Since the rotating component can be driven to rotate together with the fixed component, and can also be freely adjusted circumferentially relative to the fixed component, when the drive shaft enters a uniform operating state, the centrifugal force inherent in the rotating component will continuously overcome the damping force, causing it to automatically move to the rotor's dynamic balance compensation position, and maintain stable rotation at this position. This design enables the blower to automatically respond to and compensate for dynamic imbalances caused by manufacturing tolerances, blade angle adjustments, or long-term wear without relying on external control, thereby effectively suppressing vibration of the blower and improving operational stability and structural durability. Attached Figure Description

[0024] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0025] Figure 1 This is a partial structural schematic diagram of a blower device according to an embodiment of the present invention; Figure 2 A schematic diagram of the assembly of an impeller assembly and a motor according to an embodiment of the present invention; Figure 3 A schematic diagram of the assembly of the impeller assembly and the motor according to another embodiment of the present invention; Figure 3A A cross-sectional view of an impeller assembly and a motor according to an embodiment of the present invention; Figure 4 A schematic diagram of the assembly of the impeller assembly and the motor according to another embodiment of the present invention; Figure 5 A schematic diagram of the assembly of the impeller assembly and the motor according to another embodiment of the present invention; Figure 6 A schematic diagram of the assembly of the impeller assembly and the motor according to another embodiment of the present invention; Figure 7 A partial exploded structural diagram of a blower device according to an embodiment of the present invention; Figure 8 A partial front view of a blower device according to an embodiment of the present invention is shown in the schematic diagram. Figure 9 for Figure 8 A schematic cross-sectional view of the structure at point AA. Figure 10 A schematic diagram of the structure of an elastic connector according to an embodiment of the present invention; Figure 11 A cross-sectional view of an elastic connector according to an embodiment of the present invention; Figure 12 This is a partial front view of a blower device according to another embodiment of the present invention.

[0026] Explanation of icon numbers: 1. Impeller assembly; 11. Drive shaft; 12. Fan blade; 2. Dynamic balance adjustment assembly; 21. Fixing component; 22. Rotating component; 221. Sleeve; 222. Counterweight; 2221. Fixed bracket; 2222. Counterweight part; 3. Drive assembly; 31. Motor; 32. Mounting bracket; 4. Mounting base; 41. Support part; 5. Elastic connector; 51. Sleeve; 52. Support block; 53. Connecting part; 531. Through hole; 6. Positioning protrusion; 7. Positioning groove; 8. Mounting groove; 9. Fastener; 91. Screw; 92. Washer; 10. Opening.

[0027] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0028] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0029] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0030] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0031] In traditional fan systems, such as ordinary fans, the structure typically consists of a central column placed on the ground with the fan head at the top. This results in a relatively high center of gravity. When the fan blades at the top of the fan head rotate under the drive of the motor, the high center of gravity can cause a significant initial imbalance within the fan head itself, leading to vibration during operation. For some adjustable fan products, such as those with variable pitch blades, the rotating components contain multiple moving parts. The imbalance vector is not only constrained by manufacturing and assembly precision but also dynamically changes with the pitch adjustment, further complicating the dynamic balancing problem.

[0032] In related technologies, traditional blower equipment mostly uses integral fan blades. Due to the limitations of the molding process, the dynamic balance characteristics are difficult to control precisely, and it is difficult to cope with the initial imbalance caused by the high center of gravity. For adjustable fan blades such as variable pitch, the traditional fixed mass correction method cannot adapt to their dynamically changing working conditions, resulting in the equipment facing significant vibration challenges in different working states.

[0033] In view of this, firstly, this application proposes an impeller assembly, Figures 1 to 6 This is the first implementation of the impeller assembly.

[0034] Please see Figures 1 to 2In some embodiments of this application, the impeller assembly includes an impeller assembly 1 and at least one dynamic balance adjustment assembly 2. The impeller assembly 1 includes a drive shaft 11 and fan blades 12 disposed on the drive shaft 11. The dynamic balance adjustment assembly 2 includes a fixed member 21 and a rotating member 22. The fixed member 21 is fixedly disposed on the drive shaft 11, and the rotating member 22 is rotatably sleeved on the fixed member 21 and can rotate around the drive shaft 11. There is a damping force between the rotating member 22 and the fixed member 21, and the center of mass of the rotating member 22 is offset from the rotation center of the drive shaft 11. When the drive shaft 11 moves at a variable speed, the angular velocity of the rotating member 22 changes under the action of the damping force, and its angular velocity change lags behind the angular velocity change of the drive shaft 11. When the drive shaft 11 rotates at a constant speed, the rotating member 22 overcomes the damping force under the drive of its own centrifugal force and moves relative to the fixed member 21 to the dynamic balance compensation position.

[0035] In the technical solution of this application, a damping force is provided between the rotating component 22 and the fixed component 21, so that when the fixed component 21 accelerates or decelerates with the drive shaft 11, the change in angular velocity of the rotating component 22 lags behind the change in angular velocity of the fixed component 21, and then gradually approaches the angular velocity of the fixed component 21. Since the rotating component 22 can be driven to rotate together with the fixed component 21, and can also be freely adjusted circumferentially relative to the fixed component 21, when the drive shaft 11 enters a uniform speed running state, the centrifugal force of the rotating component 22 itself will continuously overcome the damping force, causing it to automatically move to a dynamic balance compensation position that can offset the unbalanced centrifugal force of the impeller assembly 1, and maintain stable rotation at this dynamic balance compensation position. This design enables the blower to automatically respond to and compensate for dynamic imbalance changes caused by manufacturing tolerances, blade angle adjustment, or long-term wear without relying on external control, thereby effectively suppressing the vibration of the blower and improving the smoothness of operation and structural durability.

