JPH06105521B2 - Tape loading mechanism of magnetic recording / reproducing device - Google Patents

Description

The present invention relates to a tape guide base guide mechanism of a tape loading mechanism of a helical scan type magnetic recording / reproducing apparatus.

[Conventional technology]

As an example of the structure of a conventional tape loading mechanism, as described in JP-A-57-133558, a tape guide member having a guide member having a C-shaped cross section mounted along a guide rail having a T-shaped cross section is disclosed. Is guided and moved to load the tape.

[Problems to be Solved by the Invention]

The above-mentioned conventional technology is excellent in that it simplifies the mechanism and realizes cost reduction, but when attempting to further reduce the size of the mechanism, there are the following problems. That is, when the miniaturization and thinning of the helical scan type magnetic recording / reproducing device mechanism is pursued to the utmost limit, the tape guide drum is erected upright, and the tape guide drum is made smaller in diameter and the tape winding angle to the tape guide drum is increased. Is enlarged, and the tape running path has a three-dimensional shape such as the entrance side rising and the exit side descending. At this time, a three-dimensional moving path is required as an ideal tape guide path for reducing the tape damage at the time of tape loading as much as possible, and thus the loading mechanism must be complicated.

In the above situation, the shape of the guide member that guides the tape to the tape guide drum that guides the tape to the tape guide drum needs not only the guide shape for horizontal or vertical movement but also the twist shape. The shape is three-dimensional and very complicated. Generally, the guide member as described above is mass-produced by integral molding by resin or die casting, but if the cross-sectional shape is T-shaped, the shape becomes complicated, and if it is a twisted shape, die-molding is required. It becomes very difficult and causes cost increase, and it becomes difficult to secure accuracy. Further, if the guide member having the T-shaped cross-section described above is formed into a shape that facilitates die-cut molding, the play of the guide base during tape loading becomes large,
Stable tape loading operation cannot be obtained.

An object of the present invention is to prevent the stable movement of the guide base during tape loading because it is difficult to perform high-precision die-cutting of the guide member of the conventional guide base.
It is to realize a reliable tape loading operation mechanism without increasing costs, increasing the number of parts, degrading assembly, complicating parts shapes, and increasing size.

[Means for Solving the Problems]

In order to achieve the above object, the cross-sectional shape of the guide member for guiding the movement of the guide base is Z-shaped instead of the conventional T-shape, and the shape of the guide member itself can be easily punched with high precision. It has a unique shape. In addition, the vertical height of the guide base is regulated so that the moving path of each tape guide at the time of tape loading becomes the design reference height position in the case of an optimum design that does not cause the tape to bend and twist. The above-mentioned guide member is provided with a guide surface, a second guide surface that restricts the position in the left-right direction, and a third guide surface that restricts the position in the left-right direction at a position facing the second guide surface. Is.

[Action]

The claw portion of the guide base having a C-shaped cross section is engaged with the guide member having a Z-shaped cross section so as to be movable in the longitudinal direction. As the tape loading operation progresses, the guide base moves from the inside of the cassette opening around the tape guide drum along the guide member. Along with this, the tape is pulled out from the cassette and wound around the tape guide drum to form a predetermined tape path.

At this time, the tape guide base described above is
The vertical position and the horizontal position with respect to the moving direction,
The posture in the direction of the rotation moment is restricted. As a result, the above-mentioned tape guide base can move along the guide member while always maintaining the height, position, and posture, which is optimal for stable tape loading, and being regulated, enabling stable and reliable tape loading operation. A thin mechanism can be realized.

〔Example〕

An embodiment of the present invention will be described below with reference to FIGS.

