JPS63104249A - Tape driving mechanism for magnetic recording and reproducing device - Google Patents

Abstract

PURPOSE:To make the titled device small in size and light in weight by using a pinch roller moving mechanism to engage a pinch roller support member with a pressing mechanism at the time of switching torque by a torque changeover mechanism between a loading mechanism and a mode mechanism. CONSTITUTION:A cam ring 38 is driven further in a direction of an arrow A38 from a loading stop mode and a brake or the like enters a recording mode, then a pinch roller operating lever 96 is driven in the direction H, a pinch roller arm 13 engaged with the output terminal is driven and a pinch roller is pressed against a capstan 14. The brake operating levers are all driven in the H direction to release the engagement of T, S reel bases 36, 37. An idler gear operating slider 93 is moved to the position L and the idler gear 98 meshes with a winding gear 99. The gear 99 is driven by a reel motor 105 in the direction of arrow T99. Thus, the meshed gear 98 meshes with a gear 106 of the outer circumference of the T reel base 36 to drive the T reel base 36 in the direction of an arrow T36. Then a capstan 14 and a cylinder 2 are driven counterclockwise to drive a tape.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a magnetic recording/reproducing device, and particularly to a tape drive mechanism suitable for simplifying the mechanism and ensuring reliability.

[Conventional technology]

The mainstream mechanism for driving a magnetic tape is a system using a so-called capstan and a pinch roller in terms of performance and cost. Further, in a magnetic recording/reproducing apparatus such as a VTR, a tape is usually pulled out from a cassette to form a predetermined tape running path, and then a pinch roller is pressed against a capstan with the tape in between. Therefore,
It is necessary to keep the pinch roller at a large distance from the capstan until the tape running path is formed. This method requires a predetermined pressure force between the capstan and the pinch roller, so first a moving mechanism moves the pinch roller near the capstan, and then the pinch roller is applied to the capstan with a predetermined pressure force. It consists of a crimping mechanism for crimping. From the viewpoint of power saving and weight reduction, cams and drive mechanisms that do not use solenoids are designed to be pinched from one continuous cam via a slider, arm, etc., as described in JP-A-58-147837, for example. A common method is to operate rollers. In these systems, the cams are large in diameter and the device is compact because the pinch rollers must be held in place for very long periods of time when they are not operating, such as during loading periods. This will impede the process.

On the other hand, in order to reduce the size of the cam, there is a method in which the loading mechanism and the mode operating mechanism are driven separately. In this case, if one pinch roller is operated separately by two mechanisms, the mechanism will generally be complicated, so for the purpose of simplifying the mechanism, loading the pinch roller with a large amount of movement is carried out using a normal cam, etc. For crimping with a small amount of movement, there is a method in which the crimping is operated by a solenoid or the like. However, since this method uses a solenoid, there is a limit to the reduction in weight and power consumption.

[Problem that the invention seeks to solve]

In this way, in a magnetic recording/reproducing device using a cassette,
Two types of mechanisms or operations are required in order to keep the pinch roller far away from the capstan during the tape loading operation and press it with a predetermined pressure when the tape is running. However, it has been difficult to fully meet the demands of miniaturization and reduction of power consumption.

SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned problems and provide a small and simple pinch roller movement and crimping mechanism.

[Means for solving problems]

In order to achieve the above object, the present invention includes a moving mechanism for moving the pinch roller to the vicinity of the capstan in conjunction with a tape loading mechanism, and a moving mechanism for moving the pinch roller to the vicinity of the capstan in conjunction with a mode operation mechanism. The pressure bonding mechanism to be controlled is separated into two parts, and when the mode operating mechanism operates, the pinch roller support member is engaged with the pressure bonding mechanism by a moving mechanism.

[Effect]

The present invention operates the pinch roller moving mechanism and the crimping mechanism so that they partially overlap with each other in conjunction with the separate drive of the loading mechanism and the mode operating mechanism for performing the tape loading operation. Since the supports of the roller support members are designed to be passed over, each operation can be set under optimal conditions, and each mechanism can be made suitable for downsizing.