[0036] It should be further explained that when the impeller assembly 1 is in a constant speed operation state, its speed must exceed the critical speed for the dynamic balance adjustment component 2 to work effectively; that is, when the speed of the impeller assembly 1 exceeds the critical speed, the impeller assembly 1 enters an automatic centering state. At this time, the rotating part 22 in the dynamic balance adjustment component 2, driven by centrifugal force, can overcome the damping force between itself and the fixed part 21, and automatically move to the balance compensation position opposite to the phase of the unbalance vector of the impeller assembly 1, so as to realize real-time dynamic balance adaptive adjustment.

[0037] Specifically, when the impeller assembly has only one dynamic balancing adjustment component 2, the imbalance vector of the impeller assembly 1 is U1, and the imbalance vector of the dynamic balancing adjustment component 2 is U2. After the impeller assembly 1 exceeds the critical speed and enters the automatic centering state, the rotating component 22 will adaptively adjust to make U2 and U1 have opposite directions. At this time, the specific residual imbalance of the entire impeller assembly is the vector sum of U2 and U1, with an amplitude of |U1-U2| and a direction pointing to the larger of U2 and U1, thereby effectively suppressing the vibration of the blowing equipment and improving the operational stability and structural durability.

[0038] Furthermore, the center of mass of the fixing member 21 may be offset from the rotation center of the drive shaft 11 or coincide with the rotation center of the drive shaft 11, without any limitation.

[0039] In some embodiments of this application, the rotating component 22 includes a sleeve 221 and a counterweight 222. The sleeve 221 is rotatably fitted onto the fixed component 21 and has a damping force between it and the fixed component 21. The counterweight 222 is fixedly mounted on the sleeve 221, and the center of mass of the counterweight 222 is offset from the rotation center of the drive shaft 11. In this embodiment, the sleeve 221 is rotatably fitted onto the fixed component 21, and a damping structure providing damping force is provided between the sleeve 221 and the fixed component 21. The counterweight 222 is fixedly mounted on the sleeve 221, and its center of mass is configured to be offset from the rotation center of the drive shaft 11. This structure allows for flexible setting of the unbalance vector U2 of the dynamic balance adjustment component 2 by changing or adjusting the mass and position of the counterweight 222, thereby adapting to the compensation requirements of the unbalance vector U1 of impeller components 1 of different specifications, and enhancing the configurability and applicability of the dynamic balance adjustment component 2.

[0040] It should be noted that when the blower has multiple working speeds, it is necessary to ensure that the speed of the drive shaft 11 exceeds the critical speed when the blower is in the lowest working speed, so that the adaptive adjustment of dynamic balance can be achieved when the blower is in any working speed.

[0041] In some embodiments of this application, a damping structure is provided between the fixing member 21 and the sleeve 221. The damping structure includes a viscous medium filled between the contact interface of the two. The viscous medium allows the fixing member 21 to effectively drive the rotating member 22 to rotate along with the drive shaft 11 through the viscous shear force of the viscous medium. At the same time, the viscous shear force also constitutes the damping force between the rotating member 22 and the fixing member 21, ensuring that the angular velocity change of the rotating member 22 lags behind that of the fixing member 21 during the acceleration or deceleration phase of the drive shaft 11. When the drive shaft 11 enters uniform rotation, the rotating member 22 can overcome the damping force under the drive of its own centrifugal force, thereby accurately and automatically adjusting to the dynamic balance compensation position.

[0042] The type of viscous medium is not limited; it can be grease, damping grease, lubricating grease, etc.

[0043] In some embodiments of this application, a damping structure is provided between the fixing member 21 and the sleeve 221. The damping structure includes a rolling element disposed between the two. The rolling element converts the relative motion between the fixing member 21 and the sleeve 221 from sliding friction to rolling friction. While significantly reducing motion resistance, it can still provide damping force through the slight resistance between the rolling contact interface of the rolling element and the fixing member 21 and the sleeve 221 or the preset lubricant viscosity. This ensures that during the acceleration or deceleration phase of the drive shaft 11, the angular velocity change of the rotating member 22 will lag behind that of the fixing member 21. When the drive shaft 11 enters uniform rotation, the rotating member 22 can overcome the damping force under the drive of its own centrifugal force, thereby accurately and automatically adjusting to the dynamic balance compensation position.

[0044] The type of rolling element is not limited; it can be balls, rollers, etc.

[0045] In some embodiments of this application, the damping structure includes a viscous medium and rolling elements disposed between the contact interface of the fixed member 21 and the sleeve 221. This structure, on the one hand, converts relative motion into rolling friction through the rolling elements, significantly reducing the basic resistance; on the other hand, it forms a controllable viscous shear force between the interfaces through the viscous medium. The viscous medium and the damping structure work together to ensure that the rotating member 22 can generate a stable angular velocity hysteresis change when the drive shaft 11 is in the speed change stage, and that when the drive shaft 11 is rotating at a constant speed, the centrifugal force of the rotating member 22 drives itself to make precise position adjustments.

