JPS62219255A - Mechanism operating device for magnetic recording and reproducing device - Google Patents

Abstract

PURPOSE:To improve the certainly of operation against a change in the lapse of time and an environ-change by operating a mechanism perfectly on a gear drive basis. CONSTITUTION:There are three kinds of ring, i.e. driving ring 32, cam ring 38, and loading ring 10; and the cam ring 38 is fitted to the top surface of a chassis 1 at the highest height and the driving ring 32 is fitted above it in parallel, but the loading ring 10 is fitted above the driving ring 32 slantingly to the chassis 1. The driving ring 32 and cam ring 38 are held at their outer peripheral parts by ring holders 33-a and 33-b-35-a and 35-b of two-stage structure pivoted turnably on the side part of the chassis 1. The loading ring 10, on the other hand, is held at its inner peripheral part by an L-ring holder 17 and L-ring holders 18 and 19. Those three kinds of rings are driven by a loading mode motor.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a mechanism configuration in a magnetic recording/reproducing device, and particularly to a mechanism operating mechanism suitable for achieving reduction in size and weight and high reliability.

[Conventional technology]

Magnetic recording and reproducing apparatuses have very diversified reproducing functions, and it is necessary to provide operating modes of the mechanism according to these functions, resulting in a large number of operating modes. In addition, the mode of the mechanism is generally operated by a cam rather than a plunger from the viewpoint of reducing power consumption, weight, and cost. That is, by connecting the cam to the arms, the necessary movements of each part can be obtained.

An example of such a device is JP-A-57-88558.
There is something like the one described in the publication. In this case, in addition to applying brakes to each reel stand, pressing/releasing the pinch rollers, and controlling the position of the tension arm, the tape loading mechanism is often driven.

The reason why these conventional systems employ a link mechanism with multiple arms is that the position of the cam and the operating power member are far apart, and the smaller diameter of the cam allows for a variety of operating states to be obtained from the cam shape with little change. This is due to reasons such as necessity.

[Problem that the invention seeks to solve]

However, the link mechanism generally has low operating precision, making phase alignment difficult, and increases the number of parts. Also, when transmitting driving force to the cam mechanism etc. mentioned above, the motor and cam, which are the driving sources, are often separated due to constraints on the layout of the entire device, so a rubber belt is used to transmit the driving force. Furthermore, in a mechanism that drives a reel stand as a tape drive mechanism, when driving force is obtained from a capstan motor, in order to avoid deterioration of tape running performance due to torque unevenness due to gear drive, etc. Although driving force is transmitted using a rubber belt, there is a problem in that transmission using a belt causes a large change in the transmission rate due to a loss of lateral pressure on the bearing due to the belt tension and changes in the environment, reducing the reliability of the device.

The purpose of the present invention is to solve the problems of the prior art described above,
An object of the present invention is to provide a mechanism operating mechanism for a magnetic recording/reproducing device that achieves reduction in size and weight through a simple mechanism, and also ensures high reliability by ensuring reliable transmission of driving force. .

[Means for solving problems]

In order to achieve the above object, the present invention selectively supplies a driving source from a driving source to a loading mechanism and a mode operating mechanism, and a driving force transmission mechanism between them is provided to a gear and at least a portion of the peripheral surface. It consists of a ring with a gear part.

[Effect]

Transmission of the driving force and switching of the driving force between the loading mechanism and the mode operating mechanism are performed reliably, and the operation is not affected by changes in environmental conditions, improving reliability.

〔Example〕

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

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

This figure shows the unloading stop state with the magnetic tape cartridge 77 indicated by the dashed line in the figure still attached. The magnetic tape cartridge 77 houses a take-up reel 5 and a supply reel 6 on which the magnetic tape 3 is wound. ) is mounted and engaged.

Further, on the chassis l, a cylindrical rotating cylinder 2 on which a plurality of magnetic heads (not shown) are mounted, a loading ring 10, a capstan 14, and a tension pin 16-a.
, correction guide pin 82-a.

A pinch roller 15, a guide roller 7.8.9.degree. 11, a loading mode motor 27, etc. are arranged as shown.

In this unloading dusty state, when the loading ring 10 rotates in the direction of arrow A16, the guide rollers 7, 8, 9 and the guide roller 11 engaged with the tip of the guide arm 12 move, and the magnetism of the magnetic tape 3 moves. The stretched portion of the tape cartridge 77 on the front side is pulled out and wound spirally around the rotary cylinder 2 over a predetermined angle. As a result, a travel path for the magnetic tape 3 as shown in FIG. 2 is formed. The device is operated while this travel path is maintained.

Hereinafter, the mechanism and operation of each part shown in FIGS. 1 and 2 will be explained in detail in order.

FIG. 3 is a developed view showing the attachment relationship between the rings that perform the main operations of this embodiment and the chassis I.

In the figure, drive ring 32. There are three types of rings: a cam ring 38 and a loading ring 10. The cam ring 38 is installed at a height closest to the chassis I, and the drive ring 32 is installed above it, parallel to the top surface of the chassis 1. is mounted above the drive ring 32 in an oblique manner with respect to the chassis 1.

