JP3519178B2 - Magnetic recording / reproducing device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a magnetic recording / reproducing apparatus such as a video tape recorder (hereinafter referred to as VTR), and more particularly to a structure for drive transmission and brake control.

[0002]

2. Description of the Related Art Conventionally, a drive system of a VTR, which is a magnetic recording / reproducing apparatus, is constructed as shown in FIG. As shown in FIG. 18, a deck lamp 1 which is a mounting board for mechanical parts is provided with a cassette lamp 2 as a light source for detecting the end of a magnetic tape in a tape cassette, and V
The cassette lamp 2 is arranged so that the tip of the cassette lamp 2 is introduced into substantially the center of the inside of the tape cassette which is inserted into the tape cassette insertion port of the TR main body and transferred to a predetermined position by the cassette transfer means. Light is emitted in a predetermined direction from 2 and the end of the magnetic tape is detected by discriminating the change in the light transmittance between the magnetic surface of the magnetic tape and the transparent portion of the leader tape on the side of the light receiver.

A magnetic tape in a tape cassette inserted in the VTR body is wound around a rotary drum 3 by a loading mechanism. The rotary drum 3 is an upper drum provided with a lower drum and a magnetic head. The lower drum is joined to the deck base 1, and the upper drum is rotatably provided with respect to the lower drum about an axis which is planted in the lower drum and rotated by a drum motor. The loading shaft 4 pulls out the magnetic tape from the tape cassette and moves in the direction of the rotary drum 3 along the shaft guide grooves formed in the deck base 1, so that the magnetic tape is wound around the rotary drum 3 at a winding angle of more than 180 °. It is designed to be used.

Further, the capstan 6 is driven by the capstan motor, and the pulley for driving the reel disk 8 is driven via the reel belt 7, so that the gear train whose rotation speed can be switched and the torque control. 1 and a known mechanism such as a swing idler 11 that transmits a driving force to a reel gear 9 that selectively determines the rotation directions of the pair of reel disks 8.
The rotation of the pulley described above through
On the other hand, the magnetic tape is clamped between the shaft of the capstan 6 and the pinch roller 12 at a specified pressure to run in a predetermined direction, and the capstan brake 13 controls the braking. But, Capstan 6
The mechanism described above enables the rotational drive force and the rotational speed of the reel disk 8 to be controlled with high precision.
In FIG. 18, reference numeral 15 is an arm pin, which is rotated to a position in contact with the capstan 6, and the rotation of the arm pin 15 facilitates the operation of the pinch roller 12.

By the way, the motor 17 serves as a driving source for controlling the winding of the magnetic tape around the rotating drum 3, braking control for running the magnetic tape, and driving control for a member for pressing the magnetic tape against the capstan 6. , This motor 1
The rotation of 7 is transmitted to the worm gear 19 via the belt 18, and after the rotation of the motor 17 is sufficiently reduced by the worm gear 19, the rotation is transmitted to the worm wheel 21 meshed with the worm gear 19. .

A small gear having a diameter smaller than that of the worm wheel 21 is coaxially provided, and the rotation of the worm wheel 21 is transmitted to the cam gear 22 meshed with the small gear. The main rack formed on the first cam plate 23 meshes with a small gear that is provided coaxially with the cam gear 22, and the rotation of the cam gear 22 causes the first cam plate 2 to rotate.
3 is converted into a linear motion and transmitted to the second cam plate 24, and the second cam plate 24 moves linearly in conjunction with the first cam plate 23.

At this time, a cam groove for controlling the operation of the capstan brake 13 and the arm pin 15 is formed in the cam gear 22, and the first cam plate 23 has an elongated shape in the movement direction. The first cam plate 23 is provided with some auxiliary racks in addition to the main rack described above,
The driving force of the first cam plate 23 is transmitted by these auxiliary racks and gears (not shown) and the movement of both loading shafts 4 is controlled, and moreover, the center of the first cam plate 23 is controlled. A long cutout hole 25 is formed in the portion so that the cassette lamp 2 does not interfere with the linear movement of the first cam plate 23.

The main brake 26 is the reel disc 8
The brake is applied to stop the rotation of the reel disk 8 instantly, and the auxiliary brake 27 operates so as to control to a specified torque by applying a predetermined friction coefficient and pressure to the rotating reel disk 8. The operation of the brake 27 is also controlled by the first cam plate 23.

That is, the second cam plate 24 moves in the direction of approaching the worm gear 19 in conjunction with the first cam plate 23, and the tip of the second cam plate 24 is provided coaxially with the worm gear 19. When the stop key or the pause / still key is operated at the position just before coming into contact with the second cam 28, the second cam plate 24 slightly moves in the direction of the fan 28 and its tip comes into contact with the fan 28. The contact of the second cam plate 24 with the fan 28 triggers the engagement of the claw (not shown) provided on the second cam plate 24 so as to interlock with the first cam plate 23. The interlocking of the second cam plate 24 is released, the second cam plate 24 is moved in the direction opposite to the moving direction up to then by the biasing force of the spring, etc., and the main brake 26 and the auxiliary brake 27 are moved to the reel disc 8. To be pressed There.

By the way, the above-mentioned warm wheel 21
Is also transmitted to the intermediate gear 30 meshed with the cam gear 22, and the rotation of the intermediate gear 30 is further transmitted to the pinch roller drive gear 31, and the pinch roller holding member is controlled to apply a predetermined pressure to the rotation of the pinch roller 12. It is added and stopped.

