JPH01140454A - Loading device for magnetic recording and reproducing device - Google Patents

Abstract

PURPOSE:To eliminate the twisting of a gear and to stabilize a turning by minimizing the relative displacement between a circular arc shaped slider and a driving ring. CONSTITUTION:For a cam 34, a groove 34g formed on the whole circumference of the lower part of the cam 34 is engaged to guiding pins 74a-74e planted on a chassis 1, and the cam 34 is guided on the chassis 1 turnably. An outgoing side driving member 31 is sandwiched freely turnably by the cam 34 with guiding pins 76a and 76b, oblong hole parts 31b and 31c are engaged to the guiding pins 76a and 76b, an oblong hole part 34h of the cam 34 is engaged to a pin planted on the lower part of the outgoing side driving member 31, and the member 31 turns in a concentric circle shape with the cam 34. Since an incoming side driving member 33 has a small turning angle, the member 33 is held by making its inner circumference gear with a roller 67 and making the gears 75 and 77 of its outer circumference gear with a gear part 33a in a turning range. Thus, the turning angle of the outgoing side driving member 31 can be reduced to the relative turning angle difference between the outgoing side driving member 31 and the cam 34 by making the cam 34 execute the turning and holding of the outgoing side driving member 31. Thus, the twisting of the gear can be eliminated, and the turning can be stabilized.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a magnetic recording/reproducing device, and particularly to a tape loading device suitable for reducing the size and weight of the device.

[Conventional technology]

In a magnetic recording/reproducing device, a magnetic tape (hereinafter abbreviated as tape) stored in a tape cassette.

A pair of tape guides are driven and guided to move around the rotating drum so as to wrap it around the rotating drum at a predetermined angle. As a so-called tape loading device.

For example, as described in Japanese Patent Application Laid-Open No. 58-218066, two movable rings rotate around a rotating drum and drive a pair of tape guides (hereinafter referred to as first and second guides), respectively. (hereinafter referred to as the first and second rings),
There is one in which three driving rings for driving the first and second rings are stacked one on top of the other and arranged concentrically and rotatably. Further, similar to this device, there is also known a device configured with an arcuate slider instead of a ring. In such a loading device, a method of holding and positioning a ring or an arcuate slider that rotates once is to use a gear that meshes with a gear formed on the ring or an arcuate slider, or a roller to move around the outer or inner periphery of the ring or arcuate slider. each received.

[Problem that the invention seeks to solve]

The above-mentioned prior art does not take into consideration the backlash of the arc-shaped slider and the meshing of the gears, especially when the arc-shaped slider is held.

For example, if we consider an arc-shaped slider with a gear formed on its outer periphery as shown in Fig. 2, in order to hold one arc-shaped slider, basically the first arc-shaped slider is always driven. A minimum of three members are required: a first gear, a second gear that supports the outer periphery of the arcuate slider, and a roller that is placed between these two gears and receives the inner periphery of the arcuate slider. However, when rotating over a wide angle, there may be a state in which the one-arc slider and the gear do not mesh, and if you try to engage the arc-shaped slider and the gear from this state, the arc-shaped slider may deflect or the one-arc slider may not mesh with the gear. With the gear.

2 due to backlash and play with the gear that receives the outer periphery.
There is a problem in that the meshing between the rotating arcuate slider and the gear becomes strained and the operation of the arcuate slider stops. Therefore, in order to solve this problem, it is necessary to arrange a large number of gears and rollers (three or more), and also to create a special mechanism and device to eliminate the twisting of the gears.
This caused an increase in the space for placing parts (there was a problem).

SUMMARY OF THE INVENTION An object of the present invention is to provide a loading device in which three concentrically stacked arcuate sliders are rotated stably in a space where two parts are arranged, with a small number of parts.

[Means for solving problems]

The above object is a method of holding a one-arc slider, in which a drive ring rotates in the same direction and a second ring has a large rotation angle, the drive ring is placed on the substrate, the second ring is placed on the drive ring, This is achieved by minimizing the relative displacement between the arc-shaped slider and the drive ring by using guide members (pins, etc.) arranged concentrically, and guide grooves formed in the drive ring and the second ring. be done.

