JPS63225951A - Power transmission switching mechanism for magnetic recording and reproducing device - Google Patents

Abstract

PURPOSE:To stably feed a tape by preventing disturbance from being given on a capstan at the time of reproduction, by engaging and disengaging the power of the capstan with a reel driving and transmitting system by synchronizing with the attaching/detaching operation of a pinch roller to the capstan by mode switching. CONSTITUTION:In a state where a cam ring 38 is turned in a clockwise direction and a mode is changed from a loading stop mode to a reproducing mode, a pinch roller operating lever 96 is turned in a direction of H, and thereby, the pinch roller 15 is pressurized contact with the capstan 14. By the turning of an FR lever 162 in a direction of arrow head A162 synchronizing with the pressurized contact of the pinch roller 15, an FR intermediate gear 109 is separated from both a capstan gear 108 and FR power transmission system gear strings 171-175 synchronizing with the pressurized contact of the pinch roller 15. At this time, since a device is constituted so that the pinch roller 15 can be pressurized contact with the capstan 14 after the FR intermediate gear 109 is separated, no disturbance is transmitted to the capstan at the time of feeding the tape.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a tape drive mechanism of a magnetic recording/reproducing device, and more particularly to a power transmission switching mechanism for reducing disturbances applied to a capstan.

[Conventional technology]

Conventionally, the reel drive of a magnetic recording and reproducing device has been carried out by means of transmitting power from a capstan motor via gears or belts, by means of directly installing a motor on the shaft of the reel (D, D, etc.), and by means of driving the reel separately. There was a means to install a motor for this purpose. Among these, when a capstan motor is used as the drive source, the load of driving the reel is applied to the capstan, and stable running of the tape is inhibited. In the DD method and the reel motor, no load is applied to the capstan, but high torque is required to drive the reel at high speed, and the weight of the motor increases. On the other hand, as described in Japanese Utility Model Application Publication No. 59-17053, there is a method in which an IJ motor is used to drive the reel only when the magnetic tape is running at low speed, and a capstan is used as the drive source to drive the reel when the tape is running at high speed.

[Problem that the invention seeks to solve]

However, in this method of switching the drive source, even when the capstan drives the tape, the power transmission system for driving the reel with the capstan is connected to the capstan, which causes disturbance to the capstan. It is the basis.

SUMMARY OF THE INVENTION An object of the present invention is to provide a power transmission switching mechanism that prevents the capstan from being subjected to disturbances generated by the power transmission system during recording and playback, and allows the tape to run stably. .

Means for Solving the Problem] In order to achieve the above object, the present invention synchronizes the operation of attaching and detaching the pinch roller to and from the capstan, which is operated in response to switching of the operation mode, to increase the power of the capstan. It is configured to engage or disengage from the reel drive transmission system.

[Effect]

During recording, playback, fast-forward playback, and reverse playback, the tape is transported while being held between a capstan and a pinch roller. Therefore, the reel winding torque can be small, and a low torque motor can be used as the reel motor. On the other hand, during fast forwarding and rewinding, the pinch roller separates from the capstan and the tape is wound onto a reel using the high torque capstan motor as the drive source. With this method, there is no need to apply a load to one capstan for driving the reel during recording and reproduction, and a small, low-torque motor can be used as the reel motor. However, if the power transmission system for driving the reel with the capstan is engaged with the capstan during recording and reproduction, disturbances will be applied to the capstan from this power transmission system.

Therefore, since the capstan and pinch roller drive the reel only when the tape is not being transferred, the power transmission system for driving the capstan and reel is engaged or By releasing it, it is possible to reduce disturbances applied to the capstan during recording and playback with a simple configuration.

〔Example〕

Embodiments of the present invention will be described below with reference to the drawings.

Figure ti41 is a plan view showing the whole of an embodiment of the present invention.

This figure shows the state of the unloading dust tube in which the magnetic tape cartridge 77 indicated by the dashed line in the figure is attached to the apparatus. Inside this magnetic tape cartridge 77, there is a winding (T) and a supply (S) in which the magnetic tape 3 is wound.
) Reels 5 and 6 are housed, and are mounted and engaged with reel stands rotatably supported on the chassis 1, respectively.

Further, on the disk-shaped chassis 1, a cylindrical rotating cylinder 2 on which a plurality of magnetic heads are mounted, a loading ring 10, a capstan 14, a tension pin 16-1.
Components such as the correction guide pin 82-a, the pinch roller 15, the guide rollers 7, 8, 9, 11, and the loading mode motor 27 are arranged as shown in the figure.

In this state, the arrow A of the loading ring 10
a guide roller group 7 that moves by rotation in the 1° direction;
8 and 9 and the guide roller 11 engaged with the tip of the guide arm 12 pulls out the magnetic tape 3 stretched over the front surface of the magnetic tape cartridge 77 and wraps it around the rotary cylinder 2 at a predetermined angle, as shown in Figure 2. Form the tape running path as shown in .

The device is operated while this travel path is maintained.

The operation of this device will be described in detail below.

FIG. 83 is a developed view showing the attachment relationship between the chassis 1 and rings that control the main operations of this magnetic recording/reproducing device.

Drive ring 32, cam ring A, loading ring 1
Among the three types of rings 0, cam ring ah, chassis 1
The drive ring 32 is mounted above it and parallel to the upper surface of the chassis 1, respectively, while the loading ring 1o is mounted obliquely to the chassis 1 from above the drive ring 32. It can be installed in the same position.

