WO1996037347A1 - Actionneur lineaire vibratoire et procede d'entrainement d'un tel actionneur - Google Patents
Actionneur lineaire vibratoire et procede d'entrainement d'un tel actionneur Download PDFInfo
- Publication number
- WO1996037347A1 WO1996037347A1 PCT/JP1996/001381 JP9601381W WO9637347A1 WO 1996037347 A1 WO1996037347 A1 WO 1996037347A1 JP 9601381 W JP9601381 W JP 9601381W WO 9637347 A1 WO9637347 A1 WO 9637347A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- link
- movers
- vibration
- mover
- linear actuator
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26B—HAND-HELD CUTTING TOOLS NOT OTHERWISE PROVIDED FOR
- B26B19/00—Clippers or shavers operating with a plurality of cutting edges, e.g. hair clippers, dry shavers
- B26B19/28—Drive layout for hair clippers or dry shavers, e.g. providing for electromotive drive
- B26B19/288—Balance by opposing oscillation
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26B—HAND-HELD CUTTING TOOLS NOT OTHERWISE PROVIDED FOR
- B26B19/00—Clippers or shavers operating with a plurality of cutting edges, e.g. hair clippers, dry shavers
- B26B19/02—Clippers or shavers operating with a plurality of cutting edges, e.g. hair clippers, dry shavers of the reciprocating-cutter type
- B26B19/04—Cutting heads therefor; Cutters therefor; Securing equipment thereof
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26B—HAND-HELD CUTTING TOOLS NOT OTHERWISE PROVIDED FOR
- B26B19/00—Clippers or shavers operating with a plurality of cutting edges, e.g. hair clippers, dry shavers
- B26B19/28—Drive layout for hair clippers or dry shavers, e.g. providing for electromotive drive
- B26B19/282—Motors without a rotating central drive shaft, e.g. linear motors
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/18—Mechanical movements
- Y10T74/18992—Reciprocating to reciprocating
Definitions
- the present invention relates to a vibration-type linear actuator using a reciprocating motor that electromagnetically reciprocally drives a plurality of movers with respect to a stator at the same frequency and opposite phases.
- German Patent Publication No. 1 151 130 7 is known as a vibration type linear actuator.
- a plurality of movers are supported on a stator by a spring body, and the plurality of movers are electromagnetically reciprocally oscillated with respect to the stator at opposite phases and at the same frequency. Therefore, the overall vibration is reduced by superimposing the anti-phase vibrations.
- this vibration type linear actuator is basically a spring vibration system, and is not a system stable against disturbance.
- the vibration type linear actuator Is used as an electric razor and the load fluctuates when the beard is cut, the amplitude of the mover to which the load is applied fluctuates transiently, and the balance with other movers is lost, making the user uncomfortable. It will give a lot of vibration.
- an object of the present invention is to provide a vibration type linear actuator that does not generate unpleasant vibration without disturbing the balance between movers and a driving method thereof.
- the movers that are electromagnetically reciprocally driven at the same frequency and opposite phases are mechanically linked to each other, and the directions of the vibrations are reversed to be transmitted to the other party.
- the change in the vibration is transmitted to the other mover with the direction of change reversed, so the anti-phase relationship between the movers is maintained.
- vibration balance will be maintained.
- the absolute value of the phase is equal or proportional, so that the amplitude center of the vibration system is invariable, and the overall vibration is Stabilize.
- the fulcrum of the link and the respective connection points of the link and both movers are located on the same line.
- the ratio of the distance between the fulcrum of the link and the connection point between each mover and the link is substantially the same as the ratio of the amplitudes of both movers in the state of the link.
- the ratio of the distance between the fulcrum of the link and the connection point between each mover and the link be substantially inverse to the mass ratio of each mover.
- the connecting portion between the two movers and the link is constituted by a shaft and a long hole into which the shaft is fitted. It is preferable to provide an amplitude restricting portion for preventing the amplitude of the mover from exceeding a certain value when the shaft hits the longitudinal edge of the long hole. It is also preferable that an auxiliary link is interposed between the link and the mover.
- a rack gear is provided on each of the movers having a phase relationship opposite to each other, and the rack gears are combined with a pinion gear rotatably mounted on a fixed shaft so that the rack gears are driven in opposite directions. It is good also as composition which consists of.
- the mover is supported on the fixed portion by a spring body so as to be swingable, and both movers having the opposite phase relationship are connected by a connection spring.