[Effect]

The drive ring is guided and held by pins set up on the substrate and grooves formed in the drive ring, and rotates in the same direction as the second ring, which has a larger rotation angle.

The second ring is guided and held by a pin mounted on the drive ring and a groove formed in the second ring. The first ring, which has a small rotation angle, is placed on the second ring so that it always meshes with the gear formed on the first ring during the first rotation range.

The gear is planted on the substrate. With the above configuration, the three rings (arc-shaped slider) are in a state where the gear formed on the ring does not mesh with the gear that meshes with the gear during operation. This eliminates the need for gear supports (there is no need to pass between the gears), eliminating strain between the gears.In addition, the gears are spread out in the width direction of the ring over the entire rotation range of the ring. Ta.

The gear and roller for holding the ring should be placed in the first position, which has a small rotation range.
Only the minutes used to hold the ring can be used.

〔Example〕

An embodiment of the present invention will be described below with reference to FIGS. 1 to 16.

FIG. 1 shows a plan view of a magnetic recording and reproducing apparatus 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. A built-in cassette, 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 records audio signals and control signals on the upper and lower ends of the tape 6. and an audio control head for 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, and the tilt pin 21 and capstan 7 are inserted into the opening 15 at the positions shown by broken lines and solid lines, respectively. At this time, the pinch roller 8 is also in the position shown by the broken line.

When the four- ding operation is performed, each guide moves while pulling out the tape 6.

The guide roller 17 and the inclined 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 are a pair of toners,
It moves horizontally up to the vicinity of the audio/troll head 11 and then diagonally downward until it is positioned near the tape guide drum 2, and approximately 27 Cf of the tape 6 is wound around the tape guide drum 2.

The tilted bin 21 moves horizontally from the rear 3 of the tilted bin 20 and is fixed upstream of the audio control head 11, corrects the attitude of the tape 6, and guides it to the winding wheel 5 (as a result, the tape 6 is placed in the cassette Out from 3.

Tensilon pin 16. Height regulation guide 22. Erasing head 10. Guide roller 17. The tape is wound spirally at a predetermined angle on the tape guide drum 2 through the inclined bin 18, and then wound on the guide roller 19. Tilt bin 20, tilt bin 21. Fixed Guy)”
23. Audio Control Rad 11. Height regulation guide 24. It passes through a fixed guide 25 and is driven by being pressed against it by a cab stun 7 and a pinch roller 8.

The winding reel 5 is reached. FIG. 3(α) shows a side view when loading is completed, and FIG. 3(A) shows a side view when unloading is completed. In the WJa diagram (α), 26 is a guide pace, and a guide roller 17 and an inclined bin 18 are set up, and are positioned and held by a catcher 28.
7 also guide roller 19 and inclined guide 2 at the guide pace.
0 is planted and similarly positioned by the catcher 28. As shown in the figure, the tape guide on the output side of the tape guide drum 2 is thicker (lower) by approximately the width of the tape than on the input side. By arranging the tape guide drum 2 at a slightly lower position, the tape guide drum 2 can be placed under the lid 12 of the cassette 3, thereby making the device smaller and thinner.

Next, the loading mechanism will be explained in detail. FIG. 4 shows the guide moving member on the exit side. The guide pace 27 for planting the guide roller 19 and the inclined bin 20 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 drive member 31 has an arc shape, and a gear portion 31 is provided on the outer periphery of the drive member 31.
α is provided. FIG. 5 shows the guide moving member on the entry side. The guide pace 26 for setting up the guide roller 17 and the inclined bin 18 is supported by a connecting plate 32 so as to be rotatable within a plane, and the connecting plate 32 is similarly rotatable within a plane and is supported by an inlet drive member 33. supported at one end. The inlet drive member also has an arc shape, and a gear portion 33 is provided on the outer periphery of the drive member.
α is provided. FIG. 6 shows the cam 34. cam 3
4 consists of two stages, upper and lower, and the upper stage has a gear section 34 from the left.
α, there is a cam part 34d, and the lower stage is the Geneva gear (described later)
The stopper surface 34b corresponds to the cam portion 34C, and the cam portion 34C corresponds to the mode operation after loading.

