CN222804376U - High frequency power multi-mode electric toothbrush - Google Patents

Abstract

A high-frequency power multi-mode electric toothbrush comprises a main body shell, an oscillating motor, a battery, a rotating brush rod and an oscillating brush rod, the main body shell is hollow to form a built-in space, and its rear end is closed by a detachable tail cover, the main body shell contains a control circuit board and the side wall is provided with a plurality of function buttons connected to the control circuit board, a battery is provided at the rear end of the built-in space, the battery is electrically connected to the control circuit board and the oscillating motor, a oscillating motor is provided at the front end of the built-in space of the main body shell, the output shaft of the oscillating motor extends from the front end of the main body shell and is connected to the main body shell to provide power output, the oscillating motor comprises a motor bracket, an electromagnetic coil, a vibration arm assembly, a front cover and a magnet; thus, the utility model effectively takes into account the two modes of high-frequency rotary brush rod and high-frequency oscillating brush rod, the rotation or oscillation frequency is effectively improved, and the use of flexible compensation solves the noise and life problems of the brush rod under high-frequency operation.

Description

High-frequency power multi-mode electric toothbrush

Technical Field

The utility model relates to the technical field of electric toothbrushes, in particular to a high-frequency power multi-mode electric toothbrush which can be respectively matched with a high-frequency rotary brush rod and a high-frequency vibration brush rod.

Background

The existing toothbrush with high-frequency power output can be divided into two types according to the motion mode of the brush head, wherein one type is that a brush rod and the brush head are integrated, the whole brush rod swings and shakes, the other type is that the brush head is in a round or oval reciprocating rotation mode, and generally, the technical problem faced by the brush head reciprocating rotation mode is far more than that of the whole brush rod vibration mode. The main common problems faced are:

1. The brush head acts in a rotary mode, a brush rod is often designed to be formed by combining a plurality of moving parts, and common designs comprise a rotary shaft and a mechanism for stirring or linking the movement of a brush disc. The kinematic fit of these mechanisms is difficult to avoid noise due to manufacturing tolerances.

2. The brush head can aggravate abrasion of moving components and further increase noise under the conditions of cleaning grinding materials such as toothpaste. Because the workpiece is worn, the actual movement stroke between the components is lost, and finally the progressive deterioration of the brush disc output swing angle is weakened, and the cleaning requirement cannot be met.

3. The maximum working rotating speed of the conventional economical direct current motor driven electric toothbrush is less than 133Hz, and a gear set or a lever connecting rod is required to complete torque conversion, otherwise, the torque output by direct drive is too small to meet the clean power requirement. If the brush head can effectively work at 140-350Hz, the torque of the gear set is changed, and the rotating speed of the direct current motor is necessarily far higher than the output of the brush disc by 2-4 times. Under the condition, the conventional power conversion mechanism can generate high-volume working noise which is uncomfortable to a user, the abrasion of components can be greatly increased due to the increase of the rotating speed, and the service life of the product is influenced. The utility model provides a high-frequency vibration motor directly driving a torque-free conversion mechanism.

4. The common electric toothbrush can only be matched with a brush head in one cleaning mode, namely a brush head which rotates in a reciprocating mode or a brush head which swings at high frequency, and only one of the brush heads can be selected.

Accordingly, the present utility model has been developed in view of the above-mentioned drawbacks by combining the experience and results of many years of related industries through intensive research and design, and designing a high-frequency power multi-mode electric toothbrush to overcome the above-mentioned drawbacks.

Disclosure of utility model

The utility model aims to provide a high-frequency power multimode electric toothbrush which can overcome the defects of the prior art, overcomes the defects of up-and-down push-pull moment in the prior art by driving through a swinging vibration force, effectively considers two modes of a high-frequency rotary brush rod and a high-frequency swinging vibration brush rod, effectively improves rotation or swinging frequency, and solves the problems of noise and service life of the brush rod under high-frequency work by adopting flexible compensation.

In order to achieve the above purpose, the utility model discloses a high-frequency power multimode electric toothbrush, which comprises a body shell, a vibration motor, a rotary brush rod and a vibration brush rod, wherein the body shell is hollow to form an internal space, a control circuit board is arranged in the body shell, and a plurality of functional buttons connected to the control circuit board are arranged on the side wall of the body shell, and the high-frequency power multimode electric toothbrush is characterized in that:

The vibration motor comprises a motor support, an electromagnetic coil, a vibrating arm assembly, a front cover and a magnet, wherein the front end of the motor support is provided with the front cover, the rear end of the motor support is provided with the magnet, the rear side of the magnet is also provided with a damping block, an inner cavity is formed in the motor support to accommodate the vibrating arm assembly, and the outer edge of the rear part of the inner cavity is coated with the electromagnetic coil;

The vibrating arm assembly comprises a swinging arm, a rotating shaft, a bearing and a connecting frame, wherein the rear part of the swinging arm is positioned in an electromagnetic coil at the rear part of an inner cavity body, a disc part is formed at the front part of the swinging arm and provided with a shaft hole for the rotating shaft to penetrate, two ends of the rotating shaft are rotatably supported on a motor bracket through the bearing, the rear end of the connecting frame is coated at the front part of the swinging arm and forms a cylindrical structure for accommodating the disc part of the swinging arm, and the front end of the connecting frame is connected to the rear end of an output shaft so as to transmit vibration generated by the vibrating arm assembly to the output shaft for output.

The vibration arm assembly is integrally formed by embedding the swing arm, the rotating shaft and the output shaft into a connecting frame through plastic secondary injection molding, the swing arm is a straight iron swing arm, and the rotation axis of the rotating shaft is perpendicular to the swing direction of the swing arm.

The two ends of the rotating shaft are provided with shaft shoulders matched with the bearings, and the rear end of the output shaft is provided with at least one concave ring, so that the output shaft and the connecting frame are formed firmly and integrally after secondary injection molding.

The swing arm is formed by stacking high-frequency low-eddy-current-loss silicon steel sheets.

The rotary brush rod comprises a brush rod shell, an inner support, a rotary brush head assembly and a power transmission assembly, wherein the inner support is arranged in the brush rod shell to form an inner space with the power transmission assembly, the rotary brush head assembly is arranged at the front end of the brush rod shell, the rear end of the power transmission assembly is connected to an output shaft of the vibration motor, and the front end of the power transmission assembly is connected to the rotary brush head assembly, so that output power of the vibration motor is transmitted to the rotary brush head assembly.

The rotary brush head assembly comprises a brush head seat and rotary brush hair, wherein the brush head seat is rotatably arranged in the front end of the brush rod shell, one end of the brush head seat is provided with a plurality of rotary brush hair for cleaning, and the other end of the brush head seat is provided with a base connected to the rotary power transmission assembly.

The rotary power transmission assembly comprises a swinging rod, an elastic supporting point, an elastic coupling body, a driving head, a compensating spring and a connecting sleeve, wherein the driving head extending into a base of the brush head seat is arranged at the front end of the swinging rod, a driven piece matched with the driving head in shape is formed on the base of the brush head seat, the compensating spring is sleeved between the driving head and the elastic supporting point of the swinging rod, the rear end of the swinging rod extends into the front end of the connecting sleeve, and the rear end of the connecting sleeve is connected with an output shaft through the elastic coupling body.

The swinging brush rod comprises a brush rod shell, an inner support, a swinging brush head assembly and a swinging vibration force transmission assembly, wherein the inner support is arranged in the brush rod shell to form an inner space with the swinging vibration force transmission assembly, the swinging brush head assembly is arranged at the front end of the brush rod shell, the rear end of the swinging vibration force transmission assembly is connected to an output shaft of a swinging vibration motor, and the front end of the swinging vibration force transmission assembly is connected to the swinging vibration brush head assembly, so that output power of the swinging vibration motor is transmitted to the swinging vibration brush head assembly.

The brush head assembly comprises a brush head, a rotating shaft, mao Shu and vibration bristles, wherein the rear end of the brush head stretches into the front end of a brush rod shell and is rotationally fixed to an internal support through the rotating shaft, a hair bundle seat is fixed at the front end of the brush head, and a plurality of vibration bristles for cleaning are planted in the hair bundle seat.

The swinging vibration force transmission assembly comprises a swinging shaft, a coupling block and a connecting pipe, wherein the front end of the swinging shaft is embedded into a concave hole at the rear end of the brush head, the rear end of the swinging shaft stretches into the front end of the connecting pipe, and the rear end of the connecting pipe is connected with an output shaft through the coupling block.

From the above, the high-frequency power multimode electric toothbrush of the present utility model has the following effects:

1. The technology of the high-frequency rotary toothbrush can effectively work at 140-350Hz, and the vibration motor with high torque output is adopted to replace the traditional direct current motor, so that noise caused by torque conversion links of gear sets or connecting rods is reduced. The replaceable toothbrush rod realizes power coupling through a coupler arranged on the toothbrush rod, and the body vibration moment is transmitted to the toothbrush rod through a brush rod pendulum shaft by utilizing the lever principle to drive the toothbrush rod to swing. Meanwhile, the brush rod which does not rotate and works in a swinging mode can be matched, and the brush rod can realize high-frequency reciprocating swinging under the driving of a swinging motor so as to meet the diversified requirements of users.

