JPS63125281A - Vibrationproof device of reciprocal drive apparatus - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] 【Technical field】

The present invention relates to a vibration isolating device for suppressing vibration in a reciprocating drive device in which a driver is reciprocated by a motor, such as a reciprocating device that reciprocates a movable blade of an electric razor or a hair cutter.

[Background technology]

The rotation of the output shaft of the motor is converted into the revolution motion of an eccentric cam pin provided on the rotary plate, and this revolution motion is further converted into the reciprocating motion of the driver, which causes the inner cutter block of the reciprocating electric shaver connected to the driver to rotate. In a reciprocating drive device that reciprocates a reciprocating body, the driver and the reciprocating body vibrate from side to side around the output shaft of the motor, so repeated stress is applied to the output shaft, causing fatigue of the output shaft. (At the same time, vibration was also large, causing noise.) In order to eliminate this cause, a balance weight was installed at the opposite end of the rotary plate from the eccentric cam pin, and the drive element and balance weight were used to connect the motor's output shaft. There is a device designed to take up the balance around the cam pin, but the weight of the eccentric cam pin is small, and the weight of the balance weight is large due to the need to balance it with the driver and reciprocating body. Therefore, when the driver and the reciprocating body are at the end of the reciprocating range, the balance weight is at the opposite end to maintain balance; ,
The balance weight rotates, and when the driver and reciprocating body are above the output shaft (in the center of the movement range), the driver and reciprocating body maintain their own balance, but the balance weight It is displaced laterally with respect to the vibration direction,
This balance weight generates a new load on the output shaft, causing a problem of lateral vibration. In order to solve this problem, for example,
A technique is disclosed in Japanese Patent No. 70, which has a structure as shown in FIGS. 16 and 17. This has an eccentric cam pin 4 protruding from the upper surface of the gear 7 inserted into the output shaft of the motor 1 for connection with the driver 5, and a first balance weight 8 is attached to the end opposite to the eccentric cam pin 4. However, a balance gear 9 was pivotally supported next to the gear 7 so that the gear 7 and the balance gear 9 were engaged with each other, and a second balance weight 10 was eccentrically attached to the upper surface of the balance gear 9. Gear 7 is connected to the output shaft of motor 1 at position A and rotates in the direction of the arrow around point A, and balance gear 9 meshed with gear 7 is connected to the output shaft of motor 1 at position B and rotates in the direction of the arrow at position B. The eccentric cam pin 4 and balance weights 8 and 10 rotate in the reciprocating direction of the driver 5 as shown in FIG. 17. They are arranged in a line. However,
Regarding the reciprocating direction of the driver 5, both balance weights 8 and 10 move in the opposite direction to the moving direction of the eccentric cam pin 4 and the first driver 5 to balance the vibrations.
Then, in the direction perpendicular to the reciprocating direction of
Balances vibrations. Considering the overall balance in this way, it appears that the vibrations are balanced, but gear 7 is supported by the output wheel of motor 1, and balance gear 9 is located away from the output shaft. Because it is supported by another circle,
The gear 7 and the balance gear 9 are supported by different wheels, and a second balance weight 10 provided on the balance gear 9
is around the output shaft of the motor 1 (it rotates away from the output shaft, and when the output shaft of the motor 1 and the sleeve of the balance gear 9 are observed individually, they are in the reciprocating direction and in the direction perpendicular to the reciprocating direction, respectively. It was not possible to sufficiently absorb the vibrations of the motor 1 and achieve balance.Furthermore, due to the eccentric force transmitted from the balance gear 9, which rotates away from the motor shaft, to the gear 7, This has the disadvantage that it generates a moment and can become a new source of vibration. ■Object of the invention] The present invention was made in view of the technical background of Toue, and its purpose is to reduce reciprocating vibration. An object of the present invention is to provide a vibration isolating device capable of reducing the generation of unpleasant noise from a device.

