CN221282979U - Impeller assembly, driving device and washing machine - Google Patents

Abstract

The utility model discloses an impeller assembly, a driving device and a washing machine, and relates to the technical field of motors, wherein the impeller assembly is applied to a motor and comprises a first impeller and a clutch mechanism, and the first impeller is arranged on a rotating shaft of the motor and rotates relative to the rotating shaft; the clutch mechanism is fixedly arranged on the rotating shaft, and synchronously rotates with the first impeller when the clutch mechanism is in a first state, and is separated from the first impeller when the clutch mechanism is in a second state; wherein, the rotational speed of motor is V ₁ when clutch mechanism is in the first state, and the rotational speed of motor is V ₂ when clutch mechanism is in the second state, satisfies: v ₁＜V₂. The impeller assembly can separate the first impeller from the rotating shaft of the motor when the motor rotates at a high speed, so that the generation of pneumatic noise and wind resistance loss are avoided.

Description

Impeller assembly, driving device and washing machine

Technical Field

The utility model relates to the technical field of motors, in particular to an impeller assembly, a driving device and a washing machine.

Background

Drum washing machines, pulsator washing machines and the like generally have at least two working conditions, i.e. washing and dehydrating, that is to say, the corresponding motor has at least two gears with different rotational speeds, under washing conditions, the rotational speed of the motor is generally below 1000rpm, while under dehydrating conditions, the rotational speed of the motor is much greater than 1000rpm, reaching 10000rpm or more. For motor heat dissipation, generally speaking, install the fan blade on the motor, although under the washing operating mode, the fan blade of low rotational speed can effectively dispel the heat to the motor, nevertheless, under the dehydration operating mode, the fan blade of high rotational speed will lead to pneumatic noise to increase, and windage loss is big, influences the output of motor, and current fan blade can't take into account two kinds of operating modes.

Disclosure of utility model

The present utility model aims to solve at least one of the technical problems existing in the prior art. Therefore, the utility model provides an impeller assembly which can separate the first impeller from the rotating shaft of the motor when the motor rotates at a high speed so as to avoid the generation of pneumatic noise and wind resistance loss.

The utility model also provides a driving device with the impeller assembly and a washing machine with the driving device.

An impeller assembly according to an embodiment of the first aspect of the present utility model, for use in a motor, comprises:

the first impeller is arranged on the rotating shaft of the motor and rotates relative to the rotating shaft;

The clutch mechanism is fixedly arranged, when the clutch mechanism is in a first state, the clutch mechanism and the first impeller synchronously rotate, and when the clutch mechanism is in a second state, the clutch mechanism and the first impeller are separated;

When the clutch mechanism is in the first state, the rotating speed of the motor is V ₁, and when the clutch mechanism is in the second state, the rotating speed of the motor is V ₂, so that V ₁＜V₂ is met.

An impeller assembly according to an embodiment of the first aspect of the utility model has at least the following beneficial effects: through setting up clutch mechanism, under the first state of low rotational speed, clutch mechanism can rotate with first impeller is synchronous, and first impeller and the pivot synchronous rotation of motor promptly are suitable for the heat dissipation to motor self, under the second state of high rotational speed, clutch mechanism can separate with first impeller, makes first impeller and the pivot separation of motor, and first impeller stops rotating, has avoided the pneumatic noise and the windage loss that high rotational speed brought, reduces the influence to the output of motor.

According to some embodiments of the utility model, the clutch mechanism comprises a mounting seat and a clutch member, the clutch member comprises an elastic piece and a combining piece, the mounting seat is suitable for being connected with the rotating shaft, the combining piece is movably mounted on the mounting seat, the elastic piece is arranged on the mounting seat, the first impeller comprises a transmission part, when the clutch mechanism is in the first state, the elastic piece can drive the combining piece to deviate so as to enable the combining piece to be combined with the transmission part, and when the clutch mechanism is in the second state, the combining piece can reversely deviate and be separated from the transmission part.

According to some embodiments of the utility model, the coupling is slidably mounted to the mount, and an angle between a sliding direction of the coupling and a center line of the first impeller is greater than 0 °.

According to some embodiments of the utility model, the coupling member is located on a side of a reference plane passing through a centerline of the first impeller, and the elastic member is capable of urging the coupling member toward the centerline of the first impeller when the clutch mechanism is in the first state.

According to some embodiments of the utility model, the clutch mechanism comprises a plurality of the clutch members arranged centrosymmetrically about a centre line of the first impeller.

According to some embodiments of the utility model, the coupling member is provided with a coupling portion, the centroid of the coupling member and the coupling portion are located on both sides of a reference plane passing through the center line of the first impeller, respectively, and when the clutch mechanism is in the first state, the elastic member is capable of driving the centroid to move toward the center line of the first impeller, and the coupling portion moves in a direction away from the center line of the first impeller.

According to some embodiments of the utility model, the coupling comprises a stem and a head, the head being connected to one end of the stem, the other end of the stem being provided with the coupling, the head having an outer diameter greater than the outer diameter of the stem, the head and the coupling being located on opposite sides of the reference plane, respectively.

According to some embodiments of the utility model, the transmission portion is a protrusion, and the coupling piece can abut against one side of the protrusion in the circumferential direction of the first impeller.