- the vibration type linear factory This vibration system can be stabilized against disturbance, and the imbalance of vibration caused by the disturbance can be returned to a steady state at an early stage, and the vibration can be minimized as a whole.
- an externally connected one of the two movers having the opposite phase relationship is provided in a linkage structure in which two movers having an opposite phase relationship are connected to each other via a link rotatably mounted on a fixed shaft.
- the connecting portion between the two movers and the link is constituted by the shaft and the long hole into which the shaft is fitted
- the two movers having the opposite phase relationship can be connected via the link with a simple structure.
- the amplitude limiting portion is used. If the amplitude swings excessively, the shaft contacts the amplitude limiting portion. The amplitude can be limited.
- connection between the link and the auxiliary link, and the connection between the auxiliary link and the shaft can all be made by rotation of the shaft and the hole, and slip at the connection portion. And wear is reduced.
- the link In the case where the link is provided with an elastic thin plate portion having elasticity, the variation in the distance between the shafts can be absorbed by the elastic thin plate portion. Further, in the case of providing a link pressing spring for elastically urging the link in a constant rotation direction, the link can always be pressed in the constant rotation direction, and it is possible to prevent rattling of the connecting portion.
- a rack gear is provided on each of the movers having a phase relationship opposite to each other, and the rack gears are combined with a pinion gear rotatably mounted on a fixed shaft such that the rack gears are driven in opposite directions to each other.
- the pinion and rack are simple structures such as a pinion and a rack, and can connect both movers that are in opposite phases. Since the pinion and the rack are used, there is no slip and wear is reduced.
- the movable element is supported on the fixed part by a spring body so as to be able to swing freely, and the two movable elements that are in the opposite phase to each other are connected by the connecting spring, so that the generation of vibration as a whole can be suppressed.
- FIG. 1 is an exploded perspective view showing one embodiment of the present invention.
- FIG. 2 is a front sectional view of a main part of a reciprocating electric shaver using a linear-drive reciprocating motor shown in FIG. 1 as a driving unit.
- FIG. 3 is a side sectional view of a main part of the reciprocating electric shaver shown in FIG. 4 (a) to (e) are explanatory diagrams showing the operation order of the above link.
- FIGS. 5 (a) to (e) are explanatory diagrams showing the operation order of another embodiment of the above link.
- FIG. 6 is an exploded perspective view of another embodiment of the present invention.
- FIG. 7 (a) is an exploded perspective view of still another embodiment of the present invention
- FIG. 7 (b) is a perspective view of another embodiment of the roller.
- FIG. 8 is an exploded perspective view of still another embodiment of the present invention.
- FIG. 9 is an exploded perspective view of still another embodiment of the present invention.
- FIGS. 10 (a) and 10 (b) are explanatory diagrams showing examples in which amplitude is regulated by a link.
- FIG. 11 is an exploded perspective view of still another embodiment of the present invention.
- FIG. 12 is an exploded perspective view of still another embodiment of the present invention.
- FIG. 13 is an exploded perspective view of still another embodiment of the present invention.
- FIG. 14 is an exploded perspective view of still another embodiment of the present invention.
- FIG. 15 is a schematic view of a spring vibration system in which the mover is connected and supported to a chassis, which is a fixed portion, by a spring body, and both movers are connected to each other by a connection spring.
- FIG. 16 is a graph showing the vibration mode of each mover when a constant frequency excitation force is applied as described above.
- FIG. 17 is an exploded perspective view of still another embodiment of the present invention.
- FIG. 18 is an explanatory diagram showing a drive system of the electric motor A according to the present invention.
- FIG. 19 is a waveform diagram of a signal used for driving the electric motor A.
- FIG. 1 shows an exploded perspective view of a linear drive reciprocating motor A
- Figs. 2 and 3 show a reciprocating electric shaver using a linear drive reciprocating motor A as a drive unit.
- a front cross-sectional view of the main part and a side cross-sectional view of the main part are shown.
- Reference numeral 2 denotes a mover, on which a permanent magnet 8 and a shock 9 (back yoke) are attached.
- the yoke 9 is a magnetic material and has a permanent magnet 8 adhered thereto.
- Reference numeral 1 denotes a stator which is formed by laminating a sintered body of a magnetic material or an iron plate of a magnetic material, and comprising an electromagnet provided with a winding 11.
- the stator 1 composed of an electromagnet faces the permanent magnet 8 provided on the mover 2 with a gap 12 therebetween.
- 13 is a plate-shaped spring body for securing the above-mentioned gap 12, and the upper end of the spring body 13 is fixed to the chassis 7 with screws 15 and the lower end of the spring body 13 is movable.
