JPS59186160A - Operating mechanism of video tape recorder - Google Patents

Abstract

PURPOSE:To make an operating mechanism simple and thin at its profile by the constituting that a cam shaft is placed in parallel with a chassis and various mechanism are operated via plural cams provided to this cam. CONSTITUTION:Cams 25-29 are formed to a cam shaft 9 at a prescribed interval mutually along the axial direction. The cam 25 is engaged with a slide 30 of a part A, the cam 26 is engaged with a lever 56 of a part B, the cam 27 is engaged with a lever 51 of a part C, the cam 28 is engaged with a slide 60 of a part D, and the cam 29 is engaged with a slide 70 of a part E respectively, and the slides 30, 60 and 70 are displaced in the direction (y) and the levers 51, 56 are displaced in the direction of (z) respectively. A lever 75 is displaced in the direction (x) by the movement in the direction (x) of the cam shaft 9 according to the turning of the cam shaft 9. Further, the displacement of the slides and the levers controls the operation of the prescribed part via various operating mechanisms. Thus, the operating mechanism is miniaturized.

Description

[Detailed Description of the Invention] Technical Field The present invention provides a video tape recorder (hereinafter referred to as VT"R) that can record, play, review, stop, rewind,
This relates to an operating mechanism that controls necessary operations such as power transmission to the reel stand, switching, attaching and detaching the brake, or attaching and detaching the pinch roller during operation in each mode such as fast forwarding and when transitioning between each mode. .

BACKGROUND OF THE INVENTION Some conventional VTRs use solenoids to independently drive each brake, etc., when performing operations such as attaching and detaching the brakes to and from the reel stand. Another example is one in which gears arranged in a plane are driven by a motor, and a brake or the like is operated via a slide or the like.

However, these conventional operating mechanisms have the disadvantage that the mechanical parts are thick and complicated.

Purpose: In view of the above-mentioned drawbacks, it is an object of the present invention to provide an operating mechanism that is thin and has a simple structure. The above object is achieved by controlling the operation of a predetermined portion by at least the displacement of each cam accompanying the rotation of the camshaft.

composition An embodiment of the present invention will be described below.

In FIG. 1 showing one embodiment, a motor 1 has a gear 2 fixed to its rotating shaft and a gear 4 fixed to a worm 3 meshing with each other. 5 and 6 are bearings that support the worm 3. A gear 7 meshes with the worm 3, and a gear 8 fixed coaxially with the gear 7 meshes with a gear 10 at the end of the camshaft 9. 11.12 is the bearing supporting the shaft with the gear 7.8; the bearing 12 also supports one end of the camshaft 9. Another gear 13 meshes with the worm 3, and the gear 13 has a radial protrusion 1.
A shaft 1 fixed to the chassis is provided with a cam having 4
A lever 17 rotatably supported by the cam 6 abuts the cam, and the lever 17 also abuts one end face of the camshaft 9 . Although not shown in FIG. 1, the gear 13 also constitutes a part of a loading mechanism that will be described later.

The camshaft 9 is installed parallel to the chassis, and has bearings 12, so that it can rotate around the shaft and also move in the axial direction.
18.

In the figure, only one chassis is shown with the symbol 15, but in this embodiment, it has a double chassis structure with one more chassis in parallel with this chassis 15, and most of the chassis in the figure is The mechanical part is provided between these two chassis. A camshaft 9 is also provided between the two chassis.

Cams 19 and 20 are provided on both end faces of the camshaft 9, and the height of the cams 19 and 20 in the axial direction are displaced by one rotation in the circumferential direction of the shaft. cam 1
The direction indicated by 9 is such that when the gear 13 rotates and the protrusion 14 of the cam comes into contact with the lever 17, the camshaft 9 also rotates and the lever 17 comes into contact with the maximum displacement part of the cam 19 on one end surface. It is set.

Cams 25 to 29 are formed on the camshaft 9 along the axial direction at predetermined intervals. These cams 25-2
9 engages with various levers and slides to operate various mechanical parts by rotation of the camshaft 9.