[Disclosure of the invention]

The vibration isolating device of the reciprocating drive device of the present invention includes an output shaft 2 of a motor 1.
An eccentric cam pin 4 is provided on the rotation @ 3 attached to the shaft, and this eccentric cam pin 4 is connected to a driver 5 that reciprocates, and the output shaft 2
In a reciprocating drive device that converts the rotational motion of When the drive element 5 reaches both ends of the reciprocating range, the centrifugal force due to the weight 6 becomes thick (so that when the drive element 5 is located at the center, the weight 6 Accordingly, the weight 6 is movably supported on the rotating plate 3, and the weight 6 is positioned on the opposite side to the moving direction of the driver 5. In this way, when the driver element 5 reaches both ends of the reciprocating range, the centrifugal force exerted by the weight 6 increases, so that when the driver element 5 is greatly displaced to the end, the weight 6 Since the centrifugal force is large, it is possible to effectively balance the weight 6 and the drive element 5 to balance the load applied to the output wheel 2, thereby reducing fatigue of the output shaft 2 and reducing vibration in the direction parallel to the reciprocating drive direction. In addition, since the centrifugal force caused by the weight 6 is made smaller when the drive element 5 is located at the center, the drive element 5 is located at the center and the centrifugal force by itself is reduced. When the balance is maintained, the centrifugal force of the weight 6 is also small, and the load on the output shaft 2 and the lateral vibration due to the weight 6 can be reduced. will be described in detail with reference to the attached drawings as an example. *FIGS. 1 to 3 show the structure of a first embodiment of the present invention. In FIG. 1, 1 is a motor; The output shaft 2 of the output shaft 2 of the rotary plate 3 is fitted with the hole 11 at the center of the lower surface of the rotary plate 3 so that the rotary plate 3 rotates together with the output shaft 2. An eccentric cam pin 4 is press-fitted eccentrically from the center of the rotary plate 3, and a long hole 12 that extends in the radial direction of the rotary plate 3 is opened on the opposite side of the rotary plate 3 from the eccentric cam pin 4. The drive element 5 is housed in a pair of housings 13a and 13b, and the drive element 5 is housed on the rotating plate 3.Fixing parts 14 at both ends of the drive element 5 are attached to the housing 13a.
, 13b, and is fixed to the fixing groove part 17 of the fixing part 14.
The base 15 in the center is approximately U, which is the leap between the fixed part 14 and the base 15.
Reciprocating movement is possible by deforming the thin, letter-shaped leg portions 16. A cantilevered 7-arm 18 is provided on the lower surface of the base 15 of the drive element 5, and the eccentric cam pin 4 has a long connecting slot in the lateral force direction Y (perpendicular to the reciprocating direction X) of the arm 18. It is inserted in 19. Therefore, when the motor 1 is driven to rotate the output shaft 2, the rotation of the rotary plate 3 causes the eccentric cam pin 4 to revolve around the output shaft 2. When the eccentric cam pin 4 revolves, only the movement of the eccentric cam pin 4 in the lateral force direction Y is absorbed by the connection @Ryoka 19. The arm 18 may have elasticity), the driver 5
The base 15 is connected in the direction connecting the fixed parts 14 (reciprocating direction
), it repeats reciprocating motion at a constant cycle. Furthermore,
A bushing portion 20 is erected on the upper surface of the base 15.
The bushing part 20 is connected to a contact 1 part 22 of an inner cutter block 21 which is disposed on the upper surface of the housings 13a and 13b and is a reciprocating body equipped with a large number of inner cutter blades 25, and the driver 5 is reciprocated. When driven, the inner cutter block 21 slides along the inner surface of the outer cutter 24 of the outer cutter block 23 attached to the upper surface of the housings 13m and 13b, and cuts the hair introduced into the cutter hole of the outer cutter 24. It is supposed to be done. Further, a guide plate 26 is fixed between the motor 1 and the rotary plate 3 in the hooks 13m and 13b so as to partition the two, and the guide plate 26 has an elliptical guide that is long in the reciprocating direction X. A long hole 27 is opened, and the output shaft 2 of the motor 1 is inserted through the center of the guide long hole 27. The balance weight 6 includes a connecting rod 30 having a head 28 on the upper layer and a ring 31 that can be fitted to the lower end of the connecting rod 30.