FIG. 1 is a plan view of a magnetic recording / reproducing apparatus using a tape loading mechanism according to the present invention, where 1 is a chassis, 2 is a tape guide drum on which a magnetic head is mounted, 3 is a supply reel 4 and a take-up reel 5. A cassette containing a tape 6 to be rotated, 7 a capstan to which a motor 9 is directly connected to the lower end, 8 a pinch roller, 10 fixedly supported on a catcher 28, and a full width erasing head for erasing over the entire width of the tape 6, Reference numeral 11 denotes an audio head and a control head for recording and reproducing audio signals and control signals on the upper and lower ends of the tape 6. When the cassette 3 is attached to the apparatus, the lid 12 on the front surface of the cassette 3 opens. Furthermore, in the opening 13, a tension pin 16, a guide roller 17 and an inclined pin
18 is inserted, the guide roller 19 and the inclined pin 20 are inserted into the opening 14, and the inclined pin 21 and the capstan 7 are inserted into the opening 15 at the positions shown by the broken line and the solid line, respectively. At this time, the pinch roller 8 is also in the position shown by the broken line. When the loading operation is performed, each guide moves while pulling out the tape 6. Guide roller 17 and tilt pin 18
Move horizontally as a pair and are positioned near the tape guide drum 2. The guide roller 19 and the inclined pin 20 form a pair and move horizontally up to the vicinity of the audio head and the control head 11 and thereafter move obliquely downward to be positioned near the tape guide drum 2 to be positioned on the tape guide drum 2. Wrap tape 6 approximately 270 °. Inclined pin 2
1 is horizontally moved from the back of the inclined pin 20 and is fixed on the upstream side of the audio head and the control head 11 to correct the posture of the tape 6 and guide it to the take-up reel 5. As a result, the tape 6 comes out of the cassette 3, and the tension pin 16, the impedance roller 22, the full width erasing head 10 and the guide roller.
The tape guide drum 2 is spirally wound around the tape guide drum 2 through a tilt pin 18 and a predetermined angle, and a guide roller 19, a tilt pin 20, a tilt pin 21, a fixed guide 23, an audio head and a control head 11, a height regulation guide 24 are provided. After passing through the fixed guide 25, the capstan 7 and the pinch roller 8 are pressed and driven to reach the take-up reel 5. FIG. 2 (a) shows a side view after completion of loading, and FIG. 2 (b) shows a side view after completion of unloading. In FIG. 3 (a), 26 is a guide base on which the guide roller 17 and the inclined pin 18 are planted and positioned and held by the catcher 28.
Also, the guide roller 19 and the inclined guide 20 are planted on the guide base, and similarly positioned by the catcher 28. As shown in the figure, the tape guide on the exit side of the tape guide drum 2 is descended by a width substantially larger than that on the entrance side.
As a result, the tape guide drum 2 can be arranged under the lid 12 that opens in front of the cassette 3 by reducing the inclination angle of the tape guide drum 2 and arranging the tape guide drum 2 at a position slightly lower than the cassette 3. We are trying to make it smaller and thinner.

Next, the loading mechanism will be described in detail. FIG. 3 shows the guide moving member on the exit side. Guide roller 19 and inclined pin
As shown in FIG. 3, the guide base 27 for planting the 20 is connected to the connecting plate 29 with a large backlash,
Similarly, 29 is also supported by one end of the output side drive member 31 with a large backlash. The outlet drive member 31 has an arc shape,
A gear portion 31a is provided on the outer circumference thereof. FIG. 4 shows the guide moving member on the entrance side. The guide base 26 on which the guide roller 17 and the inclined pin 18 are erected is pivotally supported about a shaft 33d erected on the entry side drive member 33 so as to be rotatable. The entrance-side drive member also has an arc shape, and a gear portion 33a is provided on the outer periphery thereof. FIG. 5 shows the cam 34.
The cam 34 consists of two upper and lower stages.
34a and a cam portion 34d, and a lower surface includes a stopper surface 34b corresponding to a Geneva gear (described later), a cam portion 34c corresponding to a mode operation after loading, a cam portion 34f corresponding to the middle of loading or unloading, and a unloading portion after unloading. There is a cam portion 34e corresponding to the mode operation, and it has an arc shape as a whole. These are the drive members from the top
33, the output drive member 31, and the cam 34 are arranged concentrically on the chassis in this order.

