JPH0346265Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a friction rotary body that controls the speed of a reciprocating controlled member on its outward path, return path, or both.

[Prior art]

Conventionally, as is already known, speed governors that control the motion speed used in soft eject devices of cassette tape recorders and cassette video tape recorders are centrifugal force type, inertia type, oil type, and air type. Although several methods can be used, the wind blowing air method is the one that is least susceptible to various requirements such as environmental changes and parts precision. However, the wind blowing air system rotates the wind blowing impeller at high speed to obtain braking force, so the speed increase ratio is larger than other types, and the disadvantage is that noise is easily generated from the speed increase gear train and wind blower. In the specification of Utility Model Application No. 57-32545, the applicant proposed a friction rotor that is thin and compact, has a simple structure, and is easy to assemble. As shown in FIG.
A sandwich structure is used in which the presser foot 17 is press-fitted one after another, but since the massing plate 9 is press-fitted to the worm shaft 2, the massing plate deforms as shown in Fig. 12 when it is press-fitted, and the press-fit slip torque is reduced. The construction is unstable, and the massing board 9 is sandwiched between the pedestal 16 and the presser foot 17, and the presser foot prevents the massaging board from coming off and slipping during rotation.
Due to the miniaturization of the braking mechanism, the strength of the pressure of the massaging plate 9 when it is sandwiched between the pedestal 16 and the presser foot 17 has become smaller and the size of the clamping has been controlled because both the pedestal and the presser foot are parts that are press-fitted into the worm shaft. Since the mounting plate is made of a single piece, it reduces the amount of work of the mounting plate, and prevents high-speed rotation or continuous operation on the inner wall surface of the cylindrical part of the sliding member of the braking mechanism, which the mounting plate slides on. Due to the generation of heat due to high-frequency repetitive operation, thermal destruction occurs due to melting of the peripheral surface, etc., and there is a limit to speed regulating performance.

Also, as shown in FIG.
Although the structure of Utility Application No. 57-183686 was proposed in which the structure was hooked on the key-shaped protrusion 19 of No. 6, the amount of deformation of the free end of the mass plate was large, and as shown in Fig. 14, the rotation speed was The characteristic curve a'' of V and torque T becomes parabolic, and the speed change δ is large with respect to the input torque change, resulting in poor speed control performance.If two mass plates are stacked on top of each other, it is difficult to assemble, making it unsuitable for rotation in the opposite direction. It was hot.

[Purpose of invention]

In view of the above-mentioned drawbacks, the present invention has been developed to provide a friction rotation system that has good assemblability of the mass plate, does not deform when incorporating the mass plate, avoids performance changes due to deformation, improves speed regulating performance, and has good speed constantity. It is to suggest the body.

[Structure of the idea]

The present invention consists of a pedestal press-fitted into the worm shaft, an axially protruding arm provided on the cradle, and an elastic body whose central hole is fitted onto the worm shaft and whose eccentric hole is fitted into the arm. Sandwich the Masatsu board and the pedestal,
It consists of a presser foot that is press-fitted into the worm shaft in a position that does not press the massaging board.

〔Example〕

The present invention will be explained below with reference to illustrated embodiments. 1st
2, the friction rotating body 1 has a worm 2a formed on a worm shaft 2, a pedestal 3 press-fitted into the outer periphery of one side of the worm shaft 2, and a center hole 4a of an elastic body plate 4 formed on the worm shaft 2. The four protruding arms 3a in the axial direction of the pedestal 3 are fitted into the eccentric holes 4b of the massing plate 4, and the spacer 10 is sandwiched between the massing plate 4 and other Masatsu board 4
Shift it by 90 degrees and insert it in the same order in the same way, and find the position where the massing board 4 is not pressed against the pedestal 3, that is, the thickness of the massing board 4 x 2 + the thickness of the spacer 10 = X dimension and the length of the protruding arm part 3a. Y is X<Y, protruding arm part 3
The presser foot 11 is attached to the worm shaft 2 so that the length A from the tip of the presser foot 11 to the step portion 2b on one side of the worm shaft 2 and the length B from the end surface of the presser foot 11 to the step portion 2b satisfy A>B.
is press-fitted with the protruding arm portion 3a against the jig.

