CN216290545U - Device for realizing high-frequency vibration by combining radial magnetization with bidirectional magnetic rebound - Google Patents

Abstract

The utility model provides a device for realizing high-frequency vibration by combining radial magnetization with bidirectional magnetic rebound, which comprises a shell, a driving piece, an output shaft, an axial magnetic rebound assembly and a circumferential magnetic rebound assembly, wherein the shell is provided with a magnetic core; the driving shaft of the driving piece is coaxially connected with a driving sleeve, and a plurality of first radial magnetizing bodies are distributed on the driving sleeve at intervals along the circumferential direction of the driving sleeve; the output shaft rotates to be connected in the casing, and has the endwise slip's of edge casing degree of freedom, and coaxial coupling has the driven cover on the output shaft, and the driven cover cup joints with the initiative cover is coaxial, and has a plurality of second radial magnet that fills along its circumference interval distribution on the driven cover. According to the device for realizing high-frequency vibration by combining radial magnetization with bidirectional magnetic rebound, the output shaft can vibrate in a circumferential direction and an axial direction in a reciprocating mode, the vibration frequency of the output shaft can be improved in multiples, the driving piece is far away from the output shaft, the waterproofness can be improved, and the overload resistance can be improved by a mode of separating, coupling and driving the output shaft and the driving shaft.

Description

Device for realizing high-frequency vibration by combining radial magnetization with bidirectional magnetic rebound

Technical Field

The utility model belongs to the technical field of vibration generating devices, and particularly relates to a device for realizing high-frequency vibration by combining radial magnetization with bidirectional magnetic rebound.

Background

Along with the improvement of life quality of people, the demand on products such as electric toothbrushes, massagers and the like is higher and higher, core components of the products are vibration generating devices capable of realizing high-frequency vibration, the conventional vibration generating devices mainly generate radial single-degree-of-freedom rotary vibration quantity by means of rotation of a motor and a pendulum, and the vibration frequency of the structural mode is extremely low and difficult to break through to a higher degree.

Because the vibration frequency is directly related to the performance of the product, the current vibration generating device extremely depends on the rotating speed of the motor, and the output rotating speed of the motor is difficult to increase under the current technical condition, so how to output higher vibration frequency is the key for increasing the performance of the vibration generating type product.

In addition, because the motor that current vibration generating device adopted mostly with the product sharing casing, through the alternating magnetic field output torque that sets up production between inside solenoid of casing and the iron core, solenoid and power take off terminal position are close, therefore the waterproof performance of product is relatively poor, and to high frequency vibration, owing to produce the overload phenomenon very easily, and can lead to solenoid burning loss during the overload to influence the life of product.

SUMMERY OF THE UTILITY MODEL

The embodiment of the utility model provides a device for realizing high-frequency vibration by combining radial magnetization with bidirectional magnetic rebound, aiming at improving the output frequency, the waterproofness and the overload resistance of a vibration generating device.

In order to achieve the purpose, the utility model adopts the technical scheme that: the device for realizing high-frequency vibration by combining radial magnetization with bidirectional magnetic rebound comprises a shell, a driving piece arranged at one end of the shell, an output shaft, an axial magnetic rebound assembly and a circumferential magnetic rebound assembly; the driving part is provided with a driving shaft which extends into the shell along the axial direction of the shell, the extending end of the driving shaft is coaxially connected with a driving sleeve, a plurality of first radial magnetizing bodies are distributed on the driving sleeve at intervals along the circumferential direction of the driving sleeve, and each first radial magnetizing body extends along the axial direction of the driving sleeve; the output shaft is rotatably connected in the shell along the axial direction of the shell and has freedom degree sliding along the axial direction of the shell, one end of the output shaft facing the driving shaft is coaxially connected with a driven sleeve, the driven sleeve is coaxially sleeved with the driving sleeve, a plurality of second radial magnetizing bodies are distributed on the driven sleeve at intervals along the circumferential direction of the driven sleeve, and each second radial magnetizing body corresponds to each first radial magnetizing body along the radial direction of the output shaft and is staggered along the axial direction of the output shaft; the axial magnetic rebound assembly comprises an axial fixed end and an axial floating end, the axial fixed end is fixedly connected with the shell, the axial floating end is fixedly connected with the output shaft, and an axial magnetic repulsion force for damping the sliding of the output shaft is arranged between the axial fixed end and the axial floating end; the circumferential magnetic resilience assembly comprises a circumferential fixed end and a circumferential floating end, the circumferential fixed end is fixedly connected with the shell, the circumferential floating end is fixedly connected with the output shaft, and a circumferential magnetic repulsion force used for damping the rotation of the output shaft is arranged between the circumferential floating end and the circumferential fixed end.

In one possible implementation manner, the axial magnetic rebound assembly comprises two fixed magnetic rings and a movable magnetic ring, wherein the two fixed magnetic rings are embedded on the inner peripheral wall of the casing at intervals along the axial direction of the casing and are sleeved on the output shaft; the movable magnetic ring is fixedly sleeved on the output shaft and is positioned between the two fixed magnetic rings, and the movable magnetic ring and the two fixed magnetic rings repel each other along the axial direction of the output shaft.

