JPH097253A - Tape driving device - Google Patents

Abstract

PURPOSE: To provide a tape driving device using an epicyclic gear device high in reliable and capable of realizing a stable tape running by reducing the loss in a tension control part and also to realize the bi-directional tension control with the simple structure. CONSTITUTION: A sub-retainer is provided so that the epicyclic gear is supported at both ends, and simultaneously independent bearing parts are constituted respectively for an inner gear and a retainer gear 25. The brake force is given to a drum gear independent from the epicycle gear device, and tension arms at the supply side and take-up side are detected by one and only detecting means so as to change over both of them by utilizing the tape tension. Further, both ends of an inner tooth rack 40 engaged with an idler gear 36 are made to high teeth, then the mode is exactly transferred.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a tape drive device such as a video tape recorder (hereinafter abbreviated as VTR).

[0002]

2. Description of the Related Art In recent years, a recording / reproducing apparatus typified by a VTR is required to be compact and lightweight, and at the same time, to reduce the cost in accordance with the decrease in the product price. Conventionally, in a recording / reproducing apparatus such as a cassette type video tape recorder, it has been common to use a method of pressing a tape against a capstan with a pinch roller as a tape driving means.

An example of a tape drive mechanism of a conventional recording / reproducing apparatus will be described below with reference to FIG. FIG. 10 is a plan view of a conventional recording / reproducing apparatus. In FIG. 10, a cassette 200 is a supply reel 20 around which a magnetic tape 212 is wound.
7, take-up reel 208, and tape guide roller 216
It contains a to 216e. Magnetic heads 203a-20
A magnetic tape 212 is wound around a rotating cylinder 201, which is arranged by dividing 3d into 90 ° on the circumference, and recording and reproducing of a video signal are performed. The audio signal and the control signal are recorded on both ends of the magnetic tape 212 by the audio control head 209. The audio signal and the video signal which have already been written during recording are erased by the audio erase head 210 and the full erase head 211, respectively. Tape guide posts 204a, 204
b, 204c, 204d, 204e and tilt post 205
a is inside the cassette opening when the cassette is installed (shown by the broken line)
The tape guide post 204 after the cassette mounting is detected by the cassette detection switch (not shown).
The a, 204b, 204c, 204d, 204e and the inclined post 205a are pulled out from the inside of the cassette opening and fixed at predetermined positions shown in the figure. On the other hand, Capstan 213
Is driven by a capstan motor 214, and when the apparatus is in a recording / reproducing mode, a rubber pinch roller 215 drives the magnetic tape 212 to the capstan 21.
The magnetic tape 212 is pressed against the magnetic tape 3 and transported at a predetermined speed. The reel drive gear 217 is configured to mesh with a gear portion formed on the take-up reel 208, and has a torque limiter mechanism (a clutch mechanism such as a magnet clutch) built therein. The rotation of the capstan motor 214 causes the capstan belt 218,
It is transmitted to the reel drive gear 217 via the relay pulley 219 and the idler gear 220, and drives the take-up reel 208 to wind up with a constant torque.

However, in the above structure, the pinch roller 215 is moved to the capstan 2 when recording / reproducing.
A mechanism for crimping with a predetermined force to 13 is required, which is a limitation in simplifying the mechanism in order to significantly reduce the cost. In addition, the pinch roller 215 is attached to the capstan 21.
Since the capstan shaft loss caused by pressing against 3 and the friction loss in the torque limiter mechanism of the reel drive gear 217 are generated, it is difficult to reduce the power consumption.

Therefore, in order to solve the above-mentioned problems, as a method that does not require a pinch roller pressure-bonding mechanism, Japanese Patent Application No. 6-299.
There is a winding tension control device shown in Japanese Patent No. 492. In this apparatus, a roller is interposed between the first capstan and the second capstan driven by the direct drive motor, and the tape is driven by using the tape tension. Then, the tape is wound from the capstan via the planetary gear device, and at the same time, as shown in FIG. 11, a braking force corresponding to the tape tension is applied to the outer periphery of the internal gear 127 constituting the planetary gear device. A tension control loop is formed by giving 128. Inside the planetary gear device, a link 123 corresponding to a retainer gear is used as a drive input source and is output to the sun gear 125 via the planet gears 124a and 124b, and the link 123, the internal gear 127 and the sun gear 125 are in the same direction. It's spinning. The configuration shown in FIG. 11 as a planetary gear device that is input from the retainer gear and is output to the sun gear is very effective for thinning.