According to some embodiments of the utility model, the transmission is a recess, and the coupling can be partially accommodated in the recess.

According to some embodiments of the utility model, the transmission portion is elongated and extends in a direction of a center line of the first impeller.

According to some embodiments of the utility model, the first impeller is provided with a sleeve, the sleeve extends along the central line direction of the first impeller, the transmission part is arranged on the sleeve, the mounting seat is sleeved on the periphery of the sleeve, or the sleeve is sleeved on the periphery of the mounting seat.

According to some embodiments of the utility model, the first impeller is provided with a bearing, through which the first impeller is adapted to be mounted to a rotating shaft of the motor.

A driving device according to an embodiment of a second aspect of the present utility model includes:

The motor body is provided with a rotating shaft;

The impeller assembly of the embodiment of the first aspect is mounted on the rotating shaft.

The driving device according to the embodiment of the second aspect of the present utility model has at least the following advantageous effects: the driving device adopts the impeller assembly, and the clutch mechanism is arranged, so that the clutch mechanism can synchronously rotate with the first impeller in the first state of low rotation speed, namely, the first impeller and the rotating shaft synchronously rotate, the driving device is suitable for radiating the motor, and in the second state of high rotation speed, the clutch mechanism can be separated from the first impeller, so that the first impeller is separated from the rotating shaft, the first impeller stops rotating, the pneumatic noise and the windage loss caused by high rotation speed are avoided, and the influence on the output power of the motor is reduced.

According to some embodiments of the utility model, the rotor further comprises a second impeller mounted to the shaft, the second impeller having an outer diameter smaller than an outer diameter of the first impeller.

According to some embodiments of the utility model, the first impeller has an outer diameter D ₁ and the second impeller has an outer diameter D ₂, satisfying: d ₁/D₂＝V₂/V₁.

According to some embodiments of the utility model, the first impeller and the second impeller are located at one end of the motor body in an axial direction of the rotation shaft, and the second impeller is closer to the motor body than the first impeller; or the first impeller and the second impeller are respectively positioned at two ends of the motor body along the axial direction of the rotating shaft.

A washing machine according to an embodiment of a third aspect of the present utility model includes the driving apparatus of the embodiment of the second aspect described above.

The washing machine according to the embodiment of the third aspect of the utility model has at least the following advantages: by adopting the driving device, the washing machine can synchronously rotate with the first impeller in the first state of low rotating speed, namely, the first impeller and the rotating shaft synchronously rotate, and is suitable for radiating the motor, and in the second state of high rotating speed, the clutch mechanism can be separated from the first impeller, so that the first impeller is separated from the rotating shaft, the first impeller stops rotating, the pneumatic noise and the windage loss caused by high rotating speed are avoided, and the influence on the output power of the motor is reduced.

Additional aspects and advantages of the utility model will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the utility model.

Drawings

The utility model is further described with reference to the accompanying drawings and examples, in which:

FIG. 1 is an exploded view of a drive device including an impeller assembly according to an embodiment of the present utility model;

FIG. 2 is a front view of a drive apparatus incorporating an impeller assembly according to an embodiment of the present utility model;

FIG. 3 is a cross-sectional view at A-A in FIG. 2;

FIG. 4 is an enlarged view at C in FIG. 3;

FIG. 5 is a cross-sectional view at B-B in FIG. 2;

FIG. 6 is a cross-sectional view of a wheel assembly in another embodiment of the present utility model.

Reference numerals:

A first impeller 100; a sleeve 110; a transmission part 120; a bearing 130;

a clutch mechanism 200; a mounting base 210; a chute 211; an end cap 212; a clutch member 220; an elastic member 221; a binder 222; a joint 2221; a lever portion 2222; a head 2223;

A second impeller 300;

A motor body 400; a rotation shaft 410.

Detailed Description

Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the utility model.

In the description of the present utility model, it should be understood that references to orientation descriptions such as upper, lower, front, rear, left, right, etc. are based on the orientation or positional relationship shown in the drawings, are merely for convenience of description of the present utility model and to simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the present utility model.

In the description of the present utility model, a number means one or more, a number means two or more, and greater than, less than, exceeding, etc. are understood to not include the present number, and above, below, within, etc. are understood to include the present number. The description of the first and second is for the purpose of distinguishing between technical features only and should not be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.

In the description of the present utility model, unless explicitly defined otherwise, terms such as arrangement, mounting, connection, assembly, cooperation, etc. should be construed broadly and the specific meaning of the terms in the present utility model can be reasonably determined by a person skilled in the art in combination with the specific contents of the technical solution.