It is given an appropriate weight so that it can be balanced with the drive element 5 and the inner cutter block 21. The connecting rod 30 of the weight 6 is inserted into the elongated hole 12 of the rotary plate 3, and is held by the head 28 so that it does not fall out of the elongated hole 12. The lower end of the connecting rod 30 inserted into the elongated hole 12 is further connected to the γ of the side plate 26.
The connecting rod 30 is inserted through the guide elongated hole 27, and a ring 31 is fitted to the lower end of the connecting rod 30 on the lower surface of the guide elongated hole 27. Thus, the weight 6 is slidably held within the elongated hole 12 and rotates together with the rotating plate 3, and furthermore, the weight 6 moves while slidingly contacting the inner periphery of the guide elongated hole 27 due to its own centrifugal force. Therefore, the base 15 of the driver 5 and the inner cutter block 21
However, the output 11 [12
When it reaches the farthest point from the end of the reciprocating range,
The weight 6 is connected to the elongated hole 12 in contact with r in the long diameter direction of the guide elongated hole 27.
Since it is located at the outer end of the drive element 5 and the inner cutter block 21 at a large distance from the output shaft 2, which is the center of rotation, on the side opposite to the moving direction of the driver element 5, maintains balance. On the other hand, as shown in FIG. 4(a) or (c), the base 15 and the inner cutter block 21 of the driver 5 are located at the center of the movement range, and the center coincides with the position of the output shaft 2. When the balance is maintained by itself, the weight 6 is located near the output shaft 2 of the inner layer of the first element 12 in contact with the end of the short diameter direction of the J-id long hole 27,
The centrifugal force is as small as possible so that the balance in the lateral direction Y is not greatly disturbed by the weight 6,
This reduces lateral vibration. Further, even in the middle of these positions, the weight 6 maintains balance in the X direction depending on the degree of movement of the drive element 5 and inner cutter block 21. What is shown in FIGS. 5 to 7 is a second embodiment of the present invention. As shown in FIG.
The upper end of a coil spring 32 is fixed to the opposite side of the eccentric cam pin 4 eccentrically from the output shaft 2, and the weight 6 is fixed to the lower end of the spring 32. In addition, motor 1 and rotating plate 3
A guide plate 26 is provided between the guide plate 2 and
6 is bored with an elliptical long guide hole 27 whose major axis is in the X direction and whose minor axis is in the Y direction.
The output shaft 2 is inserted through the center of the spring 32, and the weight 6 provided at the lower end of the spring 32 is also delivered into the guide elongated hole 27. When the rotating plate 3 rotates, the weight 6 moves due to centrifugal force. It moves while being pressed against the inner periphery of the guide elongated hole 27. Therefore, it operates in the same manner as in the first embodiment, and when the drive elements 5 and 1 inner cutter block 21 are moved to the extreme end, the 61st! As shown in I, the weight 6 fits in the long diameter end of the long hole 27 in the direction opposite to the moving direction of the drive element 5, etc., and maintains balance to prevent vibration from occurring in the X direction. When the drive element 5 and the inner cutter block 21 are located at the center, the weight 6 deforms the spring 32 and is located in the short diameter direction of the guide slot 27, as shown in FIG. The output shaft 2 is close to the output shaft 2, reducing the occurrence of vibration in the Y direction. An annular sun gear 33 is inserted through the outer periphery and is fixed to the motor 1jl?lj with a screw 34 so as to be concentric with the output shaft 2. A rotating plate 3 is fixed to the tip of the output shaft 2. An eccentric cam pin 4 connected to the driver 5 is press-fitted onto the upper surface of the rotary plate 3 at a position eccentric to the output shaft 2.
A through hole 3 is located eccentrically in the opposite direction from the eccentric cam pin 4.
A gear pongee 36 is rotatably inserted into the through hole 35, and a planetary gear 37 is inserted at the lower end of the gear pongee 36.