On the other hand, in recent years, in a stationary VTR or the like, in order to secure tape running stability in both forward and reverse directions, independent tension detecting means are mounted on the supply side and the winding side. This can apply a braking force to the reel stand on the supply side and the reel stand on the take-up side, and the tension detecting means is electrically or mechanically turned ON / O depending on the tape running direction.
It is configured to perform FF.

Further, conventionally, when driving a tape, an idler mechanism is one of the mechanisms for selectively transmitting the drive torque of the capstan to the supply reel and the take-up reel. The idler mechanism has a built-in clutch for friction and the like and can be easily moved according to the rotation direction of the capstan, so it is a very effective means as an input means when switching the mode of the mechanism.

[0008]

However, the above-mentioned structure has the following problems. (1) Since the lateral pressure of the braking member always acts on the internal gear in the Japanese Patent Application No. 6-299492 from the outer periphery, the rotation shaft of the planetary gear is bent via the internal gear. In particular, as shown in FIG. 11, when the planetary gear is supported on the retainer gear so as to be thin as shown in FIG. 11, the deflection amount becomes particularly large, and at the same time, the sun gear and the planetary gear are not meshed well, and the tape is wound. This leads to defects and poor tension control. (2) When independent tension detecting means are mounted on the supply side and the winding side, the cost is increased due to an increase in the number of parts. (3) When the idler mechanism is used as the input source for the mode transition of the mechanism, the idler mechanism needs an extra clutch torque for moving the output destination mechanism in addition to the idler itself, resulting in a large loss torque after the mode transition. Therefore, it has been an obstacle to low power consumption. (4) When the idler mechanism in Japanese Patent Application No. 6-299492 is operating, as shown in FIG. 12, when the tooth tips of the idler gear protruding into the inner tooth rack come into contact with the tooth tips of the inner tooth rack, the idler gear is locked. It becomes a state. Therefore, in order to avoid this, it is conceivable to move the inner tooth rack or elastically deform the inner tooth rack, but both of them result in cost increase.

In view of the above problems, the present invention provides a highly reliable tape drive device having a simple and cost-effective construction and capable of realizing stable tape running.

[0010]

In order to solve the above problems, a tape drive device of the present invention is, in the first invention, a sun gear, a planet gear, a retainer gear and an internal gear, and the retainer gear is an input source and a sun gear. A planetary gear device having an output source of, a motor for rotationally driving the retainer gear, a winding side tape tension detecting means, a tape winding means driven by a sun gear, and an internal gear according to the output of the tension detecting means. A braking device that changes the braking force that directly acts on the retainer gear and a sub-retainer that rotates integrally with the retainer gear are provided, and the retainer gear and the sub-retainer have a configuration in which both ends of the planetary gear are rotatably supported.

According to the second aspect of the present invention, a planetary gear unit including a sun gear, a planet gear, a retainer gear and an internal gear, the retainer gear serving as an input source and the sun gear serving as an output source, and a drum gear driven by the internal gear are provided. And a braking unit that changes the braking force that directly acts on the drum gear according to the output of the tension detecting unit.

In the third aspect of the invention, the supply side tension arm and the winding side tension arm interlocked with the tape tension, the braking force varying means for the internal gear, and the rotation of the supply side tension arm and the winding side tension arm. The braking force varying means includes a transmitting means for transmitting the variation amount to the braking force varying means, and a releasing means for releasing the engagement between the winding side tension arm and the transmitting means in the rewinding mode, and the supply side tension arm is loosely fitted to the braking force varying means. In addition, the transmission means is engaged only in the rewinding mode.

Further, according to the fourth aspect of the invention, there is provided a first rotating body, drive means for rotating the first rotating body in a reciprocal manner, and a gear portion, and the first rotating body is engaged with the first rotating body. On the other hand, on the outer periphery of the first rotating body, the second rotating body that is capable of reciprocating from the supply side reel driving position (first position) to the winding side reel driving position (second position), the first position and the second position. By engaging with the gear portion of the second rotating body between the two positions, the rotational biasing force of the driving means of the first rotating body is converted into the revolution force of the second rotating body via the first rotating body. A fixed internal tooth member for conversion, the fixed internal tooth member has a substantially arc shape centered on the rotation center of the first rotating body, and is configured such that only both end teeth thereof are high teeth Is.