Further, a tension brake is provided on the supply side of both reel disks 8, and when the tension of the running magnetic tape detected by the tension pole exceeds a set value, the tension arm 33 is planted on the deck base 1. By rotating the tension arm 33 in a certain direction by rotating about the provided shaft, the tension arm 3 is loosely wound around the reel disk 8 on the supply side and the tension arms 3 are provided at both ends.
3 and the tension belt 35 locked by the tension holding member 34 is pressed against the reel disk 8 and back tension is applied to the reel disk 8 on the supply side to keep the tension of the magnetic tape constant. At this time,
The tension arm 33 is rotated by the rotation of the cam gear 37 accompanying the movement of the first cam plate 23. In FIG. 18, reference numeral 38 denotes a pair of arm gears that convert the linear movement of the first cam plate 23 into a rotational movement and apply a driving force to both the loading shafts 4 described above.

Next, the transmission path of the rotational driving force will be summarized and described. First, the rotation of the motor 17 is transmitted to the cam gear 22 and the intermediate gear 30 via the belt 18, the worm gear 19, and the worm wheel 21, and the worm wheel 2
The rotation of the worm wheel 21 is converted into a linear motion by the main rack of the first cam plate 23 meshed with the first small gear, and the first cam plate 23 moves rightward on the paper surface of FIG. The second cam plate 24 also moves in the same direction in conjunction with each other.

When the first cam plate 23 moves in this way, an auxiliary rack provided on another portion of the first cam plate 23 rotates the arm gear 38 meshed with the auxiliary rack, and the arm gear 38 rotates to the arm portion. Both loading shafts 4 freely engaged with each other move along the shaft guide groove of the deck base 1, and the magnetic tape in the tape cassette inserted in the VTR main body is pulled out by the both loading shafts 4 to rotate the rotary drum 3 The winding angle is greater than 180 °.

Further, by the movement of the first cam plate 23, the cam gear 3 meshed with another auxiliary rack of the first cam plate 23.
7 rotates, and the boss of the tension arm 33 engaged with the cam groove formed in the cam gear 37 causes the cam gear 3 to rotate.
With the rotation of 7, the tension arm 3 slides in the cam groove.
3 rotates.

Further, the main brake 26 and the auxiliary brake 27 are rotatably supported by a shaft planted in the deck base 1 so as to be rotatable.
The operation is controlled according to the shape of the cam formed on the first cam plate 23, and the reel disk 8 is braked.

When the rotation of the worm wheel 21 is transmitted to the intermediate gear 30, the rotation of the intermediate gear 30 is also transmitted to the pinch roller driving gear 31, and the operation of the pinch roller holding member is controlled to control the capstan 6. And pinch roller 1
The feeding amount of the magnetic tape sandwiched between the two is controlled to be constant.

On the other hand, the rotation driving force of the capstan 6 is transmitted by the capstan motor via the reel belt 7. When the rotation of the capstan 6 is transmitted to the reel unit 10, the gear train of the reel unit 10 causes the rotation. At the same time that the rotation speed is converted, torque control is performed by the slip mechanism of the reel unit 10, and the swing idler 1
The rotation direction of the reel disk 8 is determined by 1 and the transmission path of the rotational driving force is switched, and both reel disks 8 are rotated in the determined direction via the reel gear 9.

[0018]

However, in the above-mentioned conventional structure, the rotation of the motor 17 is transmitted by the elongated first cam plate 23 and the second cam plate 24 to move both loading shafts 4. Since the operation of the main and auxiliary brakes 26, 27 for braking the reel disk 8 is controlled, a large space for moving the first cam plate 23 must be secured, which is more than necessary. In addition, it causes an increase in the size of the entire device.

Further, because the cassette lamp 2 is arranged so that the cassette lamp 2 is located substantially at the center of the tape cassette in the loaded state, interference between the cassette lamp 2 and the first cam plate 23 is avoided. Therefore, as described above, the cutout hole 2 is formed substantially in the center of the first cam plate 23.
5 must be formed, and thus the first cam plate 2
When the cutout hole 25 is formed in the slit 3, the cutout hole 25 is formed when the number of objects whose operations are to be controlled by the first cam plate 23 increases.
Due to the existence of the above, it is not possible to form a cam or the like for controlling the increased movement of the object on the first cam plate 23 any more, and there is a disadvantage that there is a large design constraint.

The present invention has been made to solve the above-mentioned problems, and does not require a large moving space unlike the conventional cam plate, and the object to be controlled due to the increase of ancillary functions. The purpose is to facilitate addition.

[0021]

The invention according to claim 1 is
By inserting a tape cassette, in which a magnetic tape is wound around a pair of reels, into the insertion opening of the main body of the apparatus, the tape cassette is transferred to a predetermined position inside the main body, and a pair of loading shafts are used from the tape cassette after the transfer. In a magnetic recording / reproducing apparatus having a function of pulling out the magnetic tape, winding the magnetic tape around a rotating drum, and braking the reel disk by a brake member that presses against a reel disk that rotationally drives the reel in a stop mode or a pause / still mode, A cassette lamp for detecting the end of the magnetic tape, which is arranged so as to be located substantially at the center of the tape cassette transferred to a predetermined position inside the main body, and a rotational driving force of a motor, which includes a gear train and a cam gear, is applied to the brake member. Transmitted by the cam groove pattern of the cam gear And a transmission means for controlling the operation of both loading shafts and driving the brake member in a direction in which the brake member is pressed against the reel disc in the stop mode or the pause / still mode, and the cassette lamp is provided at the rotation center of the cam gear of the transmission means. It is characterized by being located.