2. The swinging motor drives the brush rod in a connecting rod and lever mode, and a gap compensation mechanism is arranged at a connecting rod joint point and a lever fulcrum piece, so that the problem of large actual use noise and easy abrasion life is effectively solved.

3. Combines two modes of the high-frequency rotary brush rod and the high-frequency swinging brush rod,

The details of the present utility model can be found in the following description and the accompanying drawings.

Drawings

Fig. 1 shows a schematic structural view of an embodiment of the high frequency power multimode electric toothbrush of the present utility model in which a rotary brush bar is coupled with a vibration motor.

Fig. 2 shows a schematic structural view of an embodiment of the utility model in which a vibration brush bar is matched with a vibration motor in a high-frequency power multimode electric toothbrush.

Fig. 3 shows a schematic structural diagram of a pendulum motor according to the present utility model.

Fig. 4 shows a schematic diagram of the internal components of the pendulum motor of the present utility model in semi-cut-away.

Fig. 5 shows an exploded view of the pendulum motor of the present utility model.

Fig. 6 shows a cross-sectional view of a pendulum motor in accordance with the present utility model.

Fig. 7 shows a cross-sectional view of the swing motor of the present utility model in another direction.

Fig. 8 shows a schematic structural view of a vibrating arm assembly of a pendulum motor according to the present utility model.

Fig. 9A, 9B and 9C are schematic diagrams showing three states of the vibration motor under the electromagnetic force in the present utility model, wherein fig. 9A and 9C are opposite swinging states, and fig. 9B is a stationary state in which current is terminated.

Fig. 10A and 10B are schematic views showing two principles of the magnetic pole of the vibration motor according to the present utility model.

Fig. 11 shows a schematic view of the overall structure of the rotary brush bar of the present utility model.

Fig. 12 shows an exploded view of the rotary brush bar of the present utility model.

Fig. 13 shows a schematic view of the internal structure of the rotary brush bar of the present utility model.

Fig. 14 shows an internal schematic view of a rotatable brush bar of the present utility model.

Fig. 15A, 15B and 15C are schematic views showing three operational states of the rotary brush bar of the present utility model, respectively.

Fig. 16 is a schematic view showing the structure of a brush head base in a rotary brush bar according to the present utility model.

Fig. 17 shows a partial cutaway view of the elastomeric coupling element of the rotary brush bar of the present utility model.

Fig. 18A shows a partial cutaway view of an elastic fulcrum in a rotating brush bar of the present utility model.

Fig. 18B shows a cross-sectional view of another embodiment of a rotatable brush bar of the present utility model.

Fig. 19A and 19B are schematic views showing the principle of the compensation spring for rotating the brush bar according to the present utility model.

Fig. 20A and 20B are schematic structural views showing another embodiment of a rotary brush bar according to the present utility model.

Fig. 21A and 21B are schematic structural views showing another embodiment of a rotary brush bar according to the present utility model.

Fig. 22A, 22B, 22C and 22D are schematic structural views showing another embodiment of a rotary brush bar according to the present utility model.

Fig. 23A and 23B are schematic views showing the motion of the output shaft in the rotary brush bar according to the present utility model, wherein the motion trace of the output shaft is an arc circle.

Fig. 24A and 24B are schematic views showing the motion of the output shaft in the rotary brush bar according to the present utility model, wherein the motion trace of the output shaft is a reciprocating parallel line.

FIG. 25 shows an overall schematic of a pendulum vibration brush bar of the present utility model.

FIG. 26 shows a schematic view of the internal structure of a pendulum brush bar of the present utility model.

FIG. 27 shows an exploded view of a pendulum brush bar in accordance with the present utility model.

FIG. 28 shows a schematic view of the gap between a swinging brush bar according to the present utility model.

Fig. 29A, 29B and 29C are schematic views showing the motion of a swinging brush bar according to the present utility model.

Fig. 30 shows a waveform of a voltage signal of a typical H-bridge output termination pure resistive load of a pendulum motor according to the present utility model.

Fig. 31 shows a schematic diagram of the principle of the utility model for collecting power current without an additional sensor of the pendulum motor.

Fig. 32 shows a truth diagram of the typical 4 operating states of an H-bridge of a pendulum motor according to the present utility model.

FIG. 33 shows a signal diagram of an H-bridge of a pendulum motor according to the present utility model coupled to a purely resistive load and an inductive motor load.

Fig. 34 shows a schematic diagram of the voltage at the battery terminal of the pendulum motor in the direct measurement operation of the pendulum motor according to the present utility model, showing different swing amplitudes and wave clusters under different load effects.

Fig. 35 shows a spread-out view of the relevant data of fig. 34.

Fig. 36 shows a schematic of asynchronous continuous dense voltage sampling for a pendulum motor in accordance with the present utility model.

Fig. 37 shows a schematic diagram of synchronous sampling mode voltage data of a vibration motor according to the present utility model.

Fig. 38 shows a schematic diagram of the principle of absorbing back emf by a shorted H-bridge of a pendulum motor according to the present utility model.

Fig. 39 shows a graph of current signal before and after eliminating back emf of the pendulum motor of the present utility model.

FIG. 40 is a schematic block diagram showing the process of the constant amplitude correction technique of the pendulum motor of the present utility model

FIG. 41 is a graph showing the comparison of the change curves of the compensating and non-compensating swing angles when the load of the swing motor is changed in the utility model.

FIG. 42 shows a flow chart of a dynamic servo process signal processing for a vibration motor to achieve a constant output swing of the motor in the present utility model.

Reference numerals:

10. Body housing, 11, tail cap, 12, function button, 13, control circuit board, 20, pendulum motor, 21, motor bracket, 22, solenoid, 23, damper block, 24, vibrating arm assembly, 241, swing arm, 242, spindle, 243, bearing, 244, connection rack, 245, output shaft, 25, front cap, 26, seal cover, 27, magnet, 30, battery, 41, brush bar housing, 421, brush head holder, 422, rotating bristle, 423, mount, 424, swivel shaft, 425, safety pin, 426, compensation spring pad, 43, swing arm, 44, elastic pivot, 45, elastic coupling, 46, driving head, 47, inner holder, 48, compensation spring, 49, connection sleeve, 51, brush bar housing, 521, brush head, 522, rotation shaft, 523, hair bundle holder, 524, pendulum bristle, 53, pendulum shaft, 54, coupling block, 55, connection tube, 56, inner holder, 57 compensation pad.

Detailed Description

Referring to fig. 1 and 2, there is shown a high frequency power multi-mode electric toothbrush according to the present utility model, wherein fig. 1 shows a schematic structural view of an embodiment of the high frequency power multi-mode electric toothbrush according to the present utility model in which a rotary brush bar is coupled to a vibration motor, and fig. 2 shows a schematic structural view of an embodiment of the high frequency power multi-mode electric toothbrush according to the present utility model in which a vibration brush bar is coupled to a vibration motor.

Therefore, the high-frequency power multimode electric toothbrush comprises a body shell 10, a vibration motor 20, a battery 30, a rotary brush rod and a vibration brush rod, wherein the body shell 10 is hollow to form a built-in space, the rear end of the body shell is closed through a detachable tail cover 11, a control circuit board 13 is arranged in the body shell 10, a plurality of functional buttons 12 connected to the control circuit board 13 are arranged on the side wall of the body shell, and accordingly an operator can provide control signals through the functional buttons 12 to be transmitted to the control circuit board 13 so as to achieve the purpose of controlling the electric toothbrush.

The front end of the built-in space of the body shell 10 is provided with a vibration motor 20, an output shaft 245 of the vibration motor 20 extends out of the front end of the body shell 10 and is connected to a brush rod positioned in front of the body shell 10 so as to provide power output for the brush rod, the rear end of the built-in space is provided with a battery 30, and the battery 30 is electrically connected to the control circuit board 13 and the vibration motor 20 so as to provide stable and reliable power output for the two.

In the embodiment of fig. 1, the rotary brush rod is detachably connected to the front end of the body casing 10, the output shaft 245 extends into the rotary brush rod to provide driving force, in the embodiment of fig. 2, the swinging brush rod is detachably connected to the front end of the body casing 10, and the output shaft 245 extends into the swinging brush rod to provide driving force, so that the body casing 10 is detachably connected to the rotary brush rod or the swinging brush rod, and two advantages of the high-frequency rotary brush rod and the high-frequency swinging brush rod can be considered, and the application range is better improved.

Referring also to fig. 3-9C, one embodiment of the pendulum motor of the present utility model is better understood.

In this embodiment, the vibration motor 20 includes a motor support 21, an electromagnetic coil 22, a damper block 23, a vibrating arm assembly 24, a front cover 25 and a magnet 27, as can be seen more clearly from the exploded schematic diagram shown in fig. 5 and the sectional views of fig. 6 and 7, the front end of the motor support 21 is provided with the front cover 25, the rear end is provided with the magnet 27, and the rear side of the magnet 27 is further provided with the damper block 23, so that the vibration of the vibration motor 20 can be isolated from the battery at the rear side, thereby realizing the vibration absorbing function and avoiding the deterioration of comfort caused by excessive vibration of the user during use.