The drive ring 32 and the cam ring 38 are held by two-stage ring holders 33-a and 33-a, which are rotatably supported on the side of the chassis 1.
-b, 34-a, 34-b, 35-a, 35-b on the outer periphery of these rings.
and by the ring holder 18 and 19 shown in FIG.
This is done at the inner circumference of the loading ring 10.

These three types of rings are the loading mode motor 27
driven by. That is, the ring drive mechanism for this purpose is: (1) Loading mode motor 27 (hereinafter referred to as LM motor) (2) 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 ring 10.

■ A transmission gear train that transmits the rotation of the drive ring 32 to the cam ring 38.

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 transmission of the driving force when the rotational force of the drive ring 32 is not required.

Such a ring drive mechanism allows each ring 32.38
．． 10 is rotated, and the loading ring 10 performs a loading operation of winding the magnetic tape 3 around the rotating cylinder 2.
The cam ring 38 performs a mode transition operation for operating mechanical elements such as a brake using an uneven surface (cam surface) provided on the inner periphery.

In order to perform this loading operation, a guide base 29.30 on which a guide roller 7.degree. 8.9 is mounted is placed on the loading ring 10.

In addition, in order to detect the rotation angle of the cam ring 38 during the mode transition operation, the cam ring 38 has two types of conductive patterns 3B-b and 38-c (pattern 38-b is continuous, pattern 38c is intermittent). A brush 32-b is attached to the lower surface of the drive ring 32 to short-circuit the patterns 38-b and 38-C. The pattern 38-b is connected to the ground side of a system control circuit (not shown), and the pattern 38-C is connected to the mode detection terminal side of this circuit.

Here, as described later, the drive ring 32 and the cam ring 3
8 are opposite to each other, and as a result, the relative angular relationship between the drive ring 32 and the cam ring 38 changes, so that the brush 32-b and the pattern 3B-b are rotated in opposite directions.
, 38-C changes so that different portions of pattern 38-C are shorted to ground, and the two rings 32.
The system control circuit detects the angular relationship of 38 to detect the transition position in the desired mode.

The ring drive mechanism, loading mechanism, and mode operation mechanism described 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.

In the figure, an LM motor gear 50 is press-fitted into the end of the rotating shaft of the LM motor 27 which is fixed to the side wall of the LM motor holder 47 with screws. In addition, LM motor gear 5
A transmission gear 39 is engaged with the transmission gear 3.
The other part of the rotating shaft 53 into which the worm 4 is press-fitted has the worm 4 rotatably held in the LM motor holder 47.
0 is press-fitted. Further, shafts 42, 44, 46, 51, 52 are press-fitted into the LM motor holder 47 from above, and each of these shafts has a two-stage reduction gear 41, 43, 45, and one-piece structure. Transmission gears 48 and 49 are each 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-a and the lower stage 43-a of the reduction gear 43 are connected to each other.
b,! =tJJi The upper stage 45-a of the speed gear 45 are in mesh with each other, and the lower stage 45-b of the reduction gear is in mesh with the upper stage 54-a of the drive gear 54 that drives the drive ring 32. Therefore, the LM motor gear 50 press-fitted into the LM motor 27 is indicated by arrow A. When rotated in the direction, the transmission gear 39M, ohm 40. Reduction gear 41°4
3.45 are also arrows A391 A4゜+ A411 respectively
The drive gear 54 rotates in the A43+A4S direction, and the drive gear 54 rotates in the A54 direction. Also, conversely, LM motor gear 5
0 is arrow B. When rotated in the direction, each of the above gears also moves as shown in the arrow 113+9・B411・B41+B42・B
45 direction, and the drive gear 54 rotates in the arrow B5, 4 direction.

The transmission gears 48 and 49 are as shown in FIG.
Further, as specifically explained in FIG. 6, it has a role of transmitting the rotation of the switching gear 55 to the loading ring 10.

FIG. 5 shows the loading ring lO1 from the drive ring 32.
Alternatively, it is a plan view showing a power transmission mechanism to the cam ring 38.

In the figure, two fan-shaped lock plates 58 and 59 having a predetermined thickness are provided on the upper surface of the drive ring 32 on both sides of the gear portion 32-a provided on the inner periphery of the drive ring 32. The installation is fixed. The radius of curvature of the inner peripheral surface of these lock 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.

Also, the lock plate 58.5 in the drive ring 32
As shown by the broken line in FIG. 5, the inner circumferential surface of the mounting portion 9 is further depressed than the bottom circle of the gear portion 32-a. And the gear part 3 in the lock plate 58, 59
The end face near 2-a is chamfered as shown.

The shape of this chamfered portion is an involute shape similar to the tooth surface of the gear portion 32-a.

That is, the continuous tooth surface of the gear portion 32-a of the drive ring 32 is set so that the end thereof is connected to the end surface of the lock plate 58, 59 diagonally above in the same tooth surface shape.

Further, the lower stage 54-b of the drive gear 54 is connected to the drive ring 32.
The gear portion 32-a is meshed with the gear portion 32-a. By this, LM
The driving force of the motor 27 is transmitted to the drive ring 32.

6 is an exploded perspective view showing the structure of the switching gear 55 in FIG. 5. FIG.

