JPS6355140B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a loading ring in a tape loading device applied to, for example, a video tape recorder, in which a loading ring constituted by a circular ring is rotatably supported by a plurality of guide rollers. The present invention relates to a supporting device.

As is well known, in a U-loading type tape loading device, a loading ring is rotated, and multiple tape guides attached to the top of the loading ring pull out the tape in the tape cassette and wrap it around the circumferential surface of a rotating head drum. Load the tape onto the running path, fix the loading state in that loading state,
The plurality of tape guides are configured to guide the running of the tape. Therefore, important requirements for the loading ring support device are that the loading ring rotates smoothly and that its positional accuracy is high so that the loading ring does not wobble.

However, as shown in FIG. 22, the conventional support device has a support shaft 20 whose lower end is fixed to a base 200.
A roller 202 with a pair of upper and lower flanges 202a molded in plastic on 1 is rotatably supported,
E-ring 203 for preventing slipping off at the upper end of the support shaft 201
and the pair of upper and lower flanges 2 of the roller 202.
Loading ring 2 is installed in the circumferential groove 204 between 02a.
It was configured so that the inner peripheral edge of 05 was inserted and guided. However, in such a conventional structure, the molding error of the roller 202 is large, and the upper surface of the loading ring 205 and the upper flange 20
2a, between the upper surface of the roller 202 and the lower surface of the E-ring 203, and between the outer peripheral surface of the spindle 201 and the inner peripheral surface of the roller 202, respectively.
07,208 has been completed. The total amount of gaps 206 and 207 occurs as thrust play of the loading ring 205, and the gap 206 and 207 generate
7, the roller 20 within the gap 208
2 generates center runout with respect to the support shaft 201, further expanding the above-mentioned thrust backlash.

Therefore, in such a conventional structure, the loading ring 205 has a large wobbling, and not only can it not be rotated smoothly, but also the above-mentioned wobbling causes changes in the height and inclination of the tape guide on the loading ring, making it difficult to stabilize the tape guide. There was a defect that made it difficult to run the tape.

The present invention seeks to provide a loading ring support device that can correct the above-mentioned defects.

An embodiment of a tape loading device for a video tape recorder to which the present invention is applied will be described below with reference to the drawings.

First, the tape loading device 31 uses a loading ring 32, which pulls out the tape 34 in the attached tape cassette 33 by rotation of the loading ring 32, and places it in a helical shape on the circumferential surface of the rotating head drum 35. This is a so-called U-loading type tape loading ring device.

Next, the loading operation of the tape 34 will be explained with reference to FIGS. 1 to 4.

First, the tape cassette 33 has a plurality of positioning pins 38 provided on a mechanical board 37 such as a chassis.
It is mounted horizontally on top and positioned. When the cassette is attached, the front cover 39 of the tape cassette 33 is opened, and the front opening 40 of the tape cassette 33 is opened. With this cassette installed, the tape 34 in the tape cassette 33 is passed as shown by the chain line in FIG. Also, by mounting this cassette, the supply reel 41 and take-up reel 42 in the tape cassette 33 are connected to the mechanical board 3.
A supply reel stand 43 and a take-up reel stand 44 arranged on the reel 7 are engaged with each other. Note that 4 in Figure 1
Reference numeral 5 designates a downward L-shaped tape pressing plate integrally formed on the upper half of the tape cassette 33.

On the other hand, the rotary head drum 35 is arranged at a substantially central position in front of the mounted tape cassette 33.
The loading ring 32 is a rotary head drum 35
It is located at an eccentric position around the outer periphery of the The rotating head drum 35 and loading ring 32 are mounted on a tilting table 48 provided on the mechanical board 37. As shown in FIG. 4, the center P ₁ of the rotating head drum 35 is at an angle θ ₁ of 5° in the direction of arrow a in FIG. 1 with respect to the vertical reference line P ₀ .
The center P ₂ of the loading ring 32 is also inclined at an angle θ ₂ of 10° in the direction of arrow a in FIG. 1 with respect to the vertical reference line P ₀ . Therefore, the rotary head drum 35 is inclined at 5 degrees with respect to the horizontal reference plane L of the tape cassette 33 mounted and positioned horizontally, and the loading ring 3
2 is tilted 10 degrees. The loading ring 32 is configured to be rotatable within its inclined surface.

Next, on the top of the loading ring 32 are four rotating guides 49a to 49 that constitute a tape guide.
d are each rotatably attached, and a pinch roller 50 is attached near the preceding rotation guide 49a. In addition to the rotation guide described above, a pull-out guide 51 is used as the tape guide, and a tension regulator 52 is also used. The four rotation guides 49a to 49d and the pinch roller 50 are rotatably supported around a rotation axis perpendicular to the loading ring 32, and these are supported relative to the horizontal reference plane L of the tape cassette 32. It is tilted at 10 degrees. Further, the pull-out guide 51 is a fixed guide that is fixed at the forward movement position where the loading operation is performed, and in the fixed state, the center P ₃ of the pull-out guide 51 is at the vertical reference line P ₀ as shown in FIG. In Figure 1, it is inclined at a predetermined angle θ ₃ in the direction of arrow b. Also, the ten key 52 is the tape cassette 33.
It is configured to operate while maintaining a state perpendicular to a horizontal reference plane L. In addition, mechanical board 37
On top is a capstan 53, which also serves as an audio head.
CTL head 54, audio erasing head 55, exit guide 56 for tape 34 to rotating head drum 35, same entrance guide 57, full width erasing head 5
8 etc. is installed. and Capstan 5
3. The CTL head 54, audio erasing head 55, and exit guide 56 are aligned parallel to the rotation guides 49a to 49d with respect to the horizontal reference plane L of the tape cassette 33.
The entrance guide 57 and the full-width erasing head 58 are arranged perpendicular to the horizontal reference plane L of the tape cassette 33.