〔Example〕

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

FIG. 1 is a plan view showing the entire embodiment of the present invention. This figure shows a stopped state (unloading stop state) in which the magnetic tape cartridge 77 indicated by the dashed line in the figure is installed in the apparatus and the magnetic tape is not pulled out. A take-up (T) and a supply (S) reel 5.6 on which the magnetic tape 3 is wound are housed inside the magnetic tape cartridge 77, and each reel is rotatably supported on the chassis 1. The reel is mounted and engaged with the reel stand.

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

In this state, the arrow A of the loading ring 1o
,. A group of guide rollers that move by rotating in a direction? , 8
．． 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 FIG. form a tape running path.

The device is operated while this travel path is maintained.

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

FIG. 3 is a developed view showing the attachment relationship between the rings that control the main operations of this magnetic recording and reproducing apparatus and the chassis I.

Drive ring 32. Cam ring ah, loading ring 1
In the three types of rings No. 0, the cam ring is installed at the height closest to the chassis 1, and the drive ring 32 is installed above it parallel to the top surface of the chassis 1.
The loading ring 10 is attached to the chassis 1 from above the drive ring 32 in an oblique manner.

The drive ring 32 and cam ring 38 are held by two-stage ring holders 33-a and 33-b rotatably supported on the side of the chassis 1.
, 34-a, 34-b, 35-a, and 35-b, the loading ring 10 is
Regarding the ring holder 17, 1 shown in FIG.
8 and 19 on the inner periphery of the ring.

These three types of rings are the loading mode motor I
Driven by. That is, the ring drive mechanism of this device is: (1) Loading mode motor 27 (hereinafter referred to as 5M motor).

■ A reduction gear train that transmits the driving force of the LM motor 27 to the drive ring 32.

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

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

It is groove bottomed by. 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 loading ring 10 performs a loading operation of winding the magnetic tape 3 around the rotary cylinder 2, and the cam ring 38 performs a mode transition operation of operating mechanical elements such as a brake with a convex-concave surface (cam surface) provided on the inner periphery.

Note that in order to perform this loading operation, #29 and rollers equipped with guide rollers 7 and 8.9 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 discontinuous) are arranged in a concentric arc shape on the top of the cam ring. For example, it is provided by printed wiring,
A brush 32-b is attached to the lower surface of the drive ring 32 to short-circuit the two patterns. In these two patterns, the continuous pattern 38-b is connected to the ground of the system control circuit, and the intermittent pattern 38-b is connected to the ground of the system control circuit.
c is connected to the mode detection end of the circuit.

As will be described later, the rotational directions of the drive ring 32 and the cam ring are reversed, and as a result, the relative angular relationship between the drive ring 32 and the cam ring changes.
Brush 32-b and pattern 38-b.

As the positional relationship of C changes, different parts of the intermittent pattern 38-C are shorted to ground, and the system control circuit (not shown) detects the angular relationship between the two rings to achieve the desired mode transition. Get position.

The ring drive mechanism, loading mechanism, and mode operation mechanism outlined above will be detailed below.
3 is a perspective view showing a speed reduction mechanism for transmitting the driving force of an M motor n to a drive ring 32. FIG.

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. Furthermore, a transmission gear 39 is meshed with the LM motor gear (equipment), 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 rotatable in the LM motor holder 47. is maintained.

Furthermore, the LM motor holder 47 has shafts 42 , 44 , 4
G, 51, 52 are press-fitted from above, and each shaft has a two-stage reduction gear 41, 43, 4.
5 and 49 are each rotatably supported by a shaft.