In the figure, this switching gear 55 is connected to a switching plate 55.
-b is sandwiched between two gears 55-a and 55-c, resulting in a three-layer structure. The outer peripheral surface of this 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 the gear 55-C. Each radius is set to approximately match the root circle of the tooth. Switching plate 55-b and gear 55-
a, 55-c, after the holes they have are aligned, the bottle 62 is press-fitted through these holes to maintain their mutual phase relationship fixed. Then, as shown in FIG. 7, the shaft 60 is press-fitted into the chassis 1.
It is rotatably supported on the shaft.

FIG. 7 is a sectional view showing the height relationship between the switching gear 55, the drive ring 32, and the cam ring 38.

In the figure, since the switching gear 55 is placed on a boss portion on the chassis 1, it is located above the cam ring 38 and does not come into contact with it. However, the lowest gear 55-C of this switching gear 55 is the gear portion 32-C of the drive ring 32.
It meshes with a.

Further, the middle switching plate 55-b of the switching gear 55 is positioned at a height that substantially opposes the inner surface of the lock plate 58 on the drive ring 32, which is indicated by a broken line in the figure.

The upper gear 55-a of the switching gear 55 is the fourth gear 55-a.
It meshes with the transmission gear 48 shown in FIGS.

FIG. 8 is an exploded perspective view showing the structure of the switching gear 56 in FIG. 5.

In the same figure, like the switching gear 55, the switching gear 56 also includes a switching plate 56-a and gears 56-b and 55-c.
It has a three-layer structure.

However, in this case, the switching plate t-56-a is the switching gear 5.
Located at the top of 6.

These switching plate 56-a and gear 56-b.

Similar to the case of the switching gear 55, the phase relationship between the pins 63 and 56-0 is maintained fixed by aligning the holes provided in each, and then press-fitting the pins 63 through these holes. It will be done.

In addition, the outer circumference of the switching play 56-a consists of a large diameter part and a small diameter part, the large diameter part corresponds to the tip circle of the middle gear 56-b, and the small diameter part corresponds to the root circle of the gear 56-b. The respective radii are set so as to substantially match each other.

FIG. 9 is a sectional view showing the height relationship between the switching gear 56, the drive ring 32° and the cam ring 38.

The switching gear 56 is rotatably supported by a shaft 61 press-fitted into the boss portion of the chassis 1.
The middle gear 56-b 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 switching plate 56-a is connected to the drive ring 32.
The lower gear 56-C is located at a height substantially facing the outer inner circumference of the upper lock plate 59, and is located between the drive ring 32 and the cam ring 38, and is a cam drive gear shown in FIG. It meshes with 57.

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 switching gear 55 and the switching gear 56 described above are gears 55-C156-, respectively.
It has an involute curve similar to the tooth surface of b, and is set so that the tooth surface and the end surface match in plan when the pins 62 and 63 are press-fitted to fix and maintain the mutual phase relationship. There is.

FIG. 10 shows the drive ring 32 as described in FIG.
The positional relationship between the cam drive gear 57 that meshes with the second switching gear 56 and the cam ring 38 is shown below.

As shown in the figure, the cam drive gear 57 is a gear portion 38-a provided on a part of the inner peripheral surface of the cam ring 38 in plan view.
and the lower gear 56-C of the switching gear 56. Further, the upper surface of the cam drive gear 57 is
It is located at a height indicated by a dashed line in the figure, and is located at a height where it does not come into contact with the drive ring 32.

Due to this arrangement, the switching gear 56 is connected to the drive ring 3.
2, the cam ring 38 is rotated via the cam drive gear 57.

Figure 11 shows the LM motor 2 explained in Figures 4.5 and 6.7.
7 to the drive ring 32, and from the drive ring 32 to the loading ring 10 and the guide arm 12.
FIG. 3 is a plan view showing the connected state of the transmission gear train up to the present time.

In the figure, as the LM motor gear 50 shown in FIG. 4 rotates in the direction of arrow A5, the worm 4 is sequentially engaged
0, reduction gear 41, 43, 45 and drive gear 54 are:
Arrow A4° in Fig. 11, respectively.

A431 A45I Rotates in the AS4 direction. and,
The drive ring 32 is driven in the direction of arrow AH by the lower stage 54-b of the drive gear 54. Due to this rotation, the switching gear 55 meshing with the gear portion 32-a of the drive ring 32
via the lower gear 55-C of the upper gear 55-C.
a is rotated in the direction of arrow A5B, and the transmission gears 48 and 49 on the LM motor holder 47 that mesh with it are rotated in the direction of arrow A5B, respectively.
1A in the aq direction, and then the loading ring 10 is rotated in the arrow A1o direction.

Next, the operation of the transmission gear train arranged in the lower part of FIG. 11 will be explained with reference to FIG. 12, which shows a partial cross-section of the portion in FIG. 11 when viewed from the right side.

In FIGS. 11 and 12, the connecting gear 62 is pivotally supported by a shaft 65 press-fitted from above the chassis 1.
The lower gear 62-a is the lower gear 55- of the switching gear 55.
C, and the upper gear 62-b meshes with the upper gear 61-a of the two-stage gear 61, respectively. Gear 61.63.
64 is a gear holder 6 screwed onto the side of the chassis 1.
9 (shirt press-fitted from below) 66.67°68
A retaining ring rotatably supported by and engaged from below? 0.71.72.