The motor support 21 is internally provided with an inner cavity to accommodate the vibrating arm assembly 24, the outer edge of the rear portion of the inner cavity is covered with the electromagnetic coil 22, meanwhile, referring to fig. 8, the vibrating arm assembly 24 includes a swing arm 241, a rotating shaft 242, a bearing 243 and a connecting frame 244, the swing arm 241 is a linear iron swing arm, and the rear portion of the swing arm is located in the electromagnetic coil 22 at the rear portion of the inner cavity, the front portion of the swing arm 241 is provided with a disc portion and the disc portion is provided with a shaft hole through which the rotating shaft 242 penetrates, two ends of the rotating shaft 242 are rotatably supported on the motor support 21 through the bearing 243, the rear end of the connecting frame 244 is covered on the front portion of the swing arm 241 and forms a cylindrical structure for accommodating the disc portion of the swing arm 241, and the front end of the connecting frame 244 is connected to the rear end of the output shaft 245 to transmit the vibration generated by the vibrating arm assembly 24 to the output shaft 245 for outputting.

The swing arm 241, the rotation shaft 242 and the output shaft 245 are embedded integrally to form a vibrating arm assembly by adopting a mode of forming a connecting frame 244 through plastic secondary injection molding, the rotation axis of the rotation shaft 242 and the swinging direction of the swing arm 241 are perpendicular to each other, the rotation shaft 243 is preferably arranged in a rotation shaft hole at about 2/3 of the swing arm 241, so that the rotation shaft is cross-shaped after being combined with the swing arm, shaft shoulders matched with the bearings 243 are arranged at two ends of the rotation shaft 242, at least one concave ring is arranged at the rear end of the output shaft 245, so that the output shaft 245 and the connecting frame 244 are formed integrally stably after secondary injection molding, and at least one concave ring of the output shaft 245 can effectively prevent output from displacement under the action of external force.

Therefore, the swing motor is used as a power conversion device for converting electromagnetic energy into mechanical energy, and the final output driving moment of the swing motor is 2-5 times of the output moment of the traditional direct current motor under the same working condition of the same volume under the condition of the same power consumption, so that the high-frequency swing power requirement of the electric toothbrush is met.

Referring to fig. 9A, 9B and 9C, the vibrating arm assembly is arranged in the cavity, a space which can allow the swing arm 241 to swing back and forth for 20 degrees and has no collision with the motor bracket is formed between the rear part of the swing arm 241 and the inner wall of the motor bracket 21, and a step part for accommodating the magnet 27 is formed at the rear end of the motor bracket 21 so as to keep a gap of at least 0.2-0.6mm between the tail end of the swing arm 241 and the magnet, therefore, the magnet 27 at the tail part can induce magnetic acting force on the tail part of the iron swing arm, but no physical contact exists.

Two magnets are arranged in parallel at the tail part of the bracket, the magnetization surface faces the swing arm, and the same-direction polarities of the two magnets are mutually different after being combined.

The front cover 25 at the front end of the motor bracket 21 is covered with a sealing cover 26 to realize sealing, and the arrangement of the front cover strengthens the stability of bearings at two ends of the rotating shaft and provides limit for the sealing cover.

The electromagnetic force of the pendulum vibration motor provided by the utility model is converted into the pendulum mechanical energy as follows:

1. the electromagnetic coil is connected with square wave power current with alternating positive and negative polarities.

2. As shown in fig. 9A, it is assumed that, in the positive half cycle of the square wave, since an iron swing arm is built in the electromagnetic coil, the axis of the swing arm is in the same direction as the axis of the electromagnetic coil, the swing arm will be polarized to have magnetism under the action of the electromagnetic field, and it is assumed that the swing arm close to the magnetic pole is polarized to be S pole at this moment, the swing arm will swing in the direction D1 under the action of the principle that the swing arm repels at the same level and attracts at different levels.

3. As shown in fig. 9C, when the square wave current is switched to the negative half cycle, the current applied to the electromagnetic coil is reversed in polarity, the direction of the current applied to the electromagnetic coil is opposite to that of the positive half cycle, the magnetic pole induced by the swing arm is converted into N pole, and the swing arm of the vibrating arm assembly is reversely switched from the D1 direction to the D2 direction under the action of the new electromagnetic force.

4. After the current of the positive half cycle and the negative half cycle is switched, a complete vibration cycle is formed by swinging the vibrating arm assembly of the motor, the swinging frequency of the vibrating arm assembly depends on the frequency of square wave current of the driving coil, the electromagnetic coil preferably works at 140Hz-350Hz, the swinging angle of the vibrating arm assembly can be regulated by the duty ratio of the square wave, and the swinging angle is in direct proportion to the duty ratio.

The swing arm 241 is supported by ferromagnetic material, and the working frequency can reach 350Hz, so the swing arm 241 is formed by stacking high-frequency low-eddy-current-loss silicon steel sheets.

As shown in fig. 10A, the magnet 27 of the present utility model may be formed by arranging two independent magnets M1, or may be formed by magnetizing N and S poles simultaneously on the same plane by using only one magnet M2 in a coplanar multi-pole magnetizing process as shown in fig. 10B. The arrangement direction of N and S is consistent with the polarity of the two magnets, so that the requirement of the utility model can be met.

The method comprises the steps of adopting a sensorless synchronous driving pulse detection battery voltage technology, monitoring the change of driving current caused by the dynamic impedance change of a motor by means of a specific driving pulse period, combining a corresponding algorithm, and compensating driving power in real time by combining the monitored motor working condition to realize constant swing output.

In one embodiment of the vibration motor, a constant amplitude control method is involved, wherein a typical driving wave voltage is shaped as a square wave, the frequency of the square wave is consistent with the swing frequency of output, and theoretically, the duty ratio of the square wave is 100% when the motor outputs full power under the condition of constant voltage. In practical application, the most basic driving power device is an H-drive bridge formed by 4 FETs, the H-drive bridge changes along with input signals, and the output end is switched with negative voltage at high speed. Since the FET switching has a response time difference, such as switching at a duty ratio of 100%, there is a dead zone in which the H-bridge 4 FETs are simultaneously turned on to cause an internal short circuit of the H-bridge, resulting in a drive failure of the H-bridge, the fastest response interval is generally called as a drive dead zone of the H-bridge, so that the H-bridge should avoid operating in the dead zone, and power supply to the motor should be stopped in the interval. After considering the dead zone, the maximum duty cycle of the final square wave is typically 98% -99% rather than 100%.

If the duty ratio of the pulse is reversely reduced, the driving effective power is reversely reduced, so that the swing amplitude of the swing motor is reduced, and the mechanism that the output power can be changed by adjusting the duty ratio of the pulse is utilized as the basis of the output rate compensation theory of the swing motor.

In the diagram, S1 is a positive half cycle effective working pulse, S2 is a negative half cycle effective working pulse, t12 and t22 are positive and negative half cycle working stop periods respectively, the positive and negative half cycle working stop periods comprise necessary dead zone control time and stop time for adjusting the Duty ratio of the whole pulse, t is a complete driving period, t=S1+S2+t12+t22, the positive and negative half cycles of s1=S2 and t12=t22 are assumed to be completely symmetrical, the Duty ratio Duty=S1/(t12+S1) X100% or duty=S2/(t22+S2) X100%, in actual control, driving power control can be realized by synchronously adjusting the proportion of t12 and t22 in the whole pulse t, and obviously, the larger the Duty ratio of t12 and t22 is, the smaller the output power is. The control of the output power by adjusting the duty ratio is the theoretical basis of the control technology of the motor.

Before expanding and discussing how to realize the motor constant amplitude control theory, the utility model firstly explains the principle and method for realizing power current without an additional sensing device, as shown in fig. 31, a schematic diagram for realizing power current without an additional sensing device is shown, wherein BT represents a battery pack, V in the battery pack is a standard battery, R0 is the internal resistance of the battery pack, MCU is a microprocessor of a line control unit, the microprocessor internally comprises an analog-to-digital converter marked as ADC and a reference voltage reference source specially used for the ADC and internally marked with Vref, S1-S4 are output driving signal ports specially designed for the MCU to be H-bridge, H is an H-power driving bridge formed by two pairs of complementary FETs, M is a vibration motor related to the utility model, and I is power current.

Fig. 32 shows the truth values for the typical 4 operating states of an H-bridge.

The current sampling key required by the constant amplitude technology is as follows:

1. By utilizing the internal resistance R0 of the battery pack, during power driving, the variable power current I inevitably generates a variable voltage drop Vdp at R0, and the load current change can be reflected by detecting Vdp through the MCU control unit, that is, vdp=r0X I.

2. In order to simplify the hardware design, a microprocessor with an ADC (analog-to-digital converter) and Vref (digital reference standard) with a voltage reference source is selected, so that the change of power current can be calculated directly without matching with more peripheral equipment.