As shown in FIGS. 3 and 4, the pedestal 3 is formed of a press-fitting part 3b having a through hole in the center, which is press-fitted into the worm shaft 2, a disk part 3c, and an axially protruding arm part 3a.

The mass plate 4 is made of a rubber material and, as shown in FIG. 5, has an annular disk portion 4c, a center hole 4a that fits into the outer diameter of the worm shaft 2 without being deformed, and a hole 4a that extends outward from the annular disk portion 4c. An elastic arm portion 4d of the book, a weight portion 4e that connects the two arm portions, and an annular disk portion 4.
c and an eccentric hole 4b having an arc shape and 180° symmetry formed between the weight portion 4e and the weight portion 4e.

As shown in FIGS. 6 and 7, the braking mechanism in which the friction rotating body 1 is incorporated includes a cup-shaped synthetic resin sliding member 6 fitted into one side of the inside of a synthetic resin case 5. Both end shaft portions of the worm shaft 2 are fitted into the shaft hole 6a at the center of the inner side and the shaft hole 5a of the case 5, and the mass plate 4 is exposed to the inner wall circumferential surface of the sliding cylindrical portion 6b of the sliding member 6. A gear body 7 supported by a case 5 is meshed with the worm 2a of the shaft 2, and a gear body 12 supported by the case 5 is meshed with the gear body 7. An input gear body 8 is coaxially supported on the upper side of the gear body 12, a coil spring 13 whose one end is attached to the gear body 12 is in sliding contact with the inner side of the input gear body 8, and an upper case 5 is mounted on the upper side of the case 5. 14 is fixed and the braking mechanism is screwed to screw 15.
is fixed to a controlled device (not shown).

The operation of the friction rotary body 1 is such that the gear body 12 and the gear body 7 are rotated via the coil spring 13 by the external power received by the input gear body 8 from a controlled member that reciprocates, and the gear body 7 is rotated via the worm 2a. The worm shaft 2 is rotated, and as a result of this rotation, the protruding arm portion 3a is brought into contact with the elastic arm portion 4d of the mass plate 4 and rotated, and the weight portion 4e is expanded to protrude outward, and the number of rotations is set to a predetermined number. When the rotational speed exceeds the rotational speed, the outer periphery of the weight portion 4e comes into sliding contact with the inner wall surface of the sliding cylindrical portion 6b of the sliding contact member 6, and the rotation of the friction rotary body 1 causes a large change in input torque as shown in the characteristic curve a in FIG. Both are braked or controlled with a very small speed change δ.

When the friction rotor 1 is configured as described above, the torque transmission between the worm shaft 2 and the mass plate 4 is carried out by the protruding arm part 3a of the pedestal 3, so that the transmission force is reliably transmitted and the torque is transmitted between the worm shaft 2 and the mass plate 4. There is no need to press-fit the shaft 2, the deformation of the mass plate 4 due to press-fitting is eliminated, and the regulating performance is stabilized. Furthermore, when the presser foot 11 is press-fitted into the worm shaft 2, the protruding arm portion 3a is placed in contact with the press-fitting, so the mass plate 4 is not compressed and deformed, the performance is stabilized, and the press-fitting dimensions of the presser foot can be controlled. This eliminates the need for assembly, facilitates assembly, increases takt time, and reduces costs. Furthermore, when two massing boards 4 are used with spacers 10 in between and shifted by 90 degrees, dynamic balance is improved, and performance is stabilized because each massaging board 4 operates independently with spacer 10 in between. As a result, the amount of work per plate 4 is reduced, and it is possible to handle high torque ranges, and the sliding cylindrical portion 6b of the sliding contact member 6 is generated due to high-speed rotation, continuous operation, and high-frequency repetitive operation. Thermal destruction of the inner wall surface due to melting damage etc. is prevented and life performance is improved. Furthermore, if the shape of the mass plate 4 is θ-shaped, the speed change δ will be very small even if the input torque change is large, so performance can be improved, the number of parts will be reduced, assembly work will be easier, and speed control will be significantly improved. be done.