In some embodiments, the axial magnetic rebound assembly comprises a fixed magnetic ring and two movable magnetic rings, wherein the fixed magnetic ring is embedded on the inner peripheral wall of the casing and is sleeved on the output shaft; the two movable magnetic rings are fixedly sleeved on the output shaft at intervals along the axial direction of the output shaft and are respectively positioned on two sides of the fixed magnetic ring, and the two movable magnetic rings and the fixed magnetic ring repel each other along the axial direction of the output shaft.

In one possible implementation manner, the circumferential magnetic rebound assembly comprises a rotor and a stator, wherein the rotor is fixedly sleeved on the output shaft, and a first magnetic assembly is arranged on the rotor; the stator is sleeved on the rotor along the axial direction of the output shaft and fixedly connected with the inner wall of the shell, a second magnetic assembly is arranged on the stator, and a circumferential magnetic repulsion force is arranged between the second magnetic assembly and the first magnetic assembly.

Exemplarily, the second magnetic assembly comprises 2n second permanent magnets, n first sector cavities are distributed at intervals along the circumferential direction of the stator, and two second permanent magnets are respectively embedded on two plane cavity walls of each first sector cavity; the first magnetic force assembly comprises n first permanent magnets embedded on the peripheral wall of the rotor, each first permanent magnet correspondingly extends into each first sector cavity along the radial direction of the rotor, and each first permanent magnet and the corresponding two second permanent magnets repel each other along the circumferential direction of the stator.

Furthermore, n first side extension plates which correspondingly extend into the first sector cavities along the radial direction of the rotor are distributed on the peripheral wall of the rotor at intervals, and a first permanent magnet is embedded on each first side extension plate.

For example, the first magnetic assembly includes 2n first permanent magnets, n second sector cavities are circumferentially distributed on the rotor at intervals, and two planar cavity walls of each second sector cavity are respectively embedded with one first permanent magnet; the second magnetic force component comprises n second permanent magnets embedded on the inner peripheral wall of the stator, each second permanent magnet correspondingly extends into each second sector cavity along the radial direction of the stator, and each second permanent magnet and the corresponding two first permanent magnets repel each other along the circumferential direction of the stator.

Furthermore, n second side extension plates which correspondingly extend into the second sector cavities along the radial direction of the second side extension plates are distributed on the inner peripheral wall of the stator at intervals, and a second permanent magnet is embedded on each second side extension plate.

In some embodiments, the drive member is a motor.

Illustratively, the first radially charged magnet and the second radially charged magnet attract or repel each other.

The device for realizing high-frequency vibration by combining radial magnetization with bidirectional magnetic rebound has the beneficial effects that: compared with the prior art, the device for realizing high-frequency vibration by combining radial magnetization with bidirectional magnetic rebound can realize reciprocating vibration of the output shaft along the circumferential direction and the axial direction by utilizing the combined cooperation of the magnetic coupling force, the axial magnetic repulsion force and the circumferential magnetic repulsion force between the first radial magnetization body and the second radial magnetization body in the process that the driving piece drives the driving sleeve to rotate through the driving shaft, and can bring one time of reciprocating vibration along the circumferential direction and the axial direction in each alternating process of the second radial magnetization body and the first radial magnetization body, so that the output shaft can generate a plurality of times of combined vibration frequency along the circumferential direction and the axial direction in the process that the driving sleeve rotates for one circle, and the vibration frequency of the output shaft can be doubled under the condition that the input rotating speed of the driving piece is not changed; only the driving part far away from the output shaft is a charged part, and all parts in the shell have water resistance, so that the waterproof performance of the product can be improved; in addition, because output shaft and drive shaft are split type structural style, consequently transship at the output and cause the moment on the output shaft to increase to when surpassing the magnetic coupling power, the driven shaft can be under the overload force effect automatic reduction vibration frequency or stop the vibration, and the drive shaft still can normal operating to avoid the driving piece to damage because of overloading, anti overload capacity is strong, can improve product life.

Drawings

Fig. 1 is a schematic structural diagram of an apparatus for implementing high-frequency vibration by combining radial magnetization and bidirectional magnetic rebound provided in an embodiment of the present invention;

FIG. 2 is a schematic structural diagram of an apparatus for achieving high-frequency vibration by radial magnetization combined with bidirectional magnetic rebound according to another embodiment of the present invention;

FIG. 3 is a schematic cross-sectional view taken along line A-A of FIG. 1;

FIG. 4 is a schematic cross-sectional view of a first embodiment of a circumferential magnetically resilient component employed in embodiments of the present invention;

FIG. 5 is a schematic cross-sectional view of a second embodiment of a circumferential magnetically resilient component employed in embodiments of the present invention;

FIG. 6 is a schematic cross-sectional view of a third embodiment of a circumferential magnetically resilient component employed in embodiments of the present invention;

fig. 7 is a schematic cross-sectional structure diagram of a fourth embodiment of a circumferential magnetically-resilient component employed in an embodiment of the present invention.

