JP3480102B2 - Winding tension control device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a tape driving means which does not use a pinch roller crimping mechanism.

[0002]

2. Description of the Related Art In recent years, a magnetic recording / reproducing apparatus typified by a VTR has been required to reduce its size and weight, and at the same time, to reduce the cost according to the decrease in the product price.

Conventionally, in a magnetic recording / reproducing apparatus such as a cassette type video tape recorder, it has been a general practice to press a tape on a capstan with a pinch roller as a tape driving means. In addition, a clutch mechanism has been usually employed in which a magnetic tape sent from a capstan rotates a reel around which the magnetic tape is wound with a constant torque.

A tape drive mechanism of a conventional magnetic recording / reproducing apparatus will be described below with reference to FIG. FIG. 15 is a plan view of a conventional magnetic recording / reproducing apparatus. In FIG. 15, 200
Is a cassette containing a supply reel 207 around which a magnetic tape 212 is wound and a take-up reel 208, and 201 is a rotary cylinder in which magnetic heads 203a to 203d are divided into 90 ° on the circumference. Reference numeral 209 is an audio control head for recording audio signals and control signals on both ends of the magnetic tape, 210 is an audio erase head for erasing audio signals already written during recording, and 211 is for erasing video signals already written during recording. It is a full erase head. Tape guide post 2
04a, 204b, 204c, 204d, 204e and the inclined post 205a are arranged inside the cassette opening (shown by a broken line) when the cassette is mounted, and after the cassette detection switch (not shown) detects the cassette mounting, the tape guide post 204a. , 204b, 204c, 204
The d, 204e and the inclined post 205a are pulled out from the inside of the cassette opening and fixed at a predetermined position shown in the figure.
Reference numeral 214 denotes a capstan motor having a capstan 213. When the apparatus is in the recording / reproducing mode, the rubber pinch roller 215 presses the magnetic tape 212 against the capstan 213, and the magnetic tape 21 is moved at a predetermined speed.
2 is configured to be transferred. 216a to 216
Reference numeral b is a tape guide roller provided in the cassette 200. A reel drive gear 217 meshes with a gear formed on the take-up reel and has a torque limiter mechanism (a clutch mechanism such as a magnet clutch) built therein. The rotation of the capstan motor 214 is transmitted to the reel drive gear through the capstan belt 218, the relay pulley 219, and the idler gear 220, and drives the take-up reel 208 to take up with a constant torque.

[0005]

However, the above-mentioned conventional structure requires a mechanism for pressing the pinch roller against the capstan for recording / reproducing, and simplifies the mechanism in order to significantly reduce the cost. It was a constraint. Further, there is a problem that the capstan shaft loss caused by pressing the pinch roller against the capstan and the friction loss in the torque limiter mechanism of the reel drive gear are large.

SUMMARY OF THE INVENTION An object of the present invention is to provide a winding tension control mechanism for realizing a recording / reproducing apparatus which has a simple mechanism and realizes power saving.

[0007]

In order to achieve this object, a winding tension control device of the present invention uses a tape winding device.
A supply reel and the take-up reel and a sun gear, wherein
The supply reel and the winding driven by a sun gear
An idler gear that selectively drives the reel, a planet gear that revolves around the sun gear while revolving, an internal gear that meshes with the planet gear and has the same rotation center as the sun gear, and rotatably holds the planet gear. A link rotatably provided at the center of rotation of the sun gear, a capstan that rotates at a predetermined rotation speed, a first transmission mechanism that transmits the rotation of the capstan to the link, and the internal gear A braking arm that applies a braking force to rotation, a winding-side tension arm that has a tension post that wraps the tape by a predetermined angle to detect the tape tension, and a force applied to the winding-side tension arm that acts on the internal gear. a variable braking member of the brake force, a second transmission mechanism for transmitting the rotational output of the sun gear to the take-up reel, the tape tension Predetermined angle shunt-wound on the tape to detect
Has a tension post that sticks and changes in tape tension
And a supply side tension arm that rotates with
Transmits the rotation of the tension arm to the braking arm
And a connecting rod for winding the tape on the take-up reel.
Tension control while taking is done by the tension on the take-up side.
Braking of the braking member by the brake arm and the braking arm.
The tape is wound on the supply side reel by changing the force.
The tension control for
And the connecting rod and the braking arm, the braking unit
The braking force of the material is variable .