Drum washing machines, pulsator washing machines and the like generally have at least two working conditions, i.e. washing and dehydrating, that is to say, the corresponding motor has at least two gears with different rotational speeds, under washing conditions, the rotational speed of the motor is generally below 1000rpm, i.e. the motor is in a low rotational speed gear, while under dehydrating conditions, the rotational speed of the motor is much greater than 1000rpm, reaching 10000rpm or more, i.e. the motor is in a high rotational speed gear. In order to dissipate heat of a motor, in general, a fan blade is installed on the motor to drive air to flow through the fan blade, so as to dissipate heat of the motor. Although the low-rotation-speed fan blade can effectively radiate heat to the motor under the washing working condition, the high-rotation-speed fan blade can cause the increase of pneumatic noise under the dehydration working condition, so that the wind resistance loss is large, and the output power of the motor is influenced. According to simulation calculation, when the rotating speed is 1000rpm, the shaft power consumed by the fan blade is 0.19W, and when the rotating speed reaches 10000rpm, the shaft power consumed by the fan blade is increased to 176.57W, and the fan blade accounts for 26% of the maximum output power of the motor, so that the influence on the output power of the motor is large. The existing fan blade cannot take the two working conditions into consideration.

In order to solve the above-mentioned problems, referring to fig. 1 to 6, an embodiment of a first aspect of the present utility model provides an impeller assembly applied to a motor having different rotational speed gears, so as to realize rotation of the impeller at a low rotational speed and heat dissipation of the motor itself, and non-rotation of the impeller at a high rotational speed, so as to avoid noise generation and windage loss. It will be readily appreciated that the impeller assembly in combination with the motor forms the drive means. For example, the impeller assembly can be mounted on the driving motor of the washing machine, so that the driving motor can be cooled under the washing working condition (namely, the driving motor is in a low-speed gear), and the noise generation and windage loss can be avoided under the dehydration working condition (namely, the driving motor is in a high-speed gear), thereby avoiding influencing the output power of the driving motor. The washing machine herein may be a drum washing machine or a pulsator washing machine.

The structure of the impeller assembly is described in detail below by taking the impeller assembly mounted on the drum washing machine as an example.

Referring to fig. 1 and 2, it can be understood that the impeller assembly is mounted on the rotating shaft 410 of the driving motor of the drum washing machine, the impeller assembly includes the first impeller 100 and the clutch mechanism 200, wherein the first impeller 100 is rotatably mounted on the rotating shaft 410, specifically, the center line Z of the first impeller 100 has a hollow structure and is mounted with the bearing 130, the bearing 130 is fixedly mounted on the rotating shaft 410, that is, the first impeller 100 is mounted on the rotating shaft 410 through the bearing 130, so that the first impeller 100 can freely rotate relative to the rotating shaft 410, and the rotating friction force and the resistance are small. The center line Z is the rotation axis of the first impeller 100.

Referring to fig. 2 and 3, it can be understood that the clutch mechanism 200 is mounted on the rotating shaft 410 and limited to the rotating shaft 410 along the circumferential direction of the rotating shaft 410, i.e., the clutch mechanism 200 is fixedly mounted on the rotating shaft 410, so that the clutch mechanism 200 can synchronously rotate along with the rotating shaft 410. The clutch mechanism 200 is disposed on one side of the first impeller 100 along the center line direction, specifically, the clutch mechanism 200 includes a mounting base 210, the mounting base 210 is in a ring structure and is sleeved on the rotating shaft 410, and the mounting base 210 is connected with the rotating shaft 410 by means of matching of a key slot and a key, a bayonet lock or a flange plate disposed along the radial direction of the rotating shaft 410, and the like, so that the mounting base 210 and the rotating shaft 410 are relatively fixed and can synchronously rotate along with the rotating shaft 410.

Referring to fig. 3, it may be understood that, in order to facilitate the coupling mechanism 200 to be coupled with the first impeller 100, the first impeller 100 is provided with a sleeve 110, the sleeve 110 extends along a center line direction of the first impeller 100 and is sleeved on the rotating shaft 410, and the mounting seat 210 is sleeved on an outer circumference of the sleeve 110. The side of the sleeve 110 facing the center line Z of the first impeller 100 is defined as the inner side, and the side of the sleeve 110 facing away from the center line Z of the first impeller 100 is defined as the outer side.

Referring to fig. 4 and 5, it can be understood that the clutch mechanism 200 further includes a clutch member 220, the clutch member 220 is located at the outer side of the sleeve 110, the clutch member 220 is composed of an elastic member 221 and a coupling member 222, specifically, the coupling member 222 is configured in a columnar structure or a spherical structure, such as a steel column, a steel ball, etc., and the cross section of the coupling member 222 can be circular, polygonal, etc. The coupling member 222 is slidably mounted on the mounting base 210, and an included angle between a sliding direction of the coupling member 222 and a center line Z of the first impeller 100 is greater than O °, and the coupling member 222 is slidably mounted on the mounting base 210 along a radial direction of the rotation shaft 410. In other embodiments, the sliding direction of the coupling member 222 may also be inclined with respect to the radial direction of the rotation shaft 410.

Referring to fig. 4 and 5, it can be understood that the mount 210 is provided with a sliding groove 211, the sliding groove 211 is arranged along a radial direction of the rotation shaft 410, the sliding groove 211 is located at an outer side of the sleeve 110, and one end of the sliding groove 211 is opened and opened toward a center line Z of the first impeller 100, the other end of the sliding groove 211 is provided with an end cap 212, and the end cap 212 is fixedly connected with the mount 210 by means of screw connection, welding, or the like, or the end cap 212 and the mount 210 are in an integrally formed structure. The combining piece 222 is slidably mounted on the sliding slot 211 and can partially extend out of the opening of the sliding slot 211, so as to accurately guide the combining piece 222.