[0014]

According to the present invention, by adopting the structure of the first invention, the planetary gear is supported at both ends by both the retainer gear and the sub-retainer, so that the planetary gear can realize smooth rotation without bending. Further, by adopting the configuration of the second invention, the drum gear independent of the planetary gear device receives the braking force, and no loss torque is generated inside the planetary gear device. By adopting the configuration of the third aspect of the invention, the tension control mechanism, which is conventionally provided independently on each of the supply side and the winding side, is unified. Further, by adopting the configuration of the fourth aspect of the invention, the second rotary body and the fixed internal tooth member are surely meshed with each other at the high tooth portion.

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the tape drive device of the present invention will be described below with reference to the drawings. The capstan and the roller have the same configurations as in Japanese Patent Application No. 6-299492, and detailed description thereof will be omitted.

First, an outline of the entire apparatus will be described with reference to FIG. Magnetic tape 3 from supply reel 2 in cassette 1
Are guide rollers 4a and 4b provided in the cassette 1.
Through the supply side tension post 20 and the guide post 21, and is loaded from the opening of the cassette 1 and wound around the guide post 5 and the tilted post 6 positioned at predetermined positions, and then rotated. Reach cylinder 7. The magnetic tape 3 is wound around the rotary cylinder 7 at a predetermined angle, and then loaded from the opening of the cassette 1 and positioned at a predetermined position. The inclined post 9, the guide post 8, and the guide post 8 have the same opening of the cassette 1. After passing through the guide post 10 which is loaded from the inside of the unit and positioned at a predetermined position, the AC head 11 is wound at a predetermined angle and reaches the first capstan 12. Here, the second capstan 13 is arranged in parallel to the first capstan 12, and a roller 14 is provided so that the magnetic tape 3 can be wound around both capstans by a predetermined angle. After the magnetic tape 3 leaves the second capstan 13, the tension post 2 on the winding side
2 and the guide rollers 4c, 4e, 4d in the cassette 1
And reaches the take-up reel 15. The take-up reel 15 is
It has a gear portion on the outer circumference and is wound by a take-up reel drive gear 18 rotatably provided on the main substrate 90. Further, magnetic heads 16a and 16b having different azimuth angles and a flying erase head 17 are attached to the rotary cylinder 7, and a motor unit (not shown) for rotating them at a predetermined rotational speed is incorporated.

Next, the drive force transmission mechanism of the take-up reel drive gear 18 will be described with reference to FIGS. 1 and 3 to 5. All the components are mounted on the main board 90 and a sub-board 91 fixed to the main board 90. Direct drive motor that rotates the first capstan 12 (hereinafter,
A DD motor 19) and a relay pulley 23 rotatably provided on the sub-board 91 are connected by a transmission belt 24. The retainer gear 25 meshed with the gear portion formed on the relay pulley 23 is integrated by a sub-retainer 26 and a screw 27 that are rotatably provided with respect to an idler arm boss 34, which will be described later. Therefore, the retainer gear 25 includes the idler arm boss 34. It can be rotated around. The planetary gear located between the retainer gear 25 and the sub-retainer 26 can rotate about the retainer gear 25 and the sub-retainer 26 because its rotation shaft is rotatably supported by the retainer gear 25 and the sub-retainer 26, and The idler arm boss 34 can revolve around a sun gear 29 that is rotatably provided. The planetary gear is constantly meshed with the sun gear 29 and an internal gear portion 32 of a ring 31 that is rotatably provided around a differential shaft 30 provided on the sub-board 91. As described above, the retainer gear 25, the ring 31, and the sun gear 29 each have an independent bearing portion. Further, the idler arm boss 34 crimped to the idler arm 33 is provided so as to be rotatable around the differential shaft 30, and the idler arm 3 is also provided.
An idler gear 36 is rotatably provided around an idler gear shaft 35 provided at one end of the shaft 3. Idler gear 36
Is always meshed with the sun gear 29, and the gear portion of the supply reel base 37 rotatably provided on the main substrate 90 according to the rotation direction of the first capstan and the take-up reel drive gear 18.
It is configured so that it can be selectively meshed with the relay gear 38 meshed with. The idler gear 36 is pressed against the idler arm 33 by a compression spring 39 having a very weak biasing force. Further, an internal gear rack 40 for engaging the gear portion of the idler gear 36 and revolving the idler gear 36 around the sun gear 29 is provided on the sub-board 91. The internal tooth rack 40 has an internal gear shape centered on the differential shaft 30, and has both end portions 40a and the non-rush portion 4 other than both ends.
The tooth profile is different from 0b. Specifically, the tip circle diameters of the teeth of both ends 40a and the non-rushing portion 40b of the internal tooth rack 40 are φ2d _r1 and φ2d _r2 , respectively, and the distance from the center of the differential shaft 30 to the idler gear shaft 35 is L ₁ , Set the diameter of the tip circle and the diameter of the bottom circle of the idler gear 36 to φ2d, respectively.
_gt and φ2d _gb are set so that L ₁ + d _gb <d _r1 <d _r2 <L ₁ + d _gt is satisfied. That is, idler gear 3
6, the amount of engagement with the internal tooth rack 40 is larger at both end portions 40a than at the non-rushing portion 40b.
No matter what phase 6 is inserted into the internal tooth rack 40, the two are surely meshed with each other. Therefore, the idler gear 36 is separated from one of the gear portion of the supply reel base 37 or the take-up reel drive gear 18 by the weak clutch force of the compression spring 39, and after being engaged with both end portions 40a, the revolution force is generated by the internal tooth rack 40. To be given.