Further, the boss portion 13-C of the pinch roller arm 13 is held between the rotation center portion of the guide arm 12 having a U-shaped cross section via spacers 73 and 74, and is connected to the shaft 22 implanted in the chassis 1. The guide arm 12 and the fan-shaped gear 28 are rotatably supported. 11th
As shown in the figure, the projection m of this pinch roller arm 13
A pin 75 is press-fitted into the chassis 1 in a state of protruding upward into the t s -a, and is in contact with the side surface of the fan-shaped gear 28 .

As shown in FIG. 11, a return spring 76 is mounted on the cylindrical surface of the outer periphery of the boss 13-C of the pinch roller arm 13 with a margin, and one end 76-a of the return spring 76 is connected to the protrusion 13-C of the pinch roller arm 13. -a, and the other end 76-b is the connecting portion 12-a of the guide arm 12 having a U-shaped cross section.
The protruding portion 13-a of the pinch roller 13 and the connecting portion 12-a of the guide arm 12 are urged in a direction away from each other.

Then, the drive ring 32 moves to arrow A3! When rotated in the direction, the gears 62-a, 62-b, and 61-a are rotated through the lower gear 55-C of the switching gear 55.

61-b, 63-a, and 63-b are respectively arrows A62 and 63-b.
A6! - The fan gear 28 is rotated six times in the A63 direction. - The sector gear 28 is rotated in the direction of the arrow A0. As a result, the pin 75 on the pinch roller arm 13 is pressed by the side surface of the fan-shaped gear 28, and the pinch roller arm 13 is rotated in the direction of arrow AI2. The guide arm 12 moves in the direction of arrow A through the force.
It is rotated in the I□ direction.

In this way, the rotation of the LM motor 27 is controlled by the drive ring 32.
The loading operation is performed by being transmitted to the loading ring 10 and the guide arm 12 via.

Next, the loading mechanism and its operation are shown in Figure 13~
This will be explained in detail using FIG. 23.

First, in FIG. 13, pins 10-a and 10-b are press-fitted onto the loading ring 10. These pins 10-a, 10-b engage with elongated holes provided in the guide base 29, 30 with a predetermined gap. In addition, these base guides 29 and 30 have protrusions 29.
-b, 30-b are provided, and springs 10-c, 10-d are independently suspended between these and protrusions 10-e, 10-1 fixed on the loading ring 10. The position of the base 29.30 relative to the loading ring IO is regulated.

Since the loading ring IO and the guide bases 29, 30 are in the above-mentioned mounting relationship, the loading ring 10 changes from the state shown in FIG. 1 to the arrow A1 as described above. When rotated in the direction of , the base guide 29.30
will move in the same way. Through this operation, the magnetic tape 3 changes from being stretched over the front surface of the magnetic tape cartridge 77 to being gradually wound around the rotating cylinder 2, as shown in FIG.

FIG. 14 shows the state in which the guide base 29 enters the U-shaped groove 20-c of the catcher 20 and comes into contact with it as the loading ring lO rotates in this way, as seen from above the chassis 1. FIG. 15 is a side view seen from the arrow direction A in FIG. 14.

In FIGS. 14 and 15, a positioning pin 29-a is press-fitted into the base guide 29, and when the catcher 20 is approached, U-shaped grooves 29-a provided above and below the base guide 29 are pressed into the base guide 29.
-a, moves along the 1-shaped groove 20-b and the U-shaped groove 20-G while the direction of movement is corrected. At the same time, as shown in FIG. 15, the upper surface 29-c of the tip of the guide base 29 comes into contact with the lower surface 20-d of the catcher 20, and the forward and backward inclination of the guide base 29 is also corrected. Even after zero or more horizontal and vertical position correction and positioning, the loading ring 10 rotates further to give a predetermined elongation to the spring 10-C, thereby causing the guide base 29 to move relative to the catcher 20. It is crimped with a predetermined crimping force.

16 is a plan view showing a state in which the base guide 30 is moved in the direction of the catcher 21 by the loading ring 10, similar to the above, and FIG. 17 is a side view seen from the arrow direction B in FIG. 16. 18 and 19 are a plan view and a side view showing a state in which the guide base 30 is crimped onto the catcher 21. FIG.

First, in FIGS. 16 and 17, the rotation of the loading ring 10 causes the base guide 30 to move toward the catcher 2.
1, the pin 30- provided on the base guide 30
a is the groove 21 of the catcher 21 through the path shown by the broken line.
-b and installed above this 120-b.
The direction of movement is corrected toward the letter-shaped notch 21-a.

Then, as shown in FIG. 18 and FIG. 19 viewed from the arrow C side, the pin 30-a abuts on the 1-shaped notch 21-a, and the bottom surface of the base guide 30 touches the surface 21 of the catcher 21. -C, the loading ring 10 continues to move toward arrow A. direction to stretch the spring 10-d by a predetermined amount. As a result, the base guide 30 is pressed against the catcher 21, and its position on the plane and the state of inclination in the vertical direction are determined.

