JPH02210654A - Operation cam - Google Patents

Abstract

PURPOSE:To realize a simplified, small-sized, and lightweight device with high reliability and to decrease the number of parts by arranging a member to be operated in plane along the track of the reciprocal arcuate motion of an operation cam body which has cam structure formed in an arcuate structure body. CONSTITUTION:A loading ring 6 is provided with a gear over its entire outer periphery and arranged on the top surface of a chassis 1. An annular driving ring 27 as a part of a cam driving means is provided with a gear at a part of its inner periphery and rotatable nearby the reverse surface of the chassis 1. An operation ring 64 begins to rotate when a pin 71 reaching the end in the groove 64' of the operation ring 64 at loading operation of the driving ring 27 and enters arcuate motion on the arcuate track by the engagement between three holders 37 and a guide support part 64b. The operation ring 634 is equipped with an operation cam body 64a which has recessed parts and projection parts formed lengthwise and the member to be operated is arranged while distributed on this operation cam body 64a in plane along the track of the reciprocal arcuate motion of the operation can body 64a.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to an operating cam that controls a member engaged with the cam by applying a moving displacement by its own moving displacement;
In particular, making the device constructed using this smaller and thinner,
Weight reduction: 1 reduction in number of parts.

The present invention relates to a suitable configuration for improving assembly workability.

[Background of the invention]

At present, the operating cam that controls the operated member by applying a moving displacement is, for example, a mode operating cam of a magnetic recording/reproducing device described in Japanese Patent Application Laid-Open No. 114154/1983.
A cam body on a relatively small-diameter disc supported by a central shaft and having a spiral cam groove in the plane of the disc is used, and power from a drive source such as a motor is received through a gear formed on the outer periphery of the cam body. A tape drive member such as a pinch roller, a reel drive member such as an idler gear, a reel control member such as a main brake member, which transmits information to the small disc-shaped cam body to rotate it, and is engaged with the cam groove. The so-called mode operating members such as the above are moved and displaced by a cam structure.

In this conventional technology, for the cam groove of the small disc-shaped cam body,
The plurality of mode operating members disposed on the outer periphery of the cam body and located far away from the cam body are engaged three-dimensionally and intensively via long arms, sliders with complicated structures, etc. Therefore, it has disadvantages such as complicating the mechanism of the device, decreasing operational reliability, increasing the occupied area and volume, increasing the weight, increasing the number of parts, and decreasing the ease of assembly.

[Purpose of the invention]

The purpose of the present invention is to improve the above-mentioned drawbacks of the prior art, and to easily achieve simplification of the device mechanism, higher reliability, reduction in size, weight, and thickness, reduction in the number of parts, improvement of assembly workability, etc. An object of the present invention is to provide an operation cam having a configuration that allows

[Summary of the Invention 1 An operating cam which, by its own movement, causes a predetermined movement displacement to a member that is in contact with the cam structure, (1) has a cam structure on the longitudinal edge surface of the arcuate structure. and (2) a guide support mechanism that guides and supports the operating cam body so that it can move in a reciprocating arc along its arcuate structure. and (3) a cam drive connection that is arranged concentrically on the operating cam body and that is connected or disconnected within a predetermined rotation angle range to the driven connection means in the operating cam body. (4) a driving means, comprising a rotating part having a means and a motor, and applying a rotational driving force to the operating cam body;
an operated member that is engaged with the cam structure of the operating cam body;

This configuration has a simple structure with a small number of parts, small size,
Light weight and high reliability can be easily realized.

An embodiment in which the operating cam is applied to a mode operating cam of a magnetic recording/reproducing device such as a video tape recorder will be described. Note that in this embodiment, the following aspects are used as each component of the invention.

That is, (1) Operation cam body: Among the guide support mechanism members that are formed on a part of the circumference of the annular operation ring and guide and support it, the first guide support part is the part of the operation ring that is formed on the circumference of the operation ring. At the top, the circumference is integrated into a continuous shape that matches the circumference. The cam structure is formed on both the inner peripheral edge surface and the outer peripheral edge surface of the arc-shaped portion of the operating cam body. Furthermore, the operating cam body serves as a driven connection means for transmitting driving force to a portion within a predetermined angular range in the longitudinal direction of the operating cam body.