Next, the structure of the tension control mechanism of the magnetic tape 3 will be described. The band arm 41 is rotatably provided around the band arm shaft 42 that is erected on the sub-board 91, and is biased counterclockwise in FIG. 1 by the band arm spring 43. In addition, the band arm 41
A braking band 45 is fixed to the pair of fasteners 44a, 44b rotatable with respect to each other.
It is wrapped around the circumference of 1 (about 230 degrees). Therefore, in order to prevent the winding angle from decreasing due to the elastic force of the braking band 45 itself, the ring 3 of the braking band 45 is rotated when the band arm 41 rotates counterclockwise in FIG.
Fastener guide pins 46a and 46b are provided on the sub-board 91 so that only the outer peripheral winding portion 1 can be loosened.
Further, the band arm 41 can be engaged with the engaging pin 48 of the winding side tension arm 47 rotatably provided with respect to the sub-board 91. The take-up tension post 22 is erected on the take-up tension arm 47. With this configuration, for example, in FIG. 3, if the winding tension of the magnetic tape 3 increases and the winding-side tension post 22 rotates clockwise,
The band arm 41 is rotated counterclockwise via the engagement pin 48 to reduce the pressure contact force of the braking band 45 to the ring 31. In addition, in FIG. 1, the connecting rod 50 is interposed between the supply side tension arm 49 and the band arm 41 that are rotatably provided on the main substrate 90, and the elongated hole 51 provided in the connecting rod 50 is provided. Follower pin 5 on the supply side tension arm 49
2 is loosely fitted. Supply side tension post 2 at one end
The supply side tension arm 49 provided with 0 is constantly urged counterclockwise around the supply side tension arm shaft 54 by the supply side tension spring 53, and one end of a tension band 55 that applies a friction torque to the supply reel base 37. Holding The tension of the magnetic tape 3 applied to the tension post is more PLA than when it is transported in the REW direction.
By utilizing the small transfer time in the Y direction, the follower pin 52 of the supply side tension arm 49 does not contact the end surface 51a of the elongated hole 51 of the connecting rod 50 at the time of PLAY, and due to the tension of the magnetic tape 3 at the time of REW. P
The end face 51 of the long hole 51 is rotated clockwise from the time of LAY.
The elongated hole shape and the urging force of the supply side tension spring 53 are set so as to come into contact with a. Therefore, at the time of REW, the supply side tension arm 49 and the band arm 41 are connected via the connecting rod 50. In addition,
Set the position of the tension post 22 on the winding side to the braking band 45.
The band arm 41 is provided with a take-up side adjusting piece 56 for adjusting. Similarly, for the supply-side tension post 20, the supply-side adjustment piece 57 is provided on the main board 90.