The power current change detection discussed herein is based on detecting changes in the R0 voltage drop Vdp, unless specifically indicated.

The realization method and process of constant amplitude compensation are further explained in two links.

The signals of the pure resistance load and the inductive motor load connected to the H-drive bridge show a significant difference, as shown in fig. 33, in which the solid line CV1 represents the waveform of the pure resistance load, and the dotted line represents the waveform of the pendulum vibration motor actually connected to the inductive reactance. The two sets of waveforms differ significantly in that a peak ringing, denoted D, occurs at each working pulse, and each active working waveform starts a to ends b, changing from the horizontal line of a standard rectangular square wave to a sloping line under the influence of inductive reactance loading.

The driving end is connected with the motor, the square wave is obviously overshot and rings, the power supply to the motor coil is stopped in the stopping period (dead zone period+power regulation period), the coil generates counter electromotive force for inductive load, and the swinging arm continuously cuts magnetic force lines generated by the magnet under the inertia effect, so that variable impedance is formed to the coil. The superposition of the back emf and variable impedance of the coil to the power supply directly affects the stability of the square wave rising edge and pulse width.

After the coil is powered off, the swing arm continuously swings under the action of inertia, and the swing frequency is assumed to be unchanged, the larger the swing amplitude is, the larger the speed of the magnetized swing arm cutting magnetic force lines is, and the larger the variable impedance influence on the coil is. Obviously, if the relative instantaneous current quantity of the variable impedance influence can be measured, the current swinging linear speed of the swinging arm can be mapped relatively, and the current swinging relative variation quantity can be output. This idea is the most important theoretical basis for real-time swing measurement related to the constant amplitude driving technology.

In order to reduce the influence of electromagnetic interference in a stray space on signal detection, the swing-related data detection is not arranged at the tail end of a motor drive output, but is used for directly measuring the instantaneous voltage change of a battery terminal. The voltage change and the motor driving end current change have a mapping corresponding relation.

Fig. 34 shows that the voltage of the battery terminal is measured directly, the swing motor shows different swing amplitudes and wave clusters under different load, the solid curves CV1 in the figure are waveforms which are shown under no-load condition, and the dotted curves CV2, CV3, CV4 and CV5 are waveforms which are shown with small to large load respectively. The voltage of the battery terminal at a certain time sequence of each driving pulse can be observed to change along with the load, and as the interval t 1-t 2 in the drawing, the relevance between the load of the motor and the voltage can be obviously observed, and the voltage is higher when the load is heavier. The rule of the summary is:

Load, CV5> CV4> CV3> CV2> CV1;

Pulse end voltage V5> V4> V3> V2> V1.

Fig. 35 shows the data shown in a scatter diagram, in which the V-axis is the battery terminal voltage and the D-axis is the swing angle of the swing axis, and the heavier the load, the smaller the swing angle of the swing axis.

V5-V1 are 5 sampling points, and curve a is a curve formed by connecting actual sampling points in series. It is evident from the figure that the voltage at the sampling point is strongly related to the angle of the swing exhibited under different loads. In order to simplify the operation of the microprocessor. The above sampled data may be fitted to a straight line b by a least squares method.

The instantaneous voltage change U at the battery end is affected by two important factors, namely u=ub+ur, wherein Ub is counter electromotive force generated in a motor outage stop period, ur is dynamic inductance change of the coil caused by vibration arm position swing change, the dynamic inductance change directly affects transformation of current at the conduction rate of the coil, and basically, variable impedance is formed. The variation in coil impedance eventually becomes effective in the behavior of the rising edge of each pulse at the motor coil end.

Therefore, the current motor swing data can be quantized only by effectively separating out the voltage variation component of the motor caused by the impedance variation at the rising edge of each pulse.

In order to better separate the variable impedance of the motor coil, the reasonable and correct sampling point of the current is particularly important, and it can be seen from the wave cluster that, unlike the conventional sampling method, if the conventional DC motor working condition is adopted, the conventional sampling method is to disregard pulse synchronous information, continuously and densely sample at equal intervals, the longer the measurement sampling period is, the more stable the value is after weighted average, and the relationship between the voltage and the load can be well reflected. However, this asynchronous mean mode of sampling proves ineffective for brushless motors driven by pulse commutation, and continuous sampling without pulse synchronization gives no obvious correlation of voltage results with load variations.

FIG. 36 shows a plot of non-synchronous continuous dense voltage samples in a brushless motor, where V-axis is a voltage scalar, T-axis is a time scalar, S1-Sn are the timing of the non-synchronous continuous samples, T2 are the sampling periods, P1-pn are the voltage variation periodic signals observed at the battery terminal, it is apparent that the period is phase-dependent and synchronous with the motor drive pulse, T1 is the motor drive pulse period, D1-Dn are the sampled voltage values

As can be seen from the figure, if t1 and t2 are not synchronized, the sampling positions of D1 and D5 are significantly different from the pulse landing position, where D1 is close to the head of pulse P1 and D5 is close to the tail of pulse P3, and the difference between these two sampling values is large. Thus, a weighted average method may be used for data averaging, i.e., avg= (d1+d2+ Dn..)/n., where the average Avg does not correctly capture the load and voltage correctly associated data, and thus conventional asynchronous voltage sampling is not suitable for the vibration motor operating conditions mentioned in the present utility model.

FIG. 37 shows the representation of synchronous sampling mode voltage data, in which V-axis is a voltage scalar, T-axis is a time scalar, S1-Sn are the time sequences of asynchronous continuous sampling, T2 are the sampling periods, P1-pn are the voltage variation periodic signals observed at the battery terminal, and obviously the periods are related and synchronous with the pulse phase and the phase. t1 is a motor driving pulse period, and D1-Dn are sampled voltage values.

It can be observed from fig. 37 that, as t1 and t2 are synchronized, D1, D2, D3..dn sampling positions are consistent with the pulse landing positions, it is assumed that data averaging is performed by a weighted average method, that is, avg= (d1+d2+ Dn..)/n...

According to the data representation of the two graphs, the difference between the traditional simple weighted average current sampling mode and synchronous sampling is obviously explained, the swing motor belongs to the category of brushless motors in a broad sense, is driven by power pulses switched by positive and negative polarity pulses at high frequency, and the current information related to the load can be analyzed by adopting the mode sampling synchronous with the pulse phase.

When sampling using synchronous techniques, additional technical means are still required to filter the back emf signal generated by the unnecessary coils that affect the load current behavior in order to further improve the signal quality.

The rising edge overdose of the pulse includes, in addition to the coil dynamic impedance information, the back emf generated after the coil is de-energized. If the information of the rising edge overshoot of each pulse is directly used to dequantize the swing degree relationship without considering the influence of back electromotive force on signal superposition, the existence of back electromotive force can lower the quantization resolution more or less. In order to eliminate the influence of the counter electromotive force on the rising edge overshoot of each pulse, the motor coil can be instantaneously short-circuited by utilizing the H bridge in driving each stop period, so that the counter electromotive force is released quickly, and the embodiment proves that after the counter electromotive force is eliminated, the change of the swing of the motor can be monitored more sensitively, and the signal to noise ratio of signals is improved.

Therefore, fig. 38 is a schematic diagram of the principle of absorbing counter electromotive force by a short-circuit H-bridge, in which F1 to F4 are two pairs of complementary NP channel FETs to form an H-bridge as a driving of a vibration motor, M is the vibration motor, and before the current detection of the motor is started, and after the driving power is turned off, the S1 and S2 inputs are set to be at high levels F1 and F2 to enter a cut-off state. The S3 and S4 inputs are also input with high level, and F3 and F4 are conducted. After F3 and F4 are conducted, F3, F4 and M form a loop, counter electromotive force generated at two ends of the motor M is short-circuited, a short-circuit current loop C is generated, and counter electromotive force is converted into heat energy to be emitted on a motor coil.

After the back electromotive force is absorbed, S3 and S4 jump to high level to enter a cut-off state, and ADC conversion of the MCU is started to detect current.

Fig. 39 shows a comparison graph of current signals before and after eliminating back electromotive force of the vibration motor, wherein the graph comprises a V-axis and a voltage scalar, a T-axis and a time scalar, P1-P3 show 3 groups of pulse periodic signals, a CV1 solid curve is a voltage curve after eliminating back electromotive force by adopting a short circuit technology, a CV2 dotted curve is a voltage curve with the influence of back electromotive force, ts is an important area containing load change information, C does not adopt short circuit to eliminate ringing peak signals appearing in the back electromotive force, and a is an area with larger influence of back electromotive force.

The shadow area marked a and generated by the ringing peak value of the signal generated by the counter electromotive force has serious influence on the effective load signal in the Ts section, and has positive significance on analyzing the load signal after the ringing peak value is absorbed by adopting a technical means.

The back electromotive force short circuit is favorable for analyzing the change of the dynamic impedance of the coil after eliminating, but can also bring negative influence to the motor, heat energy can be generated in the coil at the moment of short-circuiting the coil current, the working temperature of the coil is caused to rise, whether a back electromotive force elimination technology is adopted or not is adopted, or a reasonable short circuit time sequence is selected, and the back electromotive force short circuit device can be selected according to practical application.