A long arc-shaped groove is provided.

(2) Guide support mechanism member... As in (1) above, the first guide support part is integrated onto the annular operation ring in a manner that matches the operation cam body in circumference. There is. The guide surface portion is formed on the inner circumferential edge of the arc-shaped first guide support portion, and is a continuous arc-shaped surface whose center is the fixed center point of the arc motion of the operating cam body. The second guide support part is arranged at three points in the circumferential direction of the guide surface with respect to an arcuate guide surface on the inner circumference of the first guide support part integrated with the operation cam body.
It consists of three roller-shaped members that come into contact at certain points and guide and support it. A member serving as a fulcrum for the three roller-shaped members is also arranged on the inner peripheral side of the operating ring, and is fixed on a chassis provided as a base of the device.

(3) Driving means: Consisting of a cam driving section that is coupled to the operating cam body and provides driving force to the operating cam body, a driving force generating section, and a transmitting section, the driving force generating section includes a motor. The transmission section has a mesh structure in which gears are combined, and the cam drive section is disposed at its output stage concentrically with the operating cam body and has a fixed center point of the circular arc movement of the operating cam body. It has an annular drive ring that rotates around the same fixed center point,
Further, on the circumference of the drive ring, a pin is provided as a cam drive connection means at a position that is engaged with the arc-shaped long groove in the operating cam body. The drive ring is always connected to the motor via the gear of the transmission section, and when the motor rotates, the drive ring is continuously rotated by the rotational driving force transmitted thereto.

The bottle is loosely engaged with a long groove provided in a plane of the operating cam body, and the bottle is brought into contact with the operating cam body at both end edges in the longitudinal direction of the long groove.

(4) Operated member: Disposed along the arcuate locus of the operating cam body. The operated member is a mode operating member, which is pressed against the capstan and drives the tape to travel.

Pinch roller and its surrounding parts, one of two reels
The idler gear and head for recording or reproducing idler signals, which are selectively engaged with and rotated by the idler gear, are mounted on a rotating structure within the rotating drum device, and the tape is placed on the outer peripheral surface of the rotating drum device. The tape is wound around the tape at a predetermined angle, and is driven to run by the tape drive member in the mode operation member.

The tape is wound on two reels within a cassette cartridge.

FIG. 1 is a plan view showing an outline of the arrangement of components on a chassis of a magnetic recording/reproducing device in which the mode operating member is engaged with the operating cam body.

The magnetic recording/reproducing apparatus of this embodiment has a disk-shaped chassis 1 on which a cassette cartridge 100 containing two reels 111, 112 and a tape 53 is mounted, as shown by dotted lines in FIG. is a cylindrical rotating drum device 2.
Capstan 3° reel stand 4,5. Main parts such as the loading ring 6 and the pinch roller 57 are arranged as shown.

The loading ring 6 is rotatably held on the chassis 1 by three hold rollers 10, 11, 127 that are in sliding contact with the inner circumference of the loading ring 6.
The tape 53 is placed on reel 1 in the cassette cartridge 100.
a tape pull-out guide roller 9 for pulling out the tape 53 from the tape 11, 112; 8 are arranged. The reel stands 4 and 5 are rotatably supported by shafts 4-α and 5-a press-fitted into the chassis 1.

Near the outer periphery of the reel stand 4.5, there are a main brake 18 and a sub brake 19.5 for braking the reels 111 and 112 as reel braking members, which are one of the mode operating members for switching the mechanical layers of the device. 20 and chassis 1
Each bottle 14, 15, 16°17 press-fitted on top
It is attached so that it can rotate around the center.

Further, between these reel stands 4 and 5, there is an idler arm 25 on which an idler gear 24 and a relay gear 26 are placed as a reel drive member which is one of the mode operation members, similar to the reel braking member. , is rotatably held relative to the shaft 25-b. The idler gear 24 selectively engages with the reel stand 4 or the reel stand 5 according to the mode operation, and transmits the rotational force of the capstan motor 80 to the reel stand 4 or 5 respectively. A band brake 22 whose one end is engaged with and fixed to a bin 35 on the chassis 1 is wound around the outer circumference of the reel stand 5 on the supply side over a predetermined angle, and the other end of the band brake 22 is connected to a tensioner. It is rotatably engaged with the bin 21 on the arm 23. The tension arm 23 includes a tension bin 95 near the tip that contacts the loading ring 6.
It has a structure that rotates around a fulcrum 90 provided at the base on the opposite side, and the loading operation of the loading ring 6 rotates the tip in contact with it in the same direction.
The tension bin 95 is brought into contact with the surface of the tape 53.