[0008]

With this structure, the tape tension when the magnetic tape is wound on the reel can be made substantially constant,
As a result, it is possible to realize a significant cost reduction of the tape drive mechanism of the system that does not require the pinch roller crimping mechanism that has been conventionally required and a reduction in the power consumption of the apparatus.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings.

FIG. 1 is a plan view of the recording / reproducing apparatus. The outline of the entire apparatus will be described with reference to this figure. The magnetic tape 3 ejected from the supply reel 2 in the cassette 1 is pulled out of the cassette via the guide rollers 4a and 4b provided in the cassette 1, passes through the supply-side tension post 39 and the guide post 40, and then is ejected from the cassette 1. After being loaded from the opening and wound around the guide post 5 and the inclined post 6 which are positioned at a predetermined position, they reach the rotating cylinder 7. The magnetic tape 3 is wound around the rotary cylinder 7 at a predetermined angle, then loaded from the opening of the cassette 1 and positioned at a predetermined position.
Similarly to the guide post 8, the AC head 11 is wound from the opening of the cassette 1 through the guide post 10 positioned at a predetermined position and wound around the AC head 11 at a predetermined angle.
Reach the first capstan 12. Second capstan 1
3 is installed parallel to the first capstan 12 and rotates in the same direction. The roller 14 is sandwiched between the first capstan and the second capstan, and the magnetic tape 3 is wound around the first capstan 12 by about 180 degrees and then wound around the roller 14 and further on the second capstan 13. About 1
Wrap around 80 degrees. Magnetic tape 3 is the second capstan 1
After being separated from 3, the winding reel 15 is wound around the winding side tension post 31 and the guide rollers 4e, 4c, 4d. Further, the rotating cylinder 7 is provided with magnetic heads 16a, 16b having different azimuth angles and a flying erase head 17, and has a built-in motor unit for rotating them at a predetermined rotation speed.

Next, the drive force transmission mechanism of the take-up reel drive gear 18 will be described with reference to FIGS. 2 and 3. A direct drive motor 19 (hereinafter referred to as a DD motor) for rotating the first capstan 12 and a relay pulley 21 rotatably provided on the substrate 20 are connected by a transmission belt 22. The gear portion provided on the relay pulley 21 is a link 2 that revolves the planetary gear 24 around the sun gear 25.
It meshes with the gear part 23a formed in 3. The sun gear 25 link 23 is mounted rotatably around a sun gear shaft 26 that is erected on the substrate 20. An internal gear 27 that meshes with the outside of the planetary gear 24 is rotatably attached to the link 23, and a braking member 29 provided on a braking arm 28 is pressed against the outer circumference. The braking arm 2
Numeral 8 is rotatably attached around an axis provided on the substrate 20, a spring 30 is attached to one end, and the other end 28a is attached.
Comes into contact with one end 32a of the winding-side tension arm 32 provided with the winding-side tension post 31, and the magnetic tape 3
The winding tension is set so that the pressure contact force of the brake pad is reduced when the winding side tension post exerts a rotational force in the counterclockwise direction. Idler gear 33
Is rotatably mounted around a rotary shaft 34 provided at one end of the idler arm 35, and meshes with the sun gear 25. The idler arm 35 is pressed against the lower surface of the link 23 by a spring 36 with a light force. The idler gear 33 acts on the sun gear 2 by the action of the spring 36.
It rotates around 5 and selectively meshes with the gear portion of the supply reel base 37 or the relay gear 38 depending on the rotation direction of the capstan. The supply side tension arm 41 having the supply side tension post 39 at one end has a rotation shaft 43 on the second substrate 42 and is biased in the counterclockwise direction by a supply tension spring 44. In addition, the tension band 4 which is wound around the supply reel stand 37 at the other end to give a friction torque
Holds one end of 5. A clutch felt 47 and a clutch plate 46 are provided below the relay gear 38, and when the main rod 48 moves to the right in the rewinding mode of the device, the pawl portion 48d formed on the main rod 48.
Are configured to regulate the rotation of the clutch plate 46. One end of the supply tension spring is attached to the main rod 48, relaxes in the rewind mode, and maintains the supply tension spring pulled leftward in the drawing in the recording / reproducing mode.