After effective swing amplitude quantification data are obtained, the data can be used for continuously increasing the pulse duty ratio by adjusting the duty ratio of the driving pulse in real time, increasing the driving power to increase the swing amplitude when the swing amplitude is lower than a set value, and otherwise, continuously reducing the duty ratio and reducing the driving pulse power to reduce the swing amplitude. By dynamically monitoring the amplitude value and dynamically adjusting the pulse driving power in real time by the method discussed above, a stable output amplitude can be obtained under load variation.

Fig. 40 is a schematic process diagram of the constant amplitude correction technique according to the present utility model, in which in addition to resolving the battery voltage variation associated with the swing, a proper sampling frequency and a proper adjustment frequency are properly selected, because the ADC collects and processes data, the too dense data sampling may interfere with the stability of the pulse phase of the drive, phase jitter occurs, and the motor swing shaft exhibits irregular swing jitter and abnormal noise. The density of the pulse duty ratio is also required to be suitable for adjusting, because the motor pendulum shaft has moment of inertia, has response time domain requirements, is too densely adjusted, and can weaken the overshoot of the analyzed useful amplitude information, so that overshoot oscillation is generated, and the motor cannot be controlled normally. Too sparse regulation, control will suffer from slow response and hysteresis, and the compensation effect is not ideal. In general, the following factors are considered in the actual control:

1. Synchronization with the motor signal-the implementation proves that the sampling data is preferably chosen to be most stable and signal to noise ratio high just before the end of the pulse.

2. The starting back electromotive force duration and density are that the back electromotive force absorption can not be started every pulse, the back electromotive force absorption can be started only before the battery voltage is detected, and the back electromotive force absorption is closed immediately after the detection is completed, otherwise, a large amount of heat is generated and dissipated on a motor coil, and the working temperature of the motor is increased sharply. Similarly, the duration of absorption is also a key point for controlling heat, and the actual situation is determined by the test result.

3. Battery voltage sampling cannot be performed every pulse, and in the example test, sampling every 20 pulses is preferable. Too dense collection can cause motor phase trembling and abnormal sounds to occur.

4. The frequency of the duty ratio of the driving pulse of the motor is also required to be reasonable. Too dense correction can generate overshoot oscillation, too sparse compensation reaction is slow, and the swing amplitude is unstable after load change.

Thus, the control method comprises the steps of:

Step one, synchronously outputting pulses (which can be the square wave pulses);

step two, starting back electromotive force absorption;

Step three, synchronously collecting battery voltage;

analyzing a variable related to the load;

Step five, calculating correction quantity;

And step six, returning to the step one after correcting the driving duty ratio.

Fig. 42 shows a flow chart of the dynamic servo process signal processing for achieving a motor constant output swing, which is mentioned for the present utility model.

The method comprises the following steps:

Step 1, judging whether 20 pulse intervals are met after the response is interrupted, if yes, entering step 2, otherwise, exiting;

Step 2, judging whether the cycle is a stop cycle, if yes, entering a step 3, otherwise, exiting;

step 3, starting back electromotive force absorption, judging whether to end driving pulse, if yes, entering step 4, otherwise, exiting;

Step 4, collecting the voltage of the battery, if the voltage value is smaller than the last collected value, entering a step 5, otherwise, entering a step 6;

Step 5, the step exits after the duty ratio of the driving pulse is increased;

And 6, judging whether the voltage value is larger than the last acquisition value, if so, decreasing the duty ratio of the driving pulse, and then exiting, otherwise, directly exiting.

The exit described above is a direct exit interrupt response.

In the embodiment of the utility model, after the system is initialized, the duty ratio of the uncompensated initial pulse is preset to be 45%, and the maximum compensation is 98%.

Fig. 41 is a graph comparing the change curves of the compensating and non-compensating pivot angles when the load changes, wherein the ordinate represents the pivot angle represented by the pivot axis and the abscissa represents the acting force applied to the pivot axis. The curve CV1 is the uncompensated output performance, and CV2 is the real-time dynamically compensated performance. As can be seen from the figure, the swing resistance to load change is significantly improved after compensation.

Referring to fig. 11 to 24B, an embodiment of the rotary brush bar of the present utility model is shown, referring to fig. 11, 12, 13 and 14, wherein fig. 11 shows a schematic view of the overall structure of the rotary brush bar of the present utility model, fig. 12 shows a schematic view of the exploded structure of the rotary brush bar of the present utility model, and fig. 13 and 14 show detailed schematic views of the internal structure of the rotary brush bar of the present utility model.

As shown in fig. 11, 12 and 13, the rotary brush rod comprises a brush rod housing 41, an inner bracket 47, a rotary brush head assembly and a power transmission assembly, the brush rod housing 41 is hollow and the rear end of the brush rod housing 41 is detachably connected to a main machine of the electric toothbrush, the rear part of the brush rod housing 41 is formed into a horn shape and is accommodated with the inner bracket 47, the inner bracket 47 is a horn shape matched with the inner cavity of the brush rod housing 41 and is hollow to form an inner space for accommodating the power transmission assembly, and the front end of the brush rod housing 41 forms a circular groove for accommodating the rotary brush head assembly.

Referring also to the mounting schematic of fig. 1, there is shown an embodiment of the rotary brush bar of the present utility model applied to an electric toothbrush, in which the rear end of the brush bar housing 41 is detachably coupled to the front end of the body housing 10, the rear end of the power transmission assembly is coupled to the output shaft 245 of the oscillating motor 20, and the front end is coupled to the rotary brush head assembly, thereby transmitting the output power of the oscillating motor 20 to the rotary brush head assembly.

Specifically, the rotary brush head assembly includes a brush head seat 421 and rotary bristles 422, the brush head seat 421 is rotatably disposed in a circular groove at the front end of the brush holder housing 41, a plurality of rotary bristles 422 for cleaning are planted at the upper end of the brush head seat, and a base is disposed at the lower end of the brush head seat, wherein in the illustrated embodiment, the brush head seat 421 is connected to the brush holder housing 41 through a rotary assembly, the rotary assembly includes a fixing frame 423, a rotary shaft 424 and a safety pin 425, the base of the brush head seat 421 is penetrated by the fixing frame 423, a side portion of the fixing frame 423 is fixed to the brush holder housing 41 through the safety pin 425, a through hole penetrating by the rotary shaft 424 is disposed in the middle of the fixing frame 423, two ends of the rotary shaft 424 extend into the brush head seat 421, so that the fixing frame 423 is relatively fixed with the brush holder housing 41 through the safety pin 425, and the brush head seat 421 rotates relative to the fixing frame 423, so that the brush head seat 421 can perform a rotary motion in the circular groove through power transmission of the rotary power assembly.

Optionally, a compensating spring 426 is provided between the base of the brush head holder 421 and the brush bar housing 41 to provide compensation in rotational movement.

The power transmission component comprises a swing rod 43, an elastic supporting point 44, an elastic coupling body 45, a driving head 46, a compensating spring 48 and a connecting sleeve 49, wherein the driving head 46 for driving the brush head seat 421 is arranged at the front end of the swing rod 43, in the embodiment of fig. 12-14, the driving head 46 is a protruding head, meanwhile, referring to fig. 16, a groove 4211 which is engaged with the protruding head in a corresponding mode is arranged on the base of the brush head seat 421, so that the protruding head serving as the driving head 46 can stretch into and be engaged with the tooth groove 4211 to realize power transmission of the two, the middle part of the swing rod 43 is elastically supported on the inner wall of the front end of the inner bracket 47 through the elastic supporting point 44, the compensating spring 48 is sleeved between the driving head 46 and the elastic supporting point 44, the connecting sleeve 49 is embedded into the rear end of the inner bracket 47, the rear end of the swing rod 43 stretches into the front end of the connecting sleeve 49, and the rear end of the connecting sleeve 49 is connected to the output shaft 245 of the vibration motor through the elastic coupling body 45 to transmit power.

Therefore, the brush head seat of the rotary brush rod is round or elliptical, the movement of the brush head seat is a rotary pair, the rotary center is the center of the brush head seat around the rotary shaft 424, the movement mode of the round brush head seat is to-and-fro opposite rotation, the rotary angle range is usually 10-120 degrees, and the conventional reciprocating rotary frequency is 80-130Hz.

In the embodiment of fig. 12-14, the rotating brush bar can reliably operate in the 80-350Hz range and maintain a payload swing angle of 20 degrees or more.

The free length of the compensation spring 48 is greater than the distance between the elastic pivot and the driving head, after the compensation spring 48 is compressed, a reaction force is generated to push the driving member toward the direction of the brush head seat, the connecting sleeve 49 is a horn-shaped sleeve, the elastic coupling body 45 is a through hole elastic body, and the protruding end of the output shaft 245 is contained by the elastic coupling body 45.