There is a cam part 34f corresponding to the middle of loading/unloading, and a cam part 34- corresponding to mode operation after unloading, and the whole has an arc shape. From the top, these are the entry side drive member 33° and the exit side drive member 3.
1. The cams 34 are arranged concentrically on the chassis in order.

FIG. 7 shows the upper stage of the cam 34 and the drive system, (α) shows the unloading time y, <h'r shows the loading state during unloading, and (C1 shows the loading state).The cam 34
is driven by a gear 35 driven by a drive source (not shown) meshing with the gear portion 34α.

As the cam 34 rotates, the gear 36 that meshes with the gear portion 34α rotates, and the output drive member 31 rotates through the gear 37°3.
A gear 39, which rotates together with the gear 38 through the gear 8 and a compression spring (not shown), is driven by meshing with the gear portion 31α. Similarly, the entrance drive member 33 has a gear 40
, 41, and a gear 55 incorporating a compression spring (not shown) is driven by meshing with the gear portion 33a.

When the loading is completed (C), the rotation of the gear 36 is stopped by a 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 engages with the arm 42, and the arm 42 rotates around the shaft 43, and the arm 44 rotates around the shaft 45.
Rotate. The arm 44 is engaged with the shaft 49 of the arm 48 by the arm 46 via the shaft 47, so that the arm 48
The pinch roller 8, which is pivotally supported by the pinch roller 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 (α
), the pinch roller 8 has retreated to the unloading position. When the cam 34 rotates further than the state shown in (b) and reaches the state shown in c), the arm 42 engages with the cam portion 34d, and the pinch roller 8 is attached to the capstan 7 by the toggle mechanism formed by the arms 44 and 46. Pressure contact. axis 45
is installed on the arm 51 supported by the shaft 52, and the arm 5
1 is constantly pulled by the spring 53 and its position is regulated by the stopper 54, so even after the pinch roller 8 stops moving, the arm 42 rotates, so that the arm 51 moves away from the stopper 54 against the spring 53. This ensures the pressure force between the pinch roller and the capstan.

FIG. 8 shows the lower stage of the cam 34 and the mode operating mechanism.

(α) shows unloading, (b) shows the loading/unloading process, and (C) shows the loading state. 36α is a Geneva gear portion that is provided integrally with the gear 36. One end of the arm 55 engages with the cam portion 34c or 341, and a spring 57 attached to the one end causes the arm 55 to engage the shaft 56.
is biased counterclockwise around the 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 34ε, and is supported by the shaft 6 by a spring 61 attached to one end.
2 is biased clockwise. Further, the arm 63 has an arm 63α that can be engaged with a shaft 60α on the arm 60, and a spring 65 is attached to one end of the arm 63 so as to be biased counterclockwise around the shaft 62. Furthermore, a brake member 64 is attached to the other end to apply a braking force to a drive disk 66 that engages with the one-winding reel 5. (α) represents a stopped state after unloading, and the arm 55 is engaged with the recessed portion of the cam portion 34ef7), and a braking force is applied to the supply reel stand 59. At this time, since the recessed portion and the arm 55 do not directly engage with each other, the braking force is determined only by the force of the spring 570, and is stable regardless of the stroke of the cam portion 34C. In addition, the arm 60 is connected to the cam portion 3.
4g and releases the engagement between the shaft 60α and the arm 63α against the spring 61, so that a braking force is applied to the drive disc 66 by the biasing force of the spring 65, and the cam portion 34
10 Stable regardless of the stroke in state (b).

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) indicates the recording/playback state,
A braking 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, and the shaft 60α engages with the arm 63α, causing the arm 63 to rotate.
is rotated against the spring 65 to release the braking force on the drive disc 66. At this time.