A mechanism for moving the main rod 48 left and right by the reversing operation of the idler arm 35 will be described with reference to FIGS. 4 and 5. When the idler gear 33 meshes with the relay gear 38, the gear portion of the relay pulley 21 and the intermittent gear formed on the outer periphery of the idler arm 35 are disengaged from each other. Further, even when the idler gear 33 is meshed with the supply reel stand, the gear portion of the relay pulley corresponds to the missing portion of the gear of the idler arm 35, and the mesh is disengaged. Further, the reversing gear 49 is always meshed with the second gear portion 35a of the idler arm 35. A reversing lever 50 is coaxially provided below the reversing gear, and an oblong hole 50a formed in the reversing lever is provided.
A boss portion 49a provided on the reversing gear is inserted in the. A boss portion 50b is formed on the reversing lever 50, and the boss portion 50b is fitted in a deformation hole portion 48a formed in the main rod 48. The deformation hole portion 48a is composed of a groove portion 60a and arc portions 60b, 60c, 60d and 60e, and the arc portions 60b and 60c are formed with a radius smaller than that of the arc portions 60d and 60e. When the main rod 48 completes its movement, the boss portion 50b of the reversing lever 50 is stopped at a position in contact with the arc 60e or 60d so as to be sucked by the taper portion 60f or 60g. As a result, the slot 50a and the boss portion 49a are in the positional relationship shown by the broken line in FIG. 4, the reversing gear 49 and the reversing lever 50 are in a free state, and the gear portion of the pulley 21 and the gear 35d of the idler arm 35 mesh smoothly. It will fall out.

Next, a tape drive mechanism including the first capstan and the second capstan will be described with reference to FIGS. FIG. 6 is a perspective view of the same mechanism. 7 is a side view of the mechanism, FIG. 8 is a top view of the mechanism, and FIG.
8B is a schematic diagram showing a state where tape loading is completed, and FIG. 8B is a schematic diagram showing an unloading state. FIG. 9 is a side view showing a configuration for holding the roller 14. In FIG. 7, the first capstan 12 is rotated by a DD motor 19 of a direct drive type at a predetermined rotation speed. D
A first capstan holder 52 for rotatably holding the first capstan 12 and fixing it to the substrate 20 is attached to the D motor 19. The first capstan holder 52 holds the second capstan 13 rotatably and has a rotation center parallel to the first capstan 12 and eccentric to the center of the second capstan shaft. The second capstan holder 53 is rotatably attached, and the gear 5 rotates in conjunction with the tape loading operation.
1 is driven to rotate. The second capstan 13 is driven by a pulley 55 provided on the first capstan 12, a pulley 56 provided on the second capstan 13, and a rubber belt 54. At this time, the second capstan 13 becomes the first capstan 12
Pulleys 55 and 56 to rotate slightly faster than
The pulley diameter of is set.

FIG. 9 is a view showing the structure of a roller arm which holds the roller 14 and pulls out the magnetic tape 3 from the cassette 1. The center of the roller 14 has a vertically conical pivot receiving structure to minimize friction loss during rotation. The cylindrical portion 14a adjacent to the conical portion is a cylindrical concave portion 57a of the roller arm 57.
The roller 14 regulates the posture of the roller 14 when the magnetic tape 3 is pulled out from the cassette 1 when the tape is loaded. In the tape running mode such as during recording / reproduction, the cylindrical portion 14a
The roller arm 57 is positioned so that it does not come into contact with the cylindrical recess 57a. Reference numeral 58 is a rotation axis of a roller arm 57 provided on the substrate 13.

Next, the operation of the winding tension control mechanism using the planetary gear mechanism will be described with reference to FIG. FIG. 10 is a schematic diagram for explaining the winding tension control mechanism.

Here, the tension t of the tape ejected from the second capstan, which is obtained by the winding tension control mechanism of this apparatus, will be obtained.