Due to the rotational movement, the end of the band brake 22 connected to the bin 21 is pulled, tightening the outer periphery of the reel stand 5, and the band brake 22 can run in a state in which a tail is applied.

FIG. 2 shows the loading ring 6 for the chassis 1.
, an annular drive ring 27 as part of the cam drive means.
An operation cam body 64a having a cam structure formed in the longitudinal direction of a nine-arc-shaped body part, and a first one of the guide support mechanism members.
FIG. 6 is a sketch showing the attachment relationship of an annular operation ring 64 that is provided with a guide support portion 64b. The loading ring 6 is provided with gears over its entire outer circumference.
It is arranged on the upper surface of the chassis 1. Above drive ring 2
7 is provided with a gear (tooth shape) on a part of its inner periphery, and is held close to the lower surface of the chassis 1 in a freely rotatable state. The operation ring 64 is.

On the side of the drive ring 27 further away from the chassis 1, it is rotatably guided and supported with respect to the chassis 1 by three holders 37, which are second guide support parts of the guide support mechanism members. The holder 37 is disposed on the inner peripheral edge of the first guide support portion 64b in the operation ring 64, and
The guide support portion 64b is guided and supported. A cam structure is provided on the inner and outer circumferential surfaces of the arc-shaped operating cam body 64a in the operating ring 64 for operating a plurality of mode operating members that engage with the arc-shaped operating cam body 64a. The operating ring 64 also has a groove 64'.
is provided over a predetermined length and is engaged with a pin 71 implanted on the drive ring 27 here.

The driving ring 27 and the arc-shaped operating cam body 64a on the operating ring 64 are arranged under the reels 111 and 112 in the cassette cartridge 100 so as to overlap each other. Furthermore, the drive ring 27 and the arc-shaped operating cam body 64
The operating ring 64 having C on its circumference is flat.

FIG. 3 is a plan view of the device structure shown in FIG. 1, viewed from the back side. The outer periphery of the chassis 1 has a cup-shaped structure protruding toward the back side thereof, and has a drive ring 27. The operating ring 64 is now protected. A flywheel 28 is press-fitted into the capstan 3, and is also used as a rotor of a concentric direct drive type capstan motor 80 that drives the capstan 3.

Between the drive pulley 28-0, which is coaxial with the flywheel 28 and press-fitted into the capstan 3, and the relay pulley 29 for transmitting the reel stand driving force to the idler gear 24, A belt 30 for transmitting driving force is stretched. The transmission gear 31 and the drive gear 66 are engaged with a gear portion provided on the inner periphery of the drive ring 27 . A cam structure provided on the inner and outer circumferential surfaces of a part of the arc-shaped operation cam body 64a on the circumference of the operation ring 64 has a circular arc movement locus of the arc-shaped operation cam body 64a on the chassis 1. A sub-brake 19 as a mode operating member arranged in a plane along the
20. Pinch roller arm 58 and main brake 1
8 etc., and pin 19-a for controlling these to mode operation.

20-a, 58-a, and 18-a penetrate through the openings of the chassis 1 and are brought into contact with each other. Above pin 18-a, 1
9-a, 2O--a, and 58-a also constitute a part of the mode operation member.

FIG. 4 shows a drive motor 65 as a drive source member of the drive means, a drive gear 66, a drive ring 27 as a part of the cam drive means, an arc-shaped operating cam body 64a, and a guide support mechanism member 64b. FIG. 6 is a cross-sectional view showing the positional relationship of an operation ring 64 provided with the same. A worm gear 67 is attached to the tip of the drive shaft of the drive motor 65, and is meshed with one gear part of a drive gear 66 having two gear parts, and the other gear part of the drive gear 66 is connected to a drive ring. It is meshed with the gear surface on the circumference of 27.

Therefore, the rotation of the drive motor 65 rotates the drive ring 27 via the drive gear 66. the drive gear 66;
The worm gear 67 also forms a driving means together with the drive motor 65.