FIG. 6 sequentially shows the operation states of the entry side guide base 26 from the unloading state (a) to the loading completion state (e). The catcher 28 and guides involved in the operation of the entry side guide base 26 are shown. Material 78, 79, guide base 2
6 is a perspective view of a bent upper surface 33c (see FIG. 4) of each of the cam portions 28j, 28k, 78a, 78b, which are the posture control members of FIG. In addition, the height relationship of each component at the time of completion of assembly is that the V groove 28a on the upper part of the catcher is from above.
Corresponds to the upper cylindrical portion 17a of the inlet side guide roller, and the inlet side guide base 26 corresponds to the cam portion 79b of the guide member 79.
And the cam portion 28j of the catcher 28 corresponds to the lower projection 26b of the entry side guide base, and the cam portion 78a of the guide member 78 and the U groove 28b at the bottom of the catcher 26 and the cam portion 28k and the entry side drive member 33. The upper concave portion 33f (see FIG. 4) corresponds to this.

FIG. 8 shows the upper stage of the cam 34 and the drive system. (A) shows the unloading state, (b) shows the loading or unloading process, and (c) shows the loading state. Cam 34
Is driven by a gear 35 driven by a drive source (not shown) meshing with a gear portion 34a. When the cam 34 rotates, the gear 36 that meshes with the gear portion 34a rotates, and the delivery-side drive member 31 rotates integrally with the gear 38 via the gears 37 and 38 via the compression spring (not shown). The gear 39 is driven by being engaged with the gear portion 31a. Similarly, the entry side drive member 33 passes through the gears 40 and 41, and a compression spring (not shown).
The gear 77 shown in FIG. 13 that incorporates the gear is driven by engaging with the gear portion 33a. Loading is completed (c)
In this state, the rotation of the gear 36 is stopped by the Geneva gear described later, and the engagement between the gear 36 and the gear portion 34 is released. On the other hand, in the state of (b) during loading, the cam
The tip end of 34 and the arm 42 are engaged, the arm 42 rotates about the shaft 43, and the arm 44 rotates about the shaft 45. Since the arm 44 is engaged with the shaft 49 of the arm 48 by the arm 46 via the shaft 47, the pinch roller 8 pivotally supported by the arm 48 is moved to the loading position. Since the arm 48 is biased by the spring in the direction of arrow A, the cam 34 and the arm 42 are
In the state of (a) where is not engaged, the pinch roller 8 is retracted to the unloading position. When the cam 34 further rotates from the state of (b) to the state of (c), the arm 42 engages with the cam portion 34d and the toggle mechanism formed by the arms 44 and 46 causes the pinch roller 8 to move to the capstan 7. Pressure contact.
The shaft 45 is erected on an arm 51 supported by the shaft 52,
Is always pulled by the spring 53 and its position is regulated by the stopper 54. Therefore, even after the movement of the pinch roller 8 is stopped, the arm 42 rotates, so that the arm 51 moves away from the stopper 54 against the spring 53. As a result, the crimping force between the pinch roller and the capstan is secured.