Next, the lock mechanism of the take-up side tension post 22 and the soft brake drive mechanism which are interlocked with the idler arm 33 will be described. The reversing arm 5 rotatably supported by the guide boss 58 provided on the sub-board 91.
An engaging portion 59a composed of a driving portion 59b and a non-driving portion 59c is formed on the member 9, and is engaged with a guide pin 60 that is set up at one end of the idler arm 33. It is connected to the locking arm 62 via. The connecting link 61 is rotatably provided with respect to the reversing arm 59 and the locking arm 62. As shown in FIGS. 1 and 5, in the non-driving section 59 c, the idler gear 36 is connected to the relay gear 38 or the supply reel base 37.
Has a shape of a substantially circular arc centered on the differential shaft 30 when engaged with each other. Therefore, the PLAY of FIG.
The idler arm 33 can rotate the reversing arm 59 according to the mode and the REW mode of FIG. 5, but conversely, the reversing arm 59 cannot rotate the idler arm 33. Also, the idler arm 33
Is rotated from the position shown in FIG. 1 or 5, and when the guide pin 60 reaches the inflection position where the non-driving portion 59c engages with the driving portion 59b, the internal gear rack 40 is already engaged with the idler gear 36. Stipulates the position of. The locking arm 62 is rotatably provided on the sub-board 91,
One end thereof can be engaged with an engagement pin 48 protruding from the winding side tension arm 47. Locking arm shaft 6
3, a soft brake arm 64 is rotatably provided coaxially with the brake shoe 65, and a brake shoe 65 is provided on the take-up reel drive gear 1.
It is arranged so that it can be attached to 8. A soft brake spring 66 is stretched between the locking arm 62 and the soft brake arm 64, and unless the soft brake arm 64 contacts the take-up reel drive gear 18, both of them are bent portions 62a of the locking arm 62. Are in contact with each other. Thus, the reversing arm 59, the connecting link 61, and the locking arm 6
2 has a so-called toggle structure.

The operation of the tape drive device constructed as described above will be described below. First, the PL shown in FIG.
The operation of each mechanism in the AY mode will be described.

In the PLAY mode, the magnetic tape 3 reaches the take-up reel 15 from the supply reel 2 along the path shown in FIG. In FIG. 1, the first capstan 12 and the second capstan 13 are rotated counterclockwise by a DD motor 19 to transfer the tape at a predetermined speed. Due to the above rotation of the first capstan 12, the retainer gear 25 is rotated in the clockwise direction via the transmission belt 24 and the relay pulley 23. The planetary gear revolves in the clockwise direction around the differential shaft 30 while rotating in the counterclockwise direction. The ring 31 whose inner gear part 32 is meshed with the planetary gear is
It is rotating clockwise. The sun gear 29 is also rotating clockwise, and the idler arm 33 is stationary at a position where the idler gear 36 meshes with the relay gear 38 due to the clutch force of the compression spring 39. The idler gear 36 is shown in FIG.
It rotates counterclockwise, and the winding reel drive gear 18 rotates counterclockwise via the relay gear 38 to wind the magnetic tape 3 on the supply reel 2. On the other hand, the engaging portion 59 a of the reversing arm 59 contacts the guide pin 60 on the idler arm 33 and is stationary. The locking arm 62 is also stationary at the position shown in FIG. 1 via the connecting link 61, and is separated from the engaging pin 48 on the winding side tension arm 47. The soft brake arm 64 is urged by the urging force of the soft brake spring 66 in the counterclockwise direction in FIG. Therefore, the brake shoe 65 is separated from the take-up reel drive gear 18, and no braking force is applied to the take-up reel drive gear 18. Focusing on the tension control mechanism, the tension post 22 on the winding side
Is given a counterclockwise moment in FIG. 3 through the band arm 41 and the engaging pin 48 by the urging force of the band arm spring 43, and at the same time, the tension of the magnetic tape 3 wound around the tension post by a predetermined angle. As a result, a moment in the clockwise direction in FIG. 3 is given, and a balanced state is maintained by both moments. During PLAY, for example, when the tape tension at the take-up side tension post 22 becomes large, the take-up side tension post 22 rotates counterclockwise in FIG.
1 can rotate clockwise around the band arm shaft 42 to reduce the pressure contact force of the braking band 45 to the outer circumference of the ring 31. Therefore, the output torque to the sun gear 29 decreases and the winding torque decreases. On the contrary, when the tension at the take-up tension post becomes small, the take-up side tension post 22 rotates clockwise in FIG. 1, and the band arm 41 rotates counterclockwise by the urging force of the band arm spring 43 to rotate the ring 31. The pressure contact force to the outer circumference can be increased. Therefore, the output torque to the sun gear 29 is increased, and the winding torque can be increased.