These rings are held by two-stage ring holders 33-a and 33-b rotatably supported on the side of the chassis l for the drive ring 32 and cam ring A.
, 34-a , 34-b , 35-a , 35-b
Loading ring 1
Regarding 0, the L-IJ Songruda 17 shown in FIG.
, 18 and 19 at the inner periphery of the ring.

These three types of rings are the loading mode motor 2
7. That is, the ring drive mechanism of this device is: (1) Loading mode motor 27 (hereinafter referred to as LM motor).

■A reduction gear train that transmits the driving force of the LM motor n to the drive ring 32.

■A transmission gear train that transmits the rotation of the drive ring 32 to the loading ring 10.

■Transmission gear train that transmits the rotation of the drive ring 32 to the cam ring A.

It is made up of. Note that (2) and (2) are equipped with a switching mechanism using a Geneva gear, and are structured to cut off the transmission of force when the rotational force of the drive ring 32 is not required.

Each ring is rotated by this ring drive mechanism,
The O-ding ring 10 performs the loading operation of winding the magnetic tape 3 around the rotating cylinder 2.
A mode shifting action is performed in which a mechanical element such as a brake is operated using the uneven surface (cam surface) provided on the inner periphery.

Incidentally, in order to perform this loading operation, boats 29 and 30 each having a guide roller 7.8° 9 mounted thereon are placed on the loading ring 10.

In addition, in order to detect the rotation angle of the cam ring during the mode transition operation, two conductive patterns 38-b and 38-c (one continuous and one intermittent) are arranged in a concentric arc shape on the upper part of the cam ring. A brush 32 is printed on the lower surface of the drive ring 32 to short-circuit the two patterns.
-b is attached.

Of these two patterns, the continuous one 38-b is connected to the ground of the system control circuit, and the discontinuous one 38-C is connected to the mode detection terminal of the circuit.

As will be described later, the rotation directions of the drive ring 32 and the cam ring 38 are reversed, so that the drive ring 32 and the cam ring 38 are
By changing the relative angular relationship of the cam ring 38, the brush 32-b and the pattern z-b.

As the positional relationship of C changes, different parts of the intermittent pattern N-0 are shorted to ground, and the system control circuit detects the angular relationship between the two connections to obtain the desired mode transition position.

The ring drive mechanism, loading mechanism, and mode operation mechanism outlined above will be described in detail below.

FIG. 4 is a perspective view showing a deceleration mechanism for transmitting the driving force of the LM motor 27 to the drive ring 32.

LM fixed to the side wall of the LM motor holder 47 with screws
An LM motor gear 50 is press-fitted into the end of the rotating shaft of the motor 27. Further, a transmission gear 39 is meshed with the LM motor gear 50, and a worm 40 is press-fitted into the other part of the rotating shaft 53 into which the transmission gear 39 is press-fitted, and is rotatably attached to the LM motor holder 47. Retained.

Furthermore, the LM motor holder 47 has shafts 42 , 44 , 4
6 , 51 , 52 are press-fitted from above, and reduction gears 41 , 43 , 4 having a two-stage structure are attached to each shaft.
5 and a single-piece transmission gear 49 are rotatably supported.

The upper stage 41-a of the reduction gear 41 is a worm wheel that meshes with the worm 40, and the lower stage 41-b (!
: The upper stage 43-a of the reduction gear, the lower stage 43-b thereof, and the upper stage 45-a of the reduction gear 45 are in mesh with each other, and the lower stage 45-b is the drive gear 5 that drives the drive ring 32.
It meshes with the upper row of 4. Therefore, when the LM motor gear 50 press-fitted into the LM motor 27 rotates in the direction of the arrow Aso, the transmission gear 39, worm 40, and reduction gears 41, 43, and 45 that are continuously meshed also move in the direction of the arrow Ass+A4c1+A41, respectively. * A4s * A
41 direction, and rotates the drive gear 54 in the arrow A direction.

Conversely, as the LM motor gear 50 rotates in the direction of arrow B9, each gear also rotates in the direction of arrow Baa 5B40.
B41 * B43 # Rotates in the direction of B45, and rotates the drive gear 54' in the direction of the arrow axis.

The transmission gears 48 and 49 have the role of transmitting the rotation of the first switching gear 55 to the loading ring 10, as will be explained later.

FIG. 5 shows the loading ring 1 from the drive ring 32.
FIG. 2 is a plan view showing a power transmission mechanism from the cam ring A to the cam ring A.

On both sides of the gear portion 32-a of the drive ring 32, there are fan-shaped W41 and jJ120 plate plates 5 having a predetermined thickness.
8 and 59 are attached and fixed from the upper surface of the ring 32.

The radius of curvature of the inner circumferential surfaces of the first and 20th catch plates 58 and 59 is set to be approximately equal to the radius of curvature of the addendum circle of the gear portion 32-a of the drive ring 32.

In addition, the inner circumferential surface of the mounting portion of the first and 20th pick plates 58 and 59 in the drive ring 32 is further outer circumferential than the bottom circle of the gear portion 32-a, as shown by the broken line in FIG. It is in a state of running away.

The end faces of the tenth pick plate 58 and the twentieth pick plate 59 near the gear portion 32-a are chamfered as shown. The shape of this chamfered part is
It has an involute shape similar to the tooth surface forming 32-a.

That is, the continuous tooth surfaces of the gear portion 32-a of the drive ring 32 are set so as to be connected at their ends to the end surfaces of the lock plates 58 and 59 diagonally upward in the same tooth surface shape.

Further, the lower gear 54-b of the drive gear 54 meshes with the gear portion 32-a of the drive ring 32.

Due to this meshing, the driving force of the LM motor 27 is transmitted to the drive ring 32.