The cam 25 is inserted into the slide 3 at the opening 31 of the slide 30.
0, and the elongated hole of the slide 30 engages with a shaft 33 fixed to the chassis, thereby making it possible to slide the slide 30. 34 is a supply reel stand which rotates around a shaft 35 fixed to the chassis, and 36 is a brake for the supply reel stand 34. The brake 36 is attached with glue 7 fixed to the chassis so that it can be attached to and detached from the supply reel stand 34.
It is rotatably supported by, and is engaged at the end by a pin 38 with a flange at the end of the slide 30. The brake 36 is also connected to the supply reel base 34 by a coil spring 39.
It is biased in the direction of being crimped.

45 is an input gear that applies rotational force to the supply reel stand 34 or the take-up reel stand 46, and the rotational torque of this gear 45 is transmitted to the gear 48 via the gear 47;
From there, it is transmitted to the supply reel stand 34 or the take-up reel stand 46 via the idler gear 49. The gear 47 is movable axially between shafts fixed to the chassis;
As a result, in the case of recording mode or playback mode, the torque of gear 45 is transmitted to gear 48 via the slip mechanism described later, and in the case of fast forward mode or rewind mode, the torque of gear 45 is not attenuated. The transmission gear is changed so that the signal is transmitted to the gear 48.

Reference numeral 51 denotes a lever for controlling the axial movement of the gear 47, whose fulcrum is supported by a shaft 52, and whose other end engages with the cam 27 of the camshaft 9 so as to move the gear 47 at one end.

In addition, in the slip mechanism of the gear 48, the shaft 5
By the rotation of Leno e-54 which is rotatably supported by 3,
The lever 54 is controlled by one end of a lever 56 whose fulcrum is supported by a shaft 55, and the other end of the lever 56 is connected to the cam 26 of the camshaft 9. It is designed to engage.

Although this will also be described later, the rotating shaft 57 of the gear 49 is connected to the lever 5.
The lever 58 rotates around a shaft 59 fixed to the chassis to either the supply reel stand 34 side or the take-up reel stand 46 side depending on the rotating direction of the gear 47, thereby connecting the gear 49 and the supply reel stand. The engagement with the stand 34 or the take-up reel stand 46 is changed.

The cam 28 of the camshaft 9 is rotatably supported by a large load brake 63 by a pin 62 at the end of the opening 616 of the slide 60. The take-up reel stand 46 rotates around a shaft 64 fixed to the chassis, and the brake 63 rotates around a shaft 65 fixed to the chassis so that it can be attached to and removed from the take-up reel stand 46 by the sliding movement of the slide 60. It is supported by a coil spring 66 in the direction of being crimped onto the take-up reel stand 46 .

The cam 29 of the camshaft 9 engages with a slide 70, and the slide 70 engages with a pin 71 at the end of a small-load brake 72 by a ridge at its end. The brake 72 is rotatably supported on a shaft 73 fixed to the chassis so that it can be attached to and removed from the take-up reel stand 46 by the sliding movement of the slide 70, and is also supported by a coil spring 68 to be attached to and removed from the take-up reel stand 46.
6 in the direction of being crimped.

A tip 76 of a lever 75 rotatably supported by a shaft 74 fixed to the chassis comes into contact with the cam 20 on the other end of the camshaft 9, and the tip 76 is pressed in the direction of the cam 20 by a coil spring 77. has been done. Cam 20 and lever 75
The contact with the tip 76 of the lever 75 is adjusted so that when the lever 17 comes into contact with the maximum displacement part of the cam 19 at one end of the camshaft 9, the tip 76 of this lever 75 also comes into contact with the maximum displacement part of the cam 20. . A lever 78 is rotatably supported on the shaft 74, and a coil spring 79 is stretched between the levers so that the lever 78 also rotates counterclockwise when the lever 75 rotates counterclockwise. Also lever 75
A pin 80 provided in the lever 78 engages with an opening 81 provided in the lever 78, so that as the L/bar 75 rotates clockwise, the lever 78 also rotates in the same direction.