By engaging the Geneva gear portion 36α and the stopper surface 34h, the rotation of the gear 36 is stopped and the driving members 31 and 3
3 is stopped, and the pressing force of each tape guide group to the positioning member is maintained. By transmitting the movement of the cam 34 to the driving member through a cut-out mechanism such as a Geneva gear in this manner, it is possible to easily cope with an increase in the number of operation modes.

FIG. 9 shows the three drive members 31 and 33 described above.

The movement of the cam 34 is shown in (a) when ejecting;
(E) indicates the loading is completed, and (F) indicates the mode operation such as recording/playback. The shape of each member is simplified and shown as an arc. As shown in FIG. 7, the entry side drive member 33 rotates in the opposite direction to the movement of the cam 34 at approximately the same speed.
The output drive member 31 rotates in the same direction at approximately twice the speed.

FIG. 10 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 entry side, the shaft part at the bottom of the guide roller 17 is connected to the V groove 2.
8α, and is regulated by the upper YU groove 28b to prevent the guide roller 17 from falling in a direction perpendicular to the direction in which it enters.

What is the height of the guide roller 17?

The top of the tip of the guide pace 27 is the stopper surface 28? It is regulated by coming into contact with. Further, the inclination of the inclined bin 18 is determined by the side surface of the guide space 27 coming into contact with the wall 28d. The same goes for the tape guide group on the exit side, the position and angle of the guide roller 19 are determined by the V groove 28g and the U groove 28f, and the height is determined by the stopper surface 28! ! It is determined by Further, the inclination of the tilting bin 20 is regulated by the wall 28A. Furthermore, a notch 28 is provided between the V groove 28g and the U groove 28f of the catcher 28.
i is provided. FIG. 11 is a partial cross-sectional side view of the catcher 28, in which (α) is in the unloaded state and (b) is in the unloaded state.
) is the loading complete state.

In the unloading state, one end of the cam 34;
One end of the delivery side drive member passes through the notch 28L, but when the loading operation button is pressed, these members are inserted into the notch 28L.
Since the guide roller 19 and the inclined pin 20 can be held at a predetermined position in the loading completion state, the guide roller 19 and the inclined pin 20 can be held at a predetermined position.

FIG. 12 is a perspective view showing the guide member 68 of the tape guide group, and FIG. 13 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 having a guide part for the inlet tape guide group and a guide part for the outlet tape guide group.

The leading end of the guide section of the output tape guide group has a descending section that descends along the tape running path. The distal end 68α of the cross section of the guide member 68 engages with the guide base 26 or 27 so as to be gripped, and restricts the moving path of the guide pace 26 or 27.

FIG. 14 shows a mechanism for moving the inclined pin 21 located on the exit side. FIG. 14 (α) is a state corresponding to the unloading state shown in FIG. 8). A gear 69 rotatably supported coaxially with the arm 48 has both ends connected to the gear 69.
The right end 48b of the arm 48 and the bent portion 69c of the gear 69 are in contact with each other by a spring 70 hooked on the bent portion 69h of the arm 48 and the left end 48α of the arm 48.

When the mode shifts from this state to the state shown in FIG. 14 (bl) corresponding to FIG.
An arm 72 having a gear portion 72α that meshes with a gear portion 69α of
rotates, and the inclined pin 21 is 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 reach the 15th position.
As shown in Figure (h), 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. Namely.

Since the movement loci of the inclined pin 21 and the guide base 27 partially overlap, the cam 34 and the arm 42 engage with each other to drive the inclined pin 21 when the guide base 27 passes through the overlapped portion in advance. The position of the arm 42 and the reduction ratio of the arm 72 drive system are set as follows. 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. 2 is a perspective view showing an assembled structure of the three arc-shaped members described above. cam 3
4 is a groove 34 formed on the entire lower circumference of the guide bins 74α to 746 installed on the chassis 1 and the cam 34! By engaging with l, it is rotatably guided on the chassis 1. The guide pins 74α to 74g are located within the rotation range of the cam 34 shown in FIG.

Three or more are arranged so as to be engaged with the groove 341 of the cam 34 at all times. The exit drive member 31 is a guide pin 76α.