When the unloading of the tape 34 is completed, the rotation guides 49a to 49d and the pinch roller 50 are moved back to the return position shown by the chain line in FIG. Similarly, the pull-out guide 51 and the balance gear 52 have also been moved back to the back-movement position shown by the chain line in FIG. In this backward motion state, the tape cassette 33 is first installed, and the preceding rotation guide 49a, pinch roller 50, pull-out guide 51, and ten-leg gear 52 are respectively attached to the tape 34 which has been passed as shown by the chain lines in FIG. inserted inside. Next, the switch detects that the cassette is installed, and the loading ring 32 is moved to the position indicated by the arrow c in FIG.
rotationally driven in the direction. As a result, the tape 34 is hooked on the preceding rotating guide 49a, and as the rotating guide 49a moves, the tape 34 is gradually drawn out of the tape cassette 33.
The drawn-out tape 34 is then gradually wound around the circumferential surface of the rotating head drum 35 from the counterclockwise direction in FIG. On the other hand, loading ring 32
In synchronization with the rotation in the direction of arrow c, the drawer guide 51
is moved in the direction of arrow d in FIG. When the preceding rotating guide 49a almost reaches the position shown by the dotted line in FIG. 1, the pull-out guide 51 reaches the forward movement position shown by the solid line in FIG. 1, and is thereafter fixed at that position. . Further, the balance gear 52 is moved in the direction of arrow e in FIG. 1 in conjunction with the forward movement of the pull-out guide 51, and once stopped at the operating position shown by the dotted line in FIG. Further, as mentioned above, the loading ring 32 is rotated in the direction of the arrow c in FIG. Rotating guide 4
9b, 49c, and 49d sequentially pass under the tape 34, enter inside the tape 34, and hook the tape 34. and rotation guide 49a
49d and the pinch roller 50 gradually ascend while sequentially catching the tape 34, and when they reach the position on the right side of the rotary head drum 35 in FIG. 1 (the left side in FIG. 4), they are raised to the highest position. Thereafter, as the loading ring 32 rotates in the direction of arrow c in FIG. 1, it is gradually lowered. Loading is completed when the loading ring 32 is rotated to a predetermined angle and the rotation guides 49a to 49d and the pinch roller 50 reach the forward movement position shown in solid lines in FIG. Immediately before this loading is completed, the balance gear 52 is further moved in the direction of arrow e from the operating position shown by the dotted line in FIG. 1 to the forward movement position shown by the solid line in FIG. Further, the completion of this loading is detected by the switch, the rotation of the loading ring 32 is stopped, and the loading ring 32 is locked at that position.

Then, upon completion of the above loading, the tape 34
is shown by a solid line in FIG. 1, and is wound around the circumferential surface of the rotating head drum 35 as shown in FIGS. ,
They are passed through an entrance guide 57 and a full-width erase head 58, respectively. At this time, since the angle difference between the rotating head drum 35 and the loading ring 32 is 5 degrees, the tape 34 is attached to the circumferential surface of the rotating head drum 35.
It is helically wound with a lead angle of 5° and a winding angle of 180° + α.

When the recording button or playback button is pressed in this loading completed state, the pinch roller 50 presses the tape 34 against the capstan 53, and the tape 34 is run at a constant speed in the direction of arrow f in FIG. Regeneration will take place.

At this time, the tape 34 is pulled out horizontally from the supply reel 41 of the tape cassette 33 as shown in FIG. Enter the periphery. The tape 34 is attached to the rotating head drum 3 as shown in FIGS. 3 and 4.
Proceed diagonally downward at an angle of 10° along the circumferential surface of 5,
It advances to the rotation guide 49a via the exit guide 56, the audio erasing head 55, the CTL head 54, and the capstan 53. Then, the tape 34 is turned by 180 degrees at this rotation guide 49a, and then diagonally upward at an angle of 10 degrees via the pinch roller 50 and rotation guides 49b, 49c, and 49d, as shown in FIGS. 4 and 3. It advances and reaches the drawer guide 51. Then, the tape 34 is returned to the same height as the horizontal pull-out height from the tape cassette 33 as shown in FIG. The direction is changed. Then, the tape 34 is horizontally fed into the take-up reel 44 of the tape cassette 33 and wound up.

However, in the running state of the tape 34,
The tape 34 is twisted only in the pull-out guide 51 portion which is a fixed guide, and the tape 34 is not twisted at all in other portions. That is, the tape 34 pulled out from the tape cassette 33 is transferred from the balance gear 52 to the rotary head drum 35, the capstan 53, the rotary guide 49a,
There is no twisting at all during the period from the rotation guide 49d to the pull-out guide 51.
It runs extremely smoothly.

Moreover, at this time, especially the loading ring 32
Since the upper guides are all rotating guides 49a to 49d, the tape 34 is attached to these rotating guides 49a to 49d.
The running resistance (frictional resistance) that occurs when running in contact with ~49d is extremely small. Therefore, the tape 34 runs extremely smoothly.

Furthermore, the tape 34 is connected to the loading ring 32.
All rotating guides 49a mounted vertically above
Since the tape 34 is guided in contact with each of the rotation guides 49a to 49d at right angles, the rotation of the rotation guides 49a to 49d causes the tape 34 to be unexpectedly moved in the direction of the rotation axis of each of the rotation guides 49a to 49d, thereby preventing vibrations, etc. This does not occur at all, and the tape 34 runs extremely stably.