In FIG. 10, the force F applied to the tension post 31 by the tensions t and t'is

[0018]

[Equation 1]

Here, η ^* is a traveling loss in the tension post, and when the tension post is a roller type,

[0020]

[Equation 2]

It can be calculated by α ₁ and α ₂ are the winding angles of the tape around the tension post, d is the diameter of the tension post shaft, D is the outer diameter of the tension roller, and μ ^* is the friction coefficient between the tension post shaft and the tension roller. Next, the balance condition of the tension arm force,

[0022]

[Equation 3]

Therefore, the pressure f generated on the brake pad
Is

[0024]

[Equation 4]

[0025] Where P is the tension spring force,
a, b, and c are arm lengths of the tension arm in FIG. Substituting (Equation 2) into (Equation 4),

[0026]

[Equation 5]

Torque Φ ₁ acting on gear 1 by pressure f
Is

[0028]

[Equation 6]

Here, e is the radius of the outer peripheral drum portion of the internal gear 27, and μ is the friction coefficient of the brake pad. further,
The rotational torque of the sun gear 25 is equal to the tangential force applied to the teeth of the internal gear 27 and the tangential force applied to the teeth of the sun gear 25 (FIG. 11).

[0030]

[Equation 7]

It becomes Here, the number of teeth of the sun gear 25 is Z
₂ and the number of teeth of the internal gear 27 is Z ₁ . Set the number of teeth on the T reel to Z
_When it is set to _T and the T drive gear and the internal gear 27 are not decelerated and are connected by a transmission gear of an idler gear and a relay gear (not shown),

[0032]

[Equation 8]

The following relationship is obtained. Here, η is a traveling loss of the rollers in the cassette and the like. (Equation 5) to (Equation 8)
Substituting into

[0034]

[Equation 9]

To obtain When this is arranged about t,

[0036]

[Equation 10]

Is obtained. Next, the sun gear 2 of the internal gear 27
5 and the rotation speeds V ₁ , V ₂ and _VL of the link 23 are obtained. The rotation speed V ₂ of the sun gear 25 is

[0038]

[Equation 11]

V ₁ , V _L obtained by

[0040]

[Equation 12]

[0041]

[Equation 13]

It is obtained by Here, n is an arbitrary number, but n is n> -1. Rotation torque of link 23 Φ _L
Is

[0043]

[Equation 14]

Organizing about Φ _L ,

[0045]

[Equation 15]

It becomes here,

[0047]

[Equation 16]

Therefore, it is substituted into (Equation 15) and Φ
_L is

[0049]

[Equation 17]

It becomes Further, the speed reduction ratio m of the belt from the first capstan to the link L is

[0051]

[Equation 18]

It is represented by Here, d _cap is the diameter (mm) of the capstan, and 33.35 is the tape speed ( ^{mm 2} / _sec ) of the VHS-SP mode.

FIG. 13 shows the rotation speed and rotation direction of each gear of the planetary gear mechanism. Here, z1, z2, and z3 are the numbers of teeth of the internal gear 27, the sun gear 25, and the planetary gear 24, and n
Is an arbitrary value.

In FIG. 13, the entire planetary gear is set to 1 in the first row.
When rotating (1), the link 23 is fixed to the second row and the internal gear 27 is rotated once (2). The third row shows (3) in which n times that of (2) is added to (1).
In (3), when the link 23 makes one rotation, the internal gear 2
7, the sun gear 25, and the planetary gear 24 are (1+
n), (1−n * z1 / z2), (1 + n * z1 / z)
3) Rotate. As an example, z1 = 51, z2 = 18,
Consider the case where z3 = 16. The changes in the rotation speed of each gear are shown in the characteristic diagram of FIG. 14, where the horizontal axis is n and the vertical axis is the rotation speed of the gear.

Since the sun gear 25 is proportional to the rotation speed of the take-up reel 15, the rotation speed gradually decreases as the tape moves from the winding start to the winding end, and the control member 29 is pressed against the outer circumference. The rotation speed of the internal gear 27 increases. Further, since the link 23 is driven by the DD motor 19, it is constantly rotating. Where the value of n is greater than -1 and z2 / z1 = 0.35
Although a smaller value may be taken, the rotational speed of the internal gear 27 should be set low in order to minimize the friction loss due to the control member 29. Therefore, at the beginning of winding, n should be set to about -0.9.

Here, the tension t of the tape ejected from the second capstan, which is obtained by the winding tension control mechanism of this apparatus, is obtained.