According to a second aspect of the present invention, there is provided a boss that slides in a cam groove formed in the cam gear of the transmission means and an elongated hole into which the cassette lamp is inserted, and by rotating the cam gear. The boss further comprises a cam that slides in the cam groove and linearly moves in the longitudinal direction of the elongated hole,
The brake member may be driven in a direction in which it is pressed against the reel disk by movement of the cam in the stop mode or the pause / still mode.

At this time, as described in claim 3, a transmission member for transmitting the rotation of one gear of the gear train of the transmission means is further provided, and the straight line in the longitudinal direction of the elongated hole of the cam is provided. It is also effective to control the target movement by the operation of the transmission member.

Further, according to a fourth aspect, one transmission gear of the gear train of the transmission means has outer teeth and inner teeth, and the cam gear of the transmission means has inner teeth of the transmission gear. It is preferable to further include a planetary gear having teeth smaller in diameter than the above, and meshing with the internal teeth of the cam gear and the transmission gear.

Further, as described in claim 5, an engaging portion is provided on the outer peripheral portion of the cam gear of the transmitting means, the engaging portion is rotatably supported by a fixed shaft near the cam gear, and a locking body is provided at a tip portion thereof. A lever formed with a boss that engages with the engaging portion and a notch groove formed in the peripheral portion of the lever that is provided coaxially with the cam gear, engages and disengageably engages the engaging body of the lever. A cam that separates the locking body from the cutout groove due to the engagement of the lever with the boss of the engagement portion accompanying the rotation of the cam gear, and the locking body when the locking body is locked in the cutout groove. A first urging means for urging the cam so as to rotate the cam in the urging direction when the locking body is disengaged from the notch groove, and when the stop mode or the pause / still mode is performed, the first urging means is provided. The brake member is released by the rotation in the urging direction. Preferably to be driven in a direction to press the disk.

By the way, as described in claim 6, the second urging means urges the unidirectional force in one direction against the urging force of the second urging means by the cam gear of the transmitting means. A cam plate which is held in a state of being moved in the opposite other direction, and linearly moves in the one direction by the biasing force in the stop mode or the pause / still mode to drive the brake member in a direction in which the brake member is pressed against the reel disc. To
It is also effective to further provide in the vicinity of the cam gear.

Further, as described in claim 7, a first arm gear provided in the vicinity of the cam gear of the transmission means, a second arm gear meshing with the first arm gear, and one end of the both arm gears. A first arm and a second arm that are pivotally supported to move the loading shafts by the rotation of the both arm gears, and the first and second arm gears are provided coaxially with the first arm gear and mesh with the cam gear to rotate the cam gears. And a cam that is formed on the tooth surface of the transmission gear and that is inserted into a tooth missing portion formed on a part of the tooth surface of the cam gear to cancel the rotation transmission of the cam gear. May be.

Further, as described in claim 8, a first intermediate member for meshing with any one of the gear trains of the transmission means and the cam gear to control the operation of the tension arm of the back tension mechanism. It is preferable to further include a second intermediate gear that controls the operation of the gear and the pinch roller.

[0029]

According to the first aspect of the present invention, the rotational driving force of the motor is transmitted to both loading shafts and the brake member by the transmission means including the gear train and the cam gear, and the both loading shafts cause the magnetic force from the tape cassette after the transfer. The tape is pulled out and wound around the rotary drum, and in the stop mode or the pause / still mode, the brake member is pressed against the reel disc to apply the braking. At this time, since the rotation center of the cam gear of the transmission means is aligned with the cassette lamp, there is no need for a space for movement unlike the conventional long cam plate, and the overall size of the device is prevented from increasing. Even if an additional function is added, it is possible to deal with it only by changing the pattern of the cam groove formed in the cam gear, and it is possible to easily increase the number of objects whose operation is controlled by the cam gear.

According to the second aspect of the present invention, since the brake member is pressed against the reel disk by the movement of the elongated hole of the cam in the longitudinal direction, the moving space is not so large as in the conventional long cam plate. However, it is effective when there are restrictions on the cam groove that can be formed in the cam gear of the transmission means.

By the way, when the restriction of the cam groove which can be formed in the cam gear is further large, the operation of the brake member can be controlled by separately providing the transmission member as described in claim 3.

Further, in the invention according to claim 4,
Since the planetary gear is provided so as to mesh with the inner teeth of the cam gear and the transmission gear, the rotation of the motor is transmitted to the transmission gear, and when the planetary gear is further transmitted to the cam gear, the speed is sufficiently reduced. Compared to the case where the rotation of the transmission gear is directly transmitted to the cam gear, the rotation amount of the cam gear is much smaller when the planet gear is used for the same rotation amount of the transmission gear, and the cam groove of the cam gear can be formed correspondingly. The area is substantially expanded, and the variety of cam grooves can be diversified.

Further, in the invention of claim 5, the braking of the brake member can be controlled by the lever, the cam and the urging means, and like the invention of claim 3, the cam gear of the transmitting means is formed. This is effective when there are restrictions on the cam grooves to be obtained.

Further, in the invention according to claim 6,
Braking is performed by driving the brake member by the movement of the cam plate.

In the invention according to claim 7, the rotational driving force of the motor is transmitted to both loading shafts via the transmission means by the first and second arm gears, the transmission gear and the first and second arms. Then, the magnetic tape is pulled out from the tape cassette after being transferred and wound around the rotary drum.

Further, in the invention according to claim 8,
The operation of the tension arm of the back tension mechanism is controlled by the first intermediate gear, and the operation of the pinch roller is controlled by the second intermediate gear.

