JPH01107359A - Tape loading mechanism for magnetic recording and reproducing device - Google Patents

Abstract

PURPOSE:To permit a tape guide to stably sandwich a rail without using a spring by setting the shapes of engagement parts in the tape guide which is engaged with the rail to arcs and engaging plural arc engagement parts with the rail with a slight clearance. CONSTITUTION:A guide base (tape guide) 27 sandwich a guide member (rail) 68 by an upper sandwiching part 27b fixed to the guide base 27 by a screw 83 and a lower sandwiching part 27a, and four arc projections 27c-27f which are engaged with the guide member 68a are formed at the lower sandwiching part 27a. The shapes are the same in the upper sandwiching part 27b, and total four parts in the guide member 68 are vertically sandwiched, whereby the guide member 68 and the arc projections 27c-27f are engaged or brought into a linear contact with mostly constant clearance. Thus, the rail and the sandwiching part except for the engagement surface of the tape guide is not brought into contact, and the tape guide can stably be held and guided.

Description

[Detailed Description of the Invention] [Industrial Field of Application] The present invention relates to a magnetic recording/reproducing device, and particularly to simplification of the device,
The present invention relates to a tape loading mechanism suitable for downsizing and weight reduction.

[Conventional technology]

A magnetic recording/reproducing device uses so-called tape loading, in which a magnetic tape (hereinafter referred to as tape) stored in a tape cassette is pulled out by a tape guide that moves along a predetermined guide path, and the tape is wound around a rotating drum at a predetermined angle. There is a device. As a method of guiding this tape guide along a predetermined guide route, for example, Japanese Patent Laid-Open No. 57-133
Like the device described in the 558 publication, a T-shaped rail (
Some use a tape guide having a C-shaped clamping part that engages with the rail. The tape guide is
In the case of a device in which the travel guide is finally arranged three-dimensionally,
Avoiding interference with tape guide groups installed on the chassis (e.g. fixed head, height regulation guide, rotating drum, etc.)
It is necessary to move along complex paths such as straight, rotational, and diagonal movement. In order to deal with this complicated movement path, conventional devices have provided a large clearance between the rail and the tape guide, and have used springs to absorb the looseness caused by this clearance.

[Problem that the invention seeks to solve]

The above conventional technology requires a spring to absorb the clearance between the rail and the tape guide, which not only poses problems with the shape of the tape guide and the downsizing of the entire device, but also increases the number of parts. was. Further, since the tape guide is simply held in contact with the rail by the spring, it is difficult to maintain the posture of the tape guide during loading, and there is a risk of damage to the tape.

An object of the present invention is to provide a tape guide in which the tape guide always stably holds the rail without using a spring for engagement between the rail and the tape guide.

[Means for solving problems]

The above object is achieved by making the shape of the engaging portion of the tape guide that engages with the rail into an arc, and by causing the plurality of arc-shaped engaging portions to engage the rail with a slight clearance.

[For production]

By making the engaging surface of the tape guide with the rail arc-shaped, the engaging surface of the tape guide and the rail are always engaged or lined at a slight constant interval, regardless of whether the L; will come into contact. Thereby, the tape guide can be stably held and guided without contact between the rail and the clamping portion other than the engagement surface of the tape guide.

〔Example〕

An embodiment of the present invention will be described below with reference to FIGS. 1 to 17.