FIG. 5 shows a transmission gear (
a) 31. Transmission gear (b) 38 and transmission gear (c) 39
FIG. As shown in FIG. 1, the transmission gear (c) 39 is engaged with the loading ring 6 on the upper surface of the chassis 1, and the transmission gear (c) 39 is connected to the shaft 41 fitted to the bearing 4° pressed against the chassis 1. Set screw 4 at one end
It is fixed by 2. A transmission gear (b) 38 is press-fitted into the other end of the shaft 41, and the transmission gear (c) 39 on the upper surface of the chassis and the transmission gear (b) 38 on the lower surface of the chassis are rotated in synchronization. Ru.

As shown in FIG. 6, the transmission gear (a) 31 is provided with a tooth profile (second drive gear) 21o over the entire circumference, and has a full-circumference gear 31A and a gear 31A that meshes with the drive ring 27 and the transmission gear (b) 38. There is only one tooth profile (holding gear) 211 on the circumference, and the other outer circumference has the same diameter as the root circle of the above-mentioned all-round gear 31A! This gear has a composite structure in which a toothless gear 31B having two concentric cylindrical surfaces and a lock 1 are fixed to each other in the axial direction by pins 43 and 44. The transmission gear (a) 31 is rotatably supported by a shaft 46 which is further fixed to a boss 45 press-fitted into the chassis 1.

In addition, in FIG. 6, one tooth profile (holding gear) 211 of the partially toothed gear 31B located below the shaft 46 in the axial direction is the same as the full circumference tooth profile (holding gear) of the full circumference gear 31A located above.
The tooth profile of one of the second driving gears 210 and its outline are configured so that they overlap and match in the axial direction. In the loading operation state, the tooth profile (second drive gear) of the all-round gear 31A is engaged with the tooth profile (first drive gear) 200 formed on the circumferential surface of the drive ring 27.
Due to the rotational driving force, the full-circumference gear 31A and the partially toothed gear 31B are rotationally driven around the shaft 46. Since the transmission gear (b) 38 is further connected to the second drive gear 210 of the all-round gear 31A, the rotation of the all-round gear 31A causes the transmission gear (
c) 39 is rotationally driven.

Since the transmission gear (c) 39 is engaged with a gear portion on the outer periphery of the loading ring 6, the rotation of the transmission gear (c) 39 also rotates the loading ring 6. By rotating the loading ring 6, the tape 53 is loaded onto the outer periphery of the rotating drum device 2.

When the loading operation is completed and the mode operation is performed, the second drive gear 210 of the all-round gear 31A reaches the flank 202 on the inner peripheral surface of the drive ring 27 and reaches the corresponding part. The holding gear 211 of the partially toothed gear 31B is not engaged with the drive ring 27, but the holding gear 211 of the partially toothed gear 31B rests on the flat holding surface 201 on the inner peripheral surface of the drive ring 27. It is slid on the holding surface 201 to maintain a constant posture. The drive ring 27 remains in a state in which the holding gear 211 of the toothless gear 31B is slid on the holding surface 201.
Furthermore, it rotates by a predetermined angle in the same direction. When the second driving gear 210 is at the flank surface 202 and the holding gear 211 is engaged with the holding surface 201, the driving ring 27 moves due to its rotational movement.
It is engaged with a concentrically disposed operating ring 64 to interlock the operating ring 64 and drive the mode operating member.

As shown in FIG. 7, the circular arc-shaped rotational movement of the drive ring 27 in the direction of arrow A is converted into the rotational movement of the loading ring 6 in the direction of arrow B by the above-mentioned transmission mechanism. As shown in FIG. 8, the entrance guide roller 8 on the loading ring 6.

Rotating drum device for tape 53! The tape pull-out guide roller 9 has its central axis fixed to the upper surface of the loading ring 6, and performs the tape pull-out operation on the inlet side of the one-rotation drum device 2.