FIG. 20 is a plan view showing the positional relationship between the catcher 31 and the guide arm 12, which is rotated by the drive ring 32 in conjunction with the loading ring 10, and FIG. 21 is a side view thereof.

20 and 21, the tip of the guide arm 12 has a lever 79 that engages with the guide base 25.
are connected in a state where they are biased counterclockwise by a return spring 78. The lever 79 has a claw-like protrusion 79-
a is provided to engage with the side wall of the guide 81.

A side wall of the guide 81 extends linearly toward the catcher 31 and regulates the posture of the lever 79 and the guide base 25 during the loading operation.

As the guide arm 12 rotates, the guide base 25 moves and comes into contact with the catcher 31. Figure 22 and 2
Figure 3 shows the contact state. At this time, the positioning pin 25-a provided on the guide base 25 is connected to the catcher 3.
It is in contact with a 1-shaped notch 31-a provided in 1. The lower surface 25-b of the base guide 25 is in contact with a locally protruding surface 81-a at the tip of the guide guide 81.

Even after such a contact state is achieved, the fan-shaped gear 28 rotates to a predetermined angle change, presses one end 76-a of the return spring 76, and presses and positions the base guide 25 against the catcher 31.

The mechanism and operation of the loading mechanism have been described above. Next, as shown in FIGS. 24 and 25, the tension bin 1
6 and the correction guide 82 will be explained.

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.

In the figure, both the tension arm 16 and the correction guide arm 82 are rotatably supported by a shaft 83 press-fitted into the chassis 1.

In this unloading state, the tension arm 16. Tension bins 16-a are press-fitted into each tip of the correction guide arm 82.

The correction guide bin 82-a is the magnetic tape cartridge 77.
The magnetic tape 3 is housed behind a magnetic tape 3 stretched over an opening.

A spring 85 is stretched between the notch 16-b provided at one end of the tension arm 16 and the shaft 84 mounted on the chassis 1, so that the tension arm 16 is It is biased in the I & direction. Further, a spring 88 is stretched between a protrusion 82-b provided on the correction guide arm 82 and a protrusion 87 provided on the outer peripheral side surface of the chassis 1. is arrow B. is biased in the direction of 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 . For this reason,
Rotation of the tension arm 16 by the spring 85 is prevented by a correction guide arm 82 urged by a spring 88.

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 protrusion 16 -C of the tension arm 16 . This band brake 86
In the unloading state, as shown in the figure,
It is mounted in a slack state on the supply side reel stand 37.

Note that the end portion of the tension arm 16 where the notch 16-b is provided, the end portion 82-d of the correction guide arm 82, and the springs 85 and 88 are shown in FIG. 26, which is a side view of the portion shown in FIG. 24. As such, it is located sufficiently above the drive ring 32, and there is no fear of contact with the drive ring 32.

During the transition from this unloading state to the loading state, when the drive ring 32 is rotated in the direction of arrow AH, the protrusion 32-C provided on the drive ring 32 is at the end of the correction guide arm 82. The correction guide arm 82 contacts the portion 82-d and rotates in the direction of arrow A62 against the reaction force of the spring 8B. When this angle of rotation exceeds a certain value, the point of application of the force of the spring 88 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. Therefore, the correction guide arm 82 is moved by the spring 88 in the direction of arrow A, which is opposite to the unloading state. is biased in the direction of .

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

In the figure, correction guide arm 82 . is biased by springs 88 and 85 . The tension arm 16 pulls out the magnetic tape 3 from the base surface side, and forms a predetermined tape running path on the exit side of the magnetic tape cartridge 77. At this time, the correction guide arm 82 comes into contact with the protrusion 150-a of the guide plate 150, and the plane position is defined.

Further, since the protrusion 16-0 on the tension arm 16 is also rotated in the direction of arrow AI, the band brake 86 comes into contact with the supply side reel stand 37 with a predetermined tension. As a result, a predetermined braking torque is generated on the supply reel stand 37, and appropriate tension is applied to the magnetic tape 3 pulled out from the supply reel 6 during recording and reproduction.

When performing an unloading operation from this loading completed state, first, the protrusion 32-C on the drive ring 32 rotated in the direction of arrow B3 presses the protrusion 82-e of the correction guide arm 82, The correction guide arm 82 is rotated in the direction of arrow B8□ against the biasing force of the spring 88. The tension arm 16 is also pressed by the protrusion 82-C on the correction guide arm 82 and rotated in the direction of the arrow BI&. When the angle of this rotation exceeds a certain value, the correction guide arm 8
2 is arrow B by the spring 88. direction, and the tip is returned to the state where it is housed in the opening of the magnetic tape cartridge 77 as shown in FIG.

The tape running path shown in FIG. 2 is formed by the loading operation, crimping, and positioning operation 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 operation, in FIG. 5, the lock plate 58 on the drive ring 32 moves in the direction of arrow A32 together with the drive ring 32 to approach the switching gear 55. The switching gear 55 has a three-stage structure as explained in FIG. 6, and the middle switching plate 55-b is located at the height explained in FIG. 32
gear part 32-a and lower gear 55-C of switching gear 55
During the loading operation where the two engage with each other, it is spinning idly above it.