Referring to fig. 4 and 5, it can be understood that, based on the clutch member 220 being located at the outside of the sleeve 110, i.e., the coupler 222 is located at one side of a reference plane passing through the center line Z of the first impeller 100. One end of the slot, which defines the coupling member 222 capable of extending out of the sliding slot 211, is defined as a coupling portion 2221, so that at this time, the centroid of the coupling member 222 and the coupling portion 2221 are located at the same side of the reference plane, and the centroid of the coupling member 222 and the coupling portion 2221 must move in the same direction.

Referring to fig. 4 and 5, it can be understood that the elastic member 221 may be a spring, a spring sheet, or the like, and the elastic member 221 is installed in the sliding slot 211 and located between the end cover 212 and the coupling member 222, and generally, the elastic member 221 is in a pre-compressed state, and the elastic member 221 applies a force F ₁ to the coupling member 222 in a radial inward direction of the rotating shaft 410 under the elastic action of the elastic member 221.

Of course, it is understood that the elastic member 221 may be in a pre-stretched state, based on which one end of the elastic member 221 is connected to the sliding slot 211 near the opening, and the other end is connected to the opening of the combining member 222 away from the sliding slot 211, for example, when the elastic member 221 is a spring, the spring is sleeved on the combining member 222, so that the elastic member 221 can apply the force F ₁ to the combining member 222 in the radial inward direction of the rotating shaft 410.

As can be appreciated from the description of fig. 4 and 5, the first impeller 100 includes the transmission portion 120 corresponding to the coupling member 222, specifically, the transmission portion 120 is provided at the outer circumferential wall of the sleeve 110, and the transmission portion 120 may be a convex portion or a concave portion. The transmission portion 120 is a protrusion, which protrudes outward along the radial direction of the rotating shaft 410, and when the engaging portion 2221 of the engaging member 222 protrudes out of the opening of the sliding slot 211 and abuts against one side of the protrusion along the circumferential direction of the rotating shaft 410, that is, the engaging member 222 is engaged with the transmission portion 120, at this time, the torque of the rotating shaft 410 can be transmitted to the first impeller 100 through the clutch mechanism 200, so that the first impeller 100 can rotate synchronously with the clutch mechanism 200 and the rotating shaft 410. In other embodiments, the transmission portion 120 is a recess, the opening of the recess faces to the outside, and when the coupling portion 2221 of the coupling member 222 protrudes out of the opening of the sliding slot 211 and is inserted into the recess, the coupling member 222 is coupled to the transmission portion 120, and similarly, the first impeller 100 can rotate synchronously with the clutch mechanism 200 and the rotating shaft 410.

As can be readily appreciated by reference to fig. 4, as the shaft 410 rotates, the clutch mechanism 200 rotates with the shaft 410, since the center of mass of the coupler 222 is offset from the axis of rotation of the shaft 410 (also the centerline Z of the first impeller 100), the coupler 222 will be subjected to centrifugal force F ₂, which is directed radially outward of the shaft 410, That is, the centrifugal force F ₂ applied to the coupling member 222 is opposite to the force F ₁ applied to the coupling member 222 by the elastic member 221. When the rotation shaft 410 does not rotate, the centrifugal force F ₂ =0, at this time, the coupling member 222 is only subjected to the force F ₁ exerted by the elastic member 221, and the coupling member 222 is driven to move toward the center line Z of the first impeller 100 under the force F ₁ of the elastic member 221, The coupling portion 2221 of the coupling member 222 is protruded from the opening of the sliding slot 211, so that the coupling member 222 is coupled with the transmission portion 120, that is, the rotation shaft 410 is coupled with the first impeller 100 through the clutch mechanism 200. As the rotating shaft 410 rotates, the rotating shaft 410 can drive the first impeller 100 to rotate through the clutch mechanism 200, and the coupling member 222 is subjected to the centrifugal force F ₂, so that the magnitude of the centrifugal force F ₂ increases with the increase of the rotation speed. It is easy to understand that the critical rotation speed N ₁ exists, when the rotation speed of the rotation shaft 410 is equal to N ₁, F ₂＝F₁, the coupling member 222 maintains the coupled state with the transmission part 120, and the first impeller 100 rotates along with the rotation shaft 410. When the rotation speed of the rotation shaft 410 (i.e., the rotation speed of the motor) is less than N ₁, F ₂＜F₁, the coupling member 222 and the transmission portion 120 maintain the coupled state, and the first impeller 100 rotates along with the rotation shaft 410. When the rotation speed of the rotation shaft 410 is greater than N ₁, under the action of the centrifugal force F ₂, F ₂＞F₁ drives the combining element 222 to move towards the direction away from the center line Z of the first impeller 100, so that the combining portion 2221 of the combining element 222 is separated from the transmission portion 120, And the coupling portion 2221 is retracted into the slide groove 211, so that the clutch mechanism 200 is separated from the first impeller 100, i.e., the rotation shaft 410 is separated from the first impeller 100, and at this time, only the rotation shaft 410 and the clutch mechanism 200 are rotated, and the first impeller 100 is not rotated.