[0046] In some embodiments of this application, the fixing member 21 and the sleeve 221 together constitute a bearing structure, which can be a rolling bearing or a sliding bearing. The rolling bearing includes, but is not limited to, rolling bearings and needle roller bearings.

[0047] Specifically, the fixed member 21 and the sleeve 221 together constitute a rolling bearing. The rolling bearing can distribute the centrifugal force on the rotating member 22 to several opposing rolling elements, thereby reducing the contact normal pressure of a single rolling element and thus reducing the overall rolling friction resistance of the rolling bearing. The lower rolling friction resistance between the fixed member 21 and the sleeve 221 allows the rotating member 22 to move more sensitively to a position closer to the theoretically optimal dynamic balance compensation position under the drive of its own centrifugal force.

[0048] Therefore, the lower the friction of the bearing structure, the better it is to reduce the residual vibration of the impeller assembly after the dynamic balance adjustment component 2 has completed adaptive balancing, thereby improving the vibration reduction performance and operational stability of the blower.

[0049] In some embodiments of this application, the bearing structure formed by the fastener 21 and the sleeve 221 is made of a hard material, such as steel or ceramic.

[0050] Please see Figure 2 In some embodiments of this application, the counterweight 222 is provided separately, that is, the counterweight 222 includes a fixed bracket 2221 and a counterweight part 2222. The fixed bracket 2221 is provided on the sleeve 221; the counterweight part 2222 is detachably provided on the fixed bracket 2221. In this embodiment, by replacing the counterweight part 2222 with different specifications or adjusting the installation position of the counterweight part 2222 on the fixed bracket 2221, the imbalance vector U2 of the dynamic balance adjustment component 2 can be adjusted, thereby adapting to impeller components 1 of different models and working conditions.

[0051] Please see Figure 3 In some embodiments of this application, the counterweight 222 is integrally formed.

[0052] Please see Figure 3A In some embodiments of this application, the fixing member 21 and the drive shaft 11 can also be integrated on the same component. Exemplarily, the fixing member 21 is directly formed on the drive shaft 11 as a locally thickened structure or irregularly shaped segment structure, without the need for an additional separate fixing structure. The rotating member 22 is sleeved on the outside of the fixing member 21, and grooves are respectively provided on the inner side of the rotating member 22 and the outer side of the fixing member 21. The rotating member 22 serves as a counterweight structure, with its center of mass offset from the rotation center of the drive shaft 11 to provide eccentric mass.

[0053] Furthermore, at least three rolling elements, such as balls or needle rollers, are arranged in the groove between the fixed member 21 and the rotating member 22 to reduce the friction when they rotate relative to each other, and the groove is filled with a viscous medium, such as grease, damping grease, lubricating grease, etc., to provide lubrication and controllable micro-damping force at the same time.

[0054] It should be noted that the rotating component 22 in the above embodiments can also adopt an integral molding structure, that is, the sleeve 221 and the counterweight 222 are integrated into a single part. The integrally molded rotating component 22 is directly sleeved on the fixed component 21.

[0055] Of course, when the fixing member 21 and the drive shaft 11 are integrated on the same component, the rotating member 22 can also be set as a separate structure of sleeve 221 and counterweight 222 as in the above embodiment. The separate structure of sleeve 221 and counterweight 222 and the structure of counterweight 222 are as in the above embodiment, and will not be described in detail here.

[0056] In some embodiments of this application, the number of the dynamic balancing adjustment components 2 is set to multiple, and the multiple dynamic balancing adjustment components 2 are distributed at intervals along the axial direction of the drive shaft 11. In this embodiment, by setting multiple dynamic balancing adjustment components 2, the vector superposition effect of multiple dynamic balancing adjustment components 2 is used to jointly compensate for the unbalance vector of the impeller assembly 1, thereby improving the adaptive balancing capability of the impeller assembly and thus coping with the unbalanced working conditions of the impeller assembly 1 with larger amplitude or more complex phase.

[0057] Taking two dynamic balancing adjustment components 2 as an example, the unbalance vector of impeller assembly 1 is U1, the unbalance vector of one dynamic balancing adjustment component 2 is U2, and the unbalance vector of the other impeller assembly 1 is U3. According to the principle of vector superposition, the total unbalance vector of the impeller assembly is the sum of the three vectors.

[0058] In one embodiment, if U1 < |U2-U3|, after the impeller assembly 1 exceeds the critical speed and enters the automatic centering state, the one with the smaller imbalance vector among the two dynamic balancing adjustment components 2, such as U3, will automatically adjust to be in phase with U1, while the dynamic balancing adjustment component 2 with the larger imbalance vector, such as U2, will stabilize on the opposite side of U1 and U3. Therefore, the imbalance vector of the impeller assembly can be adjusted to |U2-U3|-U1, that is, through the synergistic effect of the two dynamic balancing adjustment components 2, the imbalance vector of the impeller assembly is further reduced.

[0059] In another embodiment, if |U2-U3|<U1<U2+U3, after the impeller assembly 1 exceeds the critical speed and enters the automatic centering state, through the adaptive and coordinated adjustment of the two dynamic balance adjustment components 2, its unbalance vectors U2 and U3 can form a closed vector triangle with the unbalance vector U1 of the impeller assembly, that is, satisfy the vector balance condition U1+U2+U3=0. At this time, the unbalance vector of the impeller assembly can be adjusted to the theoretical balance state, thereby achieving efficient vibration suppression.