In FIG. 10, tensions t and t '
The force F applied to the tension post by

[0058]

[Formula 19]

It is represented by Here, the traveling loss of the tape guide post, the shaft loss, and the transmission loss of the gear are ignored. That is, t = t '.

From the balance condition of the moment applied to the tension arm,

[0061]

[Equation 20]

Is required. Here, f is the force with which the control member 29 is pressed against the outer periphery of the internal gear 27, b is the distance between the center of the rotation axis of the tension arm and the point of action of f, P is the spring force of the tension spring, and c is the tension arm. The distance between the center of the rotation axis and the point of action of P, a is the distance between the tension post and the center of the rotation axis of the tension arm. (Equation 20)
For f,

[0063]

[Equation 21]

To obtain Substituting (Equation 19) into (Equation 21),

[0065]

[Equation 22]

It becomes The torque Φ ₁ acting on the internal gear 27 by this f is

[0067]

[Equation 23]

It becomes Here, e is the radius of the outer peripheral drum portion of the internal gear 27, and μ is the friction coefficient of the control member 29. The relationship of forces acting on the planetary gear 24 is shown in FIG. The torque Φ ₂ applied to the sun gear 25 is equal to the sum of the force applied to the teeth engaged with the internal gear 27 and the force applied to the teeth engaged with the sun gear 25.

[0069]

[Equation 24]

It becomes Take-up reel 15 from sun gear 25
Up to ξ, the winding diameter of the take-up reel 15 is r
And The rotation torque applied to the take-up reel is the sun gear 25.
Since the value obtained by multiplying the rotation torque Φ ₂ of

[0071]

[Equation 25]

The following relationship is obtained. Substituting (Equation 22) into (Equation 25),

[0073]

[Equation 26]

Organizing (Equation 26) for t,

[0075]

[Equation 27]

It becomes In order to obtain controllability of the winding tension, the winding radius at the tape start end of the winding reel 15 is set to r.
_S, t _s / t _e the winding radius at the end of the tape as r _e is,

[0077]

[Equation 28]

It becomes Next, the internal gear 27 and the sun gear 2
5, the rotational speeds ω ₁ , ω ₂ , ω _r of the link 23 will be obtained.

The rotation speed ω ₂ of the sun gear 25 is

[0080]

[Equation 29]

Is given by where V is the tape speed. From FIG. 13, the rotational speed ω ₁ of the internal gear 27 and the rotational speed ω _r of the link 23 are

[0082]

[Equation 30]

It is Substituting (Equation 28) into (Equation 30),

[0084]

[Equation 31]

Is given by Therefore, if the reduction ratio ξ ′ from the DD motor 19 to the link 23 is the rotation speed of the DD motor 19,

[0086]

[Equation 32]

And the diameter of the first capstan 12 is d0,

[0088]

[Expression 33]

Is given by

FIG. 12 shows the tape winding radius of the T-side reel and t.
6 is a graph showing a result of calculating a DD motor load.

The tape tension t set in FIG. 12 is maintained at about 30 gr, and the capstan load increases as the winding radius of the take-up reel 15 increases.
When the tape tension t is set to be constant regardless of the winding diameter of the take-up reel 15, it has been customary to use a reel drive-dedicated motor, but in terms of cost and power consumption. However, it was not a good idea because it had no big merit. Further, when the clutch torque generated in the reel drive gear 217 in the prior art (FIG. 15) is mechanically controlled by a tension arm and a braking member (not shown) so that the winding tape tension becomes constant, The initial setting of the clutch torque must be increased by the loss of the braking member. As a result, the load torque of the capstan motor increases. Therefore, it can be said that the method of the present invention is effective in terms of both low power consumption and low cost.