FIG. 6 is an exploded perspective view showing the structure of the first switching gear 55. As shown in the figure, the first switching gear 55 connects the first switching plate 55-b to the two gears 55-a and 55-c.
It has a three-layer structure that is sandwiched between.

After the holes of the three gears are aligned, the pin 62
are press-fitted to keep their phase relationship fixed. As shown in FIG. 5, it is rotatably supported by a shaft mark press-fitted into the chassis l.

FIG. 7 shows this first switching gear 55 and the drive ring 32,
FIG. 3 is a cross-sectional view showing the height relationship of the cam ring.

Since the first switching gear 55 is placed on the boss part on the chassis 1, it is located above the cam ring and does not come into contact with the rest of the cam ring. They mesh with gear 55-C.

In addition, the first switching plate 5 at the middle stage of the first switching gear 55
5-b is attached at a height that substantially opposes the inner circumferential surface of the tenth hook plate 58, which is indicated by a broken line in the figure.

The outer circumferential surface of the first switching plate 55-b has two cylindrical surfaces, a large diameter portion and a small diameter portion, the large diameter portion being the tip circle of the lower gear 55-C, and the small diameter portion being Each radius is set to approximately match the tooth root circle.

The upper gear 55-a of the first switching gear 55 is
It meshes with the transmission gears 48, 49 and the loading ring 10 described in FIG. 4.5.

FIG. 8 is an exploded perspective view showing the structure of the second switching gear 56.

The second switching gear 56 also has a second switching gear similar to the first switching gear 55.
It has a three-layer structure including one switching play) 56-a and gears 56-b and 56-C.

However, in this case, the E2 switching plate 56-a is located at the top of the second switching gear 56.

Similar to the case of the first switching gear 55, the phase relationship between the three gears is fixed and maintained by aligning the holes and then press-fitting the pins 63 through them.

Also, the radius of the large diameter portion of the outer circumferential portion of the second switching play 56-a substantially matches the tip circle of the middle gear 56-b, and the radius of the small diameter portion substantially matches the bottom circle of the gear 56-b. It is set.

FIG. 9 shows this second switching gear 56 and the drive ring 32.
, is a sectional view showing the height relationship of the cam ring 38.

The middle gear 56-b of the second switching gear 56 is at a height that meshes with the gear portion 32-a of the drive ring 32, as shown by the broken line.

Therefore, the upper second switching plate 56-a is located at a height that substantially opposes the inner peripheral side surface of the lock plate 59 on the drive ring 32.

Further, the lower gear 56-c is located between the drive ring 327 and the cam ring 37, and meshes with the cam drive gear 57 shown in FIG.

The end surfaces connecting the large diameter portion and the small diameter portion of the outer periphery of the switching plates 55-b and 56-a in the first switching gear 55 and the second switching gear 56 described above are in contact with the tooth surface of the gear 55-c 156b, respectively. It has an equivalent involute curve, and by press-fitting pin 62 or 63,
When fixing and maintaining the mutual phase relationship, the end face and the tooth surface are set so as to coincide with each other in a plane.

FIG. 10 shows the positional relationship between the cam drive gear 57 that meshes with the second switching gear 56 and the cam ring at the lower part of the drive ring 32. As shown in the figure, the cam drive gear 57 is disposed so as to mesh with a gear portion 3B-a provided on a part of the inner circumferential surface of the cam ring blade in plan view.

Further, the upper surface of the cam drive gear 57 is at a height indicated by the dashed line in FIG. 9, and is located at a height where it does not come into contact with the drive ring 32.

Due to this arrangement, when the second switching gear 56 is rotated by the drive ring 32, the cam ring is rotated via the cam drive gear 57.

Figure 11 shows the L
FIG. 3 is a plan view showing a connected state of a reduction gear train from the M motor 27 to the drive ring 32 and a transmission gear train from the drive ring 32 to the loading ring 10 and the guide arm 12.

Arrow A of the LM motor gear (capital) shown in Figure 4! By rotation in the o direction, the worm 40. Reduction gear 41, 4
4゜45, 54 are arrows ~5A4 in Fig. 11, respectively.
1 #A44 +A41- Rotate in the Asa direction.

The drive ring 32 is connected to the lower stage 54- of the reduction gear 54.
b is driven in the direction of arrow A5. Due to this rotation, the first
The upper gear 55-a is rotated in the direction of arrow A65 through the lower gear 55-c of the switching gear 55, and the transmission gear 49 on the I and M motor holder 47 that meshes with it is rotated in the direction of arrow A65. Rotate the loading ring 10 in the direction of the arrow. Rotate in the direction.

Next, the operation of the transmission gear train arranged in the lower part of this figure will be explained with reference to a half-sectional view (FIG. 12) seen from the right side.

In FIGS. 11 and 12, the connecting gear 62 is connected to the chassis 1.
The lower gear 62-a is rotatably supported by a shaft 65 press-fitted from above, and the lower gear 62-a is connected to the lower stage 55-c of the first switching gear 55, and the upper gear 62-b is connected to the upper stage 61-a of the second gear 61. They mesh with each other.

The gears 61, 63, and 64 are rotatably supported by shafts 66, 67, and 68, which are press-fitted from below into a gear holder 69 that is screwed to the side surface of the chassis 1, and are engaged with stops from below. Rings 70, 71, 7
2, it is axially positioned.

Further, the boss portion 13-c of the pinch roller arm 13 is held between the rotation center portion of the guide arm 1-2 having a U-shaped cross section via spacers 73 and 74, and is held by the shaft 22 on the chassis 1. The guide arm 12 and the sector gear 4 are rotatably supported.