[0060] In another embodiment, if U1 > U2 + U3, after the impeller assembly 1 exceeds the first critical speed and enters the automatic centering state, the two dynamic balancing adjustment components 2 will be adjusted so that their imbalance vectors U2 and U3 are in the same direction and are located on the opposite side of U1. At this time, the imbalance vector of the impeller assembly can be adjusted to U1-U2-U3. That is, through the synergistic effect of the two dynamic balancing adjustment components 2, the imbalance vector of the impeller assembly is further reduced.

[0061] Furthermore, if the imbalance amounts of the two dynamic balancing components 2 are equal, i.e., U2 = U3.

[0062] In one embodiment, if U1 < 2U2 or U1 < 2U3, the unbalance vector of the impeller assembly can be adjusted to the theoretical equilibrium state.

[0063] In another embodiment, if U1 > 2U2 or U1 > 2U3, the unbalance vector of the impeller assembly can be adjusted to U1-2U2 or U1-2U3.

[0064] It should be noted that the number of dynamic balancing adjustment components 2 can be two or more. However, since the dynamic balancing adjustment components 2 need to occupy the axial space of the drive shaft 11, in order to ensure the aesthetics of the impeller assembly and that there is enough space on the drive shaft 11 to install the fan blades 12, in some embodiments of this application, the number of dynamic balancing adjustment components 2 is set to two.

[0065] The shapes of the multiple dynamic balance adjustment components 2 located on the drive shaft 11 can be different or the same.

[0066] For example, such as Figure 4 The two dynamic balance adjustment components 2 have the same structure, and the counterweights 222 of the two dynamic balance adjustment components 2 each include a fixed bracket 2221 and a counterweight part 2222.

[0067] like Figure 5 The two dynamic balance adjustment components 2 have the same structure, and the counterweights 222 of the two dynamic balance adjustment components 2 are integrally formed.

[0068] like Figure 6 The two dynamic balance adjustment components 2 have different structures. The counterweights 222 of one dynamic balance adjustment component 2 are integrally formed, while the counterweights 222 of the other dynamic balance adjustment component 2 include a fixed bracket 2221 and a counterweight part 2222.

[0069] Furthermore, it should be noted that the number of fan blades 12 is not specifically limited and can be one or more. Also, the type of fan blades 12 is not limited to a specific form; they can be fixed fan blades or adjustable fan blades, such as variable pitch fan blades. That is, in the above embodiment, the fan blades 12 disposed on the drive shaft 11 can be fixed relative to the drive shaft 11, or they can be rotatable relative to the drive shaft 11.

[0070] In some embodiments of this application, the impeller assembly 1 further includes a blade holder, which is fixedly sleeved on the output shaft 11, and the blade 12 is rotatably connected to the outer periphery of the blade holder. In this embodiment, by rotatably connecting the blade 12 to the outer periphery of the blade holder, the blade 12 can be rotated around the blade holder, causing the blade 12 to deflect relative to the blade holder, thereby changing the angle of attack of the blade 12. The angle of attack of the blade 12 can be the angle between the projection of the blade 12 on the periphery of the blade holder and the axial direction of the output shaft. Changing the angle of attack of the blade 12 can adjust the pitch between the blades 12 accordingly, thereby changing the air outlet angle and air outlet range of the blower, enabling the blower to achieve a better blowing effect.

[0071] It should be noted that in this embodiment, the fan blade 12 rotates relative to the fan blade seat and also rotates together with the fan blade seat.

[0072] In addition, in the embodiment where the fan blade 12 is fixed relative to the drive shaft 11 and a fan blade seat is provided, the fan blade 12 can be fixed relative to the fan blade seat, that is, the fan blade 12 and the fan blade seat are fixedly connected, and the fan blade 12 cannot deflect relative to the fan blade seat. At this time, the fan blade 12 rotates together with the fan blade seat and the drive shaft 11, forming a fixed fan blade structure.

[0073] Secondly, this application also proposes a second embodiment of an impeller assembly, which includes an impeller assembly 1 and at least one dynamic balance adjustment assembly 2. The impeller assembly 1 includes a drive shaft 11 and a fan blade 12 fixedly disposed on the drive shaft 11. The dynamic balance adjustment assembly 2 includes a rotating member 22, which is rotatably sleeved on the drive shaft 11. There is a damping force between the rotating member 22 and the drive shaft 11, and the center of mass of the rotating member 22 is offset from the rotation center of the drive shaft 11. When the drive shaft 11 moves at a variable speed, the angular velocity of the rotating member 22 changes under the action of the damping force, and its angular velocity change lags behind the angular velocity change of the drive shaft 11. When the drive shaft 11 rotates at a constant speed, the rotating member 22 overcomes the damping force under the drive of its own centrifugal force and moves relative to the drive shaft 11 to the dynamic balance compensation position.

[0074] Compared with the first embodiment, the difference in this embodiment is that: in the first embodiment, the dynamic balance adjustment component 2 includes a fixing member 21 and a rotating member 22, the fixing member 21 is fixedly disposed on the drive shaft 11, and the rotating member 22 is rotatably sleeved on the fixing member 21; while in this embodiment, the dynamic balance adjustment component 2 omits the fixing member 21, and the rotating member 22 is directly rotatably sleeved on the drive shaft 11.