When the rotation speed of the motor is defined to be less than N ₁, the clutch mechanism 200 is in a first state, and when the rotation speed of the motor is greater than N ₁, the clutch mechanism 200 is in a second state, so that in the first state of low rotation speed, the clutch mechanism 200 can synchronously rotate with the first impeller 100, namely the first impeller 100 synchronously rotates with the rotating shaft 410, and is suitable for radiating heat of the motor, in the second state of high rotation speed, the clutch mechanism 200 can be separated from the first impeller 100, so that the first impeller 100 is separated from the rotating shaft 410, the first impeller 100 stops rotating, pneumatic noise and wind resistance loss caused by high rotation speed are avoided, and the influence on the output power of the motor is reduced.

For the washing machine, at least two working conditions of washing and dehydration exist, under the washing working condition, the rotating speed of the driving motor is smaller than N ₁, namely the low rotating speed, and under the dehydration working condition, the rotating speed of the driving motor is larger than N ₁, namely the high rotating speed. Therefore, for the washing machine, under the washing condition, the first impeller 100 and the rotating shaft 410 rotate synchronously, so that heat of the driving motor can be dissipated, and the winding temperature rise of the driving motor can be reduced by 30K or more. Under the dehydration working condition, the first impeller 100 is separated from the rotating shaft 410, the first impeller 100 does not rotate, so that pneumatic noise and wind resistance loss caused by high rotation speed can be avoided, the additionally consumed shaft power is less than 0.2W, and the influence on the output power of the driving motor is reduced.

It will be appreciated that in other embodiments, the coupling member 222 may be configured as an elongated structure and rotatably mounted to the mounting base 210, specifically, based on the clutch member 220 being located at the outer side of the sleeve 110, one end of the coupling member 222 is rotatably mounted to the mounting base 210, the other end is connected to the mounting base 210 through the elastic member 221, and the direction of the force applied to the coupling member 222 by the elastic member 221 is toward the center line Z of the first impeller 100, the coupling portion 2221 is disposed between two ends of the coupling member 222 and protrudes toward the center line Z of the first impeller 100 to be engaged with the transmission portion 120, therefore, The center of mass of the coupling portion 2221 and the coupling member 222 are located at the same side of the reference plane passing through the rotation axis of the coupling member 222, and rotate along with the coupling member 222, the center of mass of the coupling portion 2221 and the coupling member 222 are necessarily offset in the same direction, and the coupling portion 2221 and the transmission portion 120 can be driven to be coupled under the force of the elastic member 221. At this time, when the rotation shaft 410 rotates, the centrifugal force F ₄ applied to the coupling member 222 is directed outward in the radial direction of the rotation shaft 410. Therefore, similarly, when the rotation shaft 410 does not rotate, F ₄ =0, the coupling member 222 only receives the force applied by the elastic member 221, and the coupling member 222 is coupled to the transmission portion 120. When the rotation speed of the rotation shaft 410 is the critical rotation speed N ₂, the acting force F ₃ of the elastic member 221 on the coupling member 222 in the radial direction of the rotation shaft 410 is equal to the centrifugal force F ₄, the coupling member 222 maintains the coupled state with the transmission portion 120, The first impeller 100 rotates with the rotation shaft 410. Therefore, when the rotation speed of the rotation shaft 410 is less than N ₂, F ₄＜F₃, the coupling member 222 and the transmission portion 120 keep the coupled state, and the first impeller 100 rotates along with the rotation shaft 410; when the rotation speed of the rotation shaft 410 is greater than N ₂, F ₄＞F₃, the coupling portion 2221 of the coupling member 222 is separated from the transmission portion 120, and the first impeller 100 does not rotate.

It will be appreciated that when the direction of the force applied by the elastic member 221 to the coupling member 222 is inward along the radial direction of the rotating shaft 410, F ₃ is the force applied by the elastic member 221 to the coupling member 222, and when the direction of the force applied by the elastic member 221 to the coupling member 222 is inclined with respect to the radial direction of the rotating shaft 410, F ₃ is the component force of the force applied by the elastic member 221 to the coupling member 222 in the radial direction of the rotating shaft 410.

It should be understood that, in other embodiments, the first impeller 100 may not be provided with the sleeve 110, the transmission portion 120 is disposed on one side of the first impeller 100 along the centerline direction, the transmission portion 120 is a concave portion opened towards the radial direction or a convex portion protruding towards the radial direction, the coupling member 222 is slidably mounted on the mounting base 210 along the radial direction of the rotating shaft 410, and one end (i.e. the coupling portion 2221) of the coupling member 222 towards the first impeller 100 extends out of the mounting base 210, and the coupling portion 2221 is located at the radial outer side of the transmission portion 120 along the first impeller 100. Therefore, when the coupling member 222 moves along the radial direction of the rotation shaft 410, the coupling portion 2221 can be coupled to or separated from the transmission portion 120, i.e. the rotation shaft 410 is coupled to or separated from the first impeller 100, which will not be described herein.