are fixed to each other, and the planetary gear 37 is meshed with the sun gear 33. Further, a rotating sub-plate 38 is fixed to the upper end of the gear pongee 36 on the upper surface of the rotating plate 3, and a weight 6 is attached to the rotating sub-plate 38 eccentrically from the center of the gear pongee 36. Here, the gear ratio between the sun gear 33 and the planet gear 37 is 2:
It is 1. When the rotary plate 3 rotates as the motor 1 rotates, and the driver 5 reciprocates to cause the inner cutter block 21 to reciprocate, the y7 pongee 36 rotates around the output shaft 2 as the rotary plate 3 rotates. The planetary gear 37 revolves around the planet and meshes with the sun gear 33.
revolves and rotates around the sun gear 33, and the planetary gear 37
Due to the rotation, the weight 6 also approaches the output shaft 2 and moves away from the output shaft 2 around the gear pongee 36 at a cycle of 180 degrees. In other words, the rotating sub-plate 38 rotates 180 degrees each time the rotating plate 3 rotates 180 degrees.
It is designed to rotate, and the weight 6 approaches the output shaft 2 twice and moves away from it twice for each rotation of the rotary plate 3. Moreover, the position where the weight 6 is separated from the output shaft 2 is the first position.
As shown in Fig. 0 and Fig. 11 (b) and (d), this is the time when the driver 5 and the inner cutter block 21 are moving the most, and the weight 6 is largely displaced and the driver 5 and the inner cutter block 21
and the balance in the X direction, and the weight 6 is connected to the output shaft 2.
The closest position is shown in Figures 9 and 11 (a) and (c).
As shown in , this is the case when the drive element 5 and the inner cutter block 21 are located at the center, and the unbalance in the Y direction due to the weight 6 is made small. 12 to 15 is a fourth embodiment of the present invention, in which the weight 6 is divided into two parts and only one weight 6 is moved. An annular sun gear 33 is inserted through the outer periphery of the output shaft 2, and is fixed to the light surface of the motor 1 with a screw 34 so as to be concentric with the output shaft 2. A rotating plate 3 is fixed to the tip of the output shaft 2.
f&6 is attached to the upper surface of the output shaft 2 at a position eccentric from the output shaft 2. *In addition, a through hole 35 is bored at a position eccentric from the output shaft 2 in the direction opposite to the weight 6, and an eccentric cam pin 4 connected to the driver 5 is rotatably inserted into the through hole 35. An N star gear 37 is fixed to the lower end of the eccentric cam pin 4, and the planetary gear 37 is meshed with the sun gear 33. Furthermore, a separate weight 6 is mounted eccentrically from the eccentric cam pin 4 at the upper end of the eccentric cam pin 4 on the upper surface of the rotating plate 3.
is fixed. Here, sun gear 33 and planetary gear 3
7. The gear ratio is 2:1, and the weight of the fixed weight 6 is greater than the weight of the weight 6 attached to the eccentric cam pin 4. As the rotating plate 3 rotates, the eccentric cam pin 4 revolves around the output shaft 2, and the planet gear 37 meshing with the sun gear 33 revolves and rotates around the sun gear 33. Due to the rotation, the center of gravity of the weight 6 on the moving side approaches the output shaft 2 around the eccentric cam pin 4 at a cycle of 180 degrees,
Move outward. In other words, the weight 6 on the moving side rotates once every time the rotary plate 3 rotates 180 degrees, and while the rotary plate 3 rotates once, the weight 6 approaches the output shaft 2 twice, and It's becoming more and more distant. Moreover, the position where this weight 6 approaches the output shaft 2 is located between the drive element 5 and the inner cutter block 2, as shown in FIGS. 13 and 15(b) and (d).
1 is moving the most, and eccentric cam pin 4
As the weight 6 attached to the output shaft 2 approaches the output shaft 2, the combined center of gravity of both the weights 6, 6 becomes in the opposite direction to the eccentric cam pin 4 and farthest away from the output shaft 2, and the driver 5 and the inner It is balanced in the X direction with the blade block 21. In addition, the weight 6 attached to the eccentric cam pin 4 is connected to the output shaft 2 and the position is 14. As shown in pile 15M (agriculture) (e), this is when the drive element 5 and the inner cutter block 21 are located at the center, and the combined center of gravity of both weights 6 is closest to the output shaft 2 in the lateral direction. This is done to reduce the imbalance in the Y direction.