27 and 28 are plan views showing the positional relationship between the drive ring 32 and lock plate 58, and the switching plate 55-b of the switching gear 55 before and after the loading operation is completed.

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 58 on the drive ring 32 at both ends thereof. Therefore, until the lock plate 58 reaches the switching gear 55, the switching gear 55 rotates in the direction of arrow A55 because the lower gear 55-C is engaged with the gear portion 32-a of the drive ring 32. Although the gear part 32-
At the end of point a, the engagement with the lower gear 55-C is released. However, the switching gear 55 is further rotated by the end portion forming the tooth surface of the lock plate 58 pressing the boundary between the large diameter portion and the small diameter portion forming the tooth surface of the switching plate 55-b. The state shown in the figure will be obtained (in this case,
The meshing phase between the gear portion 32-a and the gear 55-C is determined by the lock plate 58 and the switching plate 5 at this end.
5-b).

In this state, the two boundaries between the large diameter portion and the small diameter portion of the switching plate 55-b are both locked and held by the inner circumferential surface of the lock plate 58.

As explained in FIG. 6, the gears 5s-a, 55-C and the switching plate 55- constituting the switching gear 55 have a fixed phase relationship, so the switching play 55-
When the gear 55-b is locked with the lock plate 58, the gear 55-a
The transmission gear 48.49 that meshes with this is also prevented from rotating.
, loading ring 10, and guide arm 12 are also prevented from rotating. The timing for locking the switching gear 55 is as follows:
Base guide 29 on the loading ring 10 described above
．． 30 and the base guide 25 on the guide arm 12,
The timing is set to be approximately equal to the timing when the respective catchers 20, 21, and 31 are pressed with a predetermined force.

By the above switching operation, the guide base 29°30.25
The positioning of the guide rollers provided above is maintained,
The running path of the tape is reliably maintained.

Further, in FIGS. 29 and 30, during this loading operation period, the lock plate 59 is also rotated in the direction of the arrow Asz together with the lock plate 58. During this rotation period, the inner peripheral surface of the lock plate 59 is rotated by the switching gear 56.
It is in sliding contact with two boundary parts between the large diameter part and the small diameter part of the upper stage switching plate 56-a (FIG. 8).

Since the switching gear 56 and the drive ring 32 are installed in the relationship explained in FIG.
As shown in the figure, the switching gear 56 is prevented from rotating. Therefore, the cam ring 38 also does not rotate during this period.

After the locking of the switching gear 55 by the locking plate 58 is completed as described above, the boundary between the tooth surface of the locking plate 59 and the gear portion 32-a of the drive ring 32 that moves in the direction of arrow A32. As shown in FIG. 30, the gear portion 32-a begins to press the boundary portion forming the tooth surface of the upper switching plate 56-a of the switching gear 56, and as it moves further, the gear portion 32-a presses the boundary portion forming the tooth surface of the upper switching plate 56-a of the switching gear 56. Gear 56-
Therefore, the lower gear 5 starts meshing with gear b.
The lower cam ring 38 of the drive ring 32 begins to rotate via the cam drive gear 57 that meshes with 6-C.

Next, the mode operation performed by rotating the cam ring 38 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 38 is rotated.

In the figure, gears for driving these are arranged near the winding reel stand 36 and the supply reel stand 37, as shown in the figure, and between these gears and the chassis 1,
Braking members for braking the reel stand 36 for several windings and the supply reel stand 37 are provided.

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

In the figure, the uneven surface of the cam provided on the inner circumference of the cam ring 38 includes a main brake operating lever 91-a, a supply side reel stand sub-brake operating arm 92-a, and a take-up side reel stand brake operating arm 94-a. a, Take-up side reel stand sub-brake 95° The operating end of the pinch roller operating lever 96-a is in contact with it.

These cam surfaces provided on the inner circumference of the cam ring 38 are
It is mainly composed of two arcuate surfaces with different radii of curvature and a tapered surface connecting them.

By rotating this cam ring 38, the operated members are moved to the shaft 91-8.92-5.9 press-fitted onto the chassis 1.
4-3, 95-5, and 96-3, and performs operations such as applying braking torque to the take-up reel stand 36 and the supply reel stand 37, and pressing the pinch roller 15 onto the capstan 14. conduct.

The case where the operating end of the operated member is in contact with the arcuate surface with a small radius of curvature of the cam ring 38 is called the H position, and the case where it is in contact with the arcuate surface with a large radius of curvature is called the L position. , I will call them respectively.

The idler gear operation slider 93 is biased by a spring 110 into contact with the inner circumferential surface of the cam ring 38 . Only the cam surface of the cam ring 3B that operates this idler gear operating slider 93 is composed of circular arc surfaces with three different radii of curvature, so that the idler gear operating slider 93 can take three positions. Hereinafter, these three positions will be referred to as H, M, and L in descending order of the radius of the cam surface.

During the loading operation described in FIG. 23, the main brake 91 is activated by the take-up reel stand 36. Located in a position that does not contact the supply side reel stand 37, the supply side reel stand sub-brake 929 and the take-up side reel stand sub-brake 95
Only the supply side reel stand 372 and the take-up side reel stand 36 are in contact with each other.