Rotatably held by the cam 34 by 76b, the guide bins 75α, 75h and the elongated drive member elongated hole portions 31A, 3
1C, and the long portion 34h of the cam 34 engages with a bottle (not shown) installed at the bottom of the output side drive member 31cr5, thereby making it possible to rotate concentrically with the cam 34. . Since the entrance drive member 33 has a small rotation angle as shown in FIG.
The gears 75 and 77 on the outer periphery are the input drive member gear part 33.
It is always engaged and maintained with α. As shown in FIG. 9, the output drive member 31 and the cam 34 rotate in the same direction over an angle of about 180 degrees or more. Therefore, as shown in FIG. 2, by replacing the substrate that holds the rotation of the output drive member 31 with the cam 34, the angles of the elongated holes 31h and 31C formed in the output drive member 31 are as follows.
This can be done by changing the relative rotation angle between the output drive member 31 and the cam 34.

In other words, when holding a ring on a substrate that rotates over 180 degrees, the angle of the long hole can be reduced according to this embodiment, compared to the case where the long hole of the ring requires 180 degrees or more. , problems such as ring play and strength can be minimized. The blocks 79 and 81 are screwed to the chassis 1 by screws 80 and 82, respectively, to suppress vertical play of the cam 34.

In this example, there are three overlapping arc-shaped sliders (
Although the case of a ring) has been described, the same applies to a one-circular ring. In addition, as shown in Fig. 15, in a loading device that guides two tape guides in one direction, three tape guides or one ring that rotates in the same direction can be used as both a drive ring and a tape guide guide ring. It may be composed of two sheets.

Further, instead of the elongated holes and pins used to guide and hold the ring, it may be held using a block 78 and groove integrated with the ring as shown in FIG. 16.

[Effects of the Invention] According to the present invention, the loading device for guiding the tape guide has the following effects.

1) The rotating ring and the gears that hold the ring all mesh with each other during the loading operation, eliminating strain at the beginning of meshing between the gears (gear receivers pass), increasing the reliability of one mechanism operation. You can improve your sexuality.

2) Since the members necessary for holding the ring can be arranged within the width of the button, the space for placing one part can be minimized, and the device can be made more compact.

3) The parts required to hold the ring can be constructed from only a few parts, including those that are integrated with the ring, compared to conventional systems that have a large number of gears and rollers.

The number of parts and cost can be reduced.

[Brief explanation of the drawing]

Fig. 1 is a top view showing an embodiment of the present invention, Fig. 2 is an assembled perspective view showing the component configuration of the loading device, Fig. 3 is a side view of Fig. 1, and Figs. Perspective view of heavy ring,
Figure 7 is a top view of the pinch roller crimping mechanism, Figure 8 is a top view of the brake operating unit, Figure 9 is a model diagram showing the rotational phase of the triple ring, Figure 10 is a perspective view of the catcher, and Figure 10 is a perspective view of the catcher. 1
Figure 1 is a sectional view of the catcher, Figure 12 is a perspective view of the rail, Figure 13 is a side view of the rail and guide pace, Figure 14 is a top view of the inclined pin crimping mechanism, and Figure 15 is the double ring. The perspective view and FIG. 16 are cross-sectional views of the double ring. 2...Tape guide drum. 17, 19... Guide rollers. 26, 27... Guide base. 31... Output side drive member, 33... Inlet side drive member. 34... Cam 1 Ro 20 Suji B flash (δ) 4th 5th ward 70 8 Ro (C) 11th [D ■ (b) Suji 12 Koku wa/41D (Drink)

Claims (1)

[Claims] a chassis; a rotating drum mounted on the chassis; first and second sliders each having a tape guide at one end and moving along the outer periphery of the rotating drum to set the tape guide in a predetermined position; A first guide member provided on the chassis engages with the guide groove of the first slider to hold and guide the first slider, and a first guide member provided on the chassis engages with the guide groove of the second slider to hold and guide the first slider. 1. A loading device for a magnetic recording/reproducing device, comprising a second guide member provided on a first slider, which holds and guides the slider.