Note that when the eject button is pressed after recording or playback, the loading ring 32 is rotated in the direction of arrow c' in FIG.
is unloaded.

Next, details of each part of the tape loading device 31 will be explained.

First, FIG. 5 shows the entire tape loading device 31, which includes a reciprocating drive device 61 for the pull-out guide 51, and a ten-leg device (abbreviation for tension regulator device) 6 having a ten-leg gear 52.
2. A pinch roller pressing device 63 for pressing the pinch roller 50 onto the capstan 53 and the like are mounted on the mechanical board 37 around the loading ring 32.

Next, the reciprocating drive device 62 will be explained with reference to FIGS. 6A to 12.

First, as shown in FIGS. 6A and 7, a motor 66 for driving the loading ring is mounted on the mechanical board 37.
is attached, its motor shaft 67 protrudes below the mechanical board 37, and is supported by a pulley 68 fixed to the lower end of the motor shaft 67 and through the mechanical board 37 vertically. intermediate shaft 69
A pulley 70 fixed to the lower end of the belt 71 is interlocked with the pulley 70 . Further, as shown in FIGS. 6A and 8, a ring drive gear 73 is located near the outer side of the loading ring 32 on the mechanical board 37.
is pivotally supported via a support shaft 74. A gear 75 fixed to the upper end of the intermediate shaft 69 and a ring drive gear 73 are attached to the support shaft 7 fixed to the mechanical board 37.
They are interlocked via two-stage gears 79-81 which are pivotally supported by gears 6-78, respectively. A ring gear 82 is provided on the outer periphery of the loading ring 32, and the ring drive gear 73 is meshed with the ring gear 82.

Therefore, the loading ring 3 is rotated through the above-mentioned gear mechanism by driving the motor 66 in forward or reverse rotation.
2 is configured to be rotated forward in the direction of arrow c or reversely rotated in the direction of arrow c' in FIG.

Next, as shown in FIGS. 6A and 7A, a cam 83 is attached to one side of the support shaft 77 on the mechanical board 37 at the upper end.
A cam gear 84 integrally formed is supported via a support shaft 85. And this cam gear 84
is meshed with the small gear of the two-stage gear 80.

On the other hand, as shown in FIG. 10 to FIG.
It is attached to 8. At this time, the reciprocating lever 88
As shown in FIG. 7, the side surface is almost U-shaped, and its lower end 88a wraps around below the mechanical board 37, and is a fulcrum that is fixed close to the support shaft 85 at the lower part of the mechanical board 37. It is rotatably supported on a shaft 89. Note that the upper end 88 of the reciprocating lever 88
A lever support portion 90 is integrally formed at the tip of b. The support lever 87 has a substantially inverted T-shaped side surface, and the pull-out guide 51 is fixed vertically onto one end of the horizontal portion 87a. A fulcrum shaft 91 perpendicular to the pull-out guide 51 is horizontally fixed to the vertical portion 87b of the support lever 87, and the fulcrum shaft 91 is attached to the reciprocating lever 88.
It passes through a horizontal shaft support hole 92 provided at the upper end of the lever support part 90 and is rotatably supported. Note that the reciprocating lever 88 is rotated by a torsion spring 93 fitted to the outer circumferential portion of the fulcrum shaft 89.
The support lever 87 is urged to rotate in the direction of arrow g in the figure, and the support lever 87 is urged to rotate in the direction of arrow h in FIG. However, as shown in FIG. 11, the support lever 87 has a protrusion 95 integrally provided at its other end brought into contact with one side of the lever support portion 90, so that rotation in the direction of arrow h is restricted. And in that regulatory state, the first
As shown by the solid line in FIG. 1, the pull-out guide 51 is in a vertical state.

By the way, the cam 83 integrally formed on the upper end of the cam gear 84 has a substantially spiral shape, and the sixth cam 83 has a spiral shape.
A pin 96 integrally formed at the lower part of the upper end portion 88b of the reciprocating lever 88, which is rotationally biased in the direction of arrow g in FIG. A, is pressed against the cam 83.

Also, as shown in Figures 6A, 9, and 12,
An interlocking lever 98 is rotatably supported on the mechanical board 37 near the cam gear 84 via a fulcrum shaft 99. This interlocking lever 98 is urged to rotate in the direction of arrow i in FIG. 6A by the urging force of a spring on the balance gear device 62 side, which will be described later, and comes into contact with one end of the upper and lower intermediate portions 88c of the reciprocating lever 88. has been done. A pin 100 is fixed on one end of the interlocking lever 98, and a protrusion 101 that presses the pin 100 is integrally formed in a part of the lower end of the cam gear 84.

As shown in FIGS. 6A and 7, a guide regulating plate 10 is provided for tilting the drawer guide 51 at the forward movement position shown by the solid line in FIG. 1 to make it a fixed guide.
3 is fixedly installed on the upper part of the mechanical board 37.

Next, the reciprocating motion of the pull-out guide 51 in synchronization with the forward or reverse rotation of the loading ring 32 will be described.