[0037]

【Example】

(First Embodiment) FIGS. 1 and 2 show a first embodiment of the present invention. FIG. 1 is a plan view and FIG. 2 is a partial exploded perspective view.
However, in FIG. 1, the same reference numerals as those in FIG. 18 indicate the same or corresponding parts, and in the following description, duplicated description will be avoided and differences from FIG. 18 will be mainly described.

As shown in FIG. 1, the first transmission gear 41 meshes with the first cam gear 22, and the second cam gear 42 meshes with the first transmission gear 41. At this time, the second cam gear The second cam gear 42 is arranged so that the rotation center of 42 and the central axis of the cassette lamp 2 coincide with each other, and the rotation of the motor 17 passes through the belt 18, the worm gear 19, the worm wheel 21, the first cam gear 22 and the intermediate gear 30. The rotation of the first cam gear 22 is transmitted to the second cam gear 42 by the transmission gear 41, the second cam gear 42 rotates about the cassette lamp 2, and the second cam gear 42 rotates.
The second transmission gear 43 meshed with the second cam gear 42 is rotated by the rotation of the second cam gear 42. The worm wheel 21, the first cam gear 22, the intermediate gear 30, the pinch roller drive gear 31, the first and the first gears. A transmission means 44 is configured by the gear train including the two transmission gears 41 and 43 and the second cam gear 42.

The rotation of the second transmission gear 43 drives the tension arm 33 to control the back tension of the running magnetic tape, while the rotation of the second cam gear 42 is transmitted to the pair of arm gears 38. Is
By rotating these arm gears 38, both arm gears 3
8. The arms, one end of which is pivoted to each of them, move, and by the movement of these arms, both loading shafts 4 move in the direction of the rotating drum 3 along the shaft guide groove of the deck base 1 and are transferred to a predetermined position. The magnetic tape in the cassette is pulled out and wound around the rotary drum 3 at a winding angle of more than 180 °.

Further, the second cam gear 42 is, for example, as shown in FIG.
Several cam grooves 46 as shown in FIG. 2 are formed, and bosses provided on the main brake 26 and the auxiliary brake 27, which are brake members, are fitted and inserted into the cam grooves 46, respectively.
As the cam gear 42 rotates, the bosses of both brakes 26 and 27 slide in the cam groove 46, and the auxiliary brake 27 is urged by the urging means such as a spring (not shown) against the rotating reel disk 8. The reel disc 8 is controlled to a prescribed torque by applying a predetermined friction coefficient and pressure, while the main brake 26 resists the urging force of an urging means such as a spring (not shown) in the play, fast-forward and rewind modes. It is regulated in a direction away from the reel disc 8, and in the stop mode or the pause / still mode, such regulation is released by the pattern of the cam groove 46, and the main brake 26 causes the main disc 26 to be driven by the biasing force of the biasing means.
And the reel disk 8 is braked.

At this time, as shown in FIG. 2, the main and auxiliary brakes 26 and 27 are pivotally supported by the shaft planted in the deck base 1, and each boss is an arc-shaped transparent member formed in the deck base 1. It is inserted into the hole 47 and fitted into the cam groove 46.

Therefore, according to the first embodiment, since the center of rotation of the second cam gear 42 coincides with the cassette lamp 2, a space for movement is required like a conventional long cam plate. It is possible to prevent the size of the entire device from increasing.

Further, since the cassette lamp 2 is at a position equidistant from both reel disks 8 according to the JIS standard, and the rotation center of the second cam gear 42 is aligned with the cassette lamp 2, the supply side and the winding side. Reel disk 8
The main and auxiliary brakes 26 and 27 can have symmetrical shapes, and the control of these brakes can be performed very easily compared to the case where a conventional long cam plate is used due to the symmetrical positional relationship. become.

In addition, when another accessory function using the motor 17 as a drive source is added, it can be easily dealt with by simply changing the pattern of the cam groove 46 formed in the second cam gear 42. It is possible to easily increase the number of objects whose operations are controlled by the cam gear 42.

(Second Embodiment) FIGS. 3 and 4 show a second embodiment of the present invention. FIG. 3 is a plan view and FIG. 4 is a partial exploded perspective view. However, in FIG. 3, the same reference numerals as those in FIG. 1 indicate the same or corresponding ones, and in the following description, duplicated description will be avoided and differences from FIG. 1 will be mainly described.

As shown in FIG. 3, a substantially semi-disc shaped cam 50 is provided so as to overlap the second cam gear 42, and a long hole 51 into which the cassette lamp 2 is fitted is formed in the cam 50. Further, as shown in FIG. 4, the second cam gear 4 of the cam 50 is
A boss 52 is formed on a surface facing the cam 2, and the boss 52 is fitted into the cam groove 53 of the second cam gear 42.
Is urged in the direction opposite to the arc side, and the boss 52 slides in the cam groove 53 by the rotation of the second cam gear 42. Further, the cam 50 has several through holes 5
5 are formed, and the main and auxiliary brakes 2 are formed in these through holes 55.
The bosses 52 of 6, 27 are inserted and inserted into the other cam grooves of the second cam gear 42.

The rotation of the second cam gear 42 causes the boss 52 to slide in the cam groove 53, but in the play, fast-forward and rewind modes, the main brake 26 resists the urging force of the spring 54 and the main brake 26 moves. The cam 50 is regulated in the direction away from 8, and the stop mode or pause /
In the still mode, such regulation is released by the pattern of the cam groove 53, and the urging force of the spring 54 causes the cam 5 to move.
0 linearly and instantaneously moves along the long hole 51, and the linear movement of the cam 50 causes the main brake 26 to instantaneously move in the direction in which the main brake 26 is pressed against the reel disc 8.
Braking is performed.