The upper stage gear 41-a of the reduction gear 41 is a worm wheel that meshes with the worm 40, and its lower stage gear 41-b
and the upper gear 43-a of the reduction gear, and its lower gear o.
-b and the upper gear 45-a of the reduction gear 45 are in mesh with each other, and the lower gear 45-b is in mesh with the upper gear of the drive gear 54 that drives the drive ring 32. Therefore,
The LM motor gear (capital) press-fitted into the LM motor n is indicated by arrow A. When rotated in the direction, the transmission gear 39. is continuously engaged. Worm 40° reduction gear 41, 43, 4
5, arrow A, respectively. , A4゜+41 *9s
+ A45 direction and drive gear 54 in the direction of arrow A54.
Rotate in the direction.

Conversely, when the LM motor gear rotates in the direction of arrow Bso, each gear also rotates in the direction of arrow B. s B4゜.

B41 + 13as l Rotates in the B411 direction, and rotates the drive gear 8 in the arrow B14 direction.

The transmission gear 49 has a 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.
0. Alternatively, it is a plan view showing a power transmission mechanism to a cam ring.

On both sides of the gear portion 32-a of the drive ring 32, first and twentieth fan-shaped plates 58 having a predetermined thickness are provided.
59 is 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 10th pick plate group and the 20th pick plate 59 near the gear portion 32-a are chamfered as shown. The shape of this chamfered portion is an involute shape similar to the tooth surface forming the gear portion 32-a.

That is, the continuous gears of the gear portion 32-a of the drive ring 32 are set so that their end portions are connected 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 in the drive gear diagram meshes with the gear portion 32-a of the drive league 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 5. FIG. As shown in the figure, the first switching gear 55 has a three-layer structure in which a first switching plate 55-b is sandwiched between two gears 55-a and 55-c.

After the holes of the three gears are aligned, the pin 62
are press-fitted to maintain a fixed phase relationship with each other. As shown in Fig. m5, it is rotatably supported by a shaft ω press-fitted into the chassis 1.

FIG. 7 shows this first switching gear 55 and the drive ring 32,
This is a cross section showing the height relationship of the cam ring.

Since the first switching gear 55 is mounted 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, but the gear part 32-a of the drive ring 32
are in mesh with the gear 5-c at the lowest stage.

In addition, the first switching plate 5 at the middle stage of the first switching gear 55
5-b is attached at a height opposite to the inner circumferential surface of the tenth pick plate indicated by the 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. Each radius is set to approximately match the root circle.

The upper gear 55-a of the first switching gear 55 is
The secondary transmission gear 49 meshes with the transmission gear explained in FIG. 4.5. The rotation is transmitted to the loading ring 10.

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.
One switching plate 56-a and two gears 56-a, 5
It has a 3/ii structure of 6-c.

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

As in the case of the first switching gear 55, the phase relationship between these three gears is fixed and maintained by press-fitting the pin 63 through the hole after centering the holes.

Further, the radius of the large diameter portion of the outer circumferential portion of the second switching plate 56-a is set to approximately match the tip circle of the middle gear 56-b, and the radius of the small diameter portion is set to approximately match the root circle thereof. ing.

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

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 32 and the cam ring 37, and meshes with the cam drive gear 57 shown in FIG.

The first switching gear 55 described above. 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 second switching gear 56 each have an involute curve equivalent to the tooth surface of the gears 55-c and 56-b. The end surface and the tooth surface are set so as to coincide with each other in plan view when the pin 62 or the tooth surface is press-fitted to fix and maintain the mutual phase relationship.

FIG. 10 shows the cam drive gear 57 and the cam ring 3 that mesh with the second switching gear 56 at the lower part of the drive ring 32.
It shows the positional relationship of 8. As shown in the figure, the cam drive gear 57 is arranged so as to mesh with a gear portion 38-a provided on a part of the inner peripheral surface of the cam ring in plan view. Also, the upper surface of the cam drive gear 57 is indicated by the dashed dotted line H8? in FIG. It is located at a height indicated by , 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.

FIG. 11 shows the reduction gear train from the LM motor n to the drive ring 32, and from the drive ring 32 to the loading ring 10. Guide arm 1
FIG. 2 is a flat diagram showing a connected state of up to two transmission gear trains.