- the chassis 7 is fixed to the armature 2 with screws 15 and the chassis 7 and the armature 2 are connected by a spring body 13.
- the electromagnet constituting the stator 1 is fixed to the chassis 7 with screws 14.
- Motor A is configured.
- a plurality of movers 2 are provided, and in the embodiment shown in the attached drawings, two movers 2a and 2b are provided.
- a protrusion serving as a spring receiving portion 16 is provided on both side surfaces in the vibration direction, and an inverted L-shaped protruding piece 28 is formed from the upper portion of the protrusion.
- a sensor magnet 23 is attached to the vertical piece of the protruding piece 28 (a detection means 4 is provided on the chassis 7 at a position facing the sensor magnet 23 provided on the mover 2).
- a sensor 4a is provided, and the displacement, speed, acceleration, and the like of the moving element 2 in the moving direction are detected by the detection sensor 4a).
- a driver 17 protrudes from the upper surface of the protrusion.
- the protrusion of the central mover 2a is inserted into a rectangular opening 27 surrounded by a pair of side movers 2b and a connecting portion 26, and has an L-shaped projecting piece 2.
- a vertical piece provided with eight sensor magnets 23 is located in a recess 29 provided on one side mover 2b, and moves within the recess 29.
- the connecting part 26 also serves as a spring receiving part, and the natural vibration is generated between the two connecting parts 26 also serving as the spring receiving part and the spring receiving part 16 provided on the center movable element 2a.
- a connecting spring 5 serving as a number setting spring is interposed.
- the movable blade 3 is attached to the driver 17 so as to be movable up and down.
- the movable blade 3 is elastically pushed upward by a push-up spring 18 so that the movable blade 3 is elastically moved to the net blade 21.
- Reference numeral 22 denotes a slit blade
- 3a denotes a movable blade for the slit blade
- the movable blade 3a for the slit blade includes a movable blade for the slit blade provided on one driver 17. It is driven by a driver 17a.
- two blade heads H constituted by a combination of the movable blade 3 and the net blade 21 are constituted by two slit blades 22 and the slit blade net blade 3a.
- the blade head H has a total of three heads. Further, in the present embodiment, the polarity of the permanent magnet 8 of the mover 2 corresponding to each blade head H is made different, as a result, the reciprocating direction of each mover 2 is reversed, and vibration can be reduced. It is like that.
- the permanent magnet 8 provided on the mover 2 is vertically opposed to the stator 1 via a predetermined gap, and is magnetized in the reciprocating direction of the mover 2, as shown in FIG.
- the leaf springs 5 and 13 move to the left and right depending on the direction of the current flowing through the coil 11 of the stator 1, and the direction of the current flowing through the coil 11 can be adjusted at appropriate timing. By switching with, the reciprocating vibration of the mover 2 can be performed.
- both the movers 2a, 2b Performs a reciprocating vibration with a phase difference of 180 °.
- the spring system shown in FIG. 18 is constituted by the leaf springs 13 and the spring members 5 (strictly speaking, the spring constant component due to the magnetic attraction force further increases). Join) has been.
- the voltage of the current induced in the sensor 4a changes according to the amplitude and position of the mover 2, the speed of vibration, the direction of vibration, and the like. That is, when the armature 2 reaches one end of the amplitude of the reciprocating motion, the output of the sensor 4a becomes zero because the movement force of the magnet 23 stops and the magnetic flux does not change, and when the armature 2 reaches the amplitude center position. However, the speed of the mover 2 becomes maximum and the output voltage of the sensor 14a also becomes maximum.
- the maximum voltage is detected, the maximum speed of the mover 2 can be detected, and the above-mentioned zero point can be detected as the point of time when the moving direction is reversed (the point at which the dead point is reached).
- the moving direction of the child 2 can be detected.
- the output voltage of sensor 1a changes in a sine curve
- the AZD conversion circuit (not shown) converts the output voltage into a digital value and detects the voltage after a lapse of a predetermined time (for example, t) from zero or the output voltage from zero.
- the maximum speed at the center of the amplitude of the mover 2 can be detected by detecting the maximum voltage up to zero, and the point in time when the output voltage becomes zero detects the moving direction reversal point.
- the direction of current flow depends on whether the moving direction of the mover 2 (magnet 23) is reciprocating, From the polarity of the output voltage, it is possible to detect which of the reciprocating stroke the mover 2 is in.