In the figure: 10. a housing; 11. a bearing; 12. a sliding sleeve; 20. a drive member; 21. a drive shaft; 22. an active sleeve; 23. a first radial charging magnet; 30. an output shaft; 31. a driven sleeve; 32. a second radial charging magnet; 40. an axial magnetically resilient component; 41. a fixed magnetic ring; 42. a movable magnetic ring; 50. a circumferential magnetic rebound assembly; 51. a rotor; 511. a first permanent magnet; 512. a first side extension plate; 513. a second fan-shaped cavity; 52. a stator; 521. a second permanent magnet; 522. a first fan-shaped cavity; 523. a second side extension plate.

Detailed Description

In order to make the technical problems, technical solutions and advantageous effects to be solved by the present invention more clearly apparent, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the utility model and are not intended to limit the utility model.

Referring to fig. 1 to 4, a device for realizing high frequency vibration by combining radial magnetization and bidirectional magnetic rebound provided by the utility model will be described. The device for realizing high-frequency vibration by combining radial magnetization with bidirectional magnetic rebound comprises a machine shell 10, a driving piece 20 arranged at one end of the machine shell 10, an output shaft 30, an axial magnetic rebound assembly 40 and a circumferential magnetic rebound assembly 50; the driving member 20 has a driving shaft 21 extending into the casing 10 along the axial direction of the casing 10, the extending end of the driving shaft 21 is coaxially connected with a driving sleeve 22, a plurality of first radial magnetizing bodies 23 are distributed on the driving sleeve 22 at intervals along the circumferential direction thereof, and each first radial magnetizing body 23 extends along the axial direction of the driving sleeve 22; the output shaft 30 is rotatably connected in the machine shell 10 along the axial direction of the machine shell 10 and has a degree of freedom of sliding along the axial direction of the machine shell 10, one end of the output shaft 30 facing the driving shaft 21 is coaxially connected with a driven sleeve 31, the driven sleeve 31 is coaxially sleeved with the driving sleeve 22, a plurality of second radial magnetizing bodies 32 are distributed on the driven sleeve 31 along the circumferential direction of the driven sleeve at intervals, and each second radial magnetizing body 32 corresponds to each first radial magnetizing body 23 along the radial direction of the output shaft 30 and is staggered along the axial direction of the output shaft 30; the axial magnetic rebound component 40 comprises an axial fixed end and an axial floating end, the axial fixed end is fixedly connected with the shell 10, the axial floating end is fixedly connected with the output shaft 30, and an axial magnetic repulsion force for damping the sliding of the output shaft 30 is arranged between the axial fixed end and the axial floating end; circumferential magnetic rebound assembly 50 comprises a circumferential fixed end and a circumferential floating end, the circumferential fixed end is fixedly connected with casing 10, the circumferential floating end is fixedly connected with output shaft 30, and a circumferential magnetic repulsion force for damping rotation of output shaft 30 is provided between the circumferential fixed end and the circumferential floating end.

It should be noted that the driving member 20 may be a high-frequency motor or an electric motor or other power source with torque output, but in the present embodiment, the purpose of achieving high-frequency vibration is taken, so the high-frequency motor is preferably adopted; the sleeve connection between the driving sleeve 22 and the driven sleeve 31 can be that the driving sleeve 22 is sleeved on the periphery of the driven sleeve 31, see fig. 1, in which case the first radial magnetizing body 23 is embedded on the inner peripheral wall of the driving sleeve 22, the second radial magnetizing body 32 is embedded on the outer peripheral wall of the driven sleeve 31, or the driven sleeve 31 is sleeved on the periphery of the driving sleeve 22, see fig. 2, at this time, the first radial magnetizing body 23 is embedded on the outer peripheral wall of the driving sleeve 22, and the second radial magnetizing body 32 is embedded on the inner peripheral wall of the driven sleeve 31, which can be realized in both ways, without specific limitation, and the sleeve connection surface between the two should have a gap to avoid interference with the axial sliding of the output shaft 30 in the housing 10; the first radial magnetizing body 23 and the second radial magnetizing body 32 are both referred to as magnetizers that magnetize along the radial direction of the output shaft 30, but it should be understood that the magnetic forces between the first radial magnetizing body 23 and the second radial magnetizing body 32 may be either mutually repulsive or mutually attractive, that is, like poles may be opposite to each other to form a repulsive coupling force, or opposite poles may be opposite to each other to form an attractive coupling force, each second radial magnetizing body 32 corresponds to each second radial magnetizing body 32 along the radial direction of the output shaft 30, so that a circumferential coupling force is generated therebetween to cause the driving sleeve 22 to drive the driven sleeve 31 to rotate, and meanwhile, referring to fig. 1 or fig. 2, since each second radial magnetizing body 32 is respectively staggered with each first radial magnetizing body 23 along the axial direction of the output shaft 30 (specifically, when the axial coupling force between the driving sleeve 22 and the driven sleeve 31 and the axial magnetic repulsive force of the axial magnetic rebound assembly 40 are in a balanced state, the axial relative positions of the first radial magnetizing bodies 23 and the second radial magnetizing bodies 32 are staggered), so that when the driving sleeve 22 starts to rotate, the axial coupling force changes to generate axial vibration of the output shaft 30, and the axial staggering can be realized by aligning the axial relative positions of the first radial magnetizing bodies 23 on the driving sleeve 22 and staggering the axial relative positions of the second radial magnetizing bodies 32 on the driven sleeve 31 in pairs, or by staggering the axial relative positions of the first radial magnetizing bodies 23 on the driving sleeve 22 in pairs and aligning the axial relative positions of the second radial magnetizing bodies 32 on the driven sleeve 31.