One end of a lever 83 is rotatably supported by a pin 82 at the end of the lever 78, and a pin 84 is supported at the other end of the lever 83.
One end of the pinch lever is rotatably supported by the pinch lever. The pinch lever 85 has a pinch roller 86 at the other end and a shaft 87.
The pinch roller 86 is rotatably supported by a shaft 88 fixed to the chassis at the intermediate portion, and rotates about the shaft 88 such that the pinch roller 86 is attached to and detached from the capstan shaft 89 by displacement of the lever 83. Do the following. The capstan shaft 89 is driven and rotated by a capstan motor (not shown).

The relationship between the camshaft 9, the cams provided thereon, and the slides and levers that engage with these cams is shown in more detail in FIG. Cam 25 is connected to slide 30 and part A, and cam 2
6 is the lever 56 and part B, and the cam 27 is the lever 51 and part C.
The cam 28 engages the slide 60 at the D section, and the cam 29 engages the slide 70 at the E section, and as the camshaft 9 rotates, the slides 30, 60 and 70 move the lever in the Y direction as shown by the arrow. 51 and 56 are respectively displaced in the Z direction as indicated by the arrows.

Further, as the camshaft 9 rotates, the lever 75 changes the amount of displacement in the X direction due to the change in the height of the cam 20 on the end surface, and the cam of the gear 13 at the other end from the camshaft 9 as shown in FIG. The amount of displacement pushed in the X direction by the protrusion 14 via the lever 17 and the amount of change in the X direction due to the change in the height of the cam 19 on the other end surface are added together to produce a displacement in the X direction.

Next, the reel stand drive mechanism is shown in detail in FIG.

FIG. 3(c) shows a state in which the gear 49 is engaged with the take-up reel stand 46, and in this figure, 90 is a reel drive motor, and 91 is a belt that connects the motor 90 and the gear 45. .

In FIG. 3 CB), the gear 48 is crimped to a gear 92 of the same diameter that is slidably provided coaxially with the shaft 59 via a slip felt 93 that is fixed to the gear 92.
The gear 92 is connected to the gear 48 by a spring 95 via a sleeve 94 and a lever 54 which are also slidably provided on the shaft 59.
By being pressed in this direction, a slip mechanism is formed. 96 is a spring holder that holds the spring 95. still,
In FIG. 3) and C), some hatching is omitted for simplification.

The gear 92 is also in contact with the lever 58 via a slip felt 97 fixed to the lever 58, and the lever 58 is slidably fitted on the outside of the sleeve 94 and is engaged with the lever 54 via a spring 98. At the same time, the shaft 57 of the gear 49 is supported. 15' is the main chassis on the upper side in the figure. In this example, the chassis has a double structure, and the gears and levers shown in FIG. 3(B) are installed between the two chassis. ing. Figure 3 (
In state B), the rotational torque of the reel drive motor is the same as that of the belt 91. The signal is transmitted to gear 92 via gears 45 and 47. Since the gear 92 is pressed in the direction of the gear 48 by a spring 95, a frictional force acts between the gears 92 and 48 due to the slip felt 93, and a certain amount of torque of the gear 92 is transmitted to the gear 48.

Thereafter, the take-up reel stand 46 is rotated via the gear 49. This state is used in recording and playback modes.

The lever 54 can be rotated about the shaft 53 by rotation of a cam 56 on the camshaft shown in FIG. If the lever 54 is rotated upward in the figure in FIG. 3(B), the sleeve 94 will also rise accordingly, and the pressure bond between the gears 92 and 48 will become stronger, and the slip felt 93 interposed between the two gears will cause the sleeve 94 to rise. Since the frictional force becomes stronger, the torque transmitted from gear 92 to gear 48 increases. This state is also used in review mode, although the type of reel stand that engages with it is different.

Gear 47 has a thickness that spans gears 92 and 48, and slides smoothly on shaft 50 as lever 51 in FIG. 1 rotates.

In the state shown in Fig. 3 CB), gear 47 is only meshed with gears 45 and 92, and not with gear 48.
In FIG. 3(C), the gear 47 is pushed upward in the figure by the lever 51, and is also engaged with the gear 48. In this state shown in FIG. 3 0, the slip mechanism does not operate and the gear 47
All of the rotational torque is transmitted to gear 48. This state is used in fast forward and rewind modes, although the type of reel stand that is driven differs.