Arrow A of the LM motor gear (capital) shown in FIG. By rotation in the direction, the worm 40. Reduction gears 41, 44, 45, and 54 are indicated by arrows & in FIG. 11, respectively. *A4
1 g A44 gAas + Rotate in the AI4 direction. The drive ring 32 is connected to the lower stage h- of the reduction gear 54.
Arrow A3 by b! driven in the direction. Due to this rotation, the first
The upper gear 55-a of the switching gear 55 is connected to the arrow 2. The transmission gear 49 on the LM motor holder 47 which is rotated in the direction shown in FIG. Then, the loading ring 10 is rotated in the direction of arrow A1°.

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 supported by a shaft 65 press-fitted from above, and the lower gear 62-a is connected to the lower gear 55-C of the first switching gear 55, and the upper gear 62-b is connected to the upper gear 6 of the second gear 61.
Each meshes with 1-a.

The gears 61 , 63 , and 64 are rotatably supported by shafts 66 , 67 , and 68 that 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, 72
axially positioned by.

Further, the boss portion 13-c of the pinch roller arm 13 is located at the center of rotation of the guide arm 12 having a U-shaped cross section.
The guide arm 12 is held between spacers 73 and 74, and rotatably supported by the shaft 22 on the chassis 1 together with the guide arm 12 and the fan-shaped gear 28.

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

In FIG. 11, reference numeral 76 denotes a torsion spring mounted with a margin on the outer annular surface of the boss 13-c of the pinch roller arm 13, and one end 76-a of the torsion spring 76 is attached to the pinch roller arm The protrusion 13-a of the pinch roller arm 13 is engaged with the guide arm 13, and the other end 76-b is engaged with the connecting part 12-a of the guide arm 12 having a U-shaped cross section, and the protrusion 13-a of the pinch roller arm 13 is engaged with the guide. Connection part 1 of arm 12
2-a in the direction of separating them from each other.

Because of the above-mentioned connected state, when the drive ring 32 is rotated in the direction of arrow A□, the gears 62-a, 62-b, 61
-a, 61-b, 63-a, and 63-b are rotated in the directions of arrows A61, Ag3, and A4B, respectively, and the sector gear 4 is rotated in the direction of arrow □. As a result, the pin 75 on the pinch roller arm 13 is pressed by that side of the fan-shaped gear, and the pinch roller arm 13
is rotated in the three directions indicated by the arrows A1, . rotated in the direction.

In this manner, the rotation of the LM motor 27 is transmitted to the loading ring 10 and the guide arm 12 via the drive ring 32, thereby performing the loading operation.

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

In FIG. 13, pins 10-a and 10-b are press-fit onto the loading ring 10. These pins have the first boat 29. The second boat J is engaged at each elongated hole portion with a predetermined gap.

Also, the first red 29. placed on the loading ring 10 as described above. Protrusions 29-d and 30-b on the second boat 30
and protrusions 10-e, 1 fixed on the loading 10.
0-f, there are springs 10-c and 1, respectively.
0-d are independently suspended to 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 the first
From the state shown in the figure, by being rotated in the direction of arrow A1° as described above, the first boats 29 and g2 boats J also move in the same way.

Through this operation, the magnetic tape 3 changes from a state where it is stretched over the front surface of the cassette cartridge H 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 4 enters and comes into contact with the first catch due to the rotation of the loading ring 10, and FIG. 15 shows this in white. FIG. 3 is a side view seen from the direction of the blank arrow. A positioning pin 29-a is press-fitted into the first boat, and when the first catch is approached, a U-shaped groove 20-a, a V-shaped groove 20-b, and a U-shaped groove provided above and below the first catch Letter-shaped groove 20
-c, the direction of travel is corrected. At the same time,
The upper surface 29-c of the tip of the first boat 29 comes into contact with the lower surface 20-d of the first catcher 4, and the forward and backward inclination of the first boat 4 is also corrected. Even after the above horizontal and vertical position correction and positioning, loading ring 1
0 further rotates to give a predetermined elongation to the spring 10-c and generate a predetermined pressing force against the first catcher 20.