[0075] In this structure, the rotating component 22 directly rotates with the drive shaft 11, retaining the same dynamic working principle as the first embodiment: during the speed change phase of the drive shaft 11, the rotating component 22 experiences angular velocity lag due to damping; once the drive shaft 11 enters uniform rotation, the rotating component 22 overcomes the damping force under its own centrifugal force and automatically adjusts to the dynamic balance compensation position. This simplified design, while maintaining the adaptive balancing function, further reduces the number of parts, which helps to reduce the complexity and manufacturing cost of the impeller assembly, while improving assembly efficiency and structural reliability.

[0076] In addition, the working principle, damping force mechanism, and dynamic balance compensation position of the impeller assembly 1, fan blade 12, and dynamic balance adjustment assembly 2 in this embodiment are the same as those in the first embodiment, and will not be repeated here.

[0077] Thirdly, this application proposes a blower device. Figures 7 to 12 These are some embodiments of this application.

[0078] Please see Figures 7 to 9 In some embodiments of this application, the blower includes the impeller assembly described in any of the foregoing embodiments, and a drive assembly 3 and a mounting base 4 that are matched with the impeller assembly. The drive assembly 3 has two opposite sides along the axial direction of the drive shaft 11, with the drive shaft 11 disposed on one side; the mounting base 4 is disposed on the other side of the drive assembly 3. In this embodiment, while the drive assembly 3 drives the impeller assembly to rotate and generate airflow, the mounting base 4 provides a stable support foundation for the drive assembly 3. The impeller assembly is as described above and will not be described in detail here.

[0079] The air-blowing equipment protected by this application covers all devices that include fan blades and generate directional airflow through their rotation, including but not limited to: various types of fans (such as floor fans, table fans, circulating fans, wall fans), air circulation fans, indoor and outdoor units of air conditioners, air supply units of fresh air systems, heaters, etc.

[0080] In some embodiments of this application, the blower further includes at least one resilient connector 5. At least one elastic connector 5 is connected between the drive assembly 3 and the mounting base 4 and is capable of elastic deformation between the two, that is, elastic deformation in the axial direction of the drive shaft 11.

[0081] In this embodiment, by providing an elastic connector 5 that can elastically deform in the axial direction, the first-order natural frequency of the entire impeller assembly is effectively reduced, thereby adjusting the first-order critical speed of the impeller assembly to a lower level that is more easily achievable within the actual operating speed range. This allows the impeller assembly to quickly enter and stably operate at a supercritical speed state after normal startup, providing the necessary operating conditions for the dynamic balancing adjustment component 2 to achieve adaptive balance compensation based on the automatic centering principle.

[0082] In some embodiments, the drive shaft 11 extends horizontally. Under the action of gravity, the drive assembly 3 and the impeller assembly 1 fixed thereon are prone to large static droop displacement. This may cause the actual rotation center of the drive shaft 11 to deviate from the theoretically set position, thereby causing additional imbalance, accelerating component wear, and making the system more likely to excite the vibration modes of the floating quasi-rigid body (such as the 2nd to 6th order modes), thereby inducing resonance during operation. Therefore, in this embodiment, the elastic connector 5 is designed so that the stiffness in the axial direction of the drive shaft 11 is significantly less than its radial stiffness. This anisotropic stiffness configuration provides sufficient flexibility in the axial direction to reduce the critical speed of the system, while maintaining high stiffness in the radial direction. This effectively limits the static sag displacement caused by gravity, maintains the positioning accuracy of the rotation axis of the drive shaft 11, and widens the frequency interval between low-order and high-order modes. It prevents the actual operating speed of the blower from being equal to or close to the natural frequency (such as the frequency corresponding to the 2nd to 6th order vibration modes) of the quasi-rigid system composed of the drive component 3 and the impeller component 1 fixed on it, thereby avoiding resonance and ultimately improving the smoothness and reliability of the equipment operation.

[0083] It should be noted that the critical speed refers to the speed corresponding to the first natural frequency of impeller assembly 1.

[0084] Please see Figures 9 to 11In some embodiments of this application, the mounting base 4 is provided with a support portion 41 at a position corresponding to the elastic connector 5, and the support portion 41 extends axially along the drive shaft 11; the elastic connector 5 includes a sleeve 51 and a plurality of support blocks 52, the sleeve 51 is sleeved on the outside of the support portion 41 and extends axially along the drive shaft 11, and the sleeve 51 can elastically deform in the axial direction of the drive shaft 11; the plurality of support blocks 52 are fixedly disposed on the inner wall of the sleeve 51 and contact the support portion 41; wherein, the sleeve 5 1 is fixedly connected to the drive assembly 3; in this embodiment, in the circumferential direction of the support block 52, the stable contact between the multiple support blocks 52 and the support part 41 provides reliable position constraint and positioning, effectively avoiding the high-order modes that may be caused by insufficient radial stiffness of the elastic connector 5 on the drive shaft 11; while in the axial direction of the drive shaft 11, the elastic deformation of the sleeve 51 itself provides controllable axial low stiffness support, thereby adjusting the first-order natural frequency of the impeller assembly 1 to the required range, ensuring the effective triggering of the supercritical speed state and adaptive balance compensation.

[0085] In addition, the contact surface between the support block 52 and the support part 41 is designed to have a small area, thereby reducing the interference of friction between the two on the axial elastic deformation of the sleeve 51, ensuring that the sleeve 51 can achieve full and free flexible deformation in the axial direction, thus meeting the design requirements of axial low stiffness support.

[0086] In some embodiments of this application, the dimension of the support block 52 in the axial direction of the drive shaft 11 is smaller than the dimension of the sleeve 51 in the axial direction of the drive shaft 11, so as to avoid interference of the friction between the support block 52 and the support part 41 on the axial elastic deformation of the sleeve 51.