FIG. 2 shows a plan view of the magnetic recording/reproducing sti according to the present invention, in which 1 is a chassis, 2 is a tape guide drum on which a magnetic head is mounted, and 3 is a tape 6 wound around a supply reel 4 and a take-up reel 5. 7 is a capstan to which a motor 9 is directly connected to the lower end, 8 is a pinch roller, 10 is an erasing head that erases over the entire width of the tape 6, and 11 is an audio signal and control signal that is connected to the upper and lower ends of the tape 6. This is an audio control head for recording and playback. When the cassette 3 is installed in the apparatus, the lid 12 on the front surface of the cassette 3 is opened. Furthermore, within the opening 13 is a tension pin 16. A guide roller 17 and an inclined pin 18 are inserted, and a guide roller 19 and an inclined pin 2 are inserted into the opening 14.
0 is inserted into the opening 15, and the tilt pin 21 and the capstan 7 are inserted into the opening 15 at the positions shown by the broken lines and the actual position, 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 6 guide rollers 17 and inclined pins 18
move horizontally as a pair and are positioned near the tape guide drum 2. Guide roller 19 and inclined pin 2
0 is a pair, audio control head 1
The tape 6 is moved horizontally up to the vicinity of the tape guide drum 1, and then moved obliquely downward until it is positioned near the tape guide tram 2, and the tape 6 is wound around the tape guide drum 2 by approximately 270 degrees. The inclined pin 21 moves horizontally from behind the inclined pin 20 and is fixed on the upstream side of the audio control head 11, corrects the attitude of the tape 6, and guides it to the take-up reel 5. As a result, the tape 6 comes out of the cassette 3, and the tensile lamp 16. Height regulation guide 22° erasing head 10. Guide roller 17.
The tape is wound spirally around the tape guide drum 2 at a predetermined angle via the inclined pin 18, and then the guide roller 19. Slanted pin 20° Slanted pin 21. Fixed guide 23. Audio Control Rad 11. Height regulation guide 24. It passes through the fixed guide 25 and is driven by the capstan 7 and the pinch roller 8 in pressure contact with each other to reach the first take-up reel 5. FIG. 3 shows a side view when loading is completed, and FIG. 4 shows a side view when unloading is completed.

In Fig. 3, 26 is a guide base and guide roller 1
7 and an inclined pin 18 are erected, positioned and held by a catcher 28, and 27 is also a guide base, and a guide roller 19 and an inclined guide 20 are erected, and similarly positioned by a catcher 28. As shown in the figure, the tape guide on the output side of the tape guide drum 2 is lowered by approximately the width of the tape compared to the tape guide on the input side. This reduces the inclination angle of the tape guide drum 2.

By placing the tape guide drum 2 at a slightly lower position than the cassette 3, the tape guide drum 2 is placed under the lid 12 that opens toward the front of the cassette 3.
The aim is to make the device smaller and thinner by making it possible to place

Next, the loading mechanism will be described in detail, and FIG. 5 shows the guide moving member on the exit side. The guide base 27 on which the guide roller 19 and the inclined pin 20 are installed is supported by a connecting plate 29 so as to be rotatable within a plane as shown by the arrow in the figure, and the connecting plate 29 is also rotatable within a plane. It is supported by a connecting plate 30.

Furthermore, the connecting plate 30 is supported by one end of the output side drive member 31 so as to be able to freely swing in the vertical direction. The output side drive member 31 has an arc shape, and a gear portion 31a is provided on the outer periphery thereof. FIG. 6 shows the guide moving member on the entry side. Guide base 2 on which guide rollers 17 and inclined pins 18 are planted
6 is supported by a connecting plate 32 so as to be rotatable within a plane,
The connecting plate 32 is similarly supported by one end of the entry side drive member 33 so as to be freely rotatable within a plane. The entry side drive member also has a circular arc shape, and a gear portion 33a is provided on its outer periphery. FIG. 7 shows the cam 34.

The cam 34 consists of two stages, upper and lower. The upper stage has a gear part 34a and a cam part 34d from the left, and the lower stage has a Geneva gear (
A stopper surface 34b corresponding to (described later).

a cam portion 34c corresponding to mode operation after loading;
There is a cam portion 34' corresponding to the middle of loading/unloading, and a cam portion 34e corresponding to the mode operation after unloading, and the whole has an arc shape. These are the entry side drive member 33. Output side drive member 3
1. The cams 34 are arranged concentrically on the chassis in order.

FIG. 8 shows the upper stage of the cam 34 and the drive system, (α) shows the unloading state, (b) shows the loading/unloading process, and (C) shows the loading state. The cam 34 is driven when a gear 35 driven by a drive source (not shown) meshes with the gear portion 34 (Z.The cam 34
By rotating.