As shown in FIG. 11, a pin 75 is press-fitted into the projection 13-a of the pinch roller arm 13 with a portion thereof protruding upward from the chassis, and this pin 75 is connected to the side surface of the fan-shaped gear. are in contact.

In Figure 11, 76 is the pinch roller arm 13.
It is a torsion spring mounted on the cylindrical surface of the outer periphery of the boss 13-c with a margin, and its one end 76-a is latched to the protrusion 13-a of the pinch roller arm 13 described above,
The other end 76-b is locked to the connecting portion 12-a having a U-shaped cross section of the guide arm 12, and the pinch roller arm 1
The connecting portion 12- of the protrusion 13-a of No. 3 and the guide arm 12
a and are urged in the direction of separating them from each other.

Due to the above-mentioned connected state, when the drive ring 32 is rotated in the force direction of arrow A, the gears 62-a, 62-b, 6 are connected via the lower gear 55-c of the first switching gear 55.
1-a, 61-b, 63-a, 63
-b, are arrows respectively) -tn, A4t, A
It is rotated in the n direction, and the fan-shaped gear aha, the arrow person 1. rotated in the direction. As a result, the pin 75 on the pinch roller arm 13 is pressed by the side surface of the fan-shaped gear 4, and the pinch roller arm 13 is rotated in the direction of arrow Al11. Through the force, the guide arm 12 is rotated in the direction of arrow All.

In this way, the rotation of the LM motor 27 is transmitted via the drive ring 32 to the loading ring 101. A loading operation is performed by being transmitted to the guide arm 12.

Next, this operation will be explained in detail using FIG. 13 to FIG.

In Figure m13, pins 10-a and 10-b are press-fitted onto the loading ring 10. These pins have Ml Funa 4 and No. 2 Funa 30 in their respective elongated holes.
They are engaged with a predetermined gap.

In addition, the first boat 29 placed on the loading ring 10 as described above. Protrusions 29-d and 30-b on the second boat 30
and a protrusion 10- fixed on the O-ding ring 10.
Springs 10-c and 10-d are independently suspended between the springs 10-e and 10-f, respectively, and regulate the positions of the boats 29° and 30 relative to the loading ring 10.

Since the loading ring 10 and the boats 29 and 30 have such a mounting relationship, the loading ring 10 is
By being rotated from the state shown in FIG. 1 in the direction of arrow A1 as described above, the first boat 29. The second boat 30 also moves in the same manner. Through this operation, the magnetic tape 3 changes from a state where it is stretched over the front surface of the cassette cartridge 77 to a state where it is gradually wound around the rotating cylinder 2 as shown in FIG.

FIG. 14 is a plan view from above the chassis 1 showing the state in which the first boat 29 enters and is in contact with the first catcher 20 due to the rotation of the loading ring 10, and FIG. 15 shows this in white. It is a side view seen from the direction of the blank arrow. A positioning pin 29-a is press-fitted into the first boat 29, and when it approaches the first catcher 2o, the U
The traveling direction is corrected along the V-shaped groove 20-a, the V-shaped groove 20-b, and the U-shaped groove 20-c. At the same time, the upper surface 29-c of the tip of the first boat 29
It makes contact with the lower surface 20-d of the catcher 2o, and the forward and backward inclination of the first boat 4 is also corrected. Even after the above-described horizontal and vertical position correction and positioning, the loading ring 10 continues to rotate and the spring 10-c
A predetermined elongation is applied to the first catcher 20 to generate a predetermined pressing force against the first catcher 20.

In FIGS. 16 and 17, similarly to the above, the second boat 30 is loaded with #! by the loading ring 10. 18 and 19 are a plan view and a side view showing a state in which the catcher 21 is rotated in the direction of the catcher 21 and a side view seen from the direction of the white arrow; FIGS. .

By driving the loading ring 10, the second boat 30 approaches the @2 catcher 21, and the pin 30-a on the motherboard passes through the path shown by the broken line into the groove 21 of the second catcher 21.
-b, and the direction of movement is corrected toward the V-shaped notch 21-a above the groove 21-b.

Then, as shown in Figure jJL18.19, pin 30-a
is in contact with the V-shaped notch 21-a, and the second boat 30
Even after the bottom surface of the second catcher 21 comes into contact with the surface 21-c of the second catcher 21, the loading ring 1O continues to move in the direction of the arrow. direction to stretch the spring 10-d by a predetermined amount.

As a result, the second boat 30 is pressed against the second catcher 21, and its plane coordinates and vertical tilt state are determined.

20 and 21 show the guide arm 12 rotated by the drive ring 32 in conjunction with the loading ring 10.
and the positional relationship of the m3 catcher 31.

A lever 79 that engages with the third lever 25 is connected to the tip of the guide arm 12 in a state where it is biased counterclockwise by a torsion spring 78.

The lever 79 is provided with a claw-like projection 79-a,
It is adapted to engage with the side wall of the guide 81. The side wall of the guide 81 extends linearly toward the third catcher 31, and regulates the posture of the lever 79 and the third boat 25 during the loading operation.

Due to the rotation of the guide arm 12, the third boat 25 comes into contact with the third catcher 31. FIG. 22 and FIG. n show this state. The contact points at this time are the pin 25-a and the 7-shaped notch 31-a. The lower surface 25-b of the boat is in contact with a locally protruding surface 81-a at the tip of the guide 81.

Even after this contact, the fan-shaped gear 4 shown in FIG. position.

FIG. 24 is a plan view showing the arrangement relationship of the tension arm 16 and the correction guide arm 82 in the unloading state shown in FIG. 1.