[0087] Furthermore, the number of elastic connectors 5 provided between the mounting base 4 and the drive assembly 3 is not limited; there can be one or more.

[0088] In some embodiments of this application, the support portion 41 is disposed on one side of the drive assembly 3 in the radial direction of the drive shaft 11; at least two of the support blocks 52 in the elastic connector 5 are located on the line connecting the midpoint of the support portion 41 and the rotation center of the drive shaft 11. This arrangement... This is because when the drive shaft 11 rotates, the unbalanced centrifugal force of the impeller assembly 1 will mainly act radially on the drive assembly 3 and the elastic connector 5 connected to it. By arranging the key support block 52 on the line connecting the midpoint of the support part 41 and the rotation center of the drive shaft 11, it can be ensured that the radial support force it provides is consistent with or directly counteracts the direction of the unbalanced centrifugal force, thereby most effectively utilizing the radial high stiffness characteristics of the elastic connector 5 to limit the radial displacement of the impeller assembly 1, stabilize the rotation axis of the drive shaft 11, and suppress higher-order modes.

[0089] In one specific embodiment of this application, three elastic connectors 5 are arranged around the circumference of the drive shaft 11. They are evenly distributed between the drive assembly 3 and the mounting base 4, that is, a three-point surrounding support layout is adopted, which can provide stable support for the drive assembly 3 in the radial plane of the drive shaft 11.

[0090] In some embodiments of this application, to ensure that the circumferential installation angle of the elastic connector 5 meets the design requirement that at least two of the support blocks 52 are located on the line connecting the midpoint of the support portion 41 and the rotation center of the drive shaft 11, either the elastic connector 5 or the mounting base 4 is provided with a positioning protrusion 6, and the other is provided with a corresponding positioning groove 7. Through the cooperation of the positioning groove 7 and the positioning protrusion 6, the circumferential orientation of the elastic connector 5 can be constrained and positioned, thereby ensuring that the support block 52 automatically resides in the set position after assembly.

[0091] In some embodiments of this application, at least a portion of the periphery of the sleeve 51 is recessed to form a mounting groove 8, which is used for at least a portion of the drive assembly 3 to be embedded; in this embodiment, the mounting groove 8 is used to receive and fit a corresponding protrusion or mounting portion of the drive assembly 3, thereby achieving a reliable connection between the sleeve 51 and the drive assembly 3.

[0092] In some embodiments of this application, the drive assembly 3 includes a motor 31 and a mounting bracket 32. The motor 31 is located on one side of the mounting base 4 opposite to the drive shaft 11 along its axial direction, and its rotor is drive-connected to the drive shaft 11 to provide rotational power. The mounting bracket 32 ​​covers the side of the motor 31 facing away from the mounting base 4, providing protection and structural support. At least a portion of the mounting bracket 32 ​​is embedded in a mounting groove 8 on the sleeve 51 of the elastic connector 5, thereby achieving a stable connection between the drive assembly 3 and the elastic connector 5.

[0093] In some embodiments of this application, the motor 31 and the mounting bracket 32 ​​may also be integrated as a single unit.

[0094] In some embodiments of this application, the elastic connector 5 further includes a connecting portion 53, which is disposed at the end of the sleeve 51 away from the mounting base 4 and covers the inner cavity of the sleeve 51. The connecting portion 53 has a through hole 531 for a fastener 9 to pass through. At least a portion of the connecting portion 53 is located between the fastener 9 and the mounting base 4. This ensures that when the fastener 9 is tightened, the axial clamping force it generates is directly transmitted to the end of the sleeve 51 through the connecting part 53, rather than acting on the side wall of the sleeve 51, thereby ensuring a stable mechanical connection between the elastic connector 5 and the mounting base 4. Simultaneously, since the clamping force is concentrated at the end and aligns with the axial deformation direction of the sleeve 51, this connection method avoids interference with the free elastic deformation of the sleeve 51 in the axial direction of the drive shaft 11.

[0095] In some embodiments of this application, the fastener 9 includes a screw 91 and a washer 92. During installation, the screw 91 passes through the washer 92 and is screwed into and locked onto the support portion 41 of the mounting base 4, while the washer 92 is in direct contact with the connecting portion 53 of the elastic connector 5.

[0096] In some embodiments of this application, one end of the sleeve 51 is connected to the fastener 9 via a connecting part 53, while the other end directly abuts against the surface of the mounting base 4, thereby forming a sealed state at both ends of its inner cavity after assembly. To prevent uneven air pressure inside and outside the sealed inner cavity due to temperature changes or sleeve deformation, which would affect the stability and stiffness characteristics of the axial elastic deformation of the sleeve 51, at least one opening 10 is provided on the side wall of the sleeve 51. This opening 10 is used to connect the inner cavity of the sleeve 51 with the external environment, playing a role in ventilation and air pressure balance, and preventing the increase in inner cavity air pressure from adversely affecting the axial stiffness of the sleeve.

[0097] Please see Figure 8 In one embodiment, the mounting feet of the mounting bracket 32 ​​are provided with mounting holes, and the two are connected by fitting the mounting holes into the mounting groove 8 of the sleeve 51.