Next, the rewinding (REW, REV) operation will be described. When the device switches to REW mode, D
The D motor 19 reverses, and the spring 36 in FIG.
Due to the friction torque between the link 23 and the idler arm 35, the idler arm 35 starts rotating counterclockwise. As a result, the gear portion of the relay pulley 21 and the gear portion of the idler arm 35, which have not been in mesh with each other, start to mesh with each other. At this point, the DD motor 19 directly drives the idler arm 35. The idler arm 35 further rotates, and the idler arm 35
The reversing gear meshing with
At the same time, the reversing lever 50 also swings clockwise, and the main rod 48 moves to the right. Therefore, the one end 48b of the main rod 48 acts on the winding tension arm 32, and the winding tension arm 32 and the braking arm 28 are separated from each other. Further, the supply tension spring 44 is in a relaxed state in which the spring force does not act on the supply tension arm 41 because the supply tension spring attachment portion 48c of the main rod 48 moves to the right. Then, the claw portion 48d of the main rod 48 fixes the clutch plate 46, and generates a rotational load of the take-up reel 15 in REW. When the main rod 48 has finished moving to the right, the gear portion of the relay pulley is located in the second missing portion 35c of the gear of the idler arm 35, and the idler arm 35 meshes with the supply reel base 37 for the REW operation. Due to the tension of the magnetic tape 3 wound by the supply reel 2, the supply-side tension post 39 rotates clockwise about the rotation shaft 43.
The braking arm 28 and the supply tension arm 41 are connected by a connecting rod 59, and the pressure of the braking member 29 of the braking arm 28 is lowered if the winding tension at the time of REW is increased, and as a result, the winding of the supply reel stand 37 is performed. The torque decreases and the tension of the magnetic tape 3 decreases. Thus, the winding tension at the time of REW is kept almost constant. Conventionally, winding with REV has been performed by a clutch mechanism, so that the winding tension greatly changes depending on the winding diameter of the magnetic tape 3 of the supply reel 2. For this reason, there is a risk that the tape tension is large near the end of the tape having a low tension and the tape is damaged, and it is necessary to suppress the clutch torque for the REV.
On the contrary, there is a problem that it is difficult to set the clutch torque because the tape tension becomes low near the tape start end and the reproduction output at REV decreases. It is effective as a solution to this problem. In this embodiment, REV and RE
Although the configuration has been shown in which the supply tension spring is loosened at the time of W, the tape tension in the vicinity of the supply side tension post 39 during normal reverse traveling is higher than when the tape is traveling in the forward direction. Therefore, the supply side tension arm 41 is rotated clockwise even when the supply tension spring 44 is applied by the tape tension in the reverse running. As a result, the tension band 45 is released, and it is not always necessary to loosen the supply tension spring 44.

Next, the operation of pulling out the roller 14 will be described with reference to FIG. In FIG. 7, the roller 14 is pulled out from the cassette 1 and is sandwiched between the first capstan 12 and the second capstan 13 to have the positional relationship shown in FIG. At this time, in order to allow the roller 14 to pass through between the capstans slightly narrower than the diameter of the roller itself, FIG.
As shown in FIG. 8, the second capstan holder 53 holding the second capstan 13 is rotated to shift from the state of FIG. 8B to the state of FIG. 8A.

[0094]

The present invention as described above, according to the present invention can maintain a tape winding tension of record reproduction apparatus substantially constant, a significant cost reduction without requiring DC motor and its control circuit to the winding mechanism realizable. Furthermore, the power consumption of the DD motor can be reduced as compared with the conventional clutch system that generates a constant winding torque.

The present invention also includes a first capstan,
A second capstan provided in parallel with the first capstan, a moving means for moving the second capstan at the time of loading, and a tape passing through between the first and second capstans at the time of loading. Although it is wound around the first and second capstans, and is used for a recording / reproducing device such as a video tape recorder provided with a roller that is sandwiched between the first and second capstans after the loading is completed, a great cost reduction effect is brought about. Also in the conventional recording / reproducing apparatus, since the winding tension of the supply-side reel in the REV (REW) mode can be kept substantially constant, there is an effect that reliability against tape damage is significantly improved.

[Brief description of drawings]

FIG. 1 is a plan view of a magnetic recording / reproducing apparatus according to an embodiment of the present invention.

FIG. 2 is a plan view of a winding tension control mechanism of the magnetic recording / reproducing apparatus in the embodiment.

FIG. 3 is a side view of a winding tension control mechanism in the same embodiment.

FIG. 4 is a plan view of a main part of the idler arm mechanism in the embodiment.

FIG. 5 is a perspective view of an essential part of the idler arm mechanism in the embodiment.

FIG. 6 is a perspective view of a tape drive device including first and second capstans according to the embodiment.