Both the tension arm 16 and the correction guide arm 82 are rotatably supported by shaft blades press-fitted onto the chassis l. In this state, the tension pin 16-8 is press-fitted into the tips of the tension arm 16 and the correction guide arm 82.

The correction guide pin 82-a is attached to the magnetic tape cartridge 7.
The magnetic tape 3 is housed behind the magnetic tape 3 stretched over the opening 7.

Notch 1 provided at one end of this tension arm 16
A spring is stretched between 6-I-b and the shaft 84 press-fitted onto the chassis 1, and the tension arm 16 is biased in the direction of arrow A16.

Also, a protrusion 82-b provided on the correction guide arm 82
A spring is stretched between the projection 87 and the projection 87 provided on the outer peripheral side surface of the chassis l, and the correction guide arm 82 is biased in the direction of the arrow 13at.

A protrusion 82 - c is provided near the tip of the correction guide arm 82 and abuts against the side surface of the tension arm 16 .

Therefore, the tension arm 16 due to the spring 85
Rotation of is prevented by a correction guide arm 82 and a spring.

Further, the other end of a band brake 86 whose one end is fixed onto the chassis 1 with a screw 89 is locked to the projection 16-c of the tension arm 16.

In the unloading state, the band brake 86 is mounted on the S reel stand 37 in a relaxed state as shown in the figure.

In addition, the ends of these arms W16-b, 82-
d and springs 85 and 88 are located sufficiently above the drive ring 32, as shown in the side view of FIG.
There is no need to worry about contact with the drive ring 32.

During the transition from the unloading state to the loading state, the drive ring 32 moves as described above to the arrow head 8. When the drive ring 32 is rotated in the direction, the protrusion 32-b provided on the drive ring 32 comes into contact with the end 82-d of the pull-out arm 82, and resists the reaction force of the spring wing to move the correction guide arm 82. arrow As.

Rotate in the direction. When the rotation angle exceeds a certain value, the point of action of the force of the spring wing moves to the left with respect to the straight line connecting the shaft 83 and the protrusion 87 on the side surface of the chassis 1. For this reason, the correction guide arm 82 is moved by the spring wing to the direction indicated by the arrow A6, which is opposite to the unloading state. direction.

FIG. 25 shows the arrangement of the tension arm 16 and the correction guide arm 82 at the time when the above loading operation is completed.

Correction guide arm 8 biased by spring wings and 85
2. The tension arm 16 presses the magnetic tape 3 from the base side to form a predetermined tape running path at the cartridge exit. At this time, the correction guide arm 82 is
The side surface 150-a of the guide plate 150 comes into contact with the guide plate 150 to define the plane position.

Further, since the protrusion 16-c on the tension arm 16 is also rotated in the direction of the arrow Al11, the band brake field contacts the 31J-ru base 37 with a predetermined tension.

As a result, a predetermined braking torque is generated in the 191J-ru base 37, and an appropriate tension is applied to the magnetic tape 3 pulled out from the 31J-ru 6 during recording and reproduction.

When performing an unloading operation from this loading completed state, first, the protrusion 32-b on the drive ring 32, which is rotated in the direction of arrow B,
The correction guide arm 82 is rotated in the direction of the arrow 13at against the biasing force of the spring wing. Then, the tension arm 16 is also pressed by the projection 82-C on the correction guide arm 82, and the arrow Bta
rotated in the direction.゛When the angle of this rotation exceeds a certain value, the correction guide arm 82 is moved by the spring 88 in the direction of arrow B8M, contrary to the loading operation.
direction, and the leading end is returned to the state shown in FIG. 24 in the opening of the magnetic tape cartridge 77.

The tape running path shown in FIG. 2 is formed by the loading operation, crimping, positioning, and snapping operations caused by the rotation of the drive ring 32 described above. Operations such as recording (reproduction), rewinding, and fast forwarding are performed on this tape running path. Next, a mechanism for maintaining this tape running path will be explained.

During the loading period, the drive ring 3 described in FIG.
The tenth pick plate on the top 2 moves in the - arrow A41 direction together with the drive ring 32 and approaches the first switching gear 55. The first switching gear 55 has the three-stage structure explained in FIG. 6, and the middle first switching plate 55-b is located at the height explained in FIG.
During a loading operation in which the gear portion 32-a and the lower gear 55-c are engaged, the gear portion 32-a and the lower gear 55-c are idle above them.

FIG. 27 and FIG. 4 show the drive ring 32 and the tenth hook plate 58 before and after the loading operation is completed,
FIG. 7 is a plan view showing the operational relationship with the first switching plate 55-b.

As explained in FIG. 5, the gear surface of the gear portion 32-a of the drive ring 32 switches to the end surface of the lock plate on the drive ring 32 at both ends thereof. ·For this reason,
Until the ff110 switch plate 58 reaches the first switching gear 55, the lower gear 55-C of the first switching gear 55 meshes with the gear portion 32-a of the drive ring 32, and the first switching gear 55 rotates in the direction of arrow Al15. However, at the terminal end of the gear portion 32-a, the engagement with the lower gear 55-c is released. However, the tooth surface of the end of the lock plate 58 presses the tooth surface of the first switching plate l-55-b, so that the first switching gear 55 is rotated further and then rotated as shown in FIG. state. (Gear part 32-a
At this end, the meshing phase of the gear 55-c and the lock plate 58 (first switching play) 55-b
The tooth surfaces are set so that they engage. ) In this state, the tips of the two tooth surfaces of the first switching plate 55-b are both locked and held by the inner peripheral surface of the lock plate 58.