[0098] Please see Figure 12 In another embodiment, the mounting feet of the mounting bracket 32 ​​are provided with openings, which allow the mounting feet to be directly inserted into the mounting groove 8 of the sleeve 51. This opening design reduces the contact area between the mounting feet and the sleeve 51, thereby reducing the constraint and coverage of the effective elastic deformation part of the sleeve 51 during assembly, which is beneficial to achieving a lower first-order critical speed and better vibration isolation effect.

[0099] In addition, it should be noted that the material of the elastic connector 5 is not limited to a specific type. For example, it can be made of polymer materials with good elasticity, fatigue resistance and environmental adaptability, such as silicone.

[0100] The technical principle of this application is explained below: The core mechanism of dynamic balance adaptive adjustment is based on the automatic centering phenomenon in rotor dynamics. When the rotational speed of the rotor system exceeds its critical speed, the rotor's center of mass C will automatically tend towards the actual rotation center O under the action of dynamics. This causes the centrifugal force of the rotating component 22 to generate a component in the direction opposite to the rotor's center of mass, guiding the rotating component 22 to move towards the position opposite to the center of mass of the impeller assembly 1, thus producing a dynamic balance adaptive effect.

[0101] This application combines this principle with a flexible support structure, that is, by using the elastic connector 5 to provide controllable low stiffness support in the axial direction, the critical speed of the impeller assembly 1 is effectively reduced, so that the impeller assembly 1 can stably generate an automatic centering phenomenon within the actual working speed range.

[0102] Meanwhile, the rotating component 22 in the dynamic balancing adjustment assembly 2, under the action of its own centrifugal force, experiences a circumferential component force that causes it to move in the opposite direction to the current unbalanced mass of the impeller assembly 1. This component force drives the rotating component 22 to overcome the damping force between itself and the fixed component 21 or the drive shaft 11, gradually adjusting its circumferential position until it stabilizes on the phase opposite to the unbalance vector of the impeller assembly 1, reducing the overall unbalance of the system. Thus, the system achieves real-time, adaptive compensation for the dynamic unbalance vector without external intervention, significantly suppressing vibration.

[0103] Specifically, when impeller assembly 1 rotates, its imbalance vector is U1, with a magnitude of U1 = M1 × e1 and a direction from the axis center to the position of e1. Here, M1 is the mass of the rotor part of the fan system, and e1 is its eccentricity.

[0104] This analysis is based on an embodiment of the counterweight 222 of the dynamic balance adjustment component 2, which includes a fixed bracket 2221 and a counterweight part 2222. The mass of the fixed bracket 2221 is M. 21 The eccentricity is denoted as e. 21 The mass of the counterweight 2222 is denoted as M. 22 The eccentricity is e 22 .

[0105] In one embodiment of this application, the impeller assembly 1 has only one dynamic balancing adjustment component 2. The imbalance vector of a single dynamic balancing adjustment component 2 is U2, which is composed of a fixed bracket 2221 and a counterweight 2222. Therefore, the value of the imbalance vector U2 of a single dynamic balancing adjustment component 2 can be expressed as: U2 = M 22 ×e 22 +M 21 ×e 21 For the entire impeller assembly, the overall imbalance vector is U1 + U2.

[0106] Then, based on the principle of automatic centering, when there is only one dynamic balance adjustment component and the unbalance vector of the counterweight 222 is opposite to the unbalance vector of the impeller assembly 1, the directions of U1 and U2 are opposite, and the 总 magnitude of U is |U1 - U2|, and the direction is the direction of the larger unbalance vector between U1 and U2.

[0107] In another embodiment of the present application, there are two dynamic balance adjustment components 2 in the impeller assembly 1 to adapt to the situation where the unbalance vector of the fan blades 12 in the impeller assembly 1 is relatively large or has a certain variation range, and it is impossible to achieve a good dynamic balance self-adaptive effect through a single dynamic balance adjustment component 2.

[0108] Based on the above analysis, in the embodiment where the impeller assembly 1 is equipped with two dynamic balance adjustment components 2, their unbalance vectors are respectively denoted as U4 and U5. The calculation methods of U4 and U5 refer to the unbalance vector U2 of the前述 single dynamic balance adjustment component 2, that is, they are respectively synthesized by the mass and eccentricity of their fixed brackets 2221 and counterweight parts 2222: U4 = M 221 × e 221 + M 211 × e 211 and U5 = M 222 × e 222 + M 212 × e 212 . Similarly, for the entire impeller assembly, the overall unbalance vector is U1 + U4 + U5.

[0109] According to the rule of vector addition, when U1 < |U4 - U5|, the vector with the smaller value among U4 and U5 will coincide with U1 and stabilize opposite to the vector with the larger value among U4 and U5.

[0110] When U1 > U4 + U5, the unbalance vectors U4 and U5 of the two dynamic balance adjustment components 2 will coincide and stabilize at the opposite position of U1. That is to say, at this time, the unbalance vector obtained by adding the unbalance vectors of the two dynamic balance adjustment components 2 can cancel out a part of the unbalance vector of the impeller assembly 1.

[0111] When |U4 - U5| < U1 < U4 + U5, according to the basic rule of vector addition, the three vectors can form a closed triangle, that is, U1 + U4 + U5 = 0 is satisfied, and theoretically, the complete balance of the three unbalance vectors can be achieved, and the efficient suppression of vibration can be realized.

[0112] The above are only exemplary embodiments of the present invention, and do not limit the patent scope of the present invention. Any equivalent structural transformation made under the technical concept of the present invention by using the content of the specification and drawings of the present invention, or directly / indirectly applied in other related technical fields, is included in the patent protection scope of the present invention.