Regarding the waterproof performance, the first aspect is to solve from the sealing point of view to avoid the charged parts inside the casing 10 from contacting with water, and the second aspect is to adopt the structure insensitive to water under the condition of meeting the performance requirement from the product structure itself, in this embodiment, from the second aspect, the driving member 20 is disposed at the end of the casing 10 far from the output shaft 30, and the normal operation of the casing 10 and its internal components is not affected by water, so that the casing 10 has excellent waterproof performance.

For the overload resistance, the overload mainly has adverse effect on the driving member 20 and the transmission structure, and since the structure that the output shaft 30 is separated from the driving shaft 21 is adopted in the embodiment, and the power transmission is realized by the magnetic coupling force between the first radial magnetizing body 23 and the second radial magnetizing body 32, when the overload condition occurs on the output shaft 30, the overload torque exceeds the magnetic coupling force, at this time, the output shaft 30 automatically decelerates or stops rotating, and the driving shaft 21 can still rotate, therefore, even if the overload occurs on the output shaft 30, the normal operation of the driving shaft 21 and the driving member 20 can be prevented from being influenced, and the burning loss of the driving member 20 caused by the overload can be avoided.

Since the output shaft 30 is sliding reciprocally in its axial direction, the axial magnetic repulsion between the axially floating end and the axially fixed end of the axial magnetic rebound assembly 40 should be bidirectional, that is, the repulsion damping the sliding of the output shaft 30 toward the front end gradually increases when the output shaft 30 slides toward the front end, the repulsion damping the sliding of the output shaft 30 toward the rear end gradually increases when the output shaft slides toward the rear end, and similarly, the output shaft 30 is also reciprocating along its circumferential direction, and therefore the circumferential magnetic repulsion between the circumferentially floating end and the circumferentially fixed end of the circumferential magnetic rebound assembly 50 should also be bidirectional, that is, the repulsion damping the forward rotation of the output shaft 30 gradually increases when the output shaft 30 rotates in the forward direction, and the repulsion damping the reverse rotation of the output shaft 30 rotates in the reverse direction.

As shown in fig. 1 or 2, the output shaft 30 is connected to the housing 10 in such a manner that two sets of bearings 11 are fitted into the housing 10 at intervals in the axial direction thereof, a sliding sleeve 12 is fitted into an inner ring of each bearing 11, and the output shaft 30 is slidably inserted into the sliding sleeve 12. The bearing 11 provides the output shaft 30 with the freedom of circumferential rotation, and the sliding sleeve 12 provides the output shaft 30 with the freedom of axial sliding, and the structure is stable and reliable. Specifically, the circumferential magnetic rebound assembly 50 can be arranged between the two sets of bearings 11, so that the span between the two sets of bearings 11 can be properly increased, and the connection stability of the output shaft 30 can be improved.

The working principle of the device for realizing high-frequency vibration by combining radial magnetization and bidirectional magnetic rebound provided by the embodiment is as follows:

it is explained that the first radial magnetizing bodies 23 and the second radial magnetizing bodies 32 are used as repulsive force, in the shutdown state, each second radial magnetizing body 32 is respectively located between two adjacent first radial magnetizing bodies 23 adjacent to the second radial magnetizing body, so that the circumferential repulsive forces of the two adjacent first radial magnetizing bodies 23 to the second radial magnetizing bodies 32 are mutually cancelled out (of course, the balanced state should also consider the axial magnetic repulsive force of the axial magnetic rebound assembly 40 and the circumferential magnetic repulsive force of the circumferential magnetic rebound assembly 50), and meanwhile, the axial repulsive force generated by the staggered length (i.e. the center deviation distance in the axial direction) of the second radial magnetizing body 32 and the first radial magnetizing body 23 along the axial direction of the output shaft 30 and the axial magnetic repulsive force exerted by the axial magnetic rebound assembly 40 on the output shaft 30 are also in a balanced state, when the driving sleeve 22 is driven by the driving member 20 through the driving shaft 21 to start rotating, the relative position between the first radial charging magnet 23 and the second radial charging magnet 32 changes, and the circumferential distance between the second radial charging magnet 32 and the corresponding first radial charging magnet 23 gradually decreases, so that gradually increasing repulsive force is generated between the first radial charging magnet and the corresponding first radial charging magnet in both the circumferential direction and the axial direction (namely, the circumferential coupling force and the axial coupling force are gradually increased);