Next, from the PLAY mode, REW (RE
The operation of each mechanism when shifting to the V) mode will be described. When you press the REW button, the first capstan 1
2 reverses clockwise in FIG. As a result, the retainer gear 25 rotates counterclockwise via the transmission belt 24 and the relay pulley 23. The planet gear revolves around the differential shaft 30 in the counterclockwise direction while rotating in the clockwise direction. Sun gear 2
9 rotates counterclockwise by the above-described rotation of the planet gears. The idler arm 33 starts to rotate counterclockwise around the differential shaft 30 by the clutch force of the compression spring 39. Idler gear 36 linked to idler arm 33
Separates from the relay gear 38 and projects into both end portions 40a of the internal gear rack 40. At this time, the guide pin 60 of the idler arm 33 remains in contact with the non-driving portion 59c of the reversing arm 59. Therefore, the connecting link 61, the locking arm 62, and the soft brake arm 64 remain stationary.

Thereafter, when the idler arm 33 further rotates counterclockwise in FIG. 1 as the first capstan 12 rotates in the clockwise direction, the idler gear 36 is attached to both end portions 40a of the internal tooth rack 40 which are high teeth. It meshes surely, starts rotating in the clockwise direction around the idler gear shaft 35, and revolves in the counterclockwise direction around the differential shaft 30. At this time, the revolving force acting on the idler gear 36 is given by the driving force of the first capstan 12 in addition to the clutch force by the compression spring 39. On the other hand, as the idler gear 36 revolves in the counterclockwise direction, the reversing arm 59 moves the drive unit 5
When the guide pin 60 is engaged with 9b, it rotates clockwise. As a result, the locking arm 62 becomes
Rotate counterclockwise around the locking arm shaft 63 via 1. Interlocking with the locking arm 62, the soft brake arm 6
4 also rotates counterclockwise, and the brake shoe 65 comes into pressure contact with the take-up reel drive gear 18. Soft brake spring 6
Since 6 always biases the soft brake arm 64 counterclockwise, the pressure contact with the take-up reel drive gear 18 does not change until the idler gear 36 meshes with the supply reel base 37. With the counterclockwise rotation of the idler arm 33, the bent portion 62a of the locking arm 62 moves away from the soft brake arm 64, and the locking arm 62 is engaged with the engaging pin 48 that is set up on the winding side tension arm 47. Engage with. Therefore, the winding-side tension arm 47 rotates clockwise, and the engagement between the engagement pin 48 and the band arm 41 is released. That is, the tension control by the winding side tension post 22 becomes impossible. Then, when the idler arm 33 rotates to the position shown in FIG. 5, the guide pin 60 engages with the non-driving portion 59c.

Finally, the operation of each mechanism during REW will be described. Since the supply side tension spring 53 and the urging force of the elongated hole shape are set as described above, the supply side tension arm 49 rotates clockwise, and the follower pin 52 and the end surface 51a of the elongated hole 51 engage with each other. . Therefore,
The supply side tension arm 49 can be connected to the band arm 41 via the connecting rod 50.
For example, when the tape tension on the supply-side tension post 20 increases, the supply-side tension post 20 rotates clockwise, moving the connecting rod 50 to the left. Accordingly, the band arm 41 rotates clockwise around the band arm shaft 42 to rotate the braking band 4 to the outer circumference of the ring 31.
The pressure contact force by 5 can be reduced. On the other hand, the winding-side tension arm 47 is completely locked by the locking arm 62, and therefore is not the target of tension control.

Next, another embodiment will be described with reference to FIGS. 8 and 9. The difference from the above-described embodiment is the following two points. (1) The braking band 45 is wound around a member different from the ring 31. (2) The bearing portion of the ring 31 is provided on the outer circumference of the retainer gear 25.