The three gears and plates that make up the first switching gear 55 have a fixed mutual phase relationship, so when the rotation of the first switching plate 55-b is stopped, the rotation of the gear 55-a is also blocked. The rotation of the transmission gear 49, loading ring 10, and guide arm 12 that mesh with this is also prevented. The timing for locking the first switching gear 55 is such that the first and second boats on the loading ring 10 and the third boat on the guide arm 12 are in the first position. Second. The timing is set to be approximately equal to the timing at which each third catch is pressed with a predetermined force.

With the above switching operation, the first. Second. The positioning of the guide rollers on the third boat is maintained, and the running path of the tape is reliably maintained.

Also, during this loading period, the 20th load plate 59 as well as the 10th load plate 58 is
rotated in the direction. During this period of rotation, the inner circumferential surface of the 20th switch plate 59 is in sliding contact with the ends of the two tooth surfaces of the second switching plate 56-a on the upper stage of the second switching gear.

This second switching gear 56 and the drive ring 32 are connected to the eighth
Since the attachment explained in the figure is in the relationship, during the period when the 20th pick plate 59 is in sliding contact with the second switching plate 56-a, the rotation of the second switching gear 56 is limited as shown in FIG. 29. blocked. Therefore, the cam ring shaft does not rotate during this period.

Then, as described above, the first
After the locking of the switching gear 55 is completed, the gear portion 32-a of the drive ring 32 moving in the direction of arrow A32 and the tooth surface of the end of the 20th lock plate are connected to the second switching gear as shown in FIG. By starting to press the tooth surface of the second switching plate 56-a at the upper stage of 56 and moving further, the gear part 32-
a starts to mesh with the middle gear 56-b of the second switching gear 56, and the lower cam ring 32 of the drive ring 32 starts to rotate via the cam drive gear 57 that meshes with the lower gear 56-c. .

Next, the mode operation performed by the rotation of this cam ring will be explained.

FIG. 31 is a plan view showing the arrangement of the reel stand braking members and driving members before the cam ring blades are rotated. Gears for driving the reel stands 36 and 37 are arranged as shown in the figure, and braking members for braking the reel stands 36 and 37 are provided between the gears and the chassis 1. It is arranged. Also, disposed near the capstan 14 are a pinch roller 15, a pinch roller arm 13, a pinch roller operating lever 96, a pinch roller pressure lever 160° PR lever 162, and the like.

FIG. 32 shows the planar arrangement of the brakes located below the gears. The main brake operating lever 91-
a, s The operating ends of the sub-brake operating arm 92-a1T brake operating arm 94-a1T sub-brake 95 and the pinch roller operating lever % are in contact with each other.

The cam surface provided on the inner circumference of the cam ring is mainly composed of two arcuate surfaces with different radii and a tapered surface connecting them.

By rotating this cam ring, the operated members are attached to the support shafts 9l-392-s press-fitted onto the chassis 1,
It is rotated around 94-s, 95-s, and 96-s, and performs operations such as applying braking torque to the T and S IJ-ru tables 36 and 37, and pressing the pinch roller 15 to the capstan 14. .

Hereinafter, the case where the operating end of the operated member is in contact with a circular arc surface with a small radius such as the cam ring will be referred to as the H position, and the case where it is in contact with a circular arc surface with a large radius will be referred to as the L position.

93 is an idler gear operation slider, and the torsion spring 1
10, the cam ring 38 is urged into contact with the inner circumferential surface of the cam ring 38.

Only the cam surface for operating this idler gear operating slider 93 is constituted by a circular arc surface with three radii, and the idler gear operating slider 93 in contact takes three positions.

These three positions are H, M, and
Hereafter referred to as L.

During the loading operation shown in FIG. 32, the main brake 91 is in a position where it does not come into contact with the reel stands 36 and 37, and only the sub brakes 92 and 95 are
It is in contact with the reel stands 36 and 37. Furthermore, the pinch roller operating lever 96 is in the L position, and the pinch roller 1
5 is separated from the capstan 14.

FIG. 33 shows the idler gear operation slider 93, the idler gear support plate 97 located above it, the idler gear 98, the winding gear 99. FIG. 34 is a plan view showing the arrangement of PR gears, and FIG. 34 is a cross-sectional view thereof. However, this state indicates a state in which the idler gear operation slider 93 is in the H position.

The idler gear operation slider 93 is held by a holder 101 so as to be slidable on the upper surface of the chassis 1 in the direction of the arrow.

At one end of this idler gear operation slider 93, there is a side wall forming a substantially elliptical recess, as shown in the side view.
It protrudes upward from the chassis 1. The idler gear support plate 97 is placed on the upper surface of this protruding part, while the FR gear 100 and the winding gear 99 are mounted above it.
is rotatably arranged around a shaft press-fitted into the chassis 1, so its vertical position is restricted. A boss 102 is caulked in the center of the idler gear support plate 97, and a shaft 103 is passed through and press-fitted into the hole of the boss 102. And the idler gear 98 is the shaft 1
03 in a rotatable state and is pressed against the idler gear support plate 97 by the felt 104, so a predetermined rotational load is applied.

Further, the lower end of the shaft 103, which extends below the idler gear support plate 97 and is press-fitted therein, engages with most of the oval shape of the idler gear operation slider 93. Therefore, as the idler gear operation slider 93 slides to the M and H positions by the cam ring, the shaft 103 is pressed, and the idler gear support plate 97 and the idler gear 98 pivotally supported thereon also move to the L position.
Or move in the direction of H.