Since the lever 58 is in frictional contact with the gear 92 via the slip felt 97, when the direction of rotation of the gear 92 is reversed, the lever 58 rotates about the shaft 59 as a fulcrum and engages with the reel stand. Change relationships. Now, in the state shown in FIG. 3, such as in the playback mode, the gear 48 is rotating clockwise, so the lever 58 receives a clockwise rotational moment and moves the gear 49 onto the take-up reel stand 46. It is pressed and interlocked. For example, if the rotational direction of the reel drive motor 90 is reversed to switch to the rewind mode, the rotational direction of the gear 48 becomes counterclockwise, and the lever 58 rotates counterclockwise accordingly. The gear 49 comes to mesh with the supply reel stand 34.

In this embodiment, most of the mechanical parts such as the camshaft 9 and various gears and levers shown in FIG. 1 are housed between the dual-structured chassis. For example, a capstan motor is directly assembled with a double chassis (main chassis 15' and sub-chassis 15) as part of the motor components, as shown in FIGS. 4 and 5.

That is, the stator coil portion is fixed to the opening 100 of the sub-chassis 15 from below in the figure, and the stator coil 101 protrudes into the opening 100. A rotor 102 fixed to a capstan shaft 89 is provided opposite to the stator coil 101.
9 protrudes from the opening of the main chassis 15', and a bearing 103 is provided between the capstan shaft 89 and the opening of the main chassis 15'. 104 is the bottom plate of the motor case, and the capstan shaft 89 is connected to the bearing 103 and the bottom plate of the case 1.
It is rotatably supported by 04.

105 is a boss for maintaining the distance between the main chassis 15' and the sub-chassis 15; 106 is a magnetic circuit port;
07 is a belt. Note that 86 is a pinch roller.

FIG. 4 further shows a cylinder head 108 that holds a head cylinder, and this cylinder head 108 is fixed from the lower side of the main chassis 15', and a part of the cylinder head 108 is attached to the opening of the main chassis 15'. It is designed to protrude from 109.

110 and 111 are guide grooves for guiding the tape guide assembly of the tape loading mechanism.

Here, the operations of the above operating mechanisms except for the tape loading mechanism will be explained for each operating mode.

In FIG. 1, in the stop mode, both the reel drive motor and the capstan motor are stopped, the brake 36 is pressed against the supply reel base 34 by the tension of the spring 39, and the brakes 63 and 72 are also pressed by the tension of the springs 66 and 68, respectively. It is crimped onto the take-up reel stand 46. Further, the lever 56 engages with the cam 26 to pressurize the lever 54, and the gear 4
7 is engaged in the state shown in FIG. 3(B). The camshaft 9 is moved to the left, so that the levers 75, 78 are also rotated clockwise, and the pinch roller 86 is separated from the capstan shaft 89.

In recording or playback mode, both the drive motor and the capstan motor are activated, the cams 25, 28 and 29 engage the slides 30, 60 and 70 respectively, the brake 36 is moved away from the supply reel base 34, and the brakes 63 and 72 are also activated. They are each separated from the take-up reel stand 46. The gear 47 is engaged in the state shown in FIG. 3(B), the gears 48 and 92 are in a slip state, and the lever 54 is no longer pressurized by the lever 56. Further, the cam shaft 9 is moved to the right by the engagement between the protrusion 14 of the cam of the gear 13 and the lever 17, and by the engagement between the lever 17 and the maximum displacement part of the cam 19.
Further, due to the contact between the maximum displacement part of the cam 20 and the lever 75 at the right end of the camshaft, the levers 75 and 78 are rotated counterclockwise, and the pinch roller 86 is pressed against the capstan shaft 89. There is.

When the reno <-58 is rotated clockwise in accordance with the rotational direction of the reel drive motor, the gear 49 meshes with the take-up reel stand 46, and the take-up reel stand 46 is driven.