More specifically, the fasteners 44a, 44
The braking band 45 extending from the band arm 41 via b
Is a drum gear 67 having a rotation support shaft on the sub-board 91.
Wrapped around. The drum gear 67 constantly meshes with a gear portion provided on the outer circumference of the ring 31. Therefore, ring 3
The side pressure from the braking band 45 does not act on 1 directly. Further, although the bearing portion of the ring 31 is provided on the outer periphery of the retainer gear 25, the ring 31 is not subjected to a radial force other than its own rotation loss, so that the configuration shown in FIG. 9 does not cause a large loss. Therefore, it is possible to satisfy a very thin planetary gear device. As described above, in this configuration, the tension control of the magnetic tape 3 is performed by the winding side tension post 22 (REW).
In some cases, tension post 20 on the supply side, band arm 4
1. It can be realized by the drum gear 67 via the braking band 45. Here, the ring 31 and the drum gear 67
It is needless to say that the tension controllability can be further improved by appropriately setting the tooth number ratio of.

[0027]

As described above, according to the first aspect of the present invention, there is provided a tape drive device including a planetary gear device including a sun gear, a planetary gear, a retainer gear and an internal gear, the retainer gear being an input source and the sun gear being an output source. A retainer gear drive motor, a winding side tape tension detecting means, a tape winding means driven by a sun gear, and a braking means for changing a braking force directly acting on the internal gear according to the output of the tension detecting means. By providing the retainer gear and a sub-retainer that rotates integrally with the retainer gear and the sub-retainer so that both ends of the planetary gear are rotatably supported, it is possible for the planetary gear device to rotate smoothly without any deflection of the planetary gear. Therefore, the power consumption of the capstan can be reduced, and the stable running property of the tape can be realized.

According to a second aspect of the present invention, there is provided a tape drive device including a planetary gear device including a sun gear, a planet gear, a retainer gear and an internal gear, the retainer gear being an input source and the sun gear being an output source. Since the drum gear that is driven by and the braking means that changes the braking force that directly acts on the drum gear according to the output of the tension detection means are provided, loss torque inside the planetary gear device due to the braking means does not occur at all. In addition to achieving low power consumption, there is no need to stack the planetary gear device in terms of its structure, which is very effective for thinning. Furthermore, it is possible to contribute to the reduction in size and weight of the entire device as the capstan diameter is reduced.

According to the third aspect of the invention, the supply-side tension arm that rotates according to the supply-side tape tension, the winding-side tension arm that rotates according to the winding-side tape tension, and the internal gear Braking force varying means capable of changing the applied braking force, transmitting means for engaging the supply side tension arm and the winding side tension arm, and transmitting the rotational change amount to the braking force varying means, and the winding mode in the rewinding mode. The tension arm on the take-up side and the releasing means for releasing the engagement of the transmission means are provided, the tension arm on the supply side is loosely fitted to the braking force varying means, and is engaged with the transmission means only in the rewinding mode by the tape tension on the supply side. By configuring so as to match, the tension control mechanism, which was conventionally provided independently on each of the supply side and the winding side, is unified, and at the same time, the tape is moved in the tape running direction. The force difference is performing the switching of the tension arm of the control object by utilizing the fact that occur,
A great cost reduction effect can be obtained.

Further, in the fourth aspect of the invention, the first rotating body, the driving means for rotating the first rotating body in the forward and reverse directions, the supply side reel driving means for rotationally driving each of the pair of reels, and Having a winding side reel drive means and a gear part,
Further, between the first position engaging the supply side reel driving means and the second position engaging the winding side reel driving means on the outer periphery of the first rotating body while engaging the first rotating body. A second rotating body capable of reciprocating, and a moving means for rotatably supporting the second rotating body in a reciprocal manner and for selectively reciprocating the second rotating body between the first position and the second position. And a fixed internal tooth for converting the rotational urging force of the drive means into the revolution force of the second rotating body via the first rotating body by meshing with the gear portion between the first position and the second position. The fixed internal tooth member has a substantially circular arc shape centered on the rotation center of the first rotating body, and is configured so that only the both end teeth have high teeth. Since the swinging motion is surely realized with, it is possible to provide a highly reliable device, and its practical effect is great.

[Brief description of drawings]

FIG. 1 is a plan view showing an entire tape drive device according to an embodiment of the present invention.

FIG. 2 is a plan view showing an outline of a tape running system of the same embodiment.

FIG. 3 is a rear view of FIG. 1 in the same embodiment.

FIG. 4 is a sectional view of the main part of FIG. 1 of the same embodiment.

FIG. 5 is a plan view of the rewinding mode of the embodiment.