- the control output unit C increases the drive current amount (the energizing time T and the maximum current value in the illustrated example). To keep the amplitude at the required value.
- the drive current flow rate is controlled by PWM control, and the amount of current is such that a PWM pulse width stored in advance is output for the detected speed. Since the velocity, the displacement, and the acceleration are correlated, the displacement or the acceleration may be detected instead of the velocity.
- the start timing of the current supply to the coil 11 is set within the time from the point of reversal of the moving direction to the center of the amplitude.
- the point at which the amplitude reaches the center can be detected as the point at which the output of the sensor 4a is maximized.
- the time t here may be a value that is adjusted according to the detected speed or acceleration of the mover 2.
- the driving method of the electric motor A is not limited to the above example, but the same driving method can be used in the following embodiments.
- the link 54 has a central hole 55 at the center and an elongated hole 56 parallel to the longitudinal direction of the link 54 on both sides.
- the central hole 55 of the link 54 is fixed to the shaft base 51. It is rotatably mounted on the shaft 52.
- the shaft base 51 is fixed to the fixing holes 59 of the chassis 7 with screws 53 so that the chassis 7 and the shaft base are fixed. 51 are integrated.
- a shaft 57 is provided vertically below the center mover 2a, and a shaft 58 is provided below the side mover 2b.
- the shafts 57 and 58 are provided on both sides of the link 54, respectively.
- the center movable element 2a and the quotient-side movable element 2b which are in the opposite phase relationship, are connected via the link 54 in this manner.
- FIG. 4 shows an operation diagram of the link 54. That is, Fig. 4 operates in the order of (a) ⁇ (b) ⁇ (c) ⁇ (d) ⁇ (e).
- the link 54 is rotatable only with respect to the shaft 52, and is therefore connected to the shafts 57 and 58 when either the center mover 2a or the both-side mover 2b moves.
- the link 54 rotates about the axis 52, and moves the other mover 2 in the opposite direction. In other words, even when a load is applied, there is no difference in amplitude between the two movers 2a and 2b, and the mode in which both movers 2a and 2b move in the same direction can be suppressed. It does not generate unpleasant vibration.
- the shafts 57 and 58 slide on the inner surface of the elongated hole 56 of the link 54 to absorb the fluctuation in the distance between the shafts 57 and 58.
- FIG. 5 shows an example in which the center hole 55 of the link 54 is shifted to one side (the mover 2b side).
- the ratio of the amplitude of the two movers 2 a and 2 b in the absence of the link 54 is equal to the ratio of the distance between the shafts 52 and 57 and 58 (that is, B: C). New This is because the steady vibration does not change due to the load on link 54, This is because the load on the shafts 57 and 58 is small, and no force is applied to the fitting portions of the shafts 57 and 58 into the long holes 56 so that wear can be reduced.
- the ratio of the mass of the center mover 2a and the mass of the both-side mover 2b, which are in an opposite phase relationship, is the ratio of the distance between the axes of the shaft 52 and the wheels 57, 58 (that is, B: C) may be reversed. This is because the products of the masses and the amplitudes of the movers 2 having the opposite phases to each other become equal, so that the vibrations during the steady vibrations can be canceled out, which is effective in reducing the vibrations.
- the centers of the three holes, the center hole 55 of the link 54 and the long holes 56 on both sides be on the same line.
- the other mover 2 can always move the link 54 in the same amount.
- no force other than rotational force is generated in the center hole 55 of the link 54, and a useless load is generated. It is possible to prevent the occurrence.
- the distance (B, C) between the shaft 52 and the shafts 57, 58 be at least twice the amplitude of the mover 2.
- the fluctuation of the shaft distance due to the amplitude of the mover 2 is reduced.
- the amount of slip between the long hole 56 of the link 54 and the shafts 57 and 58 is reduced, and the load and noise can be reduced.
- FIG. 7 shows another embodiment of the present invention.
- a roller 63 is provided between the shafts 57 and 58 and the elongated holes 56. That is, the rollers 63 are rotatably fitted to the shafts 57 and 58, and the rollers 63 are inserted into the elongated holes 56. In this way, the sliding of the shafts 57 and 58 and the slot 56 can be converted into rolling. Thus, the load can be reduced.
- the roller 63 is provided with a flange 64 for preventing the roller 63 from coming off the slot 56. Note that the outer shape of the roller 63 may be a square as shown in FIG. 7 (b).
- FIG. 8 shows still another embodiment of the present invention.