for circumferential reciprocating vibration, circumferential coupling force causes the driving sleeve 22 to push the driven sleeve 31 to start to rotate in the same direction, in the process of the same-direction rotation of the driven sleeve 31, circumferential magnetic repulsion force between a circumferential fixed end and a circumferential floating end of the circumferential magnetic rebound component 50 is gradually increased, so that increasingly large damping acting force is generated on the rotation of the driven sleeve 31, the rotation angle of the driven sleeve 31 is continuously lagged behind the driving sleeve 22 until the circumferential coupling force reaches the maximum value when the first radial magnetizing body 23 and the second radial magnetizing body 32 are aligned along the axial direction of the output shaft 30, the circumferential magnetic repulsion force is continuously increased until the circumferential coupling force is exceeded, so that the first radial magnetizing body 23 is caused to rotate to the other side of the second radial magnetizing body 32, at the moment, the circumferential coupling force between the first radial magnetizing body 23 and the second radial magnetizing body is reversed, and the reversed circumferential coupling force and the circumferential magnetic repulsion force jointly push the driven sleeve to start to rotate in the opposite direction, at this time, the reverse deflection angle between the second radial magnetizing body 32 and the first radial magnetizing body 23 is increased, the circumferential magnetic repulsion force gradually starts to reverse, so as to generate an increasingly larger damping acting force on the reverse rotation of the driven sleeve 31, until the second radial magnetizing body 32 is positioned between two adjacent first radial magnetizing bodies 23 adjacent to the second radial magnetizing body, the reverse circumferential coupling force is reduced to the minimum value, at this time, the deflection angle between the driven wheel and the driving wheel continues to increase, so that the second radial magnetizing body 32 starts to approach the next first radial magnetizing body 23, so as to reverse the circumferential coupling force again, at this time, the driven sleeve 31 is pushed to rotate in the same direction with the driving sleeve 22 again under the combined action of the circumferential coupling force and the circumferential magnetic repulsion force which are reversed again, so as to realize the circumferential reciprocating motion of the output shaft 30, because the driving sleeve 22 rotates by one angle (the angle is 360 degrees divided by the distribution number of the first radial magnetizing bodies 23), if the driving sleeve 22 is provided with six first radial magnetizing bodies 23, the angle is 60 °), the first radial magnetizing bodies 23 and the second radial magnetizing bodies 32 alternate once, and each time the first radial magnetizing bodies 23 and the second radial magnetizing bodies 32 alternate once, the output shaft 30 can be caused to circumferentially reciprocate once under the damping action of the circumferential magnetic rebound assembly 50, so that the output shaft 30 can generate circumferential reciprocating vibration for multiple times in the process of one rotation of the driving shaft 21, and the circumferential vibration frequency of the output shaft 30 is multiplied by the rotating speed of the driving member 20 (the amplification factor is equal to the number of the first radial magnetizing bodies 23 distributed on the driving sleeve 22);

for the axial reciprocating vibration, the axial coupling force causes the driving sleeve 22 to push the driven sleeve 31 to start to slide away, during the process of moving the driven sleeve 31 away, the axial magnetic repulsion force between the axially fixed end and the axially floating end of the axial magnetic rebound assembly 40 is gradually increased, so as to generate an increasingly greater damping force for the sliding away of the driven sleeve 31, meanwhile, the driven sleeve 31 causes the rotation angle of the driven sleeve 31 to continuously lag behind the driving sleeve 22 under the damping action of the circumferential magnetic rebound assembly 50 until the axial coupling force reaches a maximum value when the first radial magnetizing body 23 and the second radial magnetizing body 32 are aligned in the axial direction of the output shaft 30, and when the first radial magnetizing body 23 rotates to the other side of the second radial magnetizing body 32, as the two start to gradually move away, the axial coupling force between the two starts to gradually decrease, at this time, the axial magnetic repulsion force exceeds the axial coupling force, so as to cause the driven sleeve 31 to start to slide in the opposite direction to approach the driving sleeve 22, when the first radial magnetizing body 23 rotates to pass through the middle position of the two adjacent second radial magnetizing bodies 32, the axial coupling force between the first radial magnetizing body 23 and the next second radial magnetizing body 32 starts to increase, so that the axial coupling force received by the second radial magnetizing body 32 starts to be opposite, and the axial magnetic repulsion force also starts to be opposite, until the axial coupling force and the opposite axial magnetic repulsion force reach the maximum value again when the first radial magnetizing body 23 and the next second radial magnetizing body 32 are completely aligned, so that the driven sleeve 31 slides in the opposite direction again under the combined action of the axial coupling force and the axial magnetic repulsion force in the opposite direction, the driven sleeve 31 starts to move away from the driving sleeve 22 again, and the axial reciprocating motion of the output shaft 30 is realized with the continuous rotation of the driving sleeve 22, because the driving sleeve 22 rotates by an angle (the angle is 360 degrees divided by the distribution number of the first radial magnetizing bodies 23, if the driving sleeve 22 is provided with six first radial magnetizing bodies 23, the angle is 60 °), the first radial magnetizing bodies 23 and the second radial magnetizing bodies 32 alternate once, and each alternate time between the first radial magnetizing bodies 23 and the second radial magnetizing bodies 32 can cause the output shaft 30 to axially reciprocate once under the damping action of the axial magnetic rebound assembly 40, so that the output shaft 30 can generate multiple axial reciprocating vibrations in the process of one rotation of the driving shaft 21, and the axial vibration frequency of the output shaft 30 is multiplied by the rotating speed of the driving member 20 (the amplification factor is equal to the number of the first radial magnetizing bodies 23 distributed on the driving sleeve 22);

through the process, the output shaft 30 is prompted to generate two-degree-of-freedom vibration of circumferential and axial reciprocating vibration, so that from the aspect of vibration output, the product performance can be gained by the circumferential vibration or the axial vibration, the vibration frequency of the output shaft 30 can be further multiplied by adopting a two-degree-of-freedom vibration mode, and finally the vibration frequency exceeding 400Hz can be obtained.