7 to 9 show the lower stage of the cam 34 and the mode operating mechanism. FIG. 7 shows the unloading state, FIG. 8 shows the loading or unloading process, and FIG. 9 shows the loading state. Reference numeral 36a is a Geneva gear portion provided integrally with the gear 36. One end of the arm 55 has a cam portion 34c or 3
4e is engaged and is urged counterclockwise around the shaft 56 by a spring 57 attached at one end. A brake member 58 is attached to the other end of the arm 55 to apply a braking force to the supply reel base 59. The arm 60 engages with the cam portion 34c or 34e, and is biased clockwise around the shaft 62 by the spring 61 attached to one end. The arm 63 has an arm 63a engageable with the shaft 60a on the arm 60, and a spring 65 is attached to one end of the arm 63 and is biased counterclockwise around the shaft 62. Brake member 64 at the other end
Is applied to apply a braking force to the drive disc 66 that engages with the take-up reel 5. FIG. 7 shows a stopped state after unloading, in which the arm 55 is engaged with the concave portion of the cam portion 34e and the braking force is applied to the supply reel base 59. At this time, since the concave portion and the arm 55 are not directly engaged with each other, the braking force is
It is determined only by the force of 57 and is stable regardless of the stroke of the cam portion 34c. Further, the arm 60 engages with the convex portion of the cam portion 34e, and disengages the shaft 60a and the arm 63a against the spring 61, so that the urging force of the spring 65 applies a braking force to the drive disk 66 and the cam portion. Stable regardless of the stroke of 34e, and in the state of FIG.
Only the braking force applied to the supply reel base 59 is released by engaging with f. Therefore, at the time of loading, the tape 6 is basically delivered from the supply reel side. The state of FIG. 9 shows a recording / reproducing state, in which a braking force is applied to the supply reel base 59, but the arm 60 engages with the concave portion of the cam portion 34c and the spring 6
It is rotated by the pulling force of 1 and the shaft 60a engages with the arm 63a and the arm 6a
The 3 is rotated against the spring 65 to release the braking force on the drive disc 66. At this time, the Geneva gear portion 36a and the stopper surface 34b are engaged with each other, whereby the rotation of the gear 36 is stopped, the driving members 31 and 33 are stopped, and the crimping force to the positioning member of each tape guide group is maintained. . In this way, by transmitting the movement of the cam 34 to the drive member via the switching mechanism such as the Geneva gear, it is possible to easily cope with an increase in the number of operation modes.

FIG. 10 shows the movements of the above-mentioned three driving members 31 and 33 and the cam 34. (a) is for eject, (e) is for loading, (f) is for recording or reproducing mode operation. Is. The shape of each member is simplified and shown in an arc shape. As shown in FIG. 8, with respect to the movement of the cam 34, the entrance side drive member 33 rotates in the opposite direction at substantially the same speed, and the exit side drive member 31 rotates in the same direction at about the same speed.

FIG. 11 is a perspective view of the catcher 28. The tape guide drum 2 has an integral structure for positioning the tape guide group on the input side and the tape guide group on the output side. As for the tape guide group on the entry side, the shaft portion above the guide roller 17 shown in FIG.
Positioning is performed in the groove 28a, and the lower portion is restricted by the U groove 28b to prevent the guide roller 17 from collapsing in a direction perpendicular to the entering direction. The height of the guide roller 17 is regulated by the upper end of the guide base 27 contacting the stopper surface 28c. The inclination of the inclined pin 18 is determined by the side surface of the guide base 27 contacting the wall 29d. The same applies to the tape guide group on the output side,
The position and angle of the guide roller 19 are determined by the V groove 28e and the U groove 28f, and the height is determined by the stopper surface 28g. Also tilt pin 20
The inclination of is regulated by the wall 28h. Further, a notch 29i is provided between the V groove 28e and the U groove 28f of the catcher 28.
In the unloading state shown in FIG. 2 (b),
One end of the cam 34 and one end of the output side driving member are formed in the cutout portion 28i.
However, since these members escape from the cutout portion 28i by the loading operation, the guide roller 19 and the inclined pin 20 can be held at predetermined positions in the loading operation completed state.

FIG. 12 shows a guide member 68 of the tape guide group and the guide member.
FIG. 33 is a perspective view showing a method of supporting the guide base 27 on the exit side by 68. The guide member 68 has a Z-shaped cross section, and the claw portions 27a and 27b of the guide base 27 are engaged so as to grip the Z-shaped portion and regulate the movement path of the guide base 27. This will be described in detail later. As shown in FIG. 1, the moving path of the guide base 26 on the entry side is such that the shaft portion at the lower part of the guide roller 17 and the wall 78a of the guide member 78, and the end surface 26a of the guide base 26 and the guide member 79. It is regulated by the engagement with the wall 79a of the.