In FIGS. 16 and 17, the second boat 30 is shown in the same way as above.

18 and 19 are a plan view showing a state in which the loading ring 10 is rotated in the direction of the second catcher 21 and a side view seen from the direction of the white arrow, and FIGS. 18 and 19 are plan views showing the crimped state. FIG. 2 is a diagram and a side view.

By the rotation of the loading 10, the second boat 30
Approaching the catcher 21, the pin 30-a on the motherboard is guided into the groove 21-b of the second catcher 21 through the path shown by the broken line, and the figure-7 notch 21-a is located above the groove 21-b.
The direction of travel is corrected towards a.

Then, as shown in FIGS. 18 and 19, the pin 30-a comes into contact with the V-shaped notch 21-a, and the bottom surface of the second boat 30 comes into contact with the surface 21-c of the second catcher 21. After this, the loading ring 10 further rotates in the direction of arrow A10 to stretch the spring 10-d by a predetermined amount.

As a result, the second hook 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 third catcher 31.

A lever 79 engaged with the third pontoon 4 is connected to the distal end of the guide arm 12 while being 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 4 during a loading operation.

The third boat 5 comes into contact with the third catcher 31 due to the rotation of the guide arm. FIG. 22 and FIG. n show this state. The contact points at this time are the pin 25-a and the V-shaped notch 31-a. The lower surface 5-b of the boat is in contact with a locally protruding portion 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.

Both the chingeon arm 16 and the correction guide arm 82 are rotatably supported by the shirt l-&3 press-fitted onto the chassis 1. In this state, the tension pin 16-a 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 85 is stretched between the shaft 6-b and the shaft press-fitted onto the chassis 1, and the tension arm 16 is biased in the direction of arrow A16.

Further, a protrusion 82- 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 1, and the correction guide arm 82 is biased in the direction of the arrow B0.

A protrusion 8 is provided near the tip of the correction guide arm 82.
2-c is provided and abuts against the side surface of the tension arm 16.

Therefore, rotation of the tension arm 16 by the spring b is prevented by the correction guide arm 82 and the spring a.

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

In the unloading state, this band brake blade is mounted on the 5IJ-ru base 37 in a relaxed state as shown in the figure.

Note that the ends 16-b, 82-d of these arms and the springs δ, 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 2.

During the transition from this unloading state to the loading state, when the drive ring 32 is rotated in the direction of the arrow ASt as described above, the protrusion 32-b provided on the drive ring 32 is inserted into the pull-out arm. 82, and against the reaction force of the spring, the correction guide arm 82 moves in the direction of arrow A8! Rotate in the direction. When this angle of rotation exceeds a certain value, the point of application of the force of the spring wing moves to the left with respect to the straight line connecting the shaft wing and the protrusion on the side surface of the chassis 1. Therefore, the correction guide arm 82 is urged in the direction of arrow AI by the spring element, contrary to the unloading state.

FIG. 5 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 pull 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 comes into contact with the side surface 150-a of the guide plate 150 to define its planar position.

Further, since the protrusion 16-c on the tension arm 16 is also rotated in the direction of arrow A16, the band brake field contacts the S reel stand 37 with a predetermined tension. As a result, a predetermined braking torque is generated in the S IJ-roll stand 37, and an appropriate tension is applied to the magnetic tape 3 pulled out from the S reel 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 the arrow 131g,
2, and rotates the correction guide arm 82 in the direction of arrow 13st against the biasing force of the spring. Then, the tension arm 16 is also pressed by the protrusion 82-C on the correction guide arm 82, and the arrow 13ta
rotated in the direction.

When the angle of rotation exceeds a certain value, the correction guide arm 82 is biased by the spring wing in the direction of the arrow 13 mg, contrary to the loading operation, and the tip end is rotated as shown in the figure. is returned to the state where it is housed in the opening of the magnetic tape cartridge 77.

The tape running path shown in FIG. 2 is formed by the loading operation by the rotation of the drive ring 32 and the positioning operation of the crimp 9 described above. In this tape running path, recording (playback) is performed 9 times backward.