Compared with the prior art, in the process that the driving part 20 drives the driving sleeve 22 to rotate through the driving shaft 21, the reciprocating vibration of the output shaft 30 in the circumferential direction and the axial direction can be realized by utilizing the combined cooperation of the magnetic coupling force, the axial magnetic repulsion force and the circumferential magnetic repulsion force between the first radial magnetizing body 23 and the second radial magnetizing body 32, and the circumferential and axial reciprocating vibration can be brought in each alternating process of the second radial magnetizing body 32 and the first radial magnetizing body 23, so that the output shaft 30 can generate a plurality of times of circumferential and axial combined vibration frequencies in the process that the driving sleeve 22 rotates for one circle, and the vibration frequency of the output shaft 30 can be doubled under the condition that the input rotating speed of the driving part 20 is not changed; only the driving part 20 far away from the output shaft 30 is an electrified part, and all parts in the machine shell 10 have water resistance, so that the waterproof performance of the product can be improved; in addition, because output shaft 30 and drive shaft 21 are split type structural style, consequently when the output overload causes the moment on the output shaft 30 to increase to surpass the magnetic coupling power, the driven shaft can be under the overload power automatic reduction vibration frequency or stop the vibration, and drive shaft 21 still can normal operating to avoid driving piece 20 to damage because of overloading, anti overload capacity is strong, can improve product life.

As a specific embodiment of the axial magnetic rebounding assembly 40, referring to fig. 1, the axial magnetic rebounding assembly 40 includes two fixed magnetic rings 41 and a moving magnetic ring 42, wherein the two fixed magnetic rings 41 are embedded on the inner circumferential wall of the casing 10 at intervals along the axial direction of the casing 10 and are sleeved on the output shaft 30; the moving magnetic ring 42 is fixedly sleeved on the output shaft 30 and is located between the two fixed magnetic rings 41, and the moving magnetic ring 42 and the two fixed magnetic rings 41 repel each other along the axial direction of the output shaft 30.

Two fixed magnetic rings 41 respectively generate two opposite-direction repulsive forces to the moving magnetic ring 42 along the axial direction of the output shaft 30 (the like magnetic poles of the fixed magnetic rings 41 and the moving magnetic rings 42 are opposite to each other to form repulsive forces), when the moving magnetic ring 42 slides along with the output shaft 30, the moving magnetic ring 42 gradually approaches one fixed magnetic ring 41 to damp the sliding of the output shaft 30 until the direction is reversed, and after the direction is reversed, the moving magnetic ring 42 gradually approaches the other fixed magnetic ring 41 to damp the reverse movement of the moving magnetic ring 42 by using the other fixed magnetic ring 41 until the moving magnetic ring 42 reversely slides again along with the output shaft 30.

As another embodiment of the above axial magnetic rebound assembly 40, referring to fig. 2, the axial magnetic rebound assembly 40 includes a fixed magnetic ring 41 and two moving magnetic rings 42, wherein the fixed magnetic ring 41 is embedded on the inner circumferential wall of the casing 10 and is sleeved on the output shaft 30; the two moving magnetic rings 42 are fixedly sleeved on the output shaft 30 at intervals along the axial direction of the output shaft 30 and are respectively positioned at two sides of the fixed magnetic ring 41, and the two moving magnetic rings 42 and the fixed magnetic ring 41 repel each other along the axial direction of the output shaft 30.

The fixed magnetic rings 41 respectively generate repulsive forces in opposite directions to the two movable magnetic rings 42 along the axial direction of the output shaft 30 (like magnetic poles of the fixed magnetic rings 41 and the movable magnetic rings 42 are opposite to each other to form repulsive forces), when the output shaft 30 slides, one of the movable magnetic rings 42 gradually approaches the fixed magnetic ring 41 to damp the sliding of the output shaft 30 until the direction is reversed, and the other movable magnetic ring 42 gradually approaches the fixed magnetic ring 41 after the direction is reversed, so that the reverse movement of the other movable magnetic ring 42 is damped by the fixed magnetic ring 41 until the output shaft 30 is reversed again, and it should be understood that the change of the magnetic coupling force received in the relative rotation process of the driven sleeve 31 and the driving sleeve 22 needs to be matched in the whole axial reciprocating process.

In some embodiments, referring to fig. 4 to 7, the circumferential magnetic rebounding assembly 50 is configured in such a manner that the circumferential magnetic rebounding assembly 50 includes a rotor 51 and a stator 52, wherein the rotor 51 is fixedly sleeved on the output shaft 30, and a first magnetic assembly is disposed on the rotor 51; the stator 52 is sleeved on the rotor 51 along the axial direction of the output shaft 30 and is fixedly connected with the inner wall of the casing 10, the stator 52 is provided with a second magnetic assembly, and a circumferential magnetic repulsion force is provided between the second magnetic assembly and the first magnetic assembly.