Therefore, according to the second embodiment, the same effect as that of the first embodiment can be obtained as the effect of the center of rotation of the second cam gear 42 coinciding with the cassette lamp 2, and in particular, When the cam groove that can be formed in the second cam gear 42 is restricted, by providing the cam 50 that linearly moves by the length of the elongated hole 51, the operation of the main brake 26 can be performed without requiring a large space. It is possible to control instantly, and it is possible to easily cope with the addition of an incidental function only by changing the shape of the cam 50.

(Third Embodiment) FIGS. 5 and 6 show a third embodiment of the present invention. FIG. 5 is a plan view and FIG. 6 is a partial exploded perspective view. However, in FIG. 5, the same reference numerals as those in FIG. 3 indicate the same or corresponding ones, and in the following description, duplicated description will be avoided and differences from FIG. 3 will be mainly described.

As shown in FIGS. 5 and 6, a substantially central portion of a V-shaped lever 58, which is a transmission member, is coaxially supported with the first transmission gear 41, and one end and the other end of the lever 58 are pivotally supported. Bosses 59 and 60 are formed on the respective parts, one boss 59 is fitted into a cam groove 61 formed in the first cam gear 22 and slides in the cam groove 61, and the other boss 60 is inserted into the cam 50. The cam 50 is slidably contacted with the peripheral surface opposite to the arcuate peripheral surface.
Control the behavior of.

The rotation of the first cam gear 22 causes one of the bosses 59 of the lever 58 to slide in the cam groove 61, but in the play, fast-forward and rewind modes, the lever 58 is rotated.
The other boss 60 comes into sliding contact with the peripheral surface of the cam 50 opposite to the arcuate peripheral surface thereof, so that the cam 50 is regulated in the direction in which the main brake 26 separates from the reel disk 8 against the biasing force of the spring 54. In the stop mode or the pause / still mode, the cam groove 6 of the first cam gear 22 is
According to the pattern of 1, the cam 5 by such a lever 58
0 regulation is released and the cam 50 is driven by the urging force of the spring 54.
Moves instantly in a straight line along the long hole 51, and the cam 5
By the linear movement of 0, the main brake 26 is instantaneously moved in the direction in which the main brake 26 is pressed against the reel disc 8, and the reel disc 8 is braked.

Therefore, according to the third embodiment, it is particularly effective when the constraint in forming the cam groove in the second cam gear 42 is more severe than that in the second embodiment, and the operation of the cam 50 is driven. By using the lever 58 controlled by the cam groove 61 of the first cam gear 22, the operation of the main brake 26 can be controlled without requiring a large space.

(Fourth Embodiment) FIGS. 7 and 8 show a fourth embodiment of the present invention. FIG. 7 is a plan view and FIG. 8 is a partial exploded perspective view. However, in FIG. 7, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and in the following description, duplicated description will be avoided, and differences from FIG. 1 will be mainly described.

As shown in FIGS. 7 and 8, a ring-shaped third transmission gear 64 is provided coaxially with the second cam gear 42, and external teeth 65 are provided on the outer peripheral surface of the third transmission gear 64. The inner teeth 66 are formed on the inner circumferential surface of the second cam gear 42, the teeth 69 are formed on the boss portion 68 of the second cam gear 42, and the outer teeth 65 of the third transmission gear 64 are formed. Is the first
Of the third transmission gear 64 and the teeth 69 of the second cam gear 42 are meshed with the planetary gear 70, and the planetary gear 70 is provided. It is pivotally supported by a pin 72 that is planted on a fixed plate 71 fixed to the first device. At this time, the cassette lamp 2
The fixed plate 71 is arranged so as to penetrate through the fixed plate 71, and the operation of the main and auxiliary brakes 26, 27 is controlled by the pattern of the cam groove 46 of the second cam gear 42 as in the case of FIG. It has become so.

The rotation of the first transmission gear 41 causes the third transmission gear 64 to rotate, and the third transmission gear 64 is rotated.
Rotation of the planetary gear 70 causes the second cam gear 4 to rotate.
2 rotates and the rotation of the second cam gear 42 causes both loading shafts 4, 4 to rotate in the same manner as in the first embodiment.
The operation of each of the tension arm 33, the main and the auxiliary brakes 26 and 27 is controlled. At this time, the planetary gear 70 is controlled.
By providing, the rotation of the third transmission gear 64 is sufficiently decelerated and transmitted to the second cam gear 42.

Therefore, according to the fourth embodiment, the planetary gear 7
0 allows the rotation of the third transmission gear 64 to be sufficiently reduced and transmitted to the second cam gear 42.
Compared with the case where the rotation of 1 is directly transmitted to the second cam gear 42, even if the rotation amount of the first transmission gear 41 is the same, the rotation amount of the second cam gear 42 is much larger by using the planet gear 70. It is possible to increase the substantial area in which the second cam gear 42 can be formed with the cam groove, and it is possible to diversify the variations of the cam groove to be formed in the second cam gear 42. Yes, second
The number of objects that can be controlled by the cam gear 42 can be increased.

(Fifth Embodiment) FIGS. 9 and 10 show a fifth embodiment of the present invention. FIG. 9 is a plan view and FIG. 10 is a partial exploded perspective view. However, in FIG. 9, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and in the following description, duplicated description will be avoided and differences from FIG. 1 will be mainly described.