- This embodiment shows an example in which the shaft base 51 is integrated with the chassis 7.
- the shaft 52 is directly fixed to a part of the chassis 7 constituting the shaft base 51, so that the number of parts can be reduced.
- FIG. 9 shows still another embodiment of the present invention.
- a projecting piece 68 provided with a shaft 52 is integrally formed with the stator 1 and a shaft base 51 is formed by the projecting piece 68.
- FIG. 10 shows an embodiment in which the amplitude is limited by the link 54.c
- the mover 2 is merely suspended by the spring 13 so that Since the amplitude cannot be limited, if the amplitude becomes too large, there is a problem that the spring body 13 or the connecting spring 5 is damaged and the motor does not function.
- the amplitude restricting portion 56a is provided to prevent the amplitude of the movable element 2 from becoming more than a predetermined value due to the shaft contacting the longitudinal edge of the elongated hole 56.
- the length of the link 5 4 is adjusted so that the gap 66 between the shafts 57, 58 and the amplitude regulating portion 56a, which is the longitudinal edge of the slot 56, becomes an appropriate amount.
- the size of the hole 56 is set.
- FIG. 11 shows still another embodiment of the present invention. That is, in the present embodiment, a link pressing spring 70 is attached as a means for reducing noise generated by rattling at a fitting portion between the shafts 57, 58 and the elongated hole 56. .
- the fulcrum shaft 75 provided on the shaft base 51 is fitted into the fulcrum hole 72 provided at the center of the link pressing spring 70, and the fixed shaft portion 71 at one end of the link pressing spring 70 is mounted on the shaft base.
- the mounting shaft portion 73 at the other end of the link pressing spring 70 is fitted into the mounting hole 76 provided on the side surface of the link 54, by being fitted into the fixing hole 74 of the base 51.
- the link pressing spring 70 always presses the link 54 in a constant rotation direction, and the shafts 57, 5 8 and link 5 4 can be eliminated.
- FIG. 12 shows still another embodiment of the present invention.
- This embodiment shows an example in which an auxiliary link 83 is interposed between the link 54 and the mover 2. That is, the shafts 57 and 58 are rotatably fitted into holes 84 provided at one end of the auxiliary link 83, and the shaft 85 provided at the other end of the auxiliary link 83 is provided at the link 54. It is rotatably fitted in the hole 82.
- the center hole 55 of the link 54 is rotatably mounted on a shaft 52 fixed to the shaft base 51.
- FIG. 13 shows still another embodiment of the present invention.
- an elastic thin plate portion 92 is provided on a link 54. That is, an elastic thin plate portion 92 is provided at both ends of the link 54, and a hole 93 for rotatably fitting the shafts 57, 58 is provided at the tip of the elastic thin plate portion 92.
- a projecting piece 95 protrudes from the center of the link 54, and a center hole 94 that is rotatably fitted to the shaft 52 is provided at the tip of the projecting piece 95.
- the holes 93 on both sides and the center hole 94 are arranged on the same straight line.
- the distance between the shafts 57 and 58 due to the vibration of the mover 2 can be changed by the elastic thin plate portion 92, thereby reducing the number of parts and elongating the long hole.
- FIG. 14 shows still another embodiment of the present invention.
- a rack gear 104 is provided on each of the movers 2 having a phase relationship opposite to each other, and a pinion gear 101 is rotatable on a shaft 52 fixed to the shaft base 51.
- 103 in the figure is a concave portion provided on the shaft 52, and an eyelet 102 is attached to the concave portion 103 to prevent the pinion gear 101 from coming off.
- both rack gears 104 are combined with the pinion gear 101 so that the two rack gears 104 are driven in opposite directions, and have the same function as the link. Due to the combination of the pinion gear 101 and both rack gears 104 when they move, The other mover 2 is moved in the opposite direction.
- one stator 1 always drives the two movers 2 at the same frequency and opposite phase, so that the vibration of the motor A is reduced. And the vibration transmitted to the hands can be reduced.
- the mover 2 is connected to and supported by the chassis 7 which is a fixed portion only by the spring 13, and the movers 2 are connected to each other by the connection spring 5. It has a certain configuration.
- This schematic is shown in FIG. In this model, there are two modes of vibration. That is, during normal driving, both movers 2 are driven in the drive mode (f!) In which they move in the opposite direction, so that no vibration is generated as a whole.
- each mover 2 when a constant frequency excitation force is applied is as shown in the graph of FIG. Then, since a mode (f 2 ) in which both movers 2 move in the same direction occurs transiently, the motor A vibrates in the vibration direction of the mover 2 and is transmitted to the entire electric razor, thereby shaving.