In review mode (sometimes referred to as rewind playback or picture search), the lever 58 rotates counterclockwise because the rotational direction of the reel drive motor is reversed in contrast to the recording and playback modes. The gear 49 meshes with the supply reel stand 34, and the supply reel stand 34 is driven. Also, the lever 54 is pressurized by the lever 56 (Fig. 3■)
The contact friction force between the gears 92 and 48 in the slip mechanism is increased, and the supply reel stand 34 is driven with a larger rotational torque than the take-up reel stand 46 in the recording or playback mode. The states of each brake and pinch roller 86 are the same as in the recording and playback modes.

In fast forward or rewind mode, cams 25 and 28 engage slides 30 and 60, respectively, to apply brake 36.
and 63 are separated from the supply reel stand 34 and the take-up reel stand 46, respectively, and the cam 29 and the slide 70 are disengaged, so that the brake 72 is pressed against the take-up reel stand 46. The camshaft 9 is moved to the left, and the levers 75 and 78 are rotated clockwise, so the pinch roller 86 is separated from the capstan shaft 89. In addition, the gear 47 is engaged in the state shown in FIG. 30, and the slip mechanism does not operate, and the rotational torque of the reel drive motor is directly transmitted to the gear 48 via the gear 47, and the reel stand is driven with the largest rotational torque. Ru.

However, in the fast-forward mode and the rewind mode, the rotation direction of the reel drive motor is reversed, so the lever 58 also rotates in opposite directions, and in the fast-forward mode, the gear 49 meshes with the take-up reel stand 46. The take-up reel stand 46 is driven, and conversely, in the rewind mode, the gear 49 and the supply reel stand 34 mesh to drive the supply reel stand 34. still,
The lever 54 is pressurized by a lever 56.

In eject mode, in which the tape cassette is taken out from the tape holder, the cams 25 and 28 are moved to the slide 3, respectively.
0 and 60 to engage the brake 36 and the supply reel stand 34.
The crimping between the brake 63 and the take-up reel stand 46 is released, the cam 29 and the slide 70 are released from each other, and the brake 72 is now crimped onto the take-up reel stand 46. The camshaft 9 is moved to the left and the pinch roller 86
is apart from the capstan shaft 89. The engagement between the gear 47 and the gear 48 is as shown in FIG. 3G), and the lever 5
4 is pressurized by a lever 56.

Next, FIG. 6 shows a tape loading mechanism for winding a magnetic tape around a cylinder in this embodiment.

This is the M loading method, and (see Figure 1) shows the state before loading, and Figure (B) shows the state when loading is completed.

In FIG. 1A, the motor 1, gear 2.4 and worm 3 are already shown in FIG. The gear 13 is also shown in Fig. 1, but in Fig. 1 the parts related to the loading mechanism are omitted, and conversely in Fig. 6 the parts necessary for the operating mechanism in Fig. 1 are omitted. There is.

Gear 1 rotating around a shaft 120 fixed to the chassis
3 includes a shaft l 23 as a loading mechanism part,
A lever holding wall 122 is provided for fixing movement of the lever 121 in a predetermined operating mode. Lever 121
is rotatably supported at one end by a shaft 124 fixed to the chassis, and the other end rotatably supports one end of a link 126 by a pin 125. The lever 121 also
It has a shaft 127 on its lower surface (the surface on the gear 13 side) that can engage with the lever holding wall 122. The link 126 is provided with a shaft guide groove 128 that engages with the shaft 123 during loading, but does not engage with the shaft 123 after unloading and after the loading photon.
29, it is swingably supported by one end of the lever 130. The other end of the lever 130 is rotatably supported by a shaft 131 fixed to the chassis.

The lever 121, the link 126, and the lever 130 constitute a four-bar link.

One end of lever 130 is also connected to link 1 by pin 132.
One end of the link 133 is swingably supported, and the other end of the link 133 is swingably supported by a sector gear 135 by a pin 134. The sector gear 135 is rotatably supported by a shaft 136 fixed to the chassis. lever 130
, link 133 and fan-shaped gear 135 also constitute a four-bar link.