As shown in FIGS. 9 and 10, a convex engaging portion 73 is formed on the outer peripheral portion of the second cam gear 42, and one end is pivotally supported by the fixed shaft 74 near the second cam gear 42. A lever 75 is provided, a boss 76 as a locking body is integrally formed on the other end of the upper surface of the lever 75, a cam 78 is provided coaxially with the second cam gear 42, and a peripheral edge of the cam 78 is provided. The notch groove 79 is formed, and the boss 76 is fitted into the notch groove 79.

On the other hand, the boss 80 formed near the cutout groove 79 on the lower surface of the cam 78 is inserted into the arcuate through hole 82 formed in the second cam gear 42, and the second cam gear 42 is formed.
Both ends of the spring 83, which is the first urging means, are locked to the boss 80 and the fixed boss 81 underneath, and the cam 78 is urged in the clockwise direction on the paper surface of FIG. 9 by the urging force of the spring 83. By inserting the boss 76 into the notch groove 79, the cam 78 is held in a state of rotating in the direction opposite to the biasing direction against the biasing force of the spring 83.

Then, the rotation of the motor 17 is transmitted to rotate the second cam gear 42, the second cam gear 42 further rotates in the stop mode or the pause / still mode, and the engaging portion 73 causes the lower surface of the lever 75. Abutting and engaging a boss 84 formed near one end of the
When the lever 75 is pushed and the boss 76 is detached from the notch groove 79 from the state of being fitted into, the cam 78 instantly rotates by the urging force of the spring 83, and the rotation of this cam 78 causes the main brake 26 to move the main brake 26. The reel disk 8 is braked by instantaneously moving in the direction of pressing. However, in FIG. 9, 85 is a spring. Needless to say, a biasing means such as rubber may be used instead of the spring 83.

Therefore, according to the fifth embodiment, the lever 7
5, the cam 78 and the spring 83 can actuate the main brake 26 instantly to brake the reel disk 8. Therefore, as in the case of the second and third embodiments, the second This is effective when there are restrictions on the cam grooves that can be formed in the cam gear 42, and it is possible to control the operations of the main and auxiliary brakes 26 and 27 without requiring a large space.

(Sixth Embodiment) FIG. 11 is a plan view of a sixth embodiment of the present invention. The difference between the sixth embodiment and the above-described fifth embodiment is that the fifth embodiment is different from the second embodiment. Although the convex engagement portion 73 is formed on the cam gear 42 (see FIG. 9), in the sixth embodiment, as shown in FIG. 11, the concave engagement portion 87 is formed on the outer peripheral portion of the second cam gear 42. , L-shaped lever 88 is used instead of the lever 75 (see FIG. 9).
A boss 89 as a locking body on one end side of 8 is fitted into the notch groove 79 of the cam 78, and a boss 90 on the other end side of the lever 88 is the second side.
The rotation of the cam gear 42 causes the boss 8 to be fitted into the notch groove 79 by being fitted into and engaged with the engaging portion 87.
9 is detached from the notch groove 79.

Therefore, according to the sixth embodiment, the same effect as that of the fifth embodiment can be obtained.

(Seventh Embodiment) FIGS. 12 and 13 show a seventh embodiment of the present invention. FIG. 12 is a plan view and FIG. 13 is a partial exploded perspective view. However, in FIG. 12, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and in the following description, duplicated description will be avoided and differences from FIG. 1 will be mainly described.

As shown in FIGS. 12 and 13, a cam plate 93 corresponding to the conventional second cam plate 24 (see FIG. 18) is provided near the second cam gear 42, and this cam plate 93 is provided.
Is urged by the spring 94, which is the second urging means, in the leftward direction on the paper surface of FIG. 12, and the cam plate 93 is moved by the cam groove pattern of the second cam gear 42 in the play, fast-forward and rewind modes. The cam plate 93 is held in a state of being moved rightward on the paper surface of FIG. 12 against the urging force of the spring 94, and the cam plate 93 is slightly moved further rightward in the stop mode or the pause / still mode so that the cam plate 93 is moved to the fan 28. By the contact, the holding state of the cam plate 93 by the second cam gear 42 is released, and the urging force of the spring 94 causes the cam plate 93 to move.
2, the main brake 26 is pressed against the reel disk 8 to brake the reel disk 8.

At this time, the main and auxiliary brakes 26 and 27 are pivotally supported by the shafts planted in the deck base 1, and the respective bosses are inserted into the arcuate through holes 95 formed in the deck base 1 and the cams are inserted. The cam surface of the plate 93 is slidably contacted. Particularly, the boss of the one main brake 26 is slidably contacted with the cam surface formed on the inner periphery of the through hole 96 penetrating the cam plate 93.
The boss of the other main brake 26 is in sliding contact with the cam surface formed on the outer periphery of the cam plate 93. Incidentally, the rotation of the second cam gear 42 drives both arm gears 38 to control the operation of both loading shafts 4 as in the case of FIG.

Therefore, according to the seventh embodiment, the conventional first
It is not necessary to provide a very long cam plate like the cam plate 23 (see FIG. 18) of FIG. Main brake 2 without needing space
6 controls can be performed.

(Eighth Embodiment) FIGS. 14 and 15 show an eighth embodiment of the present invention. FIG. 14 is a plan view and FIG. 15 is a partial exploded perspective view. However, in FIG. 14, the same reference numerals as those in FIG. 1 indicate the same or corresponding parts, and in the following description, duplicated description will be avoided and differences from FIG. 1 will be mainly described.