FIG. 33 shows this idler gear operation slider 93 and the idler gear support plate 97 located above it. Idler gear 981 Winding gear 99. 34 is a plan view showing the arrangement relationship with the FR gear 100, and FIG. 34 is a sectional view taken along line xx'. However, these FIGS. 33 and 34 show a state in which the idler gear operation slider 93 is in the H position.

In FIGS. 33 and 34, the idler gear operating slider 93 is held by a holder 101 so as to be slidable on the 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 substantially elliptical recess, which projects upward from the chassis 1, as shown in FIG. The idler gear support plate 97 is placed on the upper surface of this protruding part, and above it are the shafts 100-s and 99-s on which the FE gear 100 and the winding gear 99 are press-fitted into the chassis 1.
Since it is rotatably arranged around the , its vertical position is restricted. A boss 102 is caulked at the center of the idler gear support plate 97, and a shaft 103 is press-fitted through the hole in the boss 102. and,
The idler gear 98 is rotatably supported by the shaft 103 and is pressed against the idler gear support plate 97 by the felt 104.
A predetermined rotational driving 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 the elliptical large portion 93-a of the idler gear operation slider 93.

Therefore, the idler gear operation slider 93
8 to the L, M, and H positions, the shaft 103 is pressed, and the idler gear support plate 97 and the idler gear 98 pivotally supported thereon are pressed.
If or move in the H direction. When this idler gear 98 moves in the direction of arrow H, the FR gear 1
00, and the winding gear 9 moves in the direction of the arrow.
9, respectively, and when it is located at M, it does not mesh with any of these.

Therefore, when the cam ring 3 is rotated in the direction of arrow A1g from the arrangement shown in FIGS. 31 and 32, the cam surface causes each input end of the operated member to be FF/Rev to go back 7 volumes), loading dust knob (stopping with loading)
, recording (/playback/fast-forward playback) modes are shifted by a predetermined amount. The rotation angle of the cam ring 38 is detected by the printed patterns 38-b and 38-C on the cam ring 38 described in FIG.

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 38 is rotated in the direction of arrow A38 from the loading operation period shown in FIGS. 31 and 32 and enters the loading dust knob mode. It shows.

In this loading dust knob mode, only the main brake operating lever 91-a is rotated to the 1st side, and the brake section at its output end is connected to the take-up side reel stand 36. Further, the idler gear operation slider 93, which prevents the rotation of the supply side reel stand 37, is in the M position, and the idler gear 98 is not meshed with either the take-up gear 99 or the FR gear 100.

FIG. 36 shows a state in which the cam ring 38 has been further rotated in the direction of arrow A3 from the loading dust knob mode shown in FIG. 33, and the brakes have entered the recording (playback, fast forward playback) mode. ing.

In the figure, the pinch roller operating lever 96 is rotated in the H direction, the pinch roller arm 13 engaged with its output end is rotated, and the pinch roller 15 is pressed against the capstan 14. Each brake operating lever is rotated in the H direction and the take-up side reel stand 36. The connection with the supply side reel stand 37 is released. However, the band brake 86 shown in FIG. 25 comes into contact with the outer peripheral surface of the supply side reel stand 37 and applies a predetermined tension to the running magnetic tape.

Further, the idler gear operation slider 93 moves to the L position, and the idler gear 98 engages with 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 T19. As a result, the idler gear 98 that has engaged the take-up gear 99 also engages the gear 106 on the outer periphery of the take-up reel stand 36, thereby rotating the take-up reel stand 36 in the direction of arrow T3&. And capstan 14. By rotating the cylinder 2 counterclockwise, the magnetic tape 3 is run and scanned.

38 and 39 show the position of the cam ring 38 during fast forwarding or rewinding.

In this case, sub-brakes 92° 95 are in contact with the supply reel stand 36 and the take-up reel stand 37, respectively, and the pinch roller 15 is no longer pressed against the capstan 14. Then, the idler gear operation slider 93 moves toward the arrow H side, thereby causing the idler gear 98 to mesh with the FR gear 100. This FR gear 10
0 is caused by the gear 109 that engages the gear 108 of the capstan 14 in conjunction with the rotation of the pinch roller arm 13.
It is connected to the capstan 14 via a transmission gear train,
It is rotated by the rotation of the capstan 14.

Therefore, during fast forwarding, the capstan 14 rotates clockwise in the drawing, rotates the FR gear 100 counterclockwise, and the idler gear 98 caught in this is biased rightward, and the take-up reel stand Transmission gear 106.1 to 36
07 to give clockwise rotation to the take-up reel stand 36. In addition, in the case of rewinding, the capstan 14
is reversed and idler gear 9 is transmission gear 111, 112.
It is connected to the supply side reel stand 37 via, and transmits counterclockwise rotational force thereto.

The above operation satisfies the condition as a normal recording/reproducing device.

〔Effect of the invention〕

As described above, according to the present invention, all operations of the mechanism can be performed by gear drive.
The reliability of the device can be ensured by increasing the reliability of operation against environmental changes, a low-load mechanism with high transmission efficiency can be obtained, and the ease of assembly can be improved.