Thus, as shown in fig. 15A, 15B and 15C, when the output shaft swings, the power is coupled to the elastic coupling body 45 through the connecting sleeve 49, the swing rod swings around the elastic supporting point 44, the swing rod swings to drive the driving member 46 to follow, the driving member 46 further drives the bristle holder to swing at a high speed, and when the swing rod swings in the opposite direction, the movement direction of the bristle holder also changes in the opposite direction. The swinging of the swinging rod in two directions forms a complete movement period. The action mechanics of the swinging rod on the brush head seat is basically a simple lever principle, and the position of the elastic fulcrum at the top of the inner bracket determines the output swinging angle and the output torque of the brush head. The elastic pivot moves upwards towards the brush head, the swing angle of the brush head seat is smaller, the torque of the brush head seat is larger, and conversely, the swing angle of the brush head seat is larger, and the torque of the brush sheet is reduced.

As shown in fig. 17, the front end of the connecting sleeve 49 is tightly matched with the rear end of the swing rod 43, the rear end accommodates the elastic coupling body 45, the middle of the elastic coupling body 45 is provided with a concave ring protruding ring 451, the connecting sleeve 49 is correspondingly provided with an inner protrusion which is concave and extends into the concave space of the elastic coupling body 45, and the matching of the concave ring protruding ring 451 and the inner protrusion can be better matched with the output shaft of the swing motor for power transmission.

In a preferred embodiment of the present utility model, as shown in fig. 18A, the middle portion of the elastic supporting point 44 is provided with a concave ring 441, and the front end of the inner bracket 47 is correspondingly provided with an inner convex portion that is concave and extends into the concave space of the elastic supporting point 44, so that the concave ring 441 of the elastic supporting point 44 is tightly matched with the middle portion of the swinging rod 43, and the outer edge of the elastic supporting point 44 is also in contact fit with the inner bracket 47, so that the swinging rod 43 can swing stably with the elastic supporting point 44 as a supporting point.

In another embodiment shown in fig. 18B, another form of the power transmission assembly of the rotary brush rod according to the present utility model is shown, in which the structure of the connection sleeve 49 'and the elastic coupling body 45' is different from that of fig. 11 to 14, in which the elastic coupling body 45 'is provided with an outer protrusion corresponding to the outer edge of the concave-convex ring 451 to extend into a hollow groove of the connection sleeve 49' to achieve stable coupling of the connection sleeve 49 'and the elastic coupling body 45', and this structure can achieve better power coupling of the connection sleeve 49 'and the elastic coupling body 45'.

As shown in fig. 19A and 19B, by providing the compensation spring 48 between the elastic fulcrum and the driving head, the free length L2 of the compensation spring 48 is greater than the distance L1 between the elastic fulcrum and the driving head, so that the compensation spring 48 is compressed to generate a constant reaction force to push the driving head toward the brush head seat, so that the two can be closely attached at any time, and the gap between the two can be eliminated at any time, therefore, the compensation spring 48 can be simply referred to as an elastic compensation gap eliminating mechanism, and the elastic compensation gap eliminating mechanism can improve performance under the following working conditions:

1. The brush head seat is meshed with the surface of the driving head to fall off due to load change in the tooth brushing process, a fit clearance is generated, and the elastic compensation gap eliminating mechanism acts at the moment and forces the meshing surface tightly under the reaction force of the compensation spring.

2. In the use process of a user, under the action of toothpaste abrasive materials, the rolling friction between the driving head and the brush head seat causes abrasion of the matching surface, and the matching clearance is also generated, so that the elastic compensation clearance eliminating mechanism can act at the moment.

3. The main shaft of the brush head seat and the main shaft fixing frame can also generate fit clearance due to abrasion under the action of toothpaste abrasive materials in the use process of a user, and the worn component is tightly pressed due to the existence of the reaction force of the compensation spring, so that noise abnormal sound generated by the clearance impact of the high-speed moving component is solved.

4. The assembly formed by the swing rod and the driving head in a split mode has tolerance in actual manufacturing and assembling processes, a fit clearance exists in fit, and the elastic compensation clearance eliminating mechanism plays a role at the moment.

5. Errors exist in the shape theoretical design and actual manufacturing, and the errors also cause possible fit gaps between the protruding heads and the brush head seat grooves, so that the elastic compensation gap eliminating mechanism can play a role.

In summary, the elastic compensation anti-backlash mechanism formed by the compensation spring 48 can effectively stabilize the output angle and torque during the tooth brushing process, reduce noise and effectively prolong the service life.

More preferably, the brush rod motion structural member works in the working condition of toothpaste abrasive grinding liquid for a long time, and except for reasonably selecting high wear-resistant materials to manufacture the structural member, the meshing profile of the driving head and the brush head seat is reasonably designed, so that the maximum meshing area of the whole motion period is theoretically ensured, the reduction of meshing pressure intensity is facilitated, and the wear resistance is improved. And the friction between the meshing surfaces is ensured to be rolling friction in the whole friction type as far as possible, the occurrence of sliding dynamic friction is reduced as far as possible, and the abrasion resistance can be better resisted.

In a further preferred embodiment, the conventional involute profile curve is preferred to solve the above problem, and the nose and the groove 4211 are involute tooth-shaped, so that the type of meshing friction of the whole process is well ensured to be rolling friction. In order to maximize the meshing area, the maximum modulus and the maximum tooth thickness are selected as much as possible.

In the embodiment, besides the involute tooth profile, the tooth profile of the tooth profile brush rod protruding head and the tooth profile of the groove can be adopted to solve the tooth profile problem, and other contour patterns can be expanded, such as the protruding head is a columnar surface, and the groove is a trapezoid surface. However, in comparison with the involute tooth profile, the friction during the movement thereof may have sliding friction, so that the theoretical lifetime is weaker than in the involute tooth profile.

Regarding the implementation of the driving head and the driven member discussed in the present utility model, according to practical design requirements, as in the embodiment shown in fig. 20A and 20B, the front end of the driving head 46 may be formed into a driving groove 46', the brush head base 42 is provided with a corresponding driven boss 4212, and the driving groove 46' of the driving head 46 may be single tooth form or multiple tooth forms. Such morphological changes are all within the scope of the utility model.

In another embodiment of fig. 21A and 21B, the head of the driving head 46 is formed with a cylindrical protruding head 46", the brush head base 42 is provided with a corresponding accommodating recess 4213, and the front end of the cylindrical protruding head 46" is formed into a cylinder shape.

In another embodiment of fig. 22A, 22B, 22C and 22D, the head of the driving head 46 is formed with a U-shaped groove 46' ", and the brush head base 42 is provided with a corresponding passive cylinder 4214.

The base of the brush head seat 421 is a frame capable of accommodating the fixing frame 423, the fixing frame penetrates through the brush head base after being correctly arranged, the rotating shaft 424 is in interference fit with the fixing frame, no relative motion exists, and two ends of the rotating shaft 424 extend out and are in clearance fit with the base to form two independent coaxial rotating kinematic pairs.

The safety nails 425 are perpendicular to the axis of the rotating shaft 424, and are locked on the brush rod casing through the transverse holes on the brush rod casing 41 and the transverse lock of the holes on the side face of the fixing frame 423, so that the safety nails are prevented from being impacted by the vertical falling of the main body, and the safety nails are broken, loosened, sunken.

As shown in fig. 23A and 23B, fig. 23A is a schematic diagram of the output shaft of the oscillating motor in a stationary state in the present utility model, fig. 23B is a schematic diagram of the output shaft in a left-right swing, the output shaft swings around an origin O, P1 and P2 are respectively swingable limit positions at both ends, a is a swingable maximum angle, and B represents an arc-shaped motion track formed by the coupling point under swing, whereby the motion track of the power coupling point (output shaft) at the rear end of the swing shaft 53 is an arc-shaped circle, and the arc-shaped circle coincides with the center of rotation.

As shown in fig. 24A and 24B, fig. 24A is a schematic view of the output shaft in a stationary state, and fig. 24B is a schematic view of the output shaft swinging left and right, in which the output shaft moves in parallel, and swings in a non-arc manner, which is another example of the vibration motor mentioned in the present utility model. No matter the motor shaft swings or swings in parallel, the requirements of the toothbrush head driving power source can be met. The limit position D where P1 and P2 swing in parallel is the stroke of the swing.

Therefore, the main working mechanism of the rotary brush rod of the utility model is as follows:

1. The main machine of the electric toothbrush provides reciprocating swing moment through the output shaft. The horn-shaped sleeve at the tail end of the swing rod, the embedded connecting sleeve 49 and the elastic coupling body 45 form a coupler, and the output shaft of the host machine is in power coupling with the connecting sleeve 49 made of elastic materials and the inner hole of the elastic coupling body 45 to drive the swing rod to swing reciprocally.

1.1 The middle part of the elastic coupling body 45 is designed into a concave-convex ring 451, and the whole spindle extends into the concave-convex ring 451 to be in line contact with the concave-convex ring 451, so that no interference in the swinging process is realized, and the effective coupling of power is ensured.

1.2 The connecting sleeve 49 and the elastic coupling body 45 can also be made of rigid plastics or other materials, and the elastic materials are selected in the embodiment of the utility model, so that the noise generated by the impact force to the swing rod due to the swing and reversing of the output shaft of the host can be effectively absorbed.