As shown in FIGS. 14 and 15, the first arm gear 100 is provided near the second cam gear 42.
A second arm gear 101 is provided in mesh with the first arm gear 100, and one end of a pair of arms 102, 103 is pivotally supported by both arm gears 100, 101, respectively.
The fourth transmission gear 104 is coaxial with the first arm gear 100.
Is provided so that these gears 100 and 104 rotate in an interlocking manner, the fourth transmission gear 104 meshes with the second cam gear 42, and the rotation of the second cam gear 42 causes the rotation of the fourth transmission gear. Via the first arm gear 100,
Further, it is transmitted to the second arm gear 101.

Further, both arms 102 and 103 are rotated by the rotation of both arm gears 100 and 101, and the loading shaft 4 attached to the other ends of both arms 102 and 103, respectively, is a shaft guide groove 105 formed in the deck base. , 106, and the magnetic tape pulled out from the tape cassette is wound around the rotary drum 3 at a winding angle of 180 ° or more.

A cam 107 is formed on a part of the tooth surface on the outer circumference of the fourth transmission gear 104.
7 is fitted into the missing tooth portion 108 formed in a part of the tooth surface of the outer periphery of the second cam gear 42, whereby the rotation of the second cam gear 42 is not transmitted to the fourth transmission gear 104 any more, Both loading shafts 4 are self-held at predetermined loading positions.

Therefore, according to the eighth embodiment, the rotation transmission to the fourth transmission gear 104 is blocked by the insertion of the cam 107 of the fourth transmission gear 104 into the missing portion 108 of the second cam gear 42. Since both of the loading shafts 4 are self-holding at predetermined loading positions, the intermittent mechanism is configured.

(Ninth Embodiment) FIGS. 16 and 17 show a ninth embodiment of the present invention. FIG. 16 is a plan view and FIG. 17 is a partial exploded perspective view. However, in FIG. 16, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and in the following description, duplicated description will be avoided and differences from FIG. 1 will be mainly described.

As shown in FIGS. 16 and 17, a third cam gear 110 as a first intermediate gear is provided which meshes with the second transmission gear 43, and when the third cam gear 110 rotates, the third cam gear 110 rotates. The tension arm 33 is rotated by the pattern of the cam groove formed in the cam gear 110, and the back tension control of the running magnetic tape is performed.

The rotation of the worm wheel 21 is the first
In the case of FIG. 1, the rotation of the first intermediate gear 30 is transmitted to the pinch roller driving gear 31 to control the pinch roller holding member. Is the same as.

Therefore, according to the ninth embodiment, the motor 17
Since the rotation driving force is transmitted to each part by a combination of gears, it is possible to minimize the required area and effectively utilize the space of the entire apparatus.

[0077]

As described above, according to the first aspect of the present invention, since the rotation center of the cam gear of the transmission means and the cassette ramp are made to coincide with each other, the movement is performed like a conventional long cam plate. There is no need for space, it is possible to prevent the entire device from increasing in size, the cassette lamp is at a position equidistant from both reel discs, and the brake member for both reel discs may have a symmetrical shape, These controls can be performed very easily.

Further, even in the case of adding other incidental functions using the motor as a drive source, it can be easily dealt with by simply changing the pattern of the cam groove formed in the cam gear.

Further, according to the second aspect of the present invention, when there is a restriction on the cam groove that can be formed in the cam gear of the transmission means, by providing a cam that linearly moves by the length of the elongated hole, a large space is provided. It is possible to instantaneously control the operation of the brake member without requiring.

On the other hand, according to the third aspect of the invention, it is particularly effective when the restriction in forming the cam groove in the cam gear of the transmission means is more severe than that in the second embodiment.

Further, according to the invention described in claim 4, since the rotation of the transmission gear can be sufficiently reduced by the planetary gear and transmitted to the cam gear, the substantial area where the cam groove can be formed in the cam gear is enlarged. It is possible to diversify the variations of the cam grooves to be formed in the cam gear, and it is possible to easily increase the objects that can be controlled by the cam gear.

According to the invention of claim 5, the second aspect
This is effective when there are restrictions on the cam grooves that can be formed in the cam gear of the transmission means as in the embodiment, and the operation of the brake member can be controlled without requiring a large space.

Further, according to the sixth aspect of the invention, the brake member can be controlled only by providing the cam plate having the minimum length that can control the operation of the brake member. No need for big space.

According to the invention described in claim 7, since the intermittent mechanism for interrupting the rotation transmission to the transmission gear can be constructed, both loading shafts can be self-held at the predetermined loading positions.

Further, according to the invention described in claim 8, by transmitting the rotational driving force of the motor to each part by the combination of gears, the required area can be minimized and the space can be effectively used.

[Brief description of drawings]

FIG. 1 is a plan view of a first embodiment of the present invention.

FIG. 2 is a partial exploded perspective view of the first embodiment.

FIG. 3 is a plan view of a second embodiment.

FIG. 4 is a partial exploded perspective view of the second embodiment.

FIG. 5 is a plan view of a third embodiment.

FIG. 6 is an exploded perspective view of a part of the third embodiment.

FIG. 7 is a plan view of a fourth embodiment.

FIG. 8 is an exploded perspective view of part of the fourth embodiment.

FIG. 9 is a plan view of the fifth embodiment.

FIG. 10 is an exploded perspective view of part of the fifth embodiment.

FIG. 11 is a plan view of the sixth embodiment.

FIG. 12 is a plan view of a seventh embodiment.

FIG. 13 is a partial exploded perspective view of the seventh embodiment.

FIG. 14 is a plan view of the eighth embodiment.