When the idler gear support plate 97 moves in the H direction, the tapered portion 97 of the idler gear support plate 97
-a or 97-b is the center shirt of FR Gear 100)
100-s, and the tapered portion 97-a or 97-b
The center shaft 100-s and the semicircular notch 97-C of the idler gear support plate 97 engage with each other. As a result, idler gear 98 and PR gear 100
The idler gear support plate 97 is rotated around the center shaft 3 by the rotation of the PR gear. On the other hand, when moving in the L direction, the center shaft 99-s of the winding gear 99 and the semicircular notch 97-f of the idler gear support plate 97 similarly engage.

As a result, the idler gear 98 and the take-up gear 99 mesh with each other, and the idler gear support plate 97 rotates around the center shaft 99-s. It doesn't mesh with the gear.

From the arrangement shown in Figures 31 and 32, the cam ring 38
When the is rotated in the direction of arrow A411, each input end of the operated members is fast-forwarded and reversed by seven turns during the loading operation period by its cam surface.FF/)l, ew), o-
Dindust Tsubu (stopping while loading),
It is lifted by a predetermined amount corresponding to each mode of recording/playback/fast-forward playback.

The detection of this rotation angle of the cam ring is performed using the print pattern 38-b138- on the cam ring explained in FIG.
Performed by C.

Hereinafter, the state of the operated member and the rotational state of each motor in each mode will be explained.

FIG. 35 shows the arrangement of the operated members when the cam ring is rotated in the direction of arrow A88 from the state during the loading operation period shown in FIGS. 31 and 32 and enters the loading dust knob mode.

Since it is in the loading dust knob mode, only the main brake operating lever 91-a is rotated to the L side, and the brake section at the output end of the main brake operating lever 91-a is rotated to the T position.
, 37 are prevented from rotating.

Further, the idler gear operation slider 93 is in the M position, and the idler gear 98 is in the position of the winding gear 99. It does not mesh with any of the FR gear circles. The pinch roller operating lever 96 is also in the L position, and the pinch roller 15 is connected to the capstan 1.
It is separated from 4.

FIG. 36 shows how the cam ring is moved from the loading dust knob mode shown in FIG. 35 to arrow A8. This shows a state in which the operating arms have entered the recording (playback, fast forward playback) mode by being further rotated in the direction. In FIG. 36, the pinch roller operating lever 96 is rotated in the H direction, and the PR operating lever 96 is rotated in the H direction.
Press 161. As a result, the P control lever A161
The pinch roller crimping lever 1 rotates in the direction of arrow A, 6 degrees around the support shaft 161s, and is engaged by a spring 163.
60 is rotated about the support shaft 160s in the direction of arrow A180. As a result, the pin 77 grafted on the pinch roller arm 13 engages with the groove 160-a of the pinch roller crimping lever 160, and the pinch roller arm 13 is moved around the support shaft 13-8 by the arrow 13. the pinch roller 15 is pressed against the capstan 14. In addition, by rotating the pinch roller pressure bonding lever 160, the PR
The lever 162 is moved around the support shaft 162-3 in synchronization with the pressing of the pinch roller by arrow A16. direction.

All brake operating levers are rotated in the H direction and then turned in the T direction.
, 81J- The engagement with the roll bases 36 and 37 is released. However, the band brake 86 shown in FIG.
A predetermined tension is applied to the tape running in contact with the outer peripheral surface of the IJ-ru table 37.

The idler gear operation slider 93 moves to the L position and the idler gear 98 engages like a winding gear, as shown in FIG. The take-up gear is rotated by the reel motor 105 in the direction of arrow T99. As a result, the idler gear 98 that is caught also gets caught in the gear 106 on the outer periphery of the T I J-ru base 36, and the T I
The J-roll stand 36 is rotated in the direction of arrow T36 to wind up the tape.

On the other hand, as the FR lever 162 rotates in the direction of arrow A162, the support shaft 109 implanted in the PR lever 162
- The F relay gear 109 rotatably attached to the capstan 14 is press-fitted into the capstan 14 and rotates integrally with the capstan gear 108 and the PR power transmission system gear train 171 to 1.
It separates from its partner 75 in synchronization with the pressure of the pinch roller. At this time, the pinch roller 15 is configured to press against the capstan 14 after the FRR coupling gear 109 is separated. As a result, when the tape is transferred by the capstan and the pinch roller, disturbances generated from the rotation of the PRR force transmission system are not transmitted to the capstan, and the tape can be transferred stably. Furthermore, since the pinch roller presses the reel after the capstan stops driving the reel, a sudden increase in tension will not occur and the tape head will not be damaged.

In this state, the capstan 14 and cylinder 2 rotate counterclockwise, thereby running and scanning the tape.

Figure 38 shows that the cam ring 38 has the record shown in Figure 36 (
This shows a state in which the brakes are further rotated in the direction of arrow A38 from the playback, fast-forward playback) mode and enter the rewind playback mode. In FIG. 38, the pinch roller 15 remains pressed against the capstan 14. As for the brake operation levers, the main brake operation lever 91-a and the T-brake 95 remain in the H position, and 8. The T sub-brake operating arms 92-a, 94-a are rotated in the L direction, and the
, S reel stands 36 and 37. As shown in FIG. 39, the idler gear operation slider 93 remains in the L position and the idler gear 98 is engaged with the winding gear 99. The winding gear 99 is moved by the arrow T by the reel motor lO5.
99-a. As a result, the jammed idler gear 98 is also removed from the outer peripheral gear 1 of the J-ru base 37.
11, and rotates the S IJ-ru base 37 in the direction of arrow T37 via the gear 112. Then, the capstan 14 rotates clockwise to run the tape in reverse,
Wind up the tape with the S IJ-roll. Furthermore, cylinder 2
rotates counterclockwise to perform rewind playback.