For example, referring to fig. 4 and 5, the second magnetic assembly includes 2n second permanent magnets 521, n first sector cavities 522 are circumferentially distributed on the stator 52 at intervals, and two planar cavity walls of each first sector cavity 522 are respectively embedded with one second permanent magnet 521; the first magnetic assembly comprises n first permanent magnets 511 embedded on the peripheral wall of the rotor 51, each first permanent magnet 511 correspondingly extends into each first sector cavity 522 along the radial direction of the rotor 51, and each first permanent magnet 511 and two corresponding second permanent magnets 521 repel each other along the circumferential direction of the stator 52; furthermore, n first side extension plates 512 extending into the first sector-shaped cavities 522 along the radial direction are distributed on the peripheral wall of the rotor 51 at intervals, and a first permanent magnet 511 is embedded on each first side extension plate 512.

The first permanent magnet 511 may be embedded in the end wall of the first side extension plate 512 extending into the first fan-shaped cavity 522, or may be embedded in the first side extension plate 512, the second permanent magnet 521 may be embedded in the cavity wall surface of the first fan-shaped cavity 522, or may be embedded in the cavity wall of the first fan-shaped cavity 522, the first permanent magnet 511 and the like magnetic pole of the second magnetic pole are oppositely arranged to form a repulsive force, in a balanced state, the first permanent magnet 511 is located in the middle position of the two corresponding second permanent magnets 521, when the output shaft 30 drives the rotor 51 connected thereto to rotate, the first permanent magnet 511 starts to approach one of the second permanent magnets 521, the repulsive force gradually increases until the output shaft 30 reverses, the first permanent magnet 511 gradually approaches the other second permanent magnet 521 after the output shaft 30 reverses, so that the reverse repulsive force gradually increases until the output shaft 30 reverses again, of course, it should be understood that the variation of the magnetic coupling force received by the driven sleeve 31 and the driving sleeve 22 during the relative rotation process needs to be matched during the whole circumferential reciprocating process; in addition, since the first side extension plate 512 extending into the first fan-shaped cavity 522 is provided on the peripheral wall of the rotor 51, the relative rotation angle between the rotor 51 and the stator 52 can be limited, and the output shaft 30 fixedly connected to the rotor 51 can perform circumferential reciprocating vibration only within a certain angle, thereby improving the output stability.

For example, referring to fig. 6 and 7, the first magnetic assembly includes 2n first permanent magnets 511, n second sector-shaped cavities 513 are circumferentially distributed on the rotor 51 at intervals, and two planar cavity walls of each second sector-shaped cavity 513 are respectively embedded with one first permanent magnet 511; the second magnetic assembly comprises n second permanent magnets 521 embedded on the inner peripheral wall of the stator 52, each second permanent magnet 521 correspondingly extends into each second sector-shaped cavity 513 along the radial direction of the stator 52, and each second permanent magnet 521 and the corresponding two first permanent magnets 511 repel each other along the circumferential direction of the stator 52; furthermore, n second side extension plates 523 are distributed at intervals on the inner peripheral wall of the stator 52 and respectively extend into each second sector-shaped cavity 513 along the radial direction of the second side extension plate, and a second permanent magnet 521 is embedded on each second side extension plate 523.

The first permanent magnet 511 may be embedded on the wall surface of the second sector-shaped cavity 513, or embedded inside the wall of the second sector-shaped cavity 513, the second permanent magnet 521 may be embedded on the end wall of the second side extension plate 523 extending into the second sector-shaped cavity 513, or embedded inside the second side extension plate 523, the first permanent magnet 511 and the like magnetic pole of the second magnetic pole are oppositely arranged to form a repulsive force, in a balanced state, the second permanent magnet 521 is located at the middle position of the two corresponding first permanent magnets 511, when the output shaft 30 drives the rotor 51 connected with the output shaft to rotate, one of the first permanent magnets 511 starts to approach the second permanent magnet 521, the repulsive force gradually increases until the output shaft 30 reverses, and the other first permanent magnet 511 gradually starts to approach the second permanent magnet 521 after the output shaft 30 reverses, so that the repulsive force in the reverse direction gradually increases until the output shaft 30 reverses direction again, of course, it should be understood that the variation of the magnetic coupling force received by the driven sleeve 31 and the driving sleeve 22 during the relative rotation process needs to be matched during the whole circumferential reciprocating process; in addition, since the second side extension plate 523 extending into the second fan-shaped cavity 513 is disposed on the peripheral wall of the stator 52, the relative rotation angle between the rotor 51 and the stator 52 can be limited, and the output shaft 30 fixedly connected to the rotor 51 can perform circumferential reciprocating vibration only within a certain angle, thereby improving the output stability.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the utility model, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.