The gear 36 that meshes with the gear portion 34a rotates, and the output side drive member 31 passes through gears 37 and 38 and connects to the gear 38 and the compression spring (
A gear 39 that rotates integrally with the gear portion 3 via a
It is driven by meshing with 1a. Similarly, the entry side drive member 33 is driven by the gear 55, which has a built-in compression spring (not shown), meshing with the gear part 33 (2) via the gears 40 and 41. In this state, the rotation of the gear 36 is stopped by the Geneva gear, which will be described later, and the engagement between the gear 36 and the gear portion 34 is released.On the other hand, in the state (b) during loading, the tip of the cam 34 and the arm 42 is engaged, and the arm 42
The arm 4 rotates around an axis 43, and the arm 4 rotates around an axis 45.
Rotate 4. The arm 44 connects to the arm 46 via a shaft 47.
Since it is engaged with the shaft 49 of the arm 48, the arm 4
8 is moved to the loading position. Since the arm 48 is biased in the direction of the arrow by the spring, the cam 34 and the arm 42 do not engage (
In the situation (1), the pinch roller 8 has retreated to the unloading position. When the cam 34 rotates further than the state of (b) and reaches the state of C), the arm 42
d, and presses the pinch roller 8 against the capstan 7 by a toggle mechanism formed by arms 44 and 46. The shaft 45 is mounted on an arm 51 supported by a shaft 52, and the arm 51 is constantly pulled by a spring 53 and its position is regulated by a stopper 54, so that even after the pinch roller 8 stops moving, the arm 42 does not rotate. By doing this, arm 5
1 moves away from the stopper 54 against the force of the spring 53, thereby ensuring the pressing force between the pinch roller and the capstan.

FIG. 9 shows the lower stage of the cam 34 and the mode operating mechanism, (a
) shows unloading, (b) shows loading/unloading in progress, and (C) shows loading status.

36 (2 is a Geneva gear part provided integrally with the gear 36. The arm 55 has one end connected to the cam part 34c or 3
4e and is biased counterclockwise around the shaft 56 by a spring 57 attached to one end. A brake member 58 is attached to the other end of the arm 55 and applies a brake force to the supply reel stand 59. The arm 60 engages with the cam portion 34c or 34e, and is attached to the shaft 62 by a spring 61 attached to one end.
Forced clockwise. Further, the arm 63 has an arm 63a that can be engaged with a shaft 60a on the arm 60, and a spring 65 is attached to one end of the arm 63, so that the arm 63 is biased counterclockwise around the shaft 62. Furthermore, a brake member 64 is attached to the other end and applies a braking force to a drive disk 66 that engages with the take-up reel 5. (a) shows the stopped state after unloading, and the arm 55 is engaged with the recessed portion of the cam portion 34e, and a braking force is applied to the supply reel stand 59.

At this time, since the concave portion and the arm 55 do not directly engage, the braking force is determined only by the force of the spring 57, and the cam portion 34c
It is stable regardless of the stroke.

Further, the arm 60 engages with the convex portion of the cam portion 34e, and the spring 6
Since the engagement between the shaft 60 (2 and the arm 63a is released in opposition to 1), the braking force is applied to the drive disk 66 by the biasing force of the spring 65, and is maintained stably regardless of the stroke of the cam portion 34e, (b) In this state, the arms 55 and 60 engage with the cam portion 34f, and only the braking force applied to the supply reel stand 59 is released.

Therefore, during loading, the tape 6 is basically fed out from the supply reel side. The state (C) shows the recording/reproducing state, in which a brake force is applied to the supply reel stand 59, but the arm 60 engages with the recess of the cam portion 34c and rotates due to the tensile force of the spring 61. 60 (Z engages with the arm 63a, rotates the arm 63 against the spring 65, and releases the braking force on the drive disk 66.At this time, the Geneva gear portion 36a and the stopper surface 34b engage with each other, so that The rotation of the gear 36 is stopped, the driving members 31 and 33 are stopped, and the pressing force of each tape guide group to the positioning member is maintained.In this way, the movement of the cam 34 is controlled via a switching mechanism such as a Geneva gear. By transmitting the signal to the drive member, it is possible to easily cope with an increase in the number of operation modes.

FIG. 10 shows the three drive members 31 and 33 described above,
The movement of the cam 34 is shown in (a) when ejecting;
(E) shows the completion of loading, and (F) shows the mode operation such as recording/playback. The shape of each member is simplified and shown as a circular arc. As shown in FIG. 8, the inlet drive member 33 rotates in the opposite direction to the movement of the cam 34 at approximately the same speed, and the outlet drive member 31 rotates in the same direction at approximately twice the speed.