First, when the unloading is completed, the pull-out guide 51 and the reciprocating lever 88 are moved back to the return position shown in FIG. 6A. In this state, motor 6
6 is rotated in the forward direction, the loading ring 32 is driven by the ring drive gear 73, and the loading ring 32 is rotated in the direction of arrow c in FIG. 6A to perform the above-described loading. On the other hand, at this time, the cam gear 84 is rotated by the two-stage gear 80 in the direction of arrow j in FIG. 6A. Then cam 8
3 pushes the pin 96 and the reciprocating lever 88
is rotated in the direction of arrow g' in FIG. 6A against the torsion spring 93, and the pull-out guide 51 is moved in the same direction.

As the loading ring 32 rotates in the direction of the arrow c, the rotation guide 49a is moved from the return position shown by the chain line in FIG. 1 to the position shown by the dotted line as described above. The drawer guide 51 and the reciprocating lever 88 are moved to the reciprocating position shown in FIG. 6B. At this point, pin 96 is connected to cam 8.
After this, the cam gear 84 continues to rotate in the direction of arrow J, but the reciprocating lever 88 remains fixed at the forward movement position.

When the reciprocating lever 88 reaches the forward movement position shown in FIG. 6B, the upper end of the pull-out guide 51 comes into contact with the guide regulating plate 103, as shown by the chain line in FIG. As a result, the support lever 87 is rotated in the direction of arrow h' in FIG. 11 against the torsion spring 94, and at the same time, the pull-out guide 51 is tilted as shown by the chain line in FIG. After this, the drawer guide 51 is fixed in the inclined state, and becomes a so-called inclined guide. At this time, the drawer guide 51 is attached to the tape 34.
It is rotated in the direction of arrow h' about the approximately center position.

In summary, the pull-out guide 51 is moved from the backward movement position shown in FIG. 6A to the vertical state, acts perpendicularly to the tape 34 in the direction of arrow g', and is moved to the forward movement position shown in FIG. 6B as indicated by the chain line in FIG. It becomes a fixed inclined guide.

On the other hand, when the reciprocating lever 88 is rotated in the direction of arrow g' in FIG. 6A, its intermediate portion 88c rotates the interlocking lever 98 in the direction of arrow i' in FIG. 6A. Immediately before the loading is completed, the protrusion 101 of the cam gear 84 comes into contact with the pin 100 of the interlocking lever 98 and pushes it, as shown in FIG. 6B.
is rotated by the reciprocating lever 88 and further rotated in the direction of arrow i' from the position indicated by the chain line in FIG.
It is rotated to the forward movement position shown by the solid line in Figure B.

Note that when the motor 66 is driven to rotate in the reverse direction, the loading ring 32 is rotated in the direction of arrow c' in FIG. 6B, and the aforementioned unloading is performed. Then, by the aforementioned reverse operation, the pull-out guide 51, the reciprocating lever 88, and the interlocking lever 98 are each moved back to the return position shown in FIG. 6A.

Next, the balance gear device 62 will be explained with reference to FIGS. 13A to 15.

First, as shown in FIGS. 14 and 15, the balance gear 52 is composed of a rotating roller, and is rotatably mounted on a support shaft 108 fixed on the tip of a tension gear arm (abbreviation for tension regulator arm) 107. It is pivotally supported. On one side of the loading ring 32, on the mechanical board 37, a balance gear mounting plate 109 having a substantially U-shape is fixed. 111 is rotatably supported. And Tenregiam 107
is rotatably supported on the upper end of the fulcrum shaft 111 by the other end. A lever support tube 112 is inserted into the fulcrum shaft 111 and fixed with a set screw 113, and a balance gear drive lever 114 and a brake drive lever 115 are stacked vertically in the lever support tube 112 at the bottom of the balance gear arm 107. and are each rotatably supported. Then, a pin 116 integrally molded with the brake drive lever 115 and extending upwardly is inserted through one side of the balance gear drive lever 114 and is inserted into the balance gear arm 10.
It extends to a height of 7. A part of the balance gear arm 107 and the balance gear drive lever 114
claws 117 and 11 provided integrally with a part of the
8 are arranged opposite to each other on both sides of the pin 116 as shown in FIG. 13A.

By the way, a spring receiver 120 is integrally formed on a part of the balance gear arm 107, and a spring receiver 121 is integrally formed on a part of the brake drive lever 115.
A balance lever return spring 12 consisting of a tension spring between
2 is stretched. Also, ten gear drive lever 1
a spring receiver 123 integrally provided in a part of 14;
It consists of a tension spring between a spring receiver 124 integrally formed in a part of the brake drive lever 115,
A tension spring (abbreviation for tension regulator spring) 125 made of a spring stronger than the tension return spring 122 is also stretched. Therefore, both springs 122 and 125 rotate the balance gear arm 107 in the direction of the arrow k in FIG. 13A, and the balance gear drive lever 114 is urged to rotate in the direction of the arrow k' in FIG. 13A. Both claws 1
Brake drive lever 115 by 17,118
pins 116 are clamped from both sides. In this state, the above three levers 107, 11
4 and 115 are in a state where they can rotate together around the fulcrum shaft 111. Note that the lever support tube 112
is fitted around the outer periphery of the lower end of the pin 116 at both ends.
The three levers 1 are connected by a torsion spring 126 that is in contact with the lower end of the
07, 114, and 115 are integrally rotated in the direction of arrow k in FIG. 13A.

As shown in FIG. 5, the interlock lever 98 of the reciprocating drive device 61 and the balance gear drive lever 114 of the balance gear device 62 are interlocked with each other by an interlock rod 128. At this time, as shown in FIGS. 6A and 13A, respectively, U-shaped portions 128a and 128b are bent at both ends of the interlocking rod 128,
These are the interlocking lever 98 and the balance gear drive lever 1.
14, respectively, are engaged with pins 129 and 130, with some play. Further, as shown in FIG. 13A, one end of the band brake 131 is pivotally supported by the mechanical board 37 and is wound approximately 180 degrees around the circumferential surface of the supply reel stand 43. The other end of the band brake 131 is connected to the brake drive lever 1.
It is pivotally supported by a pin 132 integrally formed in a part of 15.