1.3 The hardness of the connecting sleeve 49 and the elastic coupling body 45 is moderate, and too low the hardness can affect the dynamic coupling effect of the swing rod. The final output torque performance of the brush head base is sacrificed.

2. The middle part of the swing rod and the elastic fulcrum at the top of the inner bracket form a lever fulcrum, when the coupler swings, the driving head at the other end of the swing rod swings in the opposite direction, the driving head is in conjugate fit with the brush head seat, and finally the movable brush head is driven to swing around the central rotating shaft.

2.1, An elastic fulcrum forming a fulcrum is internally provided with a concave ring 441 with an annular convex surface, and the minimum diameter of the convex surface of the concave ring 441 is slightly larger than or equal to the outer diameter of the swing rod, so that the swing rod can axially slide in the hole. The concave ring 441 can effectively avoid interference of the shaft sleeve and power loss when the swing rod swings.

2.2 The material of the elastic pivot can also be rigid plastic, and the embodiment of the utility model is specially made of elastic rubber body, so that the elastic body is utilized to effectively buffer and absorb noise abnormal sound generated by collision of components due to gaps when the elastic body swings. The hardness of the elastic pivot is moderate and cannot be too low, otherwise, the elastic body is excessively deformed under heavy load, so that the pivot position is obviously changed or displacement is lost, the swing stroke of the swing rod is lost, and the power of the tail end of the swing rod is insufficient. The preferred angle of the embodiment of the utility model is 80-90 DEG the elastic pivot is made of nitrile rubber.

3. In one embodiment, the protruding head is wrapped by the groove of the brush head seat, when the boss swings, the groove is pushed to generate displacement, and the brush head seat has a rotating shaft 424 to form a revolute pair, so that the displacement of the groove finally appears as repeated rotation of the brush head to drive the brush hair on the brush head to swing in a rotating way.

3.1 In theory, the ideal matching state of the boss and the groove is zero clearance fit in the whole reciprocating swing process, the matching friction of the surface of the raised head and the groove of the brush head seat is rolling friction non-sliding friction, at the moment, the material abrasion caused by power coupling is minimum, and the coupling power loss is minimum. The embodiment of the utility model prefers the traditional involute tooth profile to realize the fit shape envelope of the boss and the groove. Wherein, the circle center of the reference circle of the protruding head is the fulcrum of the swing rod, and the protruding head is the annular protruding head of the elastic body at the top of the bracket in the brush rod. The central shaft of the brush head seat is the reference circle center of the groove of the brush head seat. The ratio of the convex head reference circle to the brush head seat reference circle determines the torque conversion ratio of power coupling, and finally influences the swing angle and the output torque of the brush head seat. Theoretically, the distance from the pivot point of the swing rod to the boss anastomosis point is in direct proportion to the swing angle of the brush head seat and in inverse proportion to the output torque of the brush head seat.

3.2 The matching of the lug boss and the brush head seat groove adopts involute envelope, and the whole reciprocating motion anastomosis process is in gapless matching under ideal conditions. Therefore, the operation noise caused by the matching clearance between the shapes of the lug boss and the groove of the brush head can be completely eliminated in theory.

3.3 The boss and groove of the present utility model may be engaged with one or more teeth, and the single boss and single groove structure of the brush head base is preferred based on wear resistance and applicable brush head base swing angle range. The tooth form modulus can be maximally limited, and the actual strength and the wear resistance of the boss are improved.

3.4 In the embodiment of the utility model, in order to improve the matching wear resistance of the boss and the brush head seat, the tooth thickness of the boss is improved as much as possible, and the interaction pressure of the surface area is reduced. The working space of thick teeth is reserved in design.

4. In the embodiment of the utility model, stainless steel bars with better rigidity are preferred, and in the verification process, if the rigidity of the swing rod is insufficient, under the action of high-frequency swing force, the swing angle can be partially counteracted due to the flexible resonance deformation of the swing rod, and finally, the swing angle and the output torque of the brush head are reduced, so that the due performance is lost.

5. The safety nail device is perpendicular to the axial direction of the brush rod and is not in the traditional coaxial direction, so that the safety risk that the safety nail is directly impacted by falling of the head towards the ground to cause the position of the safety nail to collapse towards the main shaft of the brush head seat, so that the brush head seat is cracked or the safety nail hole is cracked, and falling off of the brush head seat is caused in the using process of the brush head seat can be effectively avoided. After the safety nail is arranged vertically to the brush dry shaft, the problems can be effectively avoided, and the use safety coefficient of various working conditions of the brush head seat is improved.

Referring to fig. 25 to 28, a rocking brush bar of the present utility model is shown, wherein fig. 25 shows an overall external schematic view of the rocking brush bar of the present utility model, fig. 26 shows an internal schematic view of the rocking brush bar of the present utility model, fig. 27 shows an exploded schematic view of the rocking brush bar of the present utility model, and fig. 28 shows a gap schematic view of the rocking brush bar of the present utility model.

The utility model discloses a swinging brush rod, which comprises a brush rod shell 51, an inner bracket 56, a swinging brush head assembly 52 and a swinging vibration force transmission assembly, wherein the rear end of the brush rod shell 51 is detachably connected to an electric toothbrush, more particularly to the front end of a body shell of the electric toothbrush, the brush rod shell 51 is formed into a horn hollow shape, the inner bracket 56 which is also in the horn hollow shape is arranged in the rear end of the brush rod shell 51, so that an inner space with the swinging vibration force transmission assembly is formed, the swinging vibration brush head assembly 52 is arranged at the front end of the brush rod shell 51, the rear end of the swinging vibration force transmission assembly is connected to an output shaft 245 of a swinging vibration motor 20 of the electric toothbrush, and the front end of the swinging vibration brush head assembly 52 is connected to the swinging vibration brush head assembly 52, so that the output power of the swinging vibration motor 20 is transmitted to the swinging vibration brush head assembly 52.

Wherein, the oscillating brush head assembly 52 comprises a brush head 521, a rotating shaft 522, a tuft block 523 and oscillating bristles 524, the rear end of the brush head 521 extends into the front end of the brush rod housing 51 and is rotationally fixed to the inner bracket 56 through the rotating shaft 522, the tuft block 523 is fixed at the front end of the brush head 521, and the tuft block 523 is planted with a plurality of oscillating bristles 524 for cleaning.

Wherein, the brush head 521 is provided with a shaft hole through which the rotation shaft 522 rotates, and two ends of the rotation shaft 522 extend into the internal bracket 56, thereby forming a swing fulcrum of the brush head.

The swinging vibration force transmission assembly comprises a swinging shaft 53 and a coupling assembly, wherein the front end of the swinging shaft 53 is embedded into a concave hole at the rear end of the brush rod head 521, the rear end of the swinging shaft is connected to the coupling assembly, the coupling assembly is used as an output power coupling point, power drives the coupling point to swing in a swinging manner, the coupling assembly comprises a coupling block 54 and a connecting pipe 55, the swinging shaft 53 extends into the front end of the connecting pipe 55, and the rear end of the connecting pipe 55 is connected to an output shaft 245 of a swinging vibration motor 20 of the electric toothbrush through the coupling block 54.

Wherein the coupling block 54 is made of an elastic material as a passive end, and the connection pipe 55 is made of a rigid material as an active end.

And the swinging process of the swinging motor is identical to the previous process as shown in fig. 23A, 23B, 24A and 24B.

Obviously, the motor output in the mode is matched with the motion track of the coupling point of the toothbrush shaft, and parallel lines of the reciprocating transformation are mutually perpendicular to the axis of the toothbrush main body.

Wherein, the concave hole at the rear end of the brush head 521 is perpendicular to the pendulum shaft 53.

When the output shaft swings, the power is coupled through the coupling component, the brush rod head 521 swings around the rotating shaft at the top of the inner bracket of the brush rod, and the swinging of the swinging shaft links the swinging of the brush rod head to realize the tooth brushing process.

The swing track of the output shaft can be arc-shaped, and can also be an axis which is perpendicular to the axis of the main body, and the two swing modes can effectively drive the swing shaft of the brush rod.

Wherein, the coupling assembly preferably adopts an elastic coupling structure, the coupling assembly is composed of a horn-shaped connecting pipe 55 and a coupling block 54 in the connecting pipe 55, the coupling block 54 is an elastomer with a through hole, the output shaft of the pendulum vibration motor is sleeved in the elastomer, and the special structural design solves two problems:

1. The through hole of elastomer cooperates with pendulum shake motor output shaft, if hole and axle are rigid coupling, under the effect of high frequency swing, wearing and tearing will appear in the potential. The worn hole is matched with the shaft, and the reciprocating high-frequency reciprocating impact can generate intense noise. After the elastic coupling design is adopted, the reciprocating impact generated after abrasion is absorbed by the elastic body to be emitted by heat energy, so that the noise problem after abrasion is effectively solved.

2. The dynamic coupling point elastic design can allow interference fit of the shaft and the hole due to the material characteristics of the elastomer. When the matched motion interference occurs in the swing and pass process, the elastic body can rely on the self-deformable characteristic to relieve the influence caused by the motion interference. The reasonable interference design of the shaft and the hole can effectively prolong the service life of the brush rod.