FIG. 13 shows a moving mechanism of the inclined pin 21 arranged on the exit side. FIG. 13 (a) shows a state corresponding to the unloading state shown in FIG. 9 (a). The gear 69, which is rotatably supported coaxially with the arm 48, has a bent portion of the gear 69 at both ends thereof.
69b and the left end 48a of the arm 48 are biased by the spring 70, and the right end 48b of the arm 48 and the bent portion 69c of the gear 69 are in contact with each other. From this state, the 13th corresponding to FIG. 9 (c)
When the mode shifts to the state shown in FIG. 7B and the arm 48 rotates so that the pinch roller 8 comes into pressure contact with the capstan 7,
An arm 72 having a gear portion 72a that meshes with a gear portion 69a of the gear 69.
Is rotated to position the inclined pin 21 implanted at the tip of the arm 72 at a predetermined position by the catcher 73. After the positioning, the arm 48 is further rotated to move the arm 48 against the spring 70 as shown in FIG.
By separating from the 69c, the crimping force of the inclined pin 21 to the catcher 73 is secured. By driving the tilt pin 21 at the above timing, the tilt pin 21 is loaded from the rear of the guide base 27. That is, since the movement loci of the inclined pin 21 and the guide base 27 partially overlap, when the guide base 27 precedes and passes the overlapping portion, the cam 34 and the arm 42 engage with each other to move the inclined pin 21. The position of the arm 42 and the reduction ratio of the drive system of the arm 72 are set so as to drive. Therefore, since the movement of the arm 72 is controlled by the movement of the cam 34, there is no interference at the overlap portion.

Next, the guide base 27 and the guide member 68 shown in FIG.
Details of the engagement state and the structure of are shown.

FIG. 15 shows a cross-sectional view of a state in which a guide member 90 having a T-shaped cross section and a guide base 27 which have been conventionally used are engaged with each other. On the other hand, FIG. 16 shows a sectional view of the guide member 68 having a T-shaped cross section according to the present invention and the guide base 27 in an engaged state. In FIG. 15, 90a, 90b,
Reference numeral 90c indicates a position regulating portion of the guide member 90 with respect to the guide base 27. 90a up and down, 90a left and right
The position is regulated at two points, b and 90c. The directions of the position regulating force at this time are shown as F _A , F _B , and F _C. In FIG. 15, the urging direction of the guide base 27 is shown by arrows A and B in the figure. Guide member 90 and guide base depending on the direction A or B indicated by the arrow in the figure
The position regulating members 90b and 90c with respect to 27 change to 90b 'and 90c', which causes backlash in the left and right direction, and the positioning with respect to the rotational moment direction changes depending on the clearance between the guide member 90 and the guide base 27. To do. On the other hand, in the case of the embodiment according to the present invention shown in FIG. 16, the guide base 27 is urged as indicated by an arrow C so that 68a in the drawing is 68b in the vertical direction and 68c in the horizontal direction facing 68b. Since the position restriction part in the left-right direction is determined by, there is no backlash in the left-right direction, and the position in the rotational moment direction is also determined. Further, in pursuit of miniaturization of the mechanism, it is necessary to bring the above-mentioned tape guide drum 2 and guide base 27 as close as possible. A guide member 90 having a T-shaped cross section shown in FIG.
In the case of, the claw portion 27b of the guide base 27 projects toward the tape guide drum 2 to the same extent as the claw portion 27a, whereas
According to the present invention, as shown in FIG. 16, the amount by which the claw portion 27b of the guide base is projected toward the tape guide drum 2 side is small. For this reason, the guide members 68, 90 are generally arranged so as to stand up from the side of the chassis 1 described above, so that the rising portions 68d, 90d of the guide members of the present invention are different from those of the conventional T-shaped cross section. The Z-shaped cross section is closer to the guide base 27 side. That is, the position of the guide base 27 can be arranged close to the tape guide drum 2, which is advantageous for downsizing of the mechanism.