The fan-shaped gear 135 includes a gear 13 whose rotation center is a shaft 137.
8 are meshed with each other, and a gear 140 whose rotation center is a shaft 139 is further meshed with the gear 138. gears 138 and 1
40 have loading arms 141 and 142, respectively.
are rotatably supported coaxially, and each loading arm 141.142 is provided with a protrusion 143.144, and these protrusions 143.144 are connected to a spring 145.1.
By contacting the stoppers 147 and 148 with the tension of 46, the gear 138,
140 and respective loading arms 141.142
The relative angle is maintained. Each end of the loading arm 141, 142 has a link 14.
Via 9.150, a tape guide assembly 151.152 with a loading pole is rotatably provided. Reference numerals 153 and 154 indicate fixing fittings for fixing the tape guide assemblies 151 and 152, respectively, upon completion of loading, and guide grooves 155 and 156 guide the tape guide assemblies 151 and 152 to the fixing fittings 151 and 152, respectively. 157 is a head cylinder provided with a video head.

The operation of this loading mechanism will be explained.

6) shows a state in which loading is started by switching from stop mode to recording or playback mode, review mode, or the like. When loading is started, the gear 13 is rotated clockwise by the motor 1, and the engagement between the shaft 127 provided on the lever 121 and the lever holding wall 122 is released, so that the lever 121 can freely rotate. At the same time, the shaft 12 on the gear 13
3 engages with the guide groove 128 and begins to drive the link 126.

The displacement of the link 126 due to the clockwise rotation of the gear 13 is transferred from the link 133 to the fan-shaped gear 135 via the lever 130.
is transmitted to gear 138.14 by sector gear 135.
0 rotate clockwise and counterclockwise, respectively. gear 1
38.140 rotations are maintained at relative angles from loading arm 141.142, to link 149.1.
50 and tape guide assemblies 151, 152, and the tape guide assemblies 151, 152 are connected to fixing fittings 153, 15 along guide grooves 155, 156, respectively.
Move to 4.

When the tape guide assemblies 151 and 152 abut against the fixing fittings 153 and 154, respectively, the loading arm 1
41.142 stops, but the gear 13 continues to rotate, so the projection 143.1 stops as shown in FIG. 6(B).
44 and the stoppers 147 and 148 are released, and the spring 1 of the loading arm 141 and 142 is released.
45.146 are extended and tape guide assembly 151.
152 are respectively crimped and fixed to the fixing fittings with a prescribed force. This is the loading completion state.

When the gear 13 further rotates clockwise from this state, the shaft 123 on the gear 13 separates from the guide groove 128, and
A shaft 127 provided on the lever 121 is attached to the lever holding wall 12
2 to begin engaging the tape guide assembly 151
．． 152 is fixed in the loading complete state shown in FIG. 6(B).

To release the loading (unloading) from the state shown in Figure 6 □□□) and return to the state shown in Figure 6), shift gear 1.
3 should be rotated counterclockwise.

In the fast forward or rewind mode, or in the eject mode, the gear 13 rotates further counterclockwise than the state shown in FIG. When released, the lever 12
The shaft 127 provided at 1 begins to engage with the lever retaining wall 122, and the movement of the lever 121 is fixed, so that the tape guide assembly 151, 152 is fixed in the state shown in FIG.

In this loading mechanism, the tape guide assemblies 151 and 152 are connected to the fixing fittings 15 from the start of loading.
3. Tape guide assembly 1 until it touches 154
No large load is applied to 51.152, and therefore the driving force is small.

However, just before the loading is completed, the springs 145 and 1
A large amount of force is required to stretch the 46.

FIG. 7 shows the state of the vicinity of the four-bar link, including the link 126, just before the loading with the link 126 is completed. However, the lever holding wall is omitted. In this state, the shaft 123 on the gear 13 and the guide groove 128 come into contact at six points, exerting a frictional force on the link 126. This frictional force F1 is resolved at the pin 125 as shown in the figure, and the force F2 by which the link 126 presses the lever 130 is greater than Fl by this toggle mechanism.

The force F2 is further decomposed into a large force in the four-bar link including the link 133. In this way, even the motor 1 with a small capacity can stretch the springs 145, 146.