FIG. 11 is a perspective view of the catcher 28. It has an integral structure for positioning the tape guide groups on the entrance and exit sides of the tape guide drum 2. For the tape guide group on the entrance side, the lower shaft part of the guide roller 17 is attached to Vill1.
28a, and the upper part is regulated by a U groove 28b to prevent the guide roller 17 from falling in a direction perpendicular to the direction in which it enters. The height of the guide roller 17 is regulated by the upper end of the guide base 27 coming into contact with the stopper surface 28c. Further, the inclination of the inclined pin 18 is determined by the side surface of the guide base 27 coming into contact with the wall 28d. The same goes for the tape guide group on the exit side, and the position and angle of the guide roller 19 are V.
The height is determined by the groove 28e and the U groove 28+, and the height is the stopper surface 2.
Determined by 8 yen. Further, the inclination of the tilt pin 20 is restricted by the wall 28.

Furthermore, a notch 28L is provided between the V-groove 28e and the U-groove 28f of the catcher 28. Figure 12 shows catcher 2
8 is a partial cross-sectional side view of 8, in which (α) is an unloading state and (b) is a loading completed state. In the unloading state, one end of the cam 34 and one end of the exit drive member pass through the notch 28L, but these members escape from the notch 28L due to the loading operation, so in the loading complete state, , the guide roller 19 and the tilt pin 20 can be held in place.

FIG. 13 is a perspective view showing the guide member 68 of the tape guide group, and FIG. 14 is a side view showing the support structure of the tape guide group by the guide member 68.

The guide member 68 has an integral structure with a guide part for the inlet tape guide group and a guide part for the outlet tape guide group, and the tip of the guide part for the outlet tape guide group descends to follow the tape running path. It has a descending part. A tip 68α of the cross section of the guide member 68 engages with the guide base 26 or 27 so as to be gripped thereto, and restricts the moving path of the guide base 26 or 27.

FIG. 15 shows a mechanism for moving the inclined pin 21 located on the exit side. FIG. 15(α) is a state corresponding to the unloading state shown in FIG. 8(a).

A gear 69 rotatably supported coaxially with the arm 48 is
The right end 484F of the arm 48 and the bent portion 69c of the gear 69 are brought into contact with each other by a spring 7o whose both ends are hooked onto the bent portion 691 of the gear 69 and the left end 48a of the arm 48. From this state, the first
When the mode shifts to the state shown in FIG. 5(I) and the arm 48 rotates so that the pinch roller 8 comes into pressure contact with the capstan 7, the arm 72 having the gear portion 72a that meshes with the gear portion 69a of the gear 69 rotates. The arm 72 rotates, and the inclined pin 21 implanted at the tip of the arm 72 is positioned at a predetermined position by the catcher 73.

After positioning, the arm 48 further rotates to move to the first position.
As shown in FIG. 5(4), the arm 48 moves away from the bent portion 69c of the gear 69 against the force of the spring 70, thereby ensuring the pressing force of the inclined pin 21 against the catcher 73. Note that by driving the tilt pin 21 at the timing described above, the tilt pin 21 is loaded from the rear of the guide base 27. That is, since the movement trajectories of the tilt pin 21 and the guide base 27 partially overlap, when the guide base 27 passes through the overlapped portion in advance, the cam 34 and the arm 42 engage and drive the tilt pin 21. The position of the arm 42 and the reduction ratio of the arm 72 drive system are set so as to. 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.

As explained above, the loading mechanism and mode operation in this device are performed by the entry side drive member 33. Output side drive member 31.
This is done centering on the cam 34. FIG. 1 is a perspective view showing an assembled configuration of the three arc-shaped members described above. The cam 34 is connected to guide pins 74a to 74e installed in the chassis 1.
The cam 34 is rotatably guided on the chassis 1 by engagement with a groove 34 formed on the entire lower circumference of the cam 34. The guide pins 74 (Z to 74e are arranged so that three or more guide pins 74 (Z to 74e) are always engaged with the groove 343 of the cam 34 in the rotation range of the cam 34 shown in FIG. 10.
1 is rotatably held by the cam 34 by guide pins '16a and 76#, and the guide pins 75a and 751 and the elongated hole portions 311 and 31c of the ejection side drive member 31 are also planted in the lower part of the ejection side drive member 31. The cam 34 is rotatable concentrically with the cam 34 by engagement between the pin (not shown) and the elongated hole 34I of the cam 34. As shown in FIG. 10, the input drive member 33 has a small rotation angle, so during its rotation range, the roller 67 is used on its inner periphery, and the gears 75 and 77 are constantly connected to the input drive member gear portion 33a on the outer periphery. Engaged and held together. As shown in FIG. 10, the output drive member 31 and the cam 34 rotate in the same direction over an angle of 80 degrees or more. Therefore, as shown in FIG.
By replacing the substrate that holds the rotation of 1 with the cam 34, the elongated holes 31z, 31 formed in the output side drive member 31
The angle c can be determined by the difference in relative rotation angle between the output drive member 31 and the cam 34. The blocks 79 and 81 are each screwed to the chassis 1 with screws 80° and 82 to suppress vertical play of the cam 34.