FIG. 15 is an exploded perspective view of part of the eighth embodiment.

FIG. 16 is a plan view of the ninth embodiment.

FIG. 17 is a partial exploded perspective view of the ninth embodiment.

FIG. 18 is a plan view of a conventional example.

[Explanation of symbols]

2 cassette lamps, 3 rotating drums, 4 loading shafts, 8 reel discs, 17 motors, 26
Main brake (brake member), 30 second intermediate gear, 41 first transmission gear, 42 second cam gear, 4
3 3rd transmission gear, 44 transmission means, 46, 53 cam groove, 50, 78, 107 cam, 51 oblong hole, 58, 7
5,88 lever, 64 third transmission gear, 65 external teeth, 66,69 internal teeth, 70 planetary gears, 73, 87
Engagement part, 76, 89 Boss (locking body), 79 Notch groove,
83, 94 springs (biasing means), 84, 90 bosses, 9
3 cam plates, 100, 101 first and second arm gears,
102, 103 arms, 104 fourth transmission gear, 1
08 Missing part.

─────────────────────────────────────────────────── ─── Continuation of the front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) G11B 15/26 G11B 15/08 G11B 15/093 G11B 15/48

Claims (8)

(57) [Claims] 1. A tape cassette in which a magnetic tape is wound around a pair of reels is inserted into an insertion opening of an apparatus main body to transfer the tape cassette to a predetermined position inside the main body.
The magnetic tape is pulled out from the tape cassette after being transferred by a pair of loading shafts and wound around a rotating drum, and braking of the reel disc is performed by a brake member that presses against a reel disc that rotationally drives the reel in a stop mode or a pause / still mode. In the magnetic recording / reproducing apparatus having a function of performing the above, a cassette lamp for detecting the end of the magnetic tape, which is arranged so as to be located at substantially the center of the tape cassette transferred to a predetermined position inside the main body, a gear train and a cam gear A direction in which the rotation driving force of the motor is transmitted to the brake member, the operation of the loading shafts is controlled by the pattern of the cam groove of the cam gear, and the brake member is pressed against the reel disc in the stop mode or the pause / still mode. And a transmitting means for driving the magnetic recording reproducing apparatus in which the cassette lamp the center of rotation of the cam gear of said transmission means is characterized by being located. 2. A boss that slides in a cam groove formed in the cam gear of the transmission means and an elongated hole into which the cassette lamp is inserted, and the boss slides in the cam groove by rotation of the cam gear. A cam that moves and linearly moves in the longitudinal direction of the slot, and drives the brake member in a direction in which the brake member is pressed against the reel disc by the movement of the cam in the stop mode or the pause / still mode. The magnetic recording / reproducing apparatus according to claim 1, which is characterized in that. 3. A transmission member for transmitting the rotation of one gear of the gear train of the transmission means, wherein the linear movement of the cam in the longitudinal direction of the elongated hole is caused by the movement of the transmission member. The magnetic recording / reproducing apparatus according to claim 2, wherein the magnetic recording / reproducing apparatus is controlled by 4. A transmission gear in one of the gear trains of the transmission means has external teeth and internal teeth, and the cam gear of the transmission means has teeth smaller in diameter than the internal teeth of the transmission gear. 2. The magnetic recording / reproducing apparatus according to claim 1, further comprising a planetary gear having a planetary gear that meshes with inner teeth of the cam gear and the transmission gear. 5. An engaging portion is provided on an outer peripheral portion of the cam gear of the transmitting means, is rotatably supported by a fixed shaft in the vicinity of the cam gear, and has a locking body formed at a tip end thereof, and the engaging portion. A lever formed with a boss that engages with the cam gear, and a locking body of the lever that is releasably locked in a notch groove that is provided coaxially with the cam gear and that is formed in the peripheral edge portion. A cam for releasing the locking body from the cutout groove by engaging the lever of the joint portion with the boss, and a cam for biasing the cam when the locking body is locked in the cutout groove. A first urging means for rotating the cam in the urging direction when the body is detached from the notch groove, and by rotating the cam in the urging direction in the stop mode or the pause / still mode, In the direction in which the brake member is pressed against the reel disc, Magnetic recording and reproducing apparatus according to claim 1, characterized in that the dynamic. 6. A state of being urged in one direction by a second urging means and moved in the other direction opposite to the one direction by the cam gear of the transmission means against the urging force of the second urging means. A cam plate, which is held in the stop mode or in the pause / still mode, linearly moves in the one direction by the urging force to drive the brake member in a direction in which the brake member is brought into pressure contact with the reel disc. The magnetic recording / reproducing apparatus according to claim 1, wherein the magnetic recording / reproducing apparatus is provided. 7. A first arm gear provided near the cam gear of the transmission means, a second arm gear meshed with the first arm gear, and one end of the both arm gears pivotally supported by the both arm gears. First and second arms that move both loading shafts by rotation;
A transmission gear that is provided coaxially with the first arm gear and that meshes with the cam gear to transmit the rotation of the cam gear to the both arm gears; and a transmission gear that is formed on a tooth surface of the transmission gear and is formed on a part of the tooth surface of the cam gear. The magnetic recording / reproducing apparatus according to claim 1, further comprising: a cam that is inserted into the missing tooth portion to release the transmission of the rotation of the cam gear. 8. The operation of a first intermediate gear and a pinch roller for controlling the operation of a tension arm of a back tension mechanism, which meshes with any one of the gear trains of the transmission means and the cam gear, respectively. 2. The magnetic recording / reproducing apparatus according to claim 1, further comprising a second intermediate gear that operates.