Next, the reciprocating operation of the balance gear 52 in conjunction with the reciprocating movement of the pull-out guide 51 will be described.

First of all, when unloading is completed, Tenregi 5
2 and the tensile gear arm 107 have been moved back to the back movement position shown in FIG. 13A. In this state, loading is performed as described above, and the cam gear 84
When the reciprocating lever 88 is rotated in the direction of arrow g' in FIG. 6A and the interlocking lever 98 is rotated in the direction of arrow i' in FIG.
It is pulled in the direction of the arrow 1 in Figures 1 and 13A. Then, the ten-leg gear drive lever 114, the brake drive lever 115, and the ten-leg gear arm 107 work together against the torsion spring 126 as shown by the arrow in FIG. 13A.
It is rotated in the k' direction, and the balance gear 52 and the balance gear arm 107 are moved to the operating position shown by the chain line in FIG. 13B. Then, as described above, when the interlocking lever 98 is rotated in the direction of arrow i' in FIG. 6B by the protrusion 101 of the cam gear 84 just before the loading is completed, the balance gear 52 and the balance gear arm 107 move forward as shown by the solid line in FIG. 6B. moved to position. At this time, the rotation of the balance gear drive lever 114 in the direction of arrow k' causes the brake drive lever 115 to rotate in the direction of arrow k' via the balance gear spring 125, and the pin 133 integrally formed on the brake drive lever 115 is rotated. Tenlegiam 107
, and move this ten-leg gear arm 107 to
Rotate in the k′ direction. And Tenregibane 125
The band brake 131 is pulled by the spring force and pressed against the circumferential surface of the supply reel stand 43.

By the way, during recording or reproduction, since tension is applied to the tape 34, the tension gear 52 and the tension gear arm 107 are moved by the tape tension against the tension spring 125 to the operating position shown by the chain line in FIG. 13B. At this time, the balance gear arm 107 rotates the brake drive lever 115 in the direction of arrow k in FIG. 13B via the pin 133, and the balance gear spring 125 is pulled. Along with this, the band brake 131 is loosened. Then, as the tape tension changes during recording or playback, the balance gear 52 and the balance gear arm 1
07 is moved in the direction of arrow k or k' in FIG. 13B, the braking force of the supply reel stand 43 by the band brake 131 is automatically adjusted, and the tape 34
The tension will be adjusted to a constant tension state.

When unloading is performed as described above and the reciprocating lever 88 is moved back to the return position shown in FIG. 6A, the balance gear 52 and the balance gear arm 107 are moved by the torsion spring 126 to the position shown in FIG. 13A in the reverse operation described above. It is moved back to the return position.

Next, the pinch roller crimping device 63 will be explained with reference to FIGS. 16A to 20.

First, as shown in FIGS. 16A and 17, the pinch roller 51 is rotatably mounted on a pinch roller lever 137 that is rotatably supported on the loading ring 32 via a fulcrum shaft 136. It is pivotally supported. The lower end of the support shaft 138 is fixed vertically by press-fitting into the pinch roller lever 137, and the pinch roller 50 is rotatably pivoted at the top and bottom of the support shaft 138 by a bearing 139 fitted approximately in the center. supported. A semicircular receiving plate 140 is fixed to the upper end of the support shaft 138 by press fitting. The pinch roller lever 137 is urged to rotate in the direction of arrow n in FIG. 16A by a torsion spring 141 fitted to the fulcrum shaft 136, and is regulated by coming into contact with a pin 142 fixed on the loading ring 32. has been done. In addition, the capstan 53 is connected to the notch 1 provided in the inclined table 48.
A pair of upper and lower oil-less metals 1 are inserted into the bearing block 146 and fixed to the inclined table 48 and the auxiliary board 145 disposed at the bottom thereof.
It is rotatably supported via 47. At this time, the lowest tilted position (the left end in FIG. 1) of the loading ring 32 tilted as described above is inserted into the notch 144 as shown in FIG. Helps reduce height.

Next, as shown in FIG. 19, the pinch roller crimping device 63 includes a plunger solenoid (hereinafter simply referred to as a plunger) 149, a pinch roller crimping lever 150, a suction operating lever 151,
These common fulcrum shafts 152, a pinch roller pressure spring 153 made of a tension spring, and a return spring 15
It is made up of 4 etc. Then, as shown in FIGS. 16A and 17, the plunger 149 is mounted on the mechanical board 37 via the mounting plate 156 at a position very close to the pinch roller 50 which has been moved to the reciprocating position shown in FIG. 16A in the loading completed state. It is being A fulcrum shaft 152 is vertically supported with its upper and lower ends supported between a support plate 157 fixed to the upper part of the plunger 149 and a mounting plate 156.