Claims

1. An impeller assembly, characterized in that, include: An impeller assembly, including a drive shaft and fan blades disposed on the drive shaft; At least one dynamic balance adjustment component includes a fixed component and a rotating component. The fixed component is fixedly disposed on the drive shaft. The rotating component is rotatably sleeved on the fixed component and can rotate around the drive shaft. There is a damping force between the rotating component and the fixed component. The center of mass of the rotating component is offset from the rotation center of the drive shaft. When the drive shaft moves at a variable speed, the angular velocity of the rotating component changes under the action of the damping force, and its angular velocity change lags behind the angular velocity change of the drive shaft. When the drive shaft rotates at a constant speed, the rotating component overcomes the damping force under its own centrifugal force and moves relative to the fixed component to the dynamic balance compensation position of the impeller assembly.

2. The impeller assembly as described in claim 1, characterized in that, The rotating component includes: The sleeve body is rotatably fitted onto the fixing member and has a damping force between it and the fixing member; and A counterweight is fixedly mounted on the sleeve, and the center of mass of the counterweight is offset from the rotation center of the drive shaft.

3. The impeller assembly as described in claim 2, characterized in that, A damping structure is provided between the fixing member and the sleeve; The damping structure includes a viscous medium filling the contact interface between the two and / or a rolling element disposed between the two.

4. The impeller assembly as described in claim 2, characterized in that, The counterweight is integrally formed; or The counterweight includes a fixed bracket and a counterweight part, wherein the fixed bracket is disposed on the sleeve body; and the counterweight part is detachably disposed on the fixed bracket.

5. The impeller assembly as described in any one of claims 1 to 4, characterized in that, The number of the dynamic balancing adjustment components is set to multiple, and the multiple dynamic balancing adjustment components are distributed at intervals along the axial direction of the drive shaft.

6. The impeller assembly as described in any one of claims 1 to 4, characterized in that, The impeller assembly also includes: The fan blade holder is fixedly sleeved on the output shaft, and the fan blade is rotatably connected to the outer periphery of the fan blade holder.

7. An impeller assembly, characterized in that, include: An impeller assembly, including a drive shaft and fan blades disposed on the drive shaft; At least one dynamic balance adjustment component includes a rotating member rotatably mounted on the drive shaft, a damping force between the rotating member and the drive shaft, and the center of mass of the rotating member being offset from the rotation center of the drive shaft. When the drive shaft moves at a variable speed, the angular velocity of the rotating component changes under the action of the damping force, and its angular velocity change lags behind the angular velocity change of the drive shaft. When the drive shaft rotates at a constant speed, the rotating component overcomes the damping force under its own centrifugal force and moves relative to the drive shaft to the dynamic balance compensation position of the impeller assembly.

8. A blower device, characterized in that, include: The impeller assembly as described in any one of claims 1 to 7; A drive assembly having opposite sides in the axial direction of the drive shaft, the drive shaft being disposed on one of the sides; and The mounting base is located on the other side of the drive assembly.

9. The blower device as described in claim 8, characterized in that, The blowing device also includes: At least one elastic connector is connected between the drive assembly and the mounting base and is capable of elastic deformation between the two.

10. The blower device as described in claim 9, characterized in that, The stiffness of the elastic connector in the axial direction of the drive shaft is less than its stiffness in the radial direction of the drive shaft.

11. The blower device as described in claim 10, characterized in that, The mounting base is provided with a support portion at the position corresponding to the elastic connector, and the support portion extends along the axial direction of the drive shaft; The elastic connector includes: A sleeve, fitted onto the outside of the support portion and extending axially along the drive shaft, the sleeve being capable of elastic deformation in the axial direction of the drive shaft; and Multiple support blocks are fixedly disposed on the inner wall of the sleeve and in contact with the support portion; The sleeve is fixedly connected to the drive assembly.

12. The blower device as described in claim 11, characterized in that, The support portion is disposed on one side of the drive assembly in the radial direction of the drive shaft; At least two of the support blocks are located on the line connecting the midpoint of the support portion and the rotation center of the drive shaft.

13. The blower device as described in claim 12, characterized in that, One of the elastic connector and the mounting base is provided with a positioning protrusion, and the other is provided with a positioning groove; The positioning groove engages with the positioning protrusion so that at least two of the support blocks in the elastic connector are located on the line connecting the midpoint of the support portion and the rotation center of the drive shaft.

14. The blower device as described in claim 11, characterized in that, At least a portion of the periphery of the sleeve is recessed to form a mounting groove for at least a portion of the drive assembly to be inserted.

15. The blower device as described in claim 14, characterized in that, The driving component includes: A motor is located on one side of the mounting base along the axial direction of the drive shaft, and the rotor of the motor is drively connected to the drive shaft; and A mounting bracket is provided on the side of the motor away from the mounting base, and at least a portion of the mounting bracket is embedded in the mounting groove.

16. The blower device as described in claim 11, characterized in that, The elastic connector further includes: A connecting portion is provided at one end of the sleeve away from the mounting base and covers the inner cavity of the sleeve. The connecting portion is provided with a through hole for fasteners to pass through. At least a portion of the connecting portion is located between the fastener and the mounting base.

17. The blower device as described in claim 16, characterized in that, The other end of the sleeve abuts against the mounting base; The sleeve is provided with at least one opening to connect the inner cavity of the sleeve with the external environment.

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