- the two movers 2 having an opposite phase relationship are rotatably mounted on the fixed shaft 52 as in the present invention. By connecting to each other via the link mechanism, when an external force is applied to one of the two movers 2 having the opposite phase relationship, the amplitude of the both movers 2 is regulated to be mutually opposite by the link 54.
- FIG. 17 shows an example in which there is no connection spring 5 which is a natural frequency setting spring.
- both movers 2 are connected by the link 54, even when a load is applied to one mover 2, the driving force of the other mover 2 is transmitted through the link 54. Therefore, stable sharpness is ensured even when there is no connecting spring 5 which is a natural frequency setting spring. It has excellent connection, space, cost, and ease of assembly because there is no connecting spring 5.
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/776,185 US5921134A (en) | 1995-05-26 | 1996-05-24 | Vibratory linear actuator and method of driving the same |
DE19680506T DE19680506C2 (de) | 1995-05-26 | 1996-05-24 | Linearer Schwingungsantrieb |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12852695A JP3266757B2 (ja) | 1995-05-26 | 1995-05-26 | 振動型リニアアクチュエータ |
JP7/128526 | 1995-05-26 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1996037347A1 true WO1996037347A1 (fr) | 1996-11-28 |
Family
ID=14986934
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1996/001381 WO1996037347A1 (fr) | 1995-05-26 | 1996-05-24 | Actionneur lineaire vibratoire et procede d'entrainement d'un tel actionneur |
Country Status (5)
Country | Link |
---|---|
US (1) | US5921134A (ja) |
JP (1) | JP3266757B2 (ja) |
CN (1) | CN1096921C (ja) |
DE (1) | DE19680506C2 (ja) |
WO (1) | WO1996037347A1 (ja) |
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WO2003107516A1 (ja) * | 2002-06-17 | 2003-12-24 | 松下電工株式会社 | 振動型リニアアクチュエータ |
EP0967022B1 (en) * | 1996-12-27 | 2008-03-05 | Delta Tooling Co., Ltd. | Vibration generating mechanism |
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US6933630B2 (en) * | 2002-06-06 | 2005-08-23 | Braun Gmbh | Drive mechanisms for small electric appliances |
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DE10242092A1 (de) * | 2002-09-11 | 2004-04-01 | Braun Gmbh | Eletrisches Kleingerät mit einer Antriebseinrichtung zur Erzeugung einer oszillierenden Bewegung |
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Cited By (9)
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EP0967022B1 (en) * | 1996-12-27 | 2008-03-05 | Delta Tooling Co., Ltd. | Vibration generating mechanism |
EP0977344A2 (en) * | 1998-07-28 | 2000-02-02 | Matsushita Electric Works, Ltd. | Drive control method for linear oscillating motors and a linear oscillating motor |
EP0977344A3 (en) * | 1998-07-28 | 2000-04-26 | Matsushita Electric Works, Ltd. | Drive control method for linear oscillating motors and a linear oscillating motor |
US6181090B1 (en) | 1998-07-28 | 2001-01-30 | Matsushita Electric Works, Ltd. | Drive control method for linear oscillating motors and a linear oscillating motor |
WO2003107516A1 (ja) * | 2002-06-17 | 2003-12-24 | 松下電工株式会社 | 振動型リニアアクチュエータ |
EP1515420A1 (en) * | 2002-06-17 | 2005-03-16 | Matsushita Electric Works, Ltd. | Vibration type linear actuator |
US6991217B2 (en) | 2002-06-17 | 2006-01-31 | Matsushita Electric Works, Ltd. | Vibration type linear actuator |
EP1515420A4 (en) * | 2002-06-17 | 2007-12-26 | Matsushita Electric Works Ltd | LINEAR ACTUATOR OF THE VIBRATION TYPE |
US20210408863A1 (en) * | 2020-06-29 | 2021-12-30 | Wahl Clipper Corporation | Hair clipper pivot motor designed for battery power |
Also Published As
Publication number | Publication date |
---|---|
JP3266757B2 (ja) | 2002-03-18 |
DE19680506C2 (de) | 2002-10-10 |
CN1096921C (zh) | 2002-12-25 |
CN1163586A (zh) | 1997-10-29 |
US5921134A (en) | 1999-07-13 |
DE19680506T1 (de) | 1997-07-31 |
JPH08318061A (ja) | 1996-12-03 |
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