Therefore, the vibration brush head component can be designed into shapes such as ellipse, circle, rectangle, triangle and the like according to actual use requirements.

Wherein, the brush rod shell 51 wraps the moving brush rod head and the pendulum shaft, effectively reduces the discomfort caused by the direct contact of the brush rod head with the oral cavity of a human body and the high-speed friction impact to the user, effectively reduces the power loss caused by the direct contact of the brush rod head with the human body, and improves the pendulum vibration output efficiency.

Wherein, the axis direction of the rotating shaft 522 is perpendicular to the swing direction of the output shaft.

Wherein the connecting tube 55 is a horn-shaped sleeve.

Wherein, the coupling block 54 is a hollow sleeve, and a concave ring is arranged in the middle of the coupling block.

Wherein a compensation pad 57 may also be provided to compensate for the swinging motion.

The front end of the brush rod housing 51 extends to form a brush head protecting cap for accommodating the brush head, the brush head protecting cap and the moving brush head 521 keep a gap G (as shown in fig. 28), the gap G ensures that the swinging brush head and the cap edge of the front section of the brush rod housing do not rub, and ensures that all high-speed moving parts work in the housing, thereby solving the uncomfortable feeling caused by the fact that the inner wall of the oral cavity of a conventional vibration brush head is directly contacted with the brush head swinging at high frequency in the using process.

Preferably, the brush head protective cap is a cap-shaped tongue edge which is half of a cap-shaped tongue edge for containing the brush head, so that the brush head can be better contained and a space for movement of the brush head can be provided.

Fig. 29A, 29B and 29C show schematic views of the swinging electric toothbrush bar with a protecting device in the present utility model, when the output shaft swings, the power is coupled by the coupling assembly, the brush head 521 swings around the rotating shaft at the top of the bracket in the brush bar as a fulcrum, and the swinging of the swinging shaft links the swinging of the brush head to realize the brushing process.

Therefore, the brush head with the conventional high-frequency swing design directly rubs with the inner wall of the oral cavity of a user in the use process of the user, and the contact of the impact mode can cause uncomfortable use feeling. The utility model discloses a swinging brush rod, wherein a cap rim surrounding the back of a brush head is arranged at the front section of a shell, and the size of the cap rim is based on the condition that the limit swinging stroke of the brush head is not influenced. Because of the existence of the cap edge, the direct contact between the inner wall of the oral cavity and the high-frequency swinging brush head can be effectively avoided in the use process of a user, and the problem of excessive stimulation to the user by the back of the brush head is solved. The cap edge also effectively reduces the pressing of the inner wall of the oral cavity on the moving brush head, so that the swing amplitude is more stable, and the power loss is effectively reduced.

In summary, the technical content of the utility model has the advantages of both, realizes the technical characteristics of high-frequency reciprocating rotary brush head, overcomes the defects of high noise, short service life and the like common to high-frequency rotary toothbrushes, and effectively improves the rotation or swinging frequency to 350Hz compared with the conventional limit index 133 Hz.

The utility model provides a flexible compensation technical means, which solves the problems of noise and service life of the brush rod under high-frequency operation.

The electric toothbrush provided by the utility model has the advantages that two modes are effectively considered, the high-frequency rotary brush head can be matched, the high-frequency vibration brush can also be matched, the power driving with 140-350Hz high-frequency vibration as a technical characteristic is realized, and the diversified and efficient cleaning requirements of users are met. And the swing and rotation torque working conditions all have the characteristics of low noise, simple structure and good economy.

It is to be clearly understood that the above description and illustration is made only by way of example and not as a limitation on the disclosure, application or use of the utility model. Although embodiments have been described in the embodiments and illustrated in the accompanying drawings, the utility model is not limited to the specific examples illustrated by the drawings and described in the embodiments as the best mode presently contemplated for carrying out the teachings of the utility model, and the scope of the utility model will include any embodiments falling within the foregoing specification and the appended claims.

Claims (10)

1. The utility model provides a high frequency power multimode electric toothbrush, includes body casing, pendulum shake motor, rotatory brush-holder stud and pendulum shake brush-holder stud, body casing is cavity form in order to form built-in space, body casing holds and has control circuit board and is equipped with a plurality of functional buttons that are connected to control circuit board on the lateral wall, its characterized in that:

The vibration motor comprises a motor support, an electromagnetic coil, a vibrating arm assembly, a front cover and a magnet, wherein the front end of the motor support is provided with the front cover, the rear end of the motor support is provided with the magnet, the rear side of the magnet is also provided with a damping block, an inner cavity is formed in the motor support to accommodate the vibrating arm assembly, and the outer edge of the rear part of the inner cavity is coated with the electromagnetic coil;

The vibrating arm assembly comprises a swinging arm, a rotating shaft, a bearing and a connecting frame, wherein the rear part of the swinging arm is positioned in an electromagnetic coil at the rear part of an inner cavity body, a disc part is formed at the front part of the swinging arm and provided with a shaft hole for the rotating shaft to penetrate, two ends of the rotating shaft are rotatably supported on a motor bracket through the bearing, the rear end of the connecting frame is coated at the front part of the swinging arm and forms a cylindrical structure for accommodating the disc part of the swinging arm, and the front end of the connecting frame is connected to the rear end of an output shaft so as to transmit vibration generated by the vibrating arm assembly to the output shaft for output.

2. The high-frequency power multimode electric toothbrush according to claim 1, wherein the swing arm, the rotating shaft and the output shaft are embedded integrally to form a vibrating arm assembly in a mode of forming a connecting frame by plastic secondary injection molding, the swing arm is a straight iron swing arm, and the rotation axis of the rotating shaft is perpendicular to the swing direction of the swing arm.

3. The high-frequency power multimode electric toothbrush according to claim 1, wherein shaft shoulders matched with the bearings are arranged at two ends of the rotating shaft, and at least one concave ring is arranged at the rear end of the output shaft, so that the output shaft and the connecting frame are formed in a stable and integrated manner after secondary injection molding.

4. The high-frequency power multimode electric toothbrush according to claim 1, wherein the swing arm is formed by stacking high-frequency low-eddy-current loss silicon steel sheets.

5. The high-frequency power multimode electric toothbrush according to claim 1, wherein the rotary brush rod comprises a brush rod shell, an inner support, a rotary brush head assembly and a power transmission assembly, the inner support is arranged in the brush rod shell to form an inner space with the power transmission assembly, the rotary brush head assembly is arranged at the front end of the brush rod shell, the rear end of the power transmission assembly is connected to an output shaft of the vibration motor, and the front end of the power transmission assembly is connected to the rotary brush head assembly, so that the output power of the vibration motor is transmitted to the rotary brush head assembly.

6. The high-frequency power multimode electric toothbrush according to claim 5, wherein the rotary brush head assembly comprises a brush head seat and rotary bristles, the brush head seat is rotatably arranged in the front end of the brush rod shell, one end of the brush head seat is provided with a plurality of rotary bristles for cleaning, and the other end of the brush head seat is provided with a base connected to the rotary power transmission assembly.

7. The high-frequency power multimode electric toothbrush according to claim 6, wherein the rotary power transmission assembly comprises a swing rod, an elastic supporting point, an elastic coupling body, a driving head, a compensation spring and a connecting sleeve, the front end of the swing rod is provided with the driving head which stretches into the base of the brush head base, the base of the brush head base forms a driven piece matched with the driving head in shape, the swing rod is sleeved with the compensation spring between the driving head and the elastic supporting point, the rear end of the swing rod stretches into the front end of the connecting sleeve, and the rear end of the connecting sleeve is connected with the output shaft through the elastic coupling body.

8. The high-frequency power multimode electric toothbrush according to claim 1, wherein the oscillating brush bar comprises a brush bar housing, an inner bracket, an oscillating brush head assembly and an oscillating force transmission assembly, the inner bracket is arranged in the brush bar housing to form an inner space with the oscillating force transmission assembly, the oscillating brush head assembly is arranged at the front end of the brush bar housing, the rear end of the oscillating force transmission assembly is connected to an output shaft of the oscillating motor, and the front end of the oscillating brush head assembly is connected to the oscillating brush head assembly, so that the output power of the oscillating motor is transmitted to the oscillating brush head assembly.

9. The high frequency powered multi-mode electric toothbrush of claim 8 wherein the oscillating brush head assembly comprises a brush head, a rotating shaft, mao Shu and oscillating bristles, the rear end of the brush head extending into the front end of the brush bar housing and being rotatably secured to the inner support by the rotating shaft, the front end of the brush head being secured with a tuft block having a plurality of oscillating bristles for cleaning planted therein.

10. The high-frequency power multimode electric toothbrush according to claim 9, wherein the oscillating force transmission assembly comprises an oscillating shaft, a coupling block and a connecting pipe, the front end of the oscillating shaft is embedded into a concave hole at the rear end of the brush head, the rear end of the oscillating shaft extends into the front end of the connecting pipe, and the rear end of the connecting pipe is connected to the output shaft through the coupling block.