FIG. 6 is a plan view showing the relationship at the start of meshing between the idler gear and the internal tooth rack of the embodiment.

FIG. 7 is a detailed view of a C portion of FIG. 6 in the same embodiment.

FIG. 8 is a plan view of a tape drive device according to another embodiment of the present invention.

FIG. 9 is a sectional view of the vicinity of the planetary gear device according to the embodiment.

FIG. 10 is a plan view of a conventional magnetic recording / reproducing apparatus.

FIG. 11 is a sectional view of a tape drive device using a conventional planetary gear device.

FIG. 12 is a plan view showing the relationship at the start of meshing between a conventional idler gear and an internal tooth rack.

[Explanation of symbols]

 18 Take-up reel drive gear 19 Direct drive motor (DD motor) 20 Supply side tension post 22 Take-up side tension post 23 Relay pulley 24 Transmission belt 25 Retainer gear 26 Sub-retainer 28 Planetary gear 29 Sun gear 31 Ring 33 Idler arm 36 Idler gear 38 Relay Gear 40 Internal tooth rack 41 Band arm 45 Braking band 47 Winding side tension arm 49 Supply side tension arm 50 Connecting rod 59 Reversing arm 62 Locking arm 64 Soft brake arm 67 Drum gear

Claims (5)

[Claims] 1. A tape drive device comprising a planetary gear device comprising a sun gear, a planetary gear, a retainer gear and an internal gear, and having the retainer gear as an input source and the sun gear as an output source, the tape drive device having a predetermined rotation speed. A motor for rotating the retainer gear, a tension detecting means for detecting the tape tension on the winding side, a tape winding means driven by the sun gear, and a tape directly for the internal gear according to the output of the tension detecting means. A tape drive device comprising: a braking unit that changes a braking force that acts; and a sub-retainer that rotates integrally with the retainer gear, and the planet gear is rotatably supported at both ends by the retainer gear and the sub-retainer. 2. The tape drive device according to claim 1, wherein the bearing portion of the retainer gear and the bearing portion of the internal gear are arranged side by side in the axial direction of the rotary shaft. 3. A tape drive device comprising a planetary gear device comprising a sun gear, a planetary gear, a retainer gear and an internal gear, and having the retainer gear as an input source and the sun gear as an output source, the tape drive device comprising: A motor for rotationally driving the retainer gear, a tension detecting means for detecting tape tension on the winding side, a tape winding means driven by the sun gear, a drum gear driven by the internal gear, and the tension detecting means. And a braking unit that changes the braking force that directly acts on the drum gear in accordance with the output of the tape drive device. 4. A tape drive device comprising a planetary gear device which comprises a sun gear, a planetary gear, a retainer gear and an internal gear, and which uses the retainer gear as an input source and the sun gear as an output source, at a predetermined rotational speed. A motor for rotationally driving the retainer gear, a tape winding device driven by the sun gear, a supply-side tension arm that rotates and moves according to the supply-side tape tension, and a rotation-movement according to the winding-side tape tension. Winding side tension arm, braking force varying means capable of changing the braking force applied to the internal gear, engaging the supply side tension arm and the winding side tension arm, and controlling the amount of rotation change thereof. A transmission means for transmitting to the power varying means, and a solution for releasing the engagement between the winding side tension arm and the transmission means in the rewinding mode. And means, the supply-side tension arm is loosely fitted to the braking force control means,
Further, the tape drive device is characterized in that it is engaged with the transmission means only in the rewinding mode by the tape tension on the supply side. 5. A first rotating body, a driving means for rotating the first rotating body in a reciprocal manner, a supply side reel driving means and a winding side reel driving means for rotationally driving each of a pair of reels. A first position having a gear portion and engaging with the supply side reel driving means on the outer periphery of the first rotation body while engaging with the first rotation body; A second rotating body that is capable of reciprocating between a second position that engages with the drive means, and the second rotating body that is rotatably supported in forward and reverse directions;
By moving means for selectively reciprocating the second rotating body between the first position and the second position, and meshing with the gear portion between the first position and the second position, A fixed internal tooth member that converts the rotational biasing force of the drive means of the first rotary member into the revolution force of the second rotary member via the first rotary member, wherein the fixed internal tooth member is A tape drive device having a substantially arcuate shape centered on a rotation center of a first rotating body, and having both end teeth having high teeth.