Referring to fig. 4 and 5, it may be understood that the clutch mechanism 200 includes a plurality of clutch members 220, and the clutch mechanism 200 includes two clutch members 220, and the two clutch members 220 are arranged centering symmetrically about the center line Z of the first impeller 100, and correspondingly, the first impeller 100 is provided with the transmission parts 120 arranged in one-to-one correspondence with the clutch members 220. Therefore, when the clutch mechanism 200 is combined with the first impeller 100, the combining pieces 222 of the two clutch members 220 are respectively combined with the two transmission parts 120, so that the clutch mechanism 200 applies forces to two positions of the first impeller 100 during rotation, and the forces at the two positions are balanced in the radial direction of the first impeller 100, so that the first impeller 100 is stressed and balanced in the radial direction, vibration and noise of the first impeller 100 in the rotation process are avoided, and meanwhile, the reliability of the combination of the clutch mechanism 200 and the first impeller 100 is improved. Of course, the number of the clutch members 220 may be three, four or more, and will not be described here.

Referring to fig. 4, it may be understood that the transmission part 120 is elongated and extends along the center line direction of the first impeller 100, and the transmission part 120 is illustratively provided as an elongated groove disposed along the center line direction of the first impeller 100, or the transmission part 120 is provided as an elongated rib disposed along the center line direction of the first impeller 100. Therefore, when the coupling member 222 is coupled with the transmission portion 120, the coupling member 222 can be coupled with any position of the transmission portion 120 along the center line direction of the first impeller 100, so that the allowable installation error range of the clutch mechanism 200 in the center line direction of the first impeller 100 can be increased, the installation difficulty can be reduced, and the assembly can be facilitated.

Referring to fig. 6, it is understood that in other embodiments, the sleeve 110 is sleeved on the outer periphery of the mounting base 210, and based on this, the transmission part 120 is disposed on the inner peripheral wall of the sleeve 110, and the clutch member 220 is located inside the sleeve 110. Specifically, the coupling 222 includes a stem 2222 and a head 2223, the head 2223 is connected to one end of the stem 2222, the outer diameter of the head 2223 is greater than the outer diameter of the stem 2222, and one end of the stem 2222 facing away from the head 2223 is the coupling portion 2221. The coupling member 222 is slidably mounted in the sliding groove 211 of the mounting base 210 along the radial direction of the rotating shaft 410, and the length direction of the rod portion 2222 is parallel to the sliding direction, so that the coupling portion 2221 can extend out of the opening of the sliding groove 211. Since the head 2223 is disposed at one end of the lever portion 2222, the centroid of the joint 222 is biased toward one end of the head 2223, so that the centroid of the joint 222 and the joint 2221 are located at both sides of a reference plane passing through the center line Z of the first impeller 100, respectively. The elastic member 221 is installed between the head 2223 and the end cap 212 at the other end of the sliding slot 211, and the force F ₅ applied by the elastic member 221 to the head 2223 is directed inward along the radial direction of the rotating shaft 410, so that the center of mass of the combining member 222 can be driven to move toward the center line Z of the first impeller 100 under the force F ₅ of the elastic member 221, and the combining portion 2221 moves along the direction away from the center line Z of the first impeller 100, so that the combining portion 2221 protrudes out of the opening of the sliding slot 211 to be combined with the transmission portion 120.

Referring to fig. 6, it can be appreciated that as the shaft 410 rotates, the coupler 222 is subjected to centrifugal force F ₆ at the center of mass, which is directed radially outward of the shaft 410. That is, at the centroid of the coupler 222, the force F ₅ applied by the elastic member 221 to the coupler 222 is opposite to the direction of the centrifugal force F ₆. Under the action of the centrifugal force F ₆, the center of mass can be driven to move along the direction away from the center line Z of the first impeller 100, and the combining portion 2221 moves toward the center line Z of the first impeller 100, so that the combining portion 2221 is separated from the transmission portion 120 and is retracted into the sliding slot 211.

Therefore, similarly, when the rotation shaft 410 does not rotate, F ₆ =0, the coupling member 222 receives only the force F ₅ applied by the elastic member 221, and the coupling member 222 is coupled with the transmission portion 120. When the rotation speed of the rotation shaft 410 is the critical rotation speed N ₃, the acting force F ₅ of the elastic member 221 on the coupling member 222 is equal to the centrifugal force F ₆, the coupling member 222 and the transmission portion 120 are kept in a coupled state, and the first impeller 100 rotates along with the rotation shaft 410. Therefore, when the rotation speed of the rotation shaft 410 is less than N ₃, F ₆＜F₅, the coupling member 222 and the transmission portion 120 keep the coupled state, and the first impeller 100 rotates along with the rotation shaft 410; when the rotation speed of the rotation shaft 410 is greater than N ₃, F ₆＞F₅, the coupling member 222 is separated from the transmission part 120, and the first impeller 100 does not rotate.