Figures 40 and 41 show the position of the cam ring during fast forwarding or rewinding. In this case, the pinch roller operating lever 9
6 rotates to the L position, and moves the PR operation lever adult 161 and the pinch roller pressure lever 160 to the arrow B-161.
, B rotate in the -160 direction. As a result, the pinch roller arm 13 rotates in the direction of arrow B-13, and the pinch roller 15 separates from the capstan 14. In synchronization with this, the PR lever 162 rotates in the direction of arrow B162. At this time, the configuration is such that the FRR joint gear is engaged after the pinch roller 15 is separated.

The brakes are 5IJ-36. 'rlJ-ru stand 37
8T sub-brakes 92 and 95 are in contact with each other.

The idler operation slider 93 moves to the H position.

In FIG. 41, the idler gear 98 is the PR gear 100.
bite into. On the other hand, due to the rotation of the PR lever 162, the F
The relay gear 109 meshes with the capstan gear 108 and the PRR force transmission gear 171 to transmit the power of the capstan. At this time, the pinch roller 15 is
Since the FRR joint gear 109 is engaged after separating from the tape head 4, a sudden increase in tension can be prevented and damage to the tape head can be prevented.

When in fast forward mode, the capstan 14 is
direction, and turns the FR gear in the direction of arrow A100 via the PRR force transmission system. As a result, the idler gear 98 is biased rightward, engages with the gear 107, rotates the reel stand 36 in the direction of arrow A36, and winds up the tape.

In the case of rewinding, the capstan 14 rotates in the direction of arrow B14 and rotates the PR gear in the direction of arrow B100 via the FRR power transmission system. This allows idler 98
is biased to the left, engages with the gear 112, rotates the reel stand 37 in the direction of arrow B-37, and winds up the tape.

The above operation satisfies the functions of a normal recording/reproducing device.

〔Effect of the invention〕

According to the present invention, when the tape is transferred by the capstan, the engagement with the power transmission system connected to the capstan can be released with a simple configuration, thereby reducing disturbances applied to the capstan and preventing uneven rotation of the capstan. By reducing this, it is possible to run the tape stably and improve its performance.

[Brief explanation of drawings]

1 and 2 are plan views showing the entire embodiment of the present invention, FIG. 3 is a developed view of rings, FIG. 4 is a perspective view of the LM motor speed reduction mechanism, and FIG. 5 is a plan view showing the structure between the rings. A plan view showing the power transmission mechanism, FIG. 6 is an exploded perspective view of the first switching gear, FIG. 7 is a sectional view of the first switching gear, cam ring, and drive ring, and FIG. 8 is an exploded perspective view of the second switching gear. , Figure 9 is a sectional view of the second switching gear, cam ring, and drive ring, and the first
Figure 0 is a plan view showing the cam ring drive gear, Figure 11 is a plan view showing the gear train from the LM motor to the O-ding ring and guide arm, Figure 12 is a half sectional view, and Figure 13 is the loading ring. and a plan view showing the arrangement of the loading guide, and Figures 14 to n are diagrams showing the O-ding guide and catcher.
, 20 and 22 are plan views, No. 15.17゜19,
21 and 23 are side views, FIG. 25 is a plan view showing the tension arm and correction guide arm, FIG. 26 is a side view thereof, and FIGS. 31 and 32 are plan views of the reel stand control member,
FIG. 33 is a plan view of the idler mechanism, FIG. 34 is a sectional view thereof, and FIGS. 35 to 41 are plan views showing the side of the reel stand controller. Explanation of symbols 1...Chassis 2...Cylinder 13...
・Pinch roller arm 14... Capstan 15... Pinch roller 32... Drive ring Ah... Cam ring 96
... Pinch roller operation lever 98 ... Idler gear 99 ... Winding gear ... PR gear 105 ... Reel motor 08 ... Capstan gear 109 ... PR relay gear 160 ... Pinch Roller crimping lever 161...PR operation lever-A 162...FR lever＼、＼・ Agent Patent attorney Katsuo Ogawa - Figure A Figure 2 Figure 5 Figure 6 Figure ■ Figure 8 Figure 9 Figure 10 Figure - 11 Figure 12 Figure 13 Figure 14 Figure 18 Figure 19 Figure 21 Notebook 26 Figure 38 Figure 28

Claims (1)

[Claims] 1. In a magnetic recording/reproducing device that winds a magnetic tape at a predetermined angle around a rotating head drum equipped with a plurality of magnetic heads to form a predetermined running path, the magnetic tape is rotated and elasticized along the running path. a first drive means for holding and transporting the magnetic tape between the magnetic tape and the body; a second drive means for winding the magnetic tape at high speed; a third drive means for winding the magnetic tape at a low speed; a first drive source that drives the first and second drive means; and a second drive source that drives the third drive means; When transporting the magnetic tape, the magnetic tape is wound by the third driving means, and when the first driving means and the rotating elastic body are separated from each other, the magnetic tape is transported by the second driving means. When the magnetic tape is transferred by the first drive means, the engagement between the second drive means and the first drive source is released in accordance with the movement of the rotary elastic body, and then the magnetic tape is transferred. When the rotary elastic body is pressed against the first drive means and the magnetic tape is transferred by the second drive means, the movement of the rotary elastic body is performed after the first drive means and the rotary elastic body are separated. A power transmission switching mechanism for a magnetic recording and reproducing apparatus, characterized in that the second drive means and the first drive source are configured to engage with each other.