On the other hand, the pinch roller crimping lever 150 has a substantially U-shaped side surface, and has a pair of upper and lower arm portions 15.
It is rotatably supported at both upper and lower ends of the fulcrum shaft 152 by a pair of through holes 158 provided in 0a and 150b. The suction operating lever 151 also has a substantially U-shaped side surface. This suction operating lever 151 is a pinch roller pressure lever 150.
is inserted inside the pair of upper and lower arm portions 151a,
It is rotatably supported on both upper and lower ends of the fulcrum shaft 152 by a pair of through holes 159 provided in the fulcrum shaft 151b. In the above-mentioned installed state, the tips of the upper and lower arm portions 150a, 150b of the pinch roller pressure bonding lever 150 are opposed to one side of the pinch roller lever 137 of the pinch roller 50 and the receiving plate 140, as shown in FIG. . A spring receiver 160 is provided integrally with a connecting portion 150c that vertically connects the upper and lower arm portions 150a and 150b of the pinch roller crimping lever 150, and a spring receiver 160 is provided integrally with a portion of the upper arm portion 151a of the suction operating lever 151. A pinch roller pressure spring 153 is stretched between the pinch roller and the spring receiver 161. At this time, Figures 16A and 18
As shown in the figure, a stopper piece 16 is provided integrally with a connecting portion 151c that vertically connects the upper and lower arm portions 151a and 151b of the suction operating lever 151.
2 is in contact with the spring receiver 160 portion which is the point of action X of the pinch roller pressure bonding lever 150, and these levers 150 and 151 are configured to come into contact with each other. Note that an arm portion 163 extending from a part of the upper arm portion 151a of the suction operation lever 151
is engaged with the lower side of an annular groove 165 provided at the distal end portion of the suction rod 164 of the plunger 149 in a state that crosses the annular groove 165. A return spring 154 is stretched between a spring receiver 166 provided at the tip of the arm portion 163 and a spring receiver 167 provided integrally with a part of the mounting plate 156.

Next, the pinch roller crimping operation will be explained.

First, when the plunger 149 is not energized, the suction operating lever 151 is urged to rotate in the direction of the arrow o by the return spring 154, as shown in FIG. 16A. Further, the suction operating lever 151 and the pinch roller pressure spring 150, which are mutually stretched by the pinch roller pressure spring 153, are brought into contact with each other by a stopper piece 162 and a spring receiver 160.

Next, loading is performed as described above, and when the loading is completed, the pinch roller 50 is moved to one side of the pinch roller pressure lever 150 and stopped at that position, as shown in FIG. 16A. Then, when the record button or playback button is pressed thereafter, the plunger 149 is energized and the suction rod 164 is attracted in the direction of arrow p as shown in FIG. 16B.
Then, the suction operating lever 151 is rotated in the direction of arrow o' in FIG. 16B against the return spring 154, and the pinch roller pressure lever 150 is rotated in the same direction via the pinch roller pressure spring 153. The upper and lower arms 15 of the pinch roller crimping lever 150
The tips of 0a and 150b are pinch roller levers 13
7 and the side surface of the receiving plate 140 and push them simultaneously in the direction of arrow q in FIG. 16B. As a result, the pinch roller lever 137 is rotated in the direction of arrow n' in FIG. do.

Note that when the plunger 149 becomes de-energized again, the return spring 154 causes the suction operating lever 1 to
51 and the pinch roller pressure lever 150 are the 16th
It is moved back to the return position shown in Figure A. Then, the pinch roller lever 137 is moved to the 16th position by the torsion spring 141.
The pinch roller 50 is moved back to the return position shown in FIG. A, and the pinch roller 50 is separated from the capstan 53.

However, according to the pinch roller crimping device 63, in the non-operating state, the pinch roller crimping lever 150 and the suction operating lever 151, which are mutually tensioned by the pinch roller crimping spring 153, At the point of action X, the spring receiver 160 and the stopper piece 162 abut each other. Therefore, the mutual tensile force caused by the pinch roller pressure spring 153 is canceled at the contact point between the spring receiver 160 and the stopper piece 162, and the pinch roller pressure bonding lever 15 due to the mutual tensile force caused by the pinch roller pressure spring 153 is canceled.
0 and the suction operating lever 151 will not act on the fulcrum shaft 152 at all.

That is, as shown in FIG. 20, for example, the stopper piece 162 is located at the point of action
If the structure is such that the connecting portion 150c of the pinch roller crimping lever 150 is brought into contact with the pinch roller crimping lever 150 at a position that is more biased towards the fulcrum shaft 152, the pinch roller crimping lever 150 is pulled by the tensile force in the directions of arrows r and r' by the pinch roller crimping spring 153. The pinch roller pressure bonding lever 150 and the suction operating lever 151 are twisted by the lever action using the stopper piece 162 as a fulcrum, and the arrows s and
When rotated in the s' direction, the fulcrum shaft 152 is strongly pulled in opposite directions (directions of arrows s and s').
As a result, the pinch roller pressure lever 150 and the suction operating lever 151 rub strongly against the fulcrum shaft 152, making it impossible for them to rotate smoothly, and the plunger 149 that drives them to rotate also overcomes the frictional force. A device with a large capacity (large size) is required. Therefore, in the structure described above, a sleeve 169 is rotatably inserted around the outer periphery of the fulcrum shaft 152 as shown in FIG.
50 and the suction operating lever 151 so as to be rotatably supported so that the above-mentioned twisting force does not act on the fulcrum shaft 152. Therefore, when the sleeve 169 is inserted around the outer periphery of the fulcrum shaft 152,
The diameter of the fulcrum shaft 152 portion is substantially enlarged, and the fulcrum shaft 152 must be separated from the center of the pinch roller 50 by a gap corresponding to the enlarged diameter.