Claims (10)

1. Radial magnetization combines two-way magnetism to kick-back to realize high frequency vibration's device, its characterized in that includes:

a housing;

the driving part is arranged at one end of the shell and is provided with a driving shaft extending into the shell along the axial direction of the shell, the extending end of the driving shaft is coaxially connected with a driving sleeve, a plurality of first radial magnetizing bodies are distributed on the driving sleeve at intervals along the circumferential direction of the driving sleeve, and each first radial magnetizing body extends along the axial direction of the driving sleeve;

the output shaft is rotatably connected in the shell along the axial direction of the shell and has freedom degree of sliding along the axial direction of the shell, one end, facing the driving shaft, of the output shaft is coaxially connected with a driven sleeve, the driven sleeve is coaxially sleeved with the driving sleeve, a plurality of second radial magnetizing bodies are distributed on the driven sleeve at intervals along the circumferential direction of the driven sleeve, and each second radial magnetizing body corresponds to each first radial magnetizing body along the radial direction of the output shaft and is staggered along the axial direction of the output shaft;

the axial magnetic rebound assembly comprises an axial fixed end and an axial floating end, the axial fixed end is fixedly connected with the shell, the axial floating end is fixedly connected with the output shaft, and an axial magnetic repulsion force for damping the sliding of the output shaft is arranged between the axial floating end and the axial fixed end;

circumference magnetism resilience subassembly, including circumference stiff end and circumference floating end, the circumference stiff end with casing fixed connection, the circumference floating end with output shaft fixed connection, and with it is used for the damping to have between the circumference stiff end output shaft pivoted circumference magnetic repulsion.

2. The device for achieving high frequency vibration in combination with bi-directional magnetic rebound of claim 1, wherein the axial magnetic rebound assembly comprises:

the two fixed magnetic rings are embedded on the inner peripheral wall of the shell at intervals along the axial direction of the shell and are sleeved on the output shaft in a sleeved mode;

and the movable magnetic ring is fixedly sleeved on the output shaft and is positioned between the two fixed magnetic rings, and the movable magnetic ring and the two fixed magnetic rings are mutually repelled along the axial direction of the output shaft.

3. The device for achieving high frequency vibration in combination with bi-directional magnetic rebound of claim 1, wherein the axial magnetic rebound assembly comprises:

the fixed magnetic ring is embedded on the inner peripheral wall of the shell and sleeved on the output shaft in a ring mode;

the two movable magnetic rings are fixedly sleeved on the output shaft at intervals along the axial direction of the output shaft and are respectively positioned on two sides of the fixed magnetic ring, and the two movable magnetic rings and the fixed magnetic ring repel each other along the axial direction of the output shaft.

4. The device for achieving high frequency vibration in combination with bi-directional magnetic rebound according to claim 1, wherein the circumferential magnetic rebound assembly comprises:

the rotor is fixedly sleeved on the output shaft, and a first magnetic assembly is arranged on the rotor;

the stator is sleeved on the rotor along the axial direction of the output shaft and fixedly connected with the inner wall of the shell, a second magnetic assembly is arranged on the stator, and the circumferential magnetic repulsion force is arranged between the second magnetic assembly and the first magnetic assembly.

5. The device for realizing high-frequency vibration by combining radial magnetization and bidirectional magnetic rebound as claimed in claim 4, wherein the second magnetic assembly comprises 2n second permanent magnets, the stator is provided with n first sector cavities at intervals along the circumferential direction of the stator, and two second permanent magnets are respectively embedded on two plane cavity walls of each first sector cavity; the first magnetic assembly comprises n first permanent magnets embedded on the peripheral wall of the rotor, each first permanent magnet correspondingly extends into each first sector cavity along the radial direction of the rotor, and each first permanent magnet and the corresponding two second permanent magnets repel each other along the circumferential direction of the stator.

6. The device for realizing high-frequency vibration by combining radial magnetization and bidirectional magnetic rebound as claimed in claim 5, wherein n first side extension plates respectively extending into each first sector cavity along the radial direction are distributed on the peripheral wall of the rotor at intervals, and each first side extension plate is embedded with one first permanent magnet.

7. The device for realizing high-frequency vibration by combining radial magnetization and bidirectional magnetic rebound as claimed in claim 4, wherein the first magnetic assembly comprises 2n first permanent magnets, n second sector cavities are distributed at intervals along the circumferential direction of the rotor, and two planar cavity walls of each second sector cavity are respectively embedded with one first permanent magnet; the second magnetic force assembly comprises n second permanent magnets embedded on the inner peripheral wall of the stator, each second permanent magnet correspondingly extends into each second sector cavity along the radial direction of the stator, and each second permanent magnet and the corresponding two first permanent magnets repel each other along the circumferential direction of the stator.

8. The device for realizing high-frequency vibration by combining radial magnetization and bidirectional magnetic rebound as claimed in claim 7, wherein n second side extension plates respectively extending into each second sector cavity along the radial direction are distributed on the inner peripheral wall of the stator at intervals, and each second side extension plate is embedded with one second permanent magnet.

9. The device for realizing high frequency vibration by combining radial magnetization and bidirectional magnetic rebound according to any one of claims 1 to 8, wherein the driving member is a motor.

10. The device for realizing high frequency vibration by combining radial magnetization and bidirectional magnetic rebound according to any one of claims 1 to 8, wherein the first radial magnetization body and the second radial magnetization body attract or repel each other.

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