It should be understood that, in other embodiments, based on the sleeve 110 being sleeved on the outer periphery of the mounting base 210, the transmission portion 120 being disposed on the inner peripheral wall of the sleeve 110, and the clutch member 220 being disposed inside the sleeve 110, the coupling member 222 is in an elongated structure and is rotatably mounted on the mounting base 210, the coupling member 222 is integrally disposed on one side of a reference plane passing through the center line Z of the first impeller 100, the rotation center of the coupling member 222 is disposed between two ends, one end of the coupling member 222 is disposed with the coupling portion 2221 facing away from the center line Z of the first impeller 100, the other end of the coupling member 222 is connected with the mounting base 210 by the elastic member 221, the center of mass of the coupling member 222 and the coupling portion 2221 are disposed on two sides of the rotation center, i.e. the elastic member 221 and the center of mass are disposed on the same side of the rotation center, the elastic member 221 applies a force to one end of the coupling member 222 facing toward the center line Z of the first impeller 100 to drive the center line Z of the first impeller 100, and the coupling portion 2221 is biased toward the direction facing away from the center line Z of the first impeller 100, so as to couple the coupling portion 2221 with the transmission portion 120. When the rotation shaft 410 rotates, the centroid of the coupling portion 2221 is acted upon by a centrifugal force, and the centroid can be driven to deviate from the central line Z of the first impeller 100 under the action of the centrifugal force, and the coupling portion 2221 deviates from the central line Z of the first impeller 100, so that the coupling portion 2221 is separated from the transmission portion 120. The matching state of the coupling portion 2221 and the transmission portion 120 when the rotation shaft 410 is at different rotation speeds is not described herein.

It should be understood that, in other embodiments, the first impeller 100 may not be provided with the sleeve 110, and the clutch mechanism 200 is disposed in the hollow structure of the first impeller 100, and the connection structure may refer to the connection structure when the sleeve 110 is sleeved on the outer periphery of the mounting base 210, which will not be described herein.

Referring to fig. 2, a second embodiment of the present utility model provides a driving device, where the driving device includes a motor body 400 and an impeller assembly of any of the above embodiments, the motor body 400 may be a driving motor of a washing machine, the motor body 400 is provided with a rotating shaft 410, and the impeller assembly is mounted on the rotating shaft 410, which is not described herein.

The driving device adopts all the technical schemes of the impeller assembly of the embodiment, so that the driving device has at least all the beneficial effects brought by the technical schemes of the embodiment.

Referring to fig. 2, it can be understood that the first impeller 100 does not rotate in the second state of the high rotation speed, and thus heat cannot be dissipated from the motor body 400. For this reason, the driving device further includes a second impeller 300, where the second impeller 300 is fixedly mounted on the rotating shaft 410 and can rotate along with the rotating shaft 410, and the second impeller 300 and the first impeller 100 are respectively located at two ends of the motor body 400 along the axial direction, or the second impeller 300 and the first impeller 100 are both located at the same end of the motor body 400 along the axial direction, so as to avoid that the first impeller 100 blocks the wind of the second impeller 300, and at this time, the second impeller 300 is closer to the motor body 400 than the first impeller 100. To avoid aerodynamic noise and windage losses associated with the second impeller 300 at high rotational speeds, the outer diameter of the second impeller 300 is smaller than the outer diameter of the first impeller 100. Generally, at a high rotation speed, the larger the outer diameter of the second impeller 300, the better the heat dissipation effect, but the larger the aerodynamic noise and windage loss, whereas the worse the heat dissipation effect, the smaller the aerodynamic noise and windage loss. The higher the rotating speed of the impeller with the same outer diameter is, the better the heat dissipation effect is, and the worse the heat dissipation effect is. Therefore, the outer diameter of the second impeller 300 is smaller, so that aerodynamic noise and windage loss caused by high rotation speed can be reduced, and at the same time, the second impeller 300 with smaller outer diameter can effectively dissipate heat of the motor body 400.

Referring to fig. 2, it can be appreciated that the first impeller 100 has an outer diameter D ₁ and the second impeller 300 has an outer diameter D ₂. For the motor body 400 having at least two different rotational speed steps, the rotational speed at the low rotational speed step (i.e., the clutch mechanism 200 is in the first state) is defined as V ₁, and the rotational speed at the high rotational speed step (i.e., the clutch mechanism 200 is in the second state) is defined as V ₂. The method meets the following conditions: d ₁/D₂＝V₂/V₁. That is, the ratio of the outer diameters of the first impeller 100 and the second impeller 300 is equal to the ratio of the rotational speed corresponding to the high rotational speed gear to the rotational speed corresponding to the low rotational speed gear. Therefore, in the low rotation speed gear, the first impeller 100 is combined with the rotating shaft 410 and rotates along with the rotating shaft 410, the outer diameter of the first impeller 100 is larger, the heat dissipation effect is obvious, the heat dissipation effect is mainly achieved by the first impeller 100 on the motor body 400, the second impeller 300 also rotates along with the rotating shaft 410, the outer diameter of the second impeller 300 is smaller, and a certain heat dissipation effect is achieved on the motor body 400. In the high-speed gear, the first impeller 100 is separated from the rotating shaft 410, the first impeller 100 does not rotate, the second impeller 300 rotates along with the rotating shaft 410 at a high speed, and at this time, the air volume of the second impeller 300 is equivalent to the air volume of the first impeller 100 at a low speed, so that heat dissipation of the motor body 400 is achieved. Therefore, the motor body 400 can be effectively cooled no matter in a low-rotation speed gear or a high-rotation speed gear, and meanwhile, the aerodynamic noise and wind resistance loss caused by high rotation speed can be reduced, and the influence on the output power of the motor body 400 is reduced.