17 and 18 show the rattling state of the guide base 27 when the biasing force is not applied to the guide base 27 in the engaged state of the guide base 27 shown in FIGS. 15 and 16 described above. It is a thing. FIG. 17 shows a conventional T-shaped cross section, and FIG. 18 shows an embodiment of the present invention having a Z-shaped cross section. In the drawing, the angle is within the rattling range of the guide base 27. When the clearances of parts are designed so that the total rattling angle of the guide member is almost the same for the T-shaped section and the Z-shaped section, the conventional sectional shape shown in FIG. In the case of the character shape, rattling occurs below the reference position, whereas in the Z-shaped cross-section according to the present invention shown in FIG. 18, there is no rattling downward and only rattling above. Miniaturization of the mechanism.
If thinning is pursued, each component of the mechanism has a laminated structure, and especially the lower surface side of the guide base 27 is provided with the drive member of the guide base 27, and the clearance becomes very severe. In this case as well, the mechanism can be made thinner by making the guide member 68 have a Z-shaped cross-section as in the present invention and almost eliminating rattling downward of the guide base 27.

〔The invention's effect〕

According to the present invention, since it is difficult to mold the guide member in the related art, it is not possible to take an ideal movement guide route for stable tape loading, but it can be realized at low cost, and the mechanism is downsized. Further simplification can be promoted.

[Brief description of drawings]

FIG. 1 is a plan view showing the entire mechanism of the recording / reproducing apparatus,
FIG. 2 is a side sectional view showing the outlet guide base portion,
FIG. 6 is a perspective view showing the driving member, FIG. 6 is a plan view showing the movement of the guide base during the loading operation, FIGS. 7, 8 and 9 are plan views showing the mode operating mechanism, and FIG. FIG. 11 is a view showing the movement of the cam, FIG. 11 is a perspective view showing the catcher,
FIG. 12 is a perspective view showing the guide mechanism of the delivery side guide base,
13 is a plan view of the tape pull-out mechanism, FIG. 14 is a perspective view showing the holding mechanism of the driving member, FIG. 15 is a sectional view showing the guide mechanism of a conventional guide base, and FIG. 16 is a guide base according to the present invention. 17 is a sectional view showing the guide mechanism of FIG. 17, FIG. 17 is a sectional view showing the rattling state of the mechanism of FIG. 15, and FIG. 18 is a sectional view showing the rattling state of the mechanism of FIG. 2 ... Tape guide drum, 6 ... Tape 3 ... Cassette, 31 ... Drive member 27 ... Outgoing guide base, 90 ... Guide member 68 ... Guide member

Claims (1)

[Claims] 1. A tape guide drum (2) having a rotary head for recording or reproducing information on a tape (6).
Then, a tape guide group for placing the tape (6) out of the cassette (3) and winding the tape (6) around the surface of the tape guide drum (2) to form a predetermined tape running path is placed, and the tape is loaded at the loading position and the unloading position. A guide base (27) that moves back and forth between the loading position and the guide base (2
In a magnetic recording / reproducing apparatus comprising a drive member (31) for connecting to and moving the guide base (27) and a guide member (68) for guiding a movement path when the guide base (27) moves, The cross-sectional shape of the engaging portion with the guide base (27) is substantially Z-shaped, and at the tape loading reference height position, the first guide surface (for restricting the position in the vertical direction with respect to the moving direction of the guide base). 68 (a)) and a second guide surface (68 (b)) for laterally regulating the position.
And a third guide surface (68 (c)) which faces the second guide surface and regulates the position in the left-right direction, the tape loading mechanism of the magnetic recording and reproducing apparatus.