FIG. 7 is a side view of the tape drive mechanism including the first and second capstans according to the embodiment.

FIG. 8 is a schematic view of the tape loading operation by the rollers of the tape drive mechanism by the first and second capstans in the same embodiment.

FIG. 9 is a cross-sectional configuration diagram of a roller arm in the example.

FIG. 10 is an operation explanatory view of the winding tension control mechanism in the embodiment.

FIG. 11 is an operation explanatory view of the winding tension control mechanism in the embodiment.

FIG. 12 is a characteristic diagram showing control characteristics by the winding tension control mechanism in the example.

FIG. 13 is a schematic diagram showing the rotation speed of each gear of the planetary gear mechanism in the winding tension control mechanism in the embodiment.

FIG. 14 is a characteristic diagram showing changes in the number of rotations of each gear in the embodiment.

FIG. 15 is a plan view of a conventional magnetic recording / reproducing apparatus.

[Explanation of symbols]

12 First Capstan 13 Second Capstan 14 roller 24 planetary gears 25 sun gear 27 Internal gear 28 Braking arm 29 Control member 30 spring 31 Winding side tension post 32 Winding side tension arm

Claims (2)

(57) [Claims] 1. A supply reel and a winding device around which a tape is wound.
Reel, sun gear and front driven by the sun gear
Selectively drive the supply reel and the take-up reel
An idler gear, a planetary gear that revolves while meshing around the sun gear, an internal gear that meshes with the planetary gear and has the same rotation center as the sun gear, and a rotation center of the sun gear that rotatably holds the planetary gear. A rotatably provided link, a capstan that rotates at a predetermined rotation speed, a first transmission mechanism that transmits the rotation of the capstan to the link, and a braking that applies a braking force to the rotation of the internal gear. an arm, may vary according to the take-up tensioning arm having a predetermined angle component wound around the tension post in the tape to detect the tape tension, the braking force acting on the internal gear by the force applied to the take-up tension arm brake A member, a second transmission mechanism for transmitting the rotation output of the sun gear to the take-up reel, and detecting the tape tension.
A tension post that wraps around the tape at a specified angle
Supply side tenn which rotates with the change of tape tension
Of the supply arm and the tension arm on the supply side
And a connecting rod for transmitting the work to the braking arm, and a tensioner for winding the tape on the take-up reel.
Control of the winding side tension arm and the braking arm.
The braking force of the braking member can be varied by
Tension control when winding on the supply side reel
Is the front side of the supply side tension arm, the connecting rod, and
The winding tension control device, wherein the braking force of the braking member is varied by the braking arm . 2. A tape-wound supply reel and winding device.
Reel, sun gear and front driven by the sun gear
Selectively drive the supply reel and the take-up reel
An idler gear, a planetary gear that revolves while meshing around the sun gear, an internal gear that meshes with the planetary gear and has the same rotation center as the sun gear, and a rotation center of the sun gear that rotatably holds the planetary gear. A rotatably provided link, a capstan that rotates at a predetermined rotation speed, a first transmission mechanism that transmits the rotation of the capstan to the link, and a braking that applies a braking force to the rotation of the internal gear. An arm , a supply-side tension arm having a supply-side tension post wound around the tape by a predetermined angle to detect the tape tension of the tape ejected from the supply reel when the tape is run in the forward direction, and the supply-side tension arm. And a tension band that applies frictional torque to the supply reel base by attaching one end to the supply reel base, A supply tension spring that is attached to the side tension arm and applies a tension to the tension band; and a braking member that varies the braking force that acts on the internal gear by the force applied to the supply side tension arm when the tape runs in the opposite direction, A tape tension is applied to the third transmission mechanism that transmits the rotation output of the sun gear to the supply reel.
The tension port that wraps around the tape at a specified angle to be detected.
Supply that has a strike and rotates as the tape tension changes
Side tension arm and the supply side tension arm
And a connecting rod for transmitting the turning motion to the braking arm.
The tension of the tape when it is wound on the take-up reel.
Control of the winding side tension arm and the braking arm.
The braking force of the braking member can be varied by
Tension control when winding on the supply side reel
Is the front side of the supply side tension arm, the connecting rod, and
The winding tension control device, wherein the braking force of the braking member is varied by the braking arm .