Operations such as fast forwarding are performed. Next, a mechanism for maintaining this tape running path will be explained.

During the loading period, the tenth pick plate 58 on the drive ring 32, which was explained in FIG.
approach. 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, they 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,
It is a top view which shows the operational relationship with the 1st switching play 1-55-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.

Therefore, the tenth pick plate 58 is connected to the first switching gear $
Until reaching , the lower gear 55-c of the first switching gear 55 is engaged with the gear portion 32-a of the drive ring 32 and rotated in the direction of arrow A0, but the gear portion 3
At the end of 2-a, the engagement with the lower gear 55-c is released. However, the tooth surface of the lock plate edge presses the tooth surface of the first switching plate 55-b, so that the first switching gear 55 is rotated further and then returned to the state shown in FIG. Become. (The meshing phase between the gear portion 32-a and the gear 55-c is set so that the tooth surfaces of the lock plate and the first switching plate 55-b engage at this end.) This state In this case, 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.

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. transmission gears 48 and 49 that mesh with this
, loading 10, and guide arm 12 are also prevented from rotating.

The timing for locking the first switching gear 55 is determined by the timing at which the first switching gear 55 is locked. 2nd boat 29.30. and the third boat 4 on the guide arm 12 is connected to the first boat 4 on the guide arm 12. 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 Tsuku Plate 59 along with the 10th Tsuku Plate Group also moved to Arrow A! Rotated in one direction. During this rotation period, the 20th plate 5
The inner peripheral surface of 9 is in sliding contact with the ends of the two tooth surfaces of the second switching plate 56-a at the upper stage of the second switching gear.

Since the second switching gear 56 and the drive ring 32 are installed in the relationship explained in FIG. As shown in the figure, rotation of the second switching gear 56 is prevented. 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 arrow will move.

The gear portion 32-a of the drive ring 32 that moves in the direction
The tooth surface at the end of the 0-tsuku plate is as shown in Fig. 30.
The second switching plate 56- on the upper stage of the second switching gear 56
By starting to press the tooth surface of the second switching gear 56 and moving further, the gear portion 32-a shifts to the middle gear 56 of the second switching gear 56.
-b, and the lower cam ring 32 of the drive ring 32 begins to rotate via the cam drive gear 57 that engages with the lower gear 56-c.

Next, the mode operation performed by the rotation of the 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 is 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 arranged between the gears and the chassis l. It is arranged.

FIG. 32 shows the planar arrangement of the brakes located below the gears.

Main brake operating lever 91-a, s-sub brake operating arm 92-a, idler gear operating slider 93. T
Brake operating arm 94-a, T sub-brake 95. The inner peripheral surface of the cam ring 38 has cam patterns A-d and 38 corresponding to each operating end of the pinch roller operating lever %-a.
-e, 38-f, 38-g, 38-ri, and a-i are provided.

The cam surface of the cam pattern is composed of an arc that has the same circular relationship as the outer circumferential circle of the cam ring, and a taber surface that connects the arc, and the former corresponds to a mode detection section and the latter corresponds to a transition section.

In addition, adjacent cam patterns have common sections having the same end shape.

The phase of the contact point of each operated member with respect to each cam pattern is the same between each cam pattern.

As the cam ring 38 rotates, the operated members are moved around the support shaft 91-8°92-8 which is press-fitted onto the chassis 1.
．． Operations such as applying braking torque to the s'r r s')-ru tables 36 and 37, pressing the pinch roller 15 to the capstan 14, etc. I do.

Hereinafter, the case where the operating end of the operated member is in contact with the arcuate surface with a small radius on the north side of the cam ring is referred to as the H position, and the case where it is in contact with the arcuate surface with a large radius is referred to as the L position. .

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

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
Hereinafter 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.