However, according to this pinch roller crimping device 63, the above-mentioned twisting force does not act on the fulcrum shaft 152 at all, and the pinch roller crimping lever 15
0 and the suction operating lever 151 rotate extremely smoothly around the fulcrum shaft 152, so there is no need to insert the sleeve 169 around the outer periphery of the fulcrum shaft 152 as in the structure shown in FIG. 152
The diameter of the pinch roller 50 can be made very small, and the fulcrum shaft 152 can be moved closer to the center of the pinch roller 50 as the diameter becomes smaller.

Therefore, according to this pinch roller crimping device 63, as shown in FIG. 16A, the diameter of the fulcrum shaft 152 is very small, and the fulcrum shaft 152 is arranged extremely close to the center of the pinch roller 50.
As a result, the plunger 149 and the fulcrum shaft 15
Even if the plunger 149 is placed very close to the fulcrum shaft 152 by making the distance l ₁ between the fulcrum shaft 152 very small, the point of action between the suction rod 164 and the suction operating lever 151 and the fulcrum shaft The arm length l ₂ of the rotational moment between the center of We were able to make the ratio of moment to arm length l ₃ sufficiently large.

As a result of the above, according to this pinch roller crimping device 63, the ratio of the arm lengths l ₂ and l ₃ of the rotational moment can be made sufficiently large, so that the plunger 14
Using a very small capacity (small) one as 9,
The pinch roller 50 can be reliably pressed against the capstan 53 with a predetermined pressing force, and the small-capacity plunger 149 can be placed very close to the fulcrum shaft 152, thereby significantly reducing the width of the entire tape loading device 31. It can be made small and the device can be made smaller. In addition, the fulcrum shaft 15 with a small diameter
2 has a mounting plate 156 and a support plate 157 at its upper and lower ends.
Since both ends are supported by , the supporting state is extremely stable.

By the way, as shown in FIG. 2, the rotation guide 49a
-49d are all composed of rotating rollers 171.

That is, a support shaft 173 is press-fitted with its lower end into a mounting boss 172 fixed on the loading ring 32 and fixed vertically. A rotary roller 171 is rotatably inserted into the support shaft 173. Note that a lower flange 174 is integrally formed at the lower end of the rotating roller 171, and an upper flange 175 is press-fitted into a recess 176 provided at the upper end of the rotating roller 171. A washer 177 is interposed between the rotating roller 171 and the attachment boss 172, and a retainer 178 is attached to the upper end of the support shaft 73 by press fitting, screwing, or the like.

Also, as shown in Fig. 5, loading ring 3
2 is rotatably mounted on the inclined table 48 while being supported by three guides 180a to 180c mounted in a circular arrangement at approximately equal intervals.
These guides 180a to 180c allow the loading ring 32 to rotate extremely smoothly with almost no wobbling. Of the three guides 180a to 180c, two guides 180a and 180b are directly attached to the inclined table 48, and one guide 180c is attached to the inclined table 48 via the radial movement adjustment plate 181 of the loading ring 32. installed. Even though there is a difference in whether they are attached to the movement adjustment plate 181 or directly to the tilt table 48, the structures of these guides 180a to 180c are substantially the same.

That is, as shown in FIG. 21, in the guide 180a, 182 is a round shaft machined with high precision using a lathe, and the lower end 182a is press-fitted into and fixed to the inclined table 48, which is a base, and the lower end 182a A circular flange 182b is integrally provided on the upper part of the flange 182b, a roller holding part 182c is provided on the upper part of the flange 182b, and the diameter of the upper end 182d is configured to be smaller than the diameter of the roller holding part 182c. On the other hand, the loading ring 32 is made of sheet metal, and the height t ₁ of the roller holding portion 182c is several microns larger than the thickness t ₂ of the loading ring 32 . A plastic roller 183 with a height equal to the thickness t ₂ of the loading ring 32 is rotatably inserted into the outer periphery of the roller holding portion 182c, and the diameter of the plastic roller 183 is smaller than the diameter of the flange 182b. There is. A circular presser plate 184 having approximately the same diameter as the flange 182d is attached to the upper end 182d.
is press-fitted, and this presser plate 184 is press-fitted and fixed up to a stepped portion 185 formed by the difference in diameter between the roller holding portion 182c and the upper end 182d.

Loading ring 32 configured as above
According to the support device of plastic crawler 183
A fixed flange 182b is arranged above and below the fixed flange 182b.
Since the plastic crawler 183 is sandwiched from above and below between the upper surface of the loading ring 32 and the presser plate 184, there is no vertical play, that is, thrust play, and the upper surface of the loading ring 32 and the presser plate 18 are slightly
There is only a gap of several microns between the two. That is, the thrust backlash of the roller due to the gap 207 in the conventional example shown in FIG. 22, and the expansion of the thrust backlash due to the gap 208, etc. do not occur at all.

Therefore, the thrust backlash of the loading ring 32 is extremely small compared to the conventional example shown in FIG. 22, and it is extremely unlikely that the height or inclination of the rotating guides 49a to 49d, which are tape guides on the loading ring 32, will change. With a small amount, stable tape running can be guaranteed.

Although the flange 182b and the holding plate 184 are both fixed, since the plastic roller 183 is disposed inside, the loading ring 32
The rotation is extremely smooth. That is, the second
In the case of the roller 202 with the flange 202a shown in FIG. Only the peripheral speeds are the same, and the rotational peripheral speed of both the upper and lower flanges 202a is greater than the rotational peripheral speed of the loading ring 205.
The upper and lower flanges 202a rotate while slipping against the loading ring 205.

Therefore, even if the flange 182b and the holding plate 184 are fixed, the loading ring 32 simply slips against them, and this is exactly the same as the conventional example shown in FIG. The rotation allows the loading ring 32 to rotate extremely smoothly.