Next, the guide base holding mechanism according to the present invention will be described in detail. FIG. 1 is a perspective view of the guide base 27 and the guide member 68, and the engaging portion of the guide member 68 with the guide base 27 is partially shown through to make the engaging surface of the guide base 27 easier to see.

The guide base 27 connects the guide member 68 to the guide base 27.
The upper clamping part of the guide base 27, which is fixed with a screw 83, is clamped by the lower clamping part 27I and the lower clamping part 27a. 1st
FIG. 7 shows a cross section of the lower protrusion 68 (2) of the guide member 68 and the lower clamping part 27 (2) of the guide base 27. Four circular arc-shaped protrusions 27 cm (27 cm) are formed that fit together. This shape is the same for the upper holding part 271 of the guide base 27, and the guide member 68 is held at four places on the left and right in the vertical direction. are the clamping portions 273, 27 holes of the guide base 27 shown in FIG.
Holding 684. Guide member 6 of guide base 27
By making the engaging surface with 8 arc-shaped as shown in FIG. 17, the guide member 68 shown in FIG. 17(a) can be straight or arc-shaped as shown in FIG. 17(I). Always guide member 68
The arcuate protrusion 27c=J of the guide base 27 maintains a substantially constant slight clearance or line contact relationship, and the guide base 27 can be held stably. The radius of this arc-shaped projection is determined by the width Q of the guide member 68, the span m of the arc-shaped projection, and the minimum radius n of the guide member 68.

In this embodiment, support at four points is shown, but support at three points is also applicable.

〔Effect of the invention〕

According to the present invention, a tape guide that engages with a single-shaped rail having multiple circular arcs including straight lines can be provided without using a spring.
In addition, since it can be held stably without wobbling, the mechanism can be made smaller, the number of parts can be reduced, and damage to the tape can be prevented.

[Brief explanation of the drawing]

Figure 1 is a perspective view of the guide base and guide member, Figure 2 is a top view of the magnetic recording and reproducing device, Figures 3 and 4 are side views of Figure 2, and Figures 5 to 7 are triple-layered views. FIG. 8 is a top view of the pinch roller crimping mechanism, FIG. 9 is a top view of the brake operating section, and FIG. 10 is a model diagram showing the rotational phase of the triple ring. Fig. 11 is a perspective view of the catcher, Fig. 12 is a sectional view of the catcher, Fig. 13 is a perspective view of the guide member, Fig. 14 is a side view of the rail and guide base, and Fig. 15 is a view of the inclined pin crimping mechanism. A top view, FIG. 16 is an assembled perspective view of the loading mechanism, and FIG. 17 is a cross-sectional view of the guide base and the guide member. 27... Guide base, 68... Guide member. 1st Figure Guan 2 Figure 3 Figure Collection-4-7 S Drawing, 1/Pa 6 Drawing Name 7 Z (b) (C) 8th q Ward (C) 8nth Drawing 12th (α) (b) 4 Suggestion 5 No 3 L? 1 2Otsu, 2ri Figure 15 (S) Figure 76

Claims (1)

[Claims] 1. A tape guide that moves along the circumference of a rotating drum and has a C-shaped clamping part on its side, and a tape guide that is included in the clamping part of the tape guide to guide the tape guide and has multiple curvatures. 1. A tape loading mechanism for a magnetic recording/reproducing device, wherein the engaging surface of a clamping portion of a tape guide that engages with the tape guide rail is arc-shaped.