In this embodiment, as detailed in FIG. 3, the slip mechanism for transmitting rotational torque to the reel stand mainly uses the spring 95 when driving the take-up reel stand 46 in the recording or playback mode. Gears 48 and 92 are moved by the friction force created by the pressure of
Also, in review mode, touch the supply reel stand 34.
When driving the lever 5, the lever 5 is added to the pressing force of the spring 95.
gears 92 and 48 by increasing the pressing force by 4.
By increasing the frictional force between the two slip mechanisms, it is possible to transmit different rotational torques with one slip mechanism. Only one mechanism is required. This has the advantage of reducing the number of parts, lowering costs, and reducing the required space, contributing to the miniaturization of VTRs. However, the present invention also includes a device having a separate slip mechanism for driving each rig as in the prior art.

In addition, since this example has a double chassis structure, even if the thickness of each chassis is made thinner, the required strength of the entire chassis can be achieved, and in the end, compared to the conventional single chassis structure, the required strength can be achieved. This can contribute to making the entire structure thinner. However, the present invention also encompasses some conventional chassis structures.

Furthermore, in this embodiment, a four-bar link structure is adopted for the loading mechanism, and by reducing the loading driving force even when a large load is required just before the loading is completed, loading can be completed with a small-capacity motor. ing. However, the present invention also encompasses the use of other known loading mechanisms.

Furthermore, although the M loading method is illustrated as the loading mechanism in this embodiment, the operating mechanism of the present invention is
Needless to say, the present invention can also be applied to a loading type VTR.

Effects As detailed above, in the present invention, a camshaft is installed parallel to the chassis, and various mechanical parts are operated via a plurality of cams provided on this camshaft. Compared to the case where a solenoid is used or many gears are arranged in a plane, the structure is significantly simpler and the thickness of the mechanism part can be reduced.

Further, in a preferred embodiment of the present invention, the rotation of this camshaft causes displacement in the axial direction, and furthermore, the camshaft itself is made movable in the axial direction to operate the mechanism part in the axial direction as well. With this structure, the effect of simplifying the structure and reducing the thickness is further enhanced.

[Brief explanation of the drawing]

FIG. 1 is a plan view showing an embodiment of the present invention, FIG. 2 is an exploded perspective view showing essential parts of the embodiment, and FIG. 3 is a diagram showing a reel stand drive mechanism in the embodiment. (A) is a plan view,
Figures (B) and (C) are cross-sectional views for explaining the operation. FIG. 4 is a partially exploded perspective view showing a double chassis structure in one embodiment, FIG. 5 is a sectional view showing a capstan motor in one embodiment, and FIG. 6 is a plan view showing a loading mechanism in one embodiment. In the figure, (B) shows the state before loading starts, and (B) shows the state when loading is completed. 7th
This figure is a plan view of a main part explaining the operation of the loading mechanism shown in FIG. 6. 1...Motor, 9...Camshaft, 15.15'...
Chassis, 19.20.25-29...Cam provided on the camshaft, 30,60.70...Slide for brake operation, 34...Supply reel stand, 46...Take-up reel stand, 51.56...Reel stand drive mechanism operation t
e-175...Lever for pinch roller operation, 86...
・Pinch roller, 89...capstan shaft. Patent Applicant Ricoh Co., Ltd. - Agent Patent Attorney Aoshihaku Sogai 2 people No. 3 (B) JP-A-59-18G160 (10) Figure 4 v 111 Total 1゜3 烹 V 09 Toru, Y. Cao: ・→. 10i; 諌: 0: ,,, ゛・1j 108 Komarota Hoe 1- Figure 6 (A) Figure 6 (B) Figure 7 + 0

Claims (3)

[Claims] (1) A camshaft installed parallel to the chassis and rotating around the axis, a plurality of cams provided along the axial direction of the camshaft, and a cam that engages with each of the cams and controls a predetermined mechanical part. An operating mechanism for a videotape recorder, comprising: an actuating member that controls the operation; (2) further comprising: a cam provided on an end surface of the cam and displaced in the axial direction by rotation of the camshaft; and an actuation member that engages with the cam on the end surface of the camshaft to control the operation of a predetermined mechanical part. The operating mechanism according to claim 1. (3) the camshaft is movable in its axial direction;
The operating mechanism according to claim 2, which displaces the cam on the end surface of the camshaft as well as the actuating member that engages with the end cam.