Of course, it is understood that the second impeller 300 may be a component directly machined on the rotation shaft 410, or the second impeller 300 may be integrated on a pulley, where the pulley is a component mounted on the rotation shaft 410 for driving the drum or impeller to rotate in the washing machine.

A washing machine according to an embodiment of a third aspect of the present utility model includes the driving apparatus of any of the above embodiments.

The washing machine adopts all the technical schemes of the driving device of the embodiment, so the washing machine has at least all the beneficial effects brought by the technical schemes of the embodiment.

The embodiments of the present utility model have been described in detail with reference to the accompanying drawings, but the present utility model is not limited to the above embodiments, and various changes can be made within the knowledge of one of ordinary skill in the art without departing from the spirit of the present utility model.

Claims (17)

1. Impeller subassembly is applied to the motor, its characterized in that, impeller subassembly includes:

the first impeller is arranged on the rotating shaft of the motor and rotates relative to the rotating shaft;

The clutch mechanism is fixedly arranged on the rotating shaft, and synchronously rotates with the first impeller when the clutch mechanism is in a first state, and is separated from the first impeller when the clutch mechanism is in a second state;

When the clutch mechanism is in the first state, the rotating speed of the motor is V ₁, and when the clutch mechanism is in the second state, the rotating speed of the motor is V ₂, so that the following conditions are satisfied: v ₁＜V₂.

2. The impeller assembly of claim 1, wherein: the clutch mechanism comprises a mounting seat and a clutch member, the clutch member comprises an elastic piece and a combining piece, the mounting seat is suitable for being connected with the rotating shaft, the combining piece is movably mounted on the mounting seat, the elastic piece is arranged on the mounting seat, the first impeller comprises a transmission part, when the clutch mechanism is in a first state, the elastic piece can drive the combining piece to deviate so that the combining piece is combined with the transmission part, and when the clutch mechanism is in a second state, the combining piece can reversely deviate and is separated from the transmission part.

3. The impeller assembly of claim 2, wherein: the combined piece is slidably mounted on the mounting seat, and an included angle between the sliding direction of the combined piece and the central line of the first impeller is larger than 0 degrees.

4. An impeller assembly according to claim 3, wherein: the combining piece is positioned on one side of a reference plane passing through the central line of the first impeller, and when the clutch mechanism is in the first state, the elastic piece can drive the combining piece to move towards the central line of the first impeller.

5. An impeller assembly according to claim 3, wherein: the clutch mechanism includes a plurality of the clutch members, and the plurality of clutch members are arranged centrally symmetrically about a center line of the first impeller.

6. An impeller assembly according to claim 3, wherein: the combined part is provided with a combined part, the mass center of the combined part and the combined part are respectively positioned at two sides of a reference plane passing through the central line of the first impeller, when the clutch mechanism is in the first state, the elastic part can drive the mass center to move towards the central line of the first impeller, and the combined part moves towards the direction deviating from the central line of the first impeller.

7. The impeller assembly of claim 6, wherein: the combination piece comprises a rod part and a head part, wherein the head part is connected to one end of the rod part, the other end of the rod part is provided with the combination part, the outer diameter of the head part is larger than that of the rod part, and the head part and the combination part are respectively positioned on two sides of the reference plane.

8. The impeller assembly of claim 2, wherein: the transmission part is a convex part, and the combining piece can be abutted against one side of the convex part along the circumferential direction of the first impeller.

9. The impeller assembly of claim 2, wherein: the transmission part is a concave part, and the combining piece can be partially accommodated in the concave part.

10. The impeller assembly of claim 2, 8 or 9, wherein: the transmission part is long-strip-shaped and extends along the central line direction of the first impeller.

11. The impeller assembly of claim 2, wherein: the first impeller is provided with a sleeve, the sleeve extends along the central line direction of the first impeller, the transmission part is arranged on the sleeve, the mounting seat is sleeved on the periphery of the sleeve, or the sleeve is sleeved on the periphery of the mounting seat.

12. The impeller assembly of claim 1, wherein: the first impeller is provided with a bearing, and the first impeller is suitable for being mounted on a rotating shaft of the motor through the bearing.

13. A drive apparatus, comprising:

The motor body is provided with a rotating shaft;

An impeller assembly according to any one of claims 1 to 12, mounted to the shaft.

14. The drive of claim 13, wherein: the rotary shaft is provided with a first impeller, and the rotary shaft is provided with a second impeller which is arranged on the rotary shaft, and the outer diameter of the second impeller is smaller than that of the first impeller.

15. The drive of claim 14, wherein: the external diameter of first impeller is D ₁, the external diameter of second impeller is D ₂, satisfies: d ₁/D₂＝V₂/V₁.

16. The drive device according to claim 14 or 15, characterized in that:

The first impeller and the second impeller are positioned at one end of the motor body along the axial direction of the rotating shaft, and the second impeller is closer to the motor body than the first impeller;

Or the first impeller and the second impeller are respectively positioned at two ends of the motor body along the axial direction of the rotating shaft.

17. Laundry washing machine, characterized by comprising a drive device according to any of claims 13 to 16.