In the above description, it has been explained that two massing plates 4 are used, but one or more massing plates may be used depending on the magnitude of the input torque. Further, the outer diameter of the presser foot 11 may be formed so as to rest on the protruding arm portion 3a, and the presser foot 11 may be press-fitted onto the worm shaft 2 without pressing the massing plate 4, thereby facilitating the press-fitting operation. Also, the length Y of the protruding arm portion 3a is such that the presser foot 11 is placed on the worm shaft 2 at a position where the massing plate 4 is not pressed.
It may be a little shorter as long as it can be press-fitted and torque can be transmitted to the mass plate 4. Further, an axially protruding arm portion 3a
Using two sets of pedestals 3 with two worm shafts 2
Alternatively, one may be press-fitted into the presser foot 11 and the number of types of parts may be reduced.

In the above explanation, the θ-shaped mass plate 4 was used, but the center hole 9a of the figure 8-shaped mass plate 4 shown in FIG. If the protruding arm portion 3a of the pedestal 3 can be fitted into the eccentric hole 9b of 9, the figure 8-shaped mass plate 9 may be used. Figure 8-shaped massatu board 4
When this is used, a characteristic curve a' as shown in FIG. 10 in which the speed change δ with respect to the input torque change is relatively small can be obtained.

[Effect of idea]

Since the present invention is constructed as described above, the mass plate is fitted to the worm shaft without deformation, so changes in performance are avoided, performance is stabilized, and reliability is improved. Torque is transmitted reliably by fitting the protruding arm in the direction into the eccentric hole of the massing plate, and the presser foot is press-fitted onto the worm shaft at a position that does not press the massing plate, so the massing plate is not deformed. It is possible to provide a friction rotating body that exhibits excellent practical effects such as significantly improved performance and good constant speed.

[Brief explanation of the drawing]

The drawings show an embodiment of the present invention; FIG. 1 is a cross-sectional side view of the friction rotor, FIG. 2 is a plan view of the friction rotor, FIG. 3 is a cross-sectional side view of the pedestal, and FIG. 4 is a cross-sectional side view of the friction rotor. A plan view, Fig. 5 is a plan view of the mass plate, Fig. 6 is a plan view of the main part of the braking mechanism, Fig. 7 is a cross-sectional side view of the same, Fig. 8 is a characteristic curve diagram of torque and rotational speed, Fig. 9 10 is a plan view of two types of figure-8-shaped mass plates, Fig. 10 is a characteristic curve of torque and rotational speed when the figure-8-shaped mass plate is used in combination with the pedestal of the present invention, and Fig. 11 is the conventional one. Figure 12 is a cross-sectional side view of a friction rotor using a figure-of-eight massaging plate, Figure 12 is a cross-sectional side view of a deformed version of the same massaging plate, and Figure 13 is an exploded perspective view of a conventional S-shaped massaging plate combined with a pedestal. 14 are characteristic curve diagrams of torque and rotational speed of the S-type mass plate. 1... Friction rotating body, 2... Worm shaft, 3...
cradle, 3a...protruding arm, 4, 9...massage plate, 4a, 9a...center hole, 4b, 9b...eccentric hole, 11...presser.

Claims (1)

[Scope of Claim for Utility Model Registration] 1. A cradle press-fitted into a worm shaft, an axially protruding arm provided on the cradle, a center hole fitted to the worm shaft, and an eccentric hole fitted into the arm. A rotary body consisting of an elastic massing plate and a presser foot that holds the massaging plate against the pedestal and is press-fitted onto the worm shaft in a position that does not press the massaging plate. 2. The friction rotating body according to claim 1, which is a utility model registration, in which two mass plates are provided with a spacer in between. 3 Utility model registration claim No. 2 in which there are two eccentric holes symmetrical at 180 degrees and the respective mass plates are shifted by 90 degrees.
Friction rotating body described in section.