[Brief explanation of drawings]

1 to 39 show one embodiment of the mechanism operating mechanism of the magnetic recording and reproducing apparatus according to the present invention,
The figure is an overall plan view showing the state at the time of unloading.
The figure is a plan view showing the state during loading, Figure 3 is a developed view showing the attachment relationship of rings to the chassis, and Figure 4 is a perspective view showing the deceleration mechanism for transmitting the driving force of the loading mode motor to the drive ring. Fig. 5 is a plan view showing the power transmission mechanism from the drive ring to the loading ring or cam ring, Fig. 6 is a developed view showing the structure of the first switching gear in Fig. 5, and Fig. 7 is a plan view showing the power transmission mechanism from the drive ring to the loading ring or cam ring. A cross-sectional view showing the height relationship between the switching gear, drive ring, and cam ring.
FIG. 8 is a developed view showing the structure of the second switching gear in FIG. 5, FIG. 9 is a sectional view showing the height relationship between the second switching gear, the drive ring, and the cam ring, and FIG. FIG. 11 is a plan view showing the positional relationship between the cam drive gear and the cam ring that mesh with the switching gear No. 2, and FIG. 11 shows the loading mode motor, the drive ring, and the loading ring. A plan view showing the connection state of the transmission gear train between the guide arms,
FIG. 12 is a partial sectional view thereof, FIG. 13 is an overall plan view of the loading mechanism, and FIG. 14 is a plan view showing the state in which the first guide base in FIG. 13 is in contact with the first catcher. FIG. 15 is a side view of the same, FIG. 16 is a plan view showing the state in which the second guide base in FIG. 13 is rotated by the loading ring, FIG. 17 is a side view of the second guide base, and FIG. FIG. 19 is a plan view showing a state where the second guide base is in contact with the second catcher, FIG. 19 is a side view thereof, and FIG. 20 is a plan view showing the positional relationship between the guide arm rotated by the guide arm and the third catcher. Plan view shown, second
Figure 1 is a side view of the same, Figure 22 is a plan view showing the third base guide in contact with the third catcher, Figure 23 is a side view of the same, and Figure 24 shows the tension arm during unloading. FIG. 25 is a plan view showing the arrangement relationship with the correction guide arm, FIG. 25 is a sectional view showing the arrangement relationship between the tension arm and the correction guide during loading, and FIG. 26 is a cross section showing the height relationship between the tension arm and the correction guide. 27 and 28 are plan views showing the positional relationship between the first lock plate of the drive ring and the switching plate of the first switching gear before and after the loading operation is completed, and FIGS. 29 and 30 are FIG. 31 is a plan view showing the positional relationship between the second lock plate of the drive ring and the switching plate of the second switching gear during the loading operation, respectively; FIG.
32 is a plan view showing the arrangement of brakes relative to the cam ring, and FIG. 33 is a plan view showing the arrangement of the reel stand braking members and driving members relative to the cam ring. A plan view showing a switching mechanism;
Figure 34 is a sectional view taken along line x-x' in Figure 33;
The figure is a plan view showing the arrangement of the operated members shown in Fig. 32 in the loading dust knob mode, Fig. 36 is a plan view showing the arrangement during recording, playback, and fast-forward playback, and Fig. 37 is a plan view showing the arrangement of the operated members shown in Fig. 32 in the loading dust knob mode. , a plan view showing the state of the driving force transmission mechanism to the reel stand during playback and fast-forward play; FIG. 38 is a plan view showing the arrangement of the operated members shown in FIG. 32 during fast-forward or rewind; FIG. 39 is a plan view showing the state of the driving force transmission mechanism to the reel stand. 1...Chassis, 2...Rotating cylinder,
3... Magnetic tape, 5... Take-up reel, 6... Supply reel, 7.8, 9.11...
... Guide roller, 10 ... Loading ring, 27 ... Loading mode motor, 3
2... Drive ring, 38... Cam ring, 55... First switching gear, 56...
...Second switching gear, 58...First lock plate, 59...Second lock plate. Figure 1 Figure 3 Figure 5 Figure 8 Figure 10 Figure 12 Figure 11 Figure 13 Figure 2! Fig. 14 Fig. 19 Fig. 22 Fig. 24 Fig. 26 Fig. 27 Fig. 28 Fig. 33 Fig. 34 Fig. 37 Fig. 38

Claims (1)

[Claims] 1. A tape guide drum equipped with a magnetic head, a tape guide group that pulls out the magnetic tape from a magnetic tape cartridge containing supply and take-up reels, and a tape guide group that pulls out the magnetic tape from the opening of the magnetic tape cartridge to the tape guide drum. There is a loading mechanism that pulls out and moves the magnetic tape to a nearby location, a mode operating mechanism that controls the operation of the reel stand, pinch rollers, etc. according to various recording and playback modes, and a motor control mechanism that controls the operation of the motor in conjunction with the operation of the mode operating mechanism. In a magnetic recording/reproducing device comprising a tape drive mechanism that transmits power to a capstan or a reel stand, and a drive force switching mechanism that selectively transmits power from the drive source to a loading mechanism and a mode operation mechanism, the drive A magnetic recording and reproducing device comprising a force switching mechanism and a power transmission mechanism from a drive source to a loading mechanism and a mode operating mechanism comprising a gear and a ring having a gear portion on at least a part of its circumferential surface. Mechanism operation mechanism.