34 is a plan view showing the arrangement relationship between the idler gear operation slider 93 and the idler gear support plate 97, the idler gear 982, the take-up gear 99, and the FR gear 100 located above it, and FIG. 34 is a cross-sectional view thereof. It is a diagram. However, in this state, the idler gear operation slider 9
3 indicates the state where it 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.

One end of the idler gear operating slider 93 has a side wall forming a roughly elliptical recess, which projects upward from the chassis 1 as shown in the sectional view of FIG. The idler gear support plate 97 is placed on the upper surface of this protruding part, and above it, the F gear 100 and the winding gear are arranged rotatably around the shaft press-fitted into the chassis 1. , the vertical position is regulated. At the center of the idler gear support plate 97, there is a boss ]02.
The shaft 103 is press-fitted through the hole of the boss 02. And idler gear 98 is
The idler gear support plate 97 is rotatably supported by the shaft 103 and supported by the felt 104.
, a predetermined rotational load is applied.

Further, the lower end of the shaft [03] 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 I, 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 98 moves in the direction of arrow H, it meshes with the PR gear Zoo, and when it moves in the direction of the arrow, it meshes with the take-up gear 99, and when it is located at M, it meshes with the PR gear Zoo. It does not mesh with any of the gears.

When the cam ring is rotated in the direction of the arrow A0 from the arrangement shown in FIGS. 31 and 32, its cam surface causes each input end of the operated members to be fast forwarded and 7 turns reversed during the loading operation period. Raw), O-Din dust whelk (stop in loaded state).

It is lifted by a predetermined amount corresponding to each mode of recording/playback/fast-forward playback.

The rotation angle of this cam ring is detected using the printed pattern on the cam ring explained in Fig. 3, 38-c.
This is done by

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

FIG. 35 shows that the cam ring is in a state indicated by arrow A during the loading operation period shown in FIGS. 31 and 32.

This figure shows the arrangement of the operated members when the load stop mode is entered by rotating in the direction of .

Since the main brake operating lever 91a is in the loading dust knob mode, only the main brake operating lever 91a is rotated toward the L side, and the brake section at its output end prevents the rotation of the sTs8'J-ru blocks 36 and 37. . In addition, the idler gear operation slider 93 is in the M position, and the idler gear 9
8 is a winding gear 99. It does not mesh with any of the PR gears 100.

FIG. 36 shows a state in which the cam ring has been further rotated in the 8 direction indicated by the arrow from the loading stop mode shown in FIG. 35, and the brakes have entered the recording (playback, fast-forward playback) mode. In FIG. A, the pinch roller operating lever % is rotated in the H direction, the pinch roller arm 13 that engages with its output end is rotated, and the pinch roller 15 is pressed against the capstan 14. The brake operating levers are all rotated in the H direction, and the
The attachment with the bases 36 and 37 is released. However, the band brake 86 shown in FIG. 5 applies a predetermined tension to the tape running in contact with the outer peripheral surface of the S reel stand 37. The idler gear operation slider 93 moves to the L position, and the idler gear 98 engages the take-up gear 99 as shown in FIG. The take-up gear 99 is the reel motor 1
05, it is rotated in the direction of arrow 'I'oo. As a result, the engaged idler gear 98 also engages with the gear 106 on the outer periphery of the T-reel stand 36, causing the T-reel stand 36 to rotate in the direction of the arrow 'I'ms. and capstan 14
By rotating the cylinder 2 counterclockwise, the tape is run and scanned.

FIG. 39 shows the position of the cam ring during fast forwarding or rewinding.

In this case, the S reel stand 36. S on the T reel stand 37.

The T sub-brakes 92 and 95 come into contact with each other, and the pinch roller 15 is released from being pressed against the capstan 14. Then, the idler gear operation slider 93 moves toward the arrow H side, and the idler gear 98 engages with the PR gear 100. This FR gear 100 has a pinch roller arm 13
The capstan 14 is connected via a transmission gear train by a gear 109 that engages the gear 108 of the capstan 14, and is rotated by the rotation of the capstan 14. During fast forwarding, the capstan 14 rotates clockwise, rotates the PR gear 100 counterclockwise, and the idler gear 98 that is caught is biased to the right.
It meshes with the transmission gears 106 and 107 to the IJ-reel stand 36, giving clockwise rotation to the T-reel stand 36. In the case of rewinding, the capstan 14 is reversed and the idler gear 98 is transferred to the 31J-
counterclockwise rotational force is transmitted to the rotary table 37.