FIG. 9 shows the loading ring 6 and the pinch roller 57.
FIG. b Relay gear 61.
This is converted into a rotation of the arm operating gear 60 in the direction indicated by the maple mark in the figure. The arm operating pin 60-a then presses the torsion spring 59 in the direction of the arrow in the figure. At this time, the elastic force due to the distortion of the torsion spring 59 is
9-a to push the guide arm 56 in the direction of the arrow in the figure. This suppression causes the guide arm 56 to move toward the shaft 6.
2 as a fulcrum, and the winding pin 63 of the exit guide roller 552 fixed thereon is rotated in the direction of arrow C and moved to a predetermined stop position where the loading operation is completed. . 56-a is a projection provided on the edge of this guide arm 56, and has a structure in which it contacts a part of the pinch roller arm 58. As the guide arm 56 is rotationally displaced by the above loading operation, the pinch roller arm 58 engages with the protrusion 56-a.
A pinch roller 57 rotatably supported thereon is also rotated in the direction of arrow C.

By the above operation, the tape 53 is also wound around the exit side of the rotary drum device 2. The above guide roller 8,
9.55 continues until the guide rollers 8, 55 reach the catcher 13.54 shown in FIGS. 8 and 9, respectively.

The pinch roller 57, the pinch roller arm 58, and the operating bin 58-a are tape drive members. Since the pinch roller arm 58 is engaged with the operation ring 64 at the operation pin 58-a at the tip, the rotation of the operation ring 64 causes the pinch roller arm 58 to move deeper in the direction of arrow C and away from the protrusion 56-a. The pinch roller 57 is displaced and the tape 53 is sandwiched between the pinch rollers 57 and the capstan 3. Conversely, in the unloading operation in which the loading state is released, the mode operating members are operated in the order and direction described above.

FIG. 10 is a side view showing the positional relationship of the moving entrance guide roller 8 with respect to the loading ring 6.

The entrance guide roller 8 passes through an elongated hole 6-a provided in the loading ring 6 with a predetermined gap. The entrance side guide roller 8 is fixed to the boss 48 by a set screw 49 provided on the side of the boss 48. Further, a flange is provided below the boss 48, and this has a structure to prevent it from coming off from the elongated hole 6-a. A receiving plate 50 is press-fitted onto the outer peripheral surface of the boss 48.

FIG. 13 is a perspective view showing the general shape of the plate 50. A bin 50-a is provided at the rear of the receiving plate 50. This pin 50-a is connected to a protrusion on 6 shown in FIG.

FIG. 11 shows a state in which the entrance guide roller 8 in FIG. 10 has been further moved and is pressed against the catcher 13.

FIG. 12 is a perspective view showing the structure of the catcher 13. The catcher 13 has two upper and lower 7-shaped receivers that engage with the cylindrical portion of the boss 48 and the guide roller 8.
A loading ring 6 is located below the plane of the upper catch of the catcher 13, which positions the chassis 1 on the plane.
are pressed against each other in the direction of entry.

In this way, the compression spring 5 is released at a position where the entry side guide roller 8 is displaced by a predetermined amount after it starts contacting the catcher 13.
1 is compressed, a predetermined pressing force is generated between the boss portion 48 of the entrance guide roller 8 and the surface of the figure 7-shaped receiver of the catcher 13. The structure of this crimping portion is the same for the exit guide roller 55 and the catcher 54, and the exit guide roller 55 is crimped against the catcher 54 by the compression force due to the elasticity of the torsion spring 59.

The timing at which the two guide rollers 8 and 55 press against the catchers 13 and 54, respectively, can be synchronized by adjusting the meshing phases of the loading ring 6, the relay gear 61, and the arm operation gear 60. ing.

Next, the operation of the drive ring 27 when the guide rollers 8 and 55 are pressed against the catchers 13 and 54 with a predetermined force, respectively, will be explained.

FIG. 14 shows that the half on the chassis 1 side in the positional relationship between the drive ring 27, the full-circumference gear 31A, and the partially toothed gear 31B at the time when the compression spring 51 has compressed to a predetermined amount. It is designed to have a concave relief surface. Therefore, when only the single holding gear 211 of the partially toothed gear 31B engages with the last tooth profile of the gear portion 200 on the inner peripheral surface of the drive ring 27, when it is rotated in the direction of arrow A, the drive ring is rotated. The posture of the toothless gear 31B in state No. 4 is maintained constant at that position. The timing of this pushing operation is adjusted so that the phase relationship between the tooth profiles of the gears is synchronized with the timing at which a predetermined pressure force is generated between the guide rollers 8 and 55 and the catcher 13 and sA described above upon completion of the loading operation. has been done.