【Effect of the invention】

As described above, in the present invention, the weight is movably supported on the rotary plate so that the weight is positioned W1 on the opposite side to the moving direction of the driver, and the driver reaches both ends of the reciprocating radius R. Since the centrifugal force caused by the weight increases at times, the centrifugal force of the weight is large when the driver is displaced farthest to the end, so the balance between the weight and the driver is effectively balanced and the output is increased. It is possible to reduce fatigue of the output shaft by balancing the load applied to the shaft, and also to reduce vibration in a direction parallel to the reciprocating drive direction. In addition, when the driver is located in the center, the centrifugal force due to the weight is small, so if the driver is located in the center and is balanced by itself, the centrifugal force of the weight is also small. This makes it possible to reduce the load on the output shaft due to the weight and the lateral vibration.

[Brief explanation of the drawing]

Fig. 1 is an exploded perspective view showing a first embodiment of the present invention, Figs. 2 and 3 are sectional views of the same, and Fig. 4 (a), (b), and (c).
(d) is an explanatory diagram of the same operation as above, FIG. 5 is an exploded perspective view showing the second embodiment of the present invention, FIG. 6 is a sectional view of the same as above, FIG. An exploded perspective view showing the second embodiment, FIGS. 9 and 10 are sectional views of the same as above, and FIG. 11 (a
)(b)(c)(d) are explanatory diagrams of the same operation as above, FIG. 12 is an exploded perspective view showing the fourth embodiment of the present invention, FIGS. 13 and 14 are sectional views of the same as above, and FIG. 15 (a) (b) (c) (
d) is an explanatory view of the same operation as above, FIG. 16 is a partially cutaway front view of the conventional example, and Figure #17 is an explanatory view of the same operation. 1... Motor, 2... Output wheel, 3... Turning board, 4
... Eccentric cam pin, 5... Drive element, 6... Weight. Agent Patent Attorney Ishi 1) Chief 7th Drawing 8th Figure 112th Figure 16th Figure 17th Figure 112 Figure 16 Figure 17

Claims (5)

[Claims] (1) An eccentric cam pin is provided on the rotary plate attached to the output shaft of the motor, and this eccentric cam pin is connected to a driver that drives the driver reciprocally. In a reciprocating drive device that converts motion into motion,
A weight is movably supported on the rotary plate so that the weight is positioned on the opposite side to the moving direction of the driver, and when the driver reaches both ends of the reciprocating movement range, the centrifugal force due to the weight is large. A vibration isolating device for a reciprocating drive device, characterized in that the centrifugal force caused by the weight is reduced when the drive element is located at the center. (2) providing a guide plate fixed parallel to the rotating plate;
A long elongated hole in the radial direction is drilled on the opposite side of the rotary plate from the eccentric cam pin, and a elongated guide hole that is elongated in the reciprocating direction of the driver is bored in the guide plate, so that the elongated hole on the rotary plate and the guide length of the guide plate are formed. A vibration isolating device for a reciprocating drive device according to claim 1, characterized in that the weight is movably supported by the hole. (3) providing a guide plate fixed parallel to the rotating plate;
A long hole is bored in the guide plate in the direction of reciprocating movement of the driver, and a weight is movably supported on the rotary plate by a spring.
A vibration isolating device for a reciprocating drive device according to claim 1, characterized in that this weight is delivered into the guide elongated hole. (4) A sun gear is fixed on a shaft concentric with the output shaft of the motor, and a planetary gear is meshed with the outer periphery of the sun gear, and the gear shaft integrated with the planetary gear is rotated on the opposite side from the eccentric cam pin. A vibration isolator for a reciprocating drive device according to claim 1, characterized in that the vibration isolator is rotatably supported on a plate and has a weight eccentrically attached to a gear shaft. (5) A sun gear is fixed on a shaft concentric with the output shaft of the motor, and a planetary gear is meshed with the outer periphery of the sun gear, and the eccentric cam pin integrated with the planetary gear is rotatably pivoted on the rotary plate. The reciprocating device according to claim 1, wherein the weight is mounted eccentrically on an eccentric cam pin, and another weight is mounted on the opposite side of the rotary plate from the eccentric cam pin. Vibration isolation device for drive equipment.