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

〔Effect of the invention〕

As described above, according to the present invention, it is possible to obtain a desired operating state of the pinch roller by linking the loading mechanism and the mode operating mechanism with separate driving. The pinch roller movement and crimping can be optimally designed under each condition without sacrificing the effect of making the unit smaller, and the pinch roller support member can be transferred using a simple mechanism. Therefore, the device can be made smaller and lighter.

[Brief explanation of the drawing]

1 and 2 are plan views showing the entire device according to an embodiment of the present invention, FIG. 3 is an exploded perspective view illustrating the arrangement of the drive ring, cam ring, etc., and FIG. 4 is an implementation of the gear block. FIG. 5 is a plan view showing an example of the drive ring, FIGS. 6 and 8 are exploded perspective views showing an example of the switching gear, and FIGS. 7 and 9 are the switching gears. 10 is a plan view showing an embodiment of the cam ring, FIG. 11 is a plan view of a gear train that operates the drive ring, FIG. 12 is a sectional view thereof, and FIG. 13 is a plan view of the loading mechanism. FIG. 14 is a plan view of the main part, FIG. 15 is a side view taken in the direction of arrow A showing a part of FIG. Figure 17 and 1st
9 is a side view as seen from the direction of the arrow shown in FIGS. 16 and 18, respectively. FIGS. 4 and 22 are plan views showing other main parts of the loading mechanism. FIGS. 3 and 5 are plan views of the tension arm, FIG. 26 is a side view thereof, and FIGS. N to 30 are plan views of main parts showing the relationship between the drive ring and the switching gear. , 3rd
1 and 32 are plan views showing an embodiment of the cam ring and the operated member, and the second figure is a plan view of the main part of the idler gear section.
FIG. 3 is a sectional view thereof, and FIGS. 35 to 39 are plan views illustrating the operation of the cam ring and the wrinkle operating member. l... Chassis 2... Rotating cylinder 3.
... Magnetic tape 10 ... Loading ring 13 ... Pinch roller arm 14 ... Capstan 15 ... Pinch roller 32 ... Drive ring 96 ... Pinch roller operating lever 1 Hard L Z Figure Atsushi 3 figure 5'l 1 3 notification 1+(i
Iil 15 Kuchiman et al. , 8 Mouth version 9 Figure L IQ Loss 1 (day Figure 13 Figure 14 Figure 15 Figure 17 Figure 19 Figure 21 Figure 22 Page 26 Prisoner 383'2 Figure n Figure 28 Figure 29 Figure 31 Figure 320 Figure 33 Figure 34 Figure 35 Figure 36 Figure 38

Claims (1)

[Claims] 1. A rotating cylinder on which a magnetic head is mounted, a loading mechanism that pulls out a magnetic tape from a cassette containing a supply reel and a take-up reel for winding the magnetic tape, and winds the magnetic tape at a predetermined angle on the rotating cylinder, the supply reel and A magnetic sensor equipped with a mode operating mechanism that operates an operating member that controls the rotation of the take-up reel according to the command mode, and a driving force switching mechanism that switches and transmits the driving force from the drive source to the loading mechanism and the mode operating mechanism. In a recording/playback device,
It has a pinch roller moving mechanism that moves the pinch roller near the capstan in conjunction with the loading mechanism, and a pinch roller crimping mechanism that controls the pressing of the pinch roller against the capstan in conjunction with the mode operation mechanism, and A magnetic recording/reproducing device characterized in that when the switching mechanism switches the driving force between the loading mechanism and the mode operating mechanism, the pinch roller moving mechanism engages the pinch roller supporting member with the pinch roller pressing mechanism. The device's tape drive.