As explained above, during the loading operation, the drive ring 27 is driven in an arcuate trajectory in the direction of the arrow A in FIG.
The bottle 71 fixed above moves inside the groove 64' provided in the operating ring 64 in the direction of the β beam arrow A. During this time, the operating ring 64 is maintained in a stopped state by the tension of the tension spring 69. When the above loading operation is completed, the pin 71 on the drive ring 27 reaches the end point 71' of the groove 64' of the operating ring 64 and contacts the operating ring 64. When the drive ring 27 is further advanced from this loading completion state and rotated in the direction of arrow A, the operating ring 64 is driven to rotate precisely.

In FIG. 3, 68 is a slide switch fixed inside the outer peripheral edge of the chassis 1. As shown in FIG. The operating part of this switch is engaged with a pin 72 disposed on the operating ring 64, and the operating part detects the rotation angle of the operating ring 64 forming the operating cam body 64α and selects the operating mode. Detect. The cam structures provided independently on the inner and outer circumferential surfaces of the operating cam body 64a on the circumference of the operating ring 64 also respond to the movement of the drive ring 27 described above. It is rotated in an arc around a fixed center point via a groove 64' formed in a part. For this reason, the main brakes 18 . Sub brake 19.20. Pinch roller arm 58. Each operation bin 18 of the idler arm 25 (2, 19at20-a, 58-a
, 25-a to move and displace them to the state corresponding to the operation mode detected by the slide switch 68 shown on the back. Furthermore, the rotating drum device 2.corresponds to the operation mode detected by the slide switch 68. The capstan 3 is also selectively rotated, and operations in modes such as recording/reproduction, fast forwarding, and rewinding are also performed.

〔Effect of the invention〕

As explained above, according to the invention, 1) the operated members are distributed in a planar manner along the locus of the reciprocating circular arc movement of the operating cam body in which the cam structure is formed in the circular arc structure part; And against the cam surface of the operating cam body,
Since these elements can be directly engaged with each other, the operated member and the operating cam body can be placed in close proximity to each other, such as adjacent to each other. For this reason,
There is no need for connecting parts such as long arms or complicated sliders, and the cam structure itself is simplified. Also.

The number of component parts, mainly the above-mentioned connecting part, has also been significantly increased. Therefore, by creating a mechanism that includes the operating cam body, the operated member that is engaged with the operating cam body, and the surrounding members thereof, it is possible to simplify the structure, improve reliability, reduce size and weight, and reduce the thickness. It is possible to easily improve assembly workability and improve problems such as aggravation.

[Brief explanation of the drawing]

Figure 2 is a plan view of the recording and reproducing device seen from above, showing its chassis, loading ring, and drive ring. A sketch showing the mutual positional relationship of the operation rings, Fig. 3 is a plan view of the chassis seen from the back, Fig. 4 is a cross-sectional view showing the mounting relationship of the drive motor to the chassis, and Fig. 5 shows the loading driving force transmission. 6 is a sketch of the transmission gear, FIG. 7 is a plan view showing the engagement positional relationship between the drive ring and the transmission gear, and FIG. 8 is a plan view of tape loading operation by the loading member. Figure 9 is a plan view of the area around the pinch roller arm, Figures 10 and 11 are side views of the guide roller, Figure 12 is a perspective view of the catcher, and Figure 12 is a perspective view of the catcher.
FIG. 3 is a perspective view of the plate, and FIG. 14 is a plan view showing the state of engagement between the drive ring and the transmission gear immediately before shifting to the rotational position holding state. 1... Chassis, 2... Rotating drum device, 53...
- Tape, 3... Capstan, 4.5... Reel stand, 18... Main brake, 8... Inlet guide roller. 19.20...Sub brake, 55...Output side guide roller, 9...Tape pull-out guide roller, 31A
...Full circumference gear, 31B...Toothless gear, 38.3
9... Loading drive force transmission gear, 64... Operating ring, 64a... Operating cam body, 64b... First guide support part, 37... Holder, 65... Drive motor, 27... Drive ring, 57... Pinch roller,
71...Pin, 111.112...Reel, 64'
...Groove, 100...Cassette cartridge, 200
...first drive gear, 210...second drive gear,
211... Holding gear. 201... Holding surface, 202... Relief surface. Taku 8"... Entering liquid 0-ra 24- Mydra now 1-7-mu///, ITt-+) l+ 25- Y-Y-ra arm 1 Chassis concave 2oo・-l 1 Mashiburu Azor -S, Ba Ho Ho 2 No + --. Idetu Moon Yumbi Azumu Hanawa Peach Low Utakuni I4 8 Laps! ! Oia

Claims (1)

[Scope of Claims] 1. A plurality of cam structures each having concave portions and convex portions formed in the longitudinal direction of an arcuate structure, and a driven connection for rotationally driving the cam structure around a fixed center point. an operating cam body (64a) comprising means; and a first guide that is concentrically integrated with the operating cam body (64a) and moves in an arc around the same fixed center point as the operating cam body (64a). a support portion (64b); and a second guide disposed on the fixed structure side along the locus of the arcuate movement of the first guide support portion (64b) and engaged with the first guide support portion (64b). The operating cam body (64a) is configured to be movable in an arc around the center of the arc of the arc-shaped structure portion as a fixed center point. ), a motor (65) that generates rotational driving force, and a mechanism that is always connected to the motor (65) and continuously transmits the rotational driving force from the motor (65). and is continuously driven to rotate over a predetermined rotation angle, and its output stage is connected to the operation cam body (64a) over a partial angular range of the total rotation angle continuously driven, and is rotationally driven. a cam drive section that transmits force to at least the operating cam body (64a);
) is arranged concentrically with the operating cam body (64a) and is continuously rotated over a predetermined rotation angle range by the motor (65). It has a rotating part (27), and the rotating part (27)
A cam drive connection means is provided on the top, and the cam drive connection means is connected to the driven connection means provided in the operating cam body (64a) by a predetermined rotation of the rotating part (27). It is continuously connected or disconnected in the circumferential direction at a position within the moving angle range, and in the connected state, the operating cam body (64a) is controlled and driven in the tangential direction of its arc. A driving means configured to apply a force; and an operated member that is engaged with the cam structure of the operating cam body (64a) and is moved and displaced in accordance with the shape of the cam structure. An operation cam characterized by its configuration. 2. The operating cam according to claim 1, wherein a plurality of the operated members are provided corresponding to each of the plurality of cam structures in the operating cam body (64a). 3. The drive connection means provided on the operation cam body (64a) has a structure formed along the longitudinal direction of the arc-shaped structure part, as set forth in claim 1 or 2. Operation cam. 4. According to claim 1, 2 or 3, the driven connection means provided on the operating cam body (64a) is a concave structure formed within the plane of the operating cam body (64a). Operation cam as described. 5. The rotating part (27) in the drive means rotates the operating cam body (64a) with respect to the operating cam body (64a).
A patent claim in which the plane perpendicular to the rotational center axis of a), and the plane on which the cam structure is provided, is arranged within a plane at a position separated by a predetermined distance in the direction of the rotational center axis. The operating cam according to item 1, 2, 3 or 4 of the above range. 6. The guide support mechanism member includes the operation cam body (64a) and the first guide support part (
The first guide support part (64b) and the second guide support part (37) are engaged so that the guide support part (64b) moves in an arc on a circular arc locus at one predetermined constant radius position. An operating cam according to claim 1, 2, 3, 4 or 5. 7. The operation cam body (64a) includes the first guide support part (64a) in the guide support mechanism member.
It is a structure that is combined with b) to form an annular structure (64),
An operating cam according to claim 1, 2, 3, 4, 5 or 6. 8. The guide support mechanism member has a structure in which the first guide support part (64b) has a continuous arc-shaped guide surface whose arc center is a fixed center point of its arc motion. Range 1st, 2nd, 3rd, 4th,
The operating cam according to item 5, 6 or 7. 9. In the guide support mechanism member, the second guide support part (37) contacts the continuous arc-shaped guide surface of the first guide support part (64b) at a plurality of locations in the arc direction. Claims 1, 2, 3, and 3 are configured to include a plurality of support members that engage with each other.
The operating cam according to item 4, 5, 6, 7 or 8.