In this tape loading device 31, as shown in FIG. 5, a plastic tape receiving guide 192 is fixed to a position further forward of the leading rotating guide 49a on the loading ring 32. If the tape 34 becomes loose and accidentally falls from the rotation guide 49a onto the loading ring 32 during loading and unloading, the tape 34
4 is received on the tape receiving guide 192 to prevent the tape 34 from coming into contact with the ring gear 82 and being significantly damaged.

Further, as shown in FIG. 5, a pinch roller guide 193 is attached along a part of the outer periphery of the loading ring 32 at a position immediately before the tape cassette 33 mounted on the mechanical board 37. During loading and unloading of the tape 34 described above, when the pinch roller 50 moves in and out of the front opening 40 of the tape cassette 33, the first
As shown in Fig. 6A, the pinch roller lever 137, which is urged to rotate outside the loading ring 32 (in the direction of arrow n) by the torsion spring 141, comes into contact with the pinch roller guide 193, and the torsion spring 1
41 and is pushed slightly inside the loading ring 32 (in the direction of arrow n'). This prevents the pinch roller 50 portion from coming into contact with the opening edge 194 portion of the roller cassette 33, and also allows the tape cassette 33 to be mounted very close to the loading ring 32. ing.

As described above, the present invention relates to a loading ring support device in which a loading ring constituted by a circular ring is rotatably supported by a plurality of guide rollers. A flange is integrally provided near the lower end, and a roller holding part is provided on the upper part of the flange of the round shaft, and the upper end of the round shaft is configured to have a smaller diameter than the roller holding part, and has a smaller diameter than the flange and the roller holding part. A roller having a thickness substantially equal to the height of the holding portion is rotatably fitted to the outer periphery of the holding portion, and a presser plate having a diameter substantially equal to the flange is fitted and fixed to the upper end of the round shaft. , the loading ring is configured such that the loading ring is fitted between the flange and the presser plate on the outer periphery of the roller, and the loading ring is sandwiched between the flange and the presser plate. It is a support device.

Therefore, according to the present invention, by eliminating the thrust play of the roller itself, the thrust play of the loading ring can be made much smaller than in the past, and the loading ring can be made extremely smooth. Although it can guarantee rotation, the positioning accuracy of the loading ring is extremely high, and there is almost no change in height or tilt of the tape guide on the loading ring, ensuring extremely stable tape running. You can.

[Brief explanation of the drawing]

The drawings show an embodiment of a tape loading device for a video tape recorder to which the present invention is applied, in which FIG. 1 is an overall plan view showing a tape loading state, and FIG. Fig. 3 is a view taken along the line 3-3 of Fig. 1, Fig. 4 is a view taken taken the line 4-4 of Fig. 1, and Fig. 5 shows details of the tape loading device. Overall plan view, No. 6A
7 and 6B are plan views showing the operating state of the reciprocating drive unit of the drawer guide, FIG. 7 is a developed sectional view showing the transmission system between the motor and the reciprocating lever, and FIG. The figure is an exploded sectional view showing the transmission system between the motor and the ring drive gear, Figure 9 is an exploded sectional view showing the transmission system between the cam gear and the interlocking lever, and Figure 10 is the reciprocating A partially cutaway side view showing the attachment part of the pull-out guide to the movable lever, Fig. 11 is a view taken along the line 11-11 in Fig. 10, and Fig. 12 is an exploded view showing the reciprocating lever, cam gear, and interlocking lever part. A perspective view, and FIGS. 13A and 13B are plan views showing the operating state of the balance gear device, FIG. 14 is a partially cutaway side view showing the pivot portion of the balance gear arm, and FIG. 15 is an exploded view of the balance gear device. A perspective view, FIGS. 16A and 16B are plan views showing the operating state of the pinch roller crimping device portion, and FIG. 17 is a developed sectional view of the pinch roller crimping operating portion between the suction rod of the plunger solenoid and the capstan. , FIG. 18 is 18 in FIG. 16A.
-18 line arrow view, Figure 19 is an exploded perspective view of the pinch roller crimping device, Figure 20 is a plan view showing a reference example of the pinch roller crimping device, and Figure 21 is the rotation guide and loading ring guide. It is an enlarged sectional view showing this. FIG. 22 is a sectional view showing a conventional example. Also, in the symbols used in the drawings, 31
...Tape loading device, 32...Loading ring, 180a, 180b, 180c...
Guide, 182...Round shaft, 182a...Lower end of round shaft, 182b...Flange of round shaft, 182c...
Round shaft roller holding part, 182d...Top end of round shaft,
183... Plastic crawler, 184... Holding plate, 185... Step portion.

Claims (1)

[Claims] 1. A loading ring support device in which a loading ring composed of a circular ring is rotatably supported by a plurality of guide rollers,
A flange is integrally provided near the lower end of a round shaft whose lower end is fixed to the base, a roller holding section is provided above the flange of the round shaft, and the upper end of the round shaft is configured to have a smaller diameter than the roller holding section. A roller having a diameter smaller than that of the flange and having a thickness substantially equal to the height of the roller holding portion is rotatably fitted around the outer periphery of the holding portion, and a presser plate having a diameter substantially equal to that of the flange is fitted to the outer periphery of the holding portion. The loading ring is fitted onto the upper end of the round shaft and fixed, and the loading ring is fitted between the flange and the holding plate on the outer periphery of the roller, so that the loading ring is sandwiched between the flange and the holding plate. A loading ring support device comprising: