JPH0397155A - Tape loading mechanism for magnetic recording and reproducing device - Google Patents

Abstract

PURPOSE:To certainly load a tape without increasing the number of parts and making a device large by providing a first guide surface which regulates the height in the up-and-down direction of a guide base, a second guide surface which regulates the position in the right-and-left direction thereof and a third guide surface which regulates the position in the rotating direction thereof. CONSTITUTION:The pawl part of the guide base 27 whose cross section is C-shaped is engaged with a guide member 68 whose cross section is Z-shaped so that it can be moved in a longitudinal direction and it is engaged with the guide member 68. Accompanied with the progress of tape loading action, the tape 6 is drawn from a cassette 3 and wound o a tape guiding drum 2. Then, a prescribed tape path is formed. At this time, the positions in the up-and-down direction and the right-and-left direction of the tape guide base 27 with respect to the moving direction and the posture of the rotating moment direction thereof are regulated by the first - third guide surfaces 68a - 68c of the guide member 68. Thus, the tape guide base can be moved along the guide member 68 while the height, position and posture thereof are always held and regulated to the optimum for the stable tape loading. As the result, the tape is stably and certainly loaded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a tape guide pace guide Ia structure of a tape loading mechanism of a helical scan type magnetic recording/reproducing device.

[Conventional technology]

An example of the structure of a conventional tape loading mechanism is a tape guide member in which a guide member having a C-shaped cross section is mounted along a guide rail having a T-shaped cross-section, as described in Japanese Patent Application Laid-Open No. 57-135558. The structure is such that the tape is loaded by guided movement. [Problems to be Solved by the Invention] The above-mentioned conventional technology is excellent in that it promotes the use of carbon atoms in the mechanism and achieves cost reduction, but when trying to make the mechanism even more compact, the following points are required. There is a problem with TG. In other words, when trying to make the mechanism of a helical scan type magnetic recording/reproducing device smaller and thinner, the tape guide drum was made upright, and the tape guide drum was made smaller in diameter. The tape wrapping angle has been expanded, and the tape running path has a 5K three-dimensional shape, with the entrance side rising and the exit side falling. At this time, the ideal tape guide path to minimize tape damage during tape loading requires a three-dimensional movement path, and for this reason, the rowing mechanism must be complicated. In the above situations, the shape of the guide member such as the tape guide base that guides the tape to the tape guide drum must not only be shaped to move horizontally or vertically, but also have a twisted shape. The shape is three-dimensional and extremely complex. Generally, the above-mentioned guide members are mass-produced using paulownia resin or die-casting in an integral shape.
If the shape is complicated, such as a K-shaped helical shape,
Is it very difficult to form similar forms? This also increases costs and makes it difficult to maintain accuracy. If the guide member with the above-mentioned T-shaped cross section is shaped so that it can be easily molded by molding, the guide base (
27) The play becomes large and stable tape loading operation cannot be obtained.

The purpose of the present invention is to eliminate the cost and cost reduction of the conventional guide base (27) in which stable movement of the guide base at the time of tape loading was not possible due to the difficulty of forming the guide member with high precision. winding force 1-4h increase in number of parts,
The object of the present invention is to realize a reliable k-tape loading operation mechanism without deteriorating assembly performance, complicating the shape of parts, or increasing the size.

[Means to solve the problem]

In order to achieve the above purpose, the cross-sectional shape of the guide member for guiding the movement of the force-id base is made into a Z-shape instead of the conventional T-shape, and the shape of the guide member itself is made by high-precision molding. It has an easy shape. The height of the guide base is regulated in the vertical direction so that the movement locus of each tape guide when loading the tape in the case is at the design standard height position in the case of an optimal design that does not cause tape bending or leakage. The guide member is provided with a first guide surface, a second guide surface that regulates the position in the left-right direction, and a third guide surface that regulates the position in the left-right direction at a position facing the second guide surface. It is something. [Function] The claw portion of the guide base (27), which has a C-shaped cross-section, is engaged with the above-mentioned guide member having a Z-shaped cross-section so as to be movable in the longitudinal force direction. As the tape loading operation progresses, the guide pace moves from inside the cassette opening around the tape guide drum along the aforementioned guide member. Along with this, the tape is pulled out from the cassette and wound around the tape guide drum, forming a predetermined tape path. At this time. The tape guide pace described in a is controlled by the guide member in its vertical position, horizontal position in accordance with the moving direction, and posture in the rotational moment direction. Thereby, the tape guide base is always positioned along the guide member at an optimal height for stable tape ading. It is possible to maintain the position and posture and move while being regulated, and a thin mechanism that can perform stable and reliable table loading operations can be realized.

〔Example〕

An embodiment of the present invention will be described below with reference to FIGS. 1 to 18.
5! I will clarify.

FIG. 1 shows a plan view of a magnetic recording and reproducing apparatus using a tape loading mechanism 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 wound on a supply reel 4 and a take-up reel 5. A cassette containing the tape 6 to be rotated; 7 a cab stan to which a motor 9 is directly connected to the lower end; 8 a pinch roller; 10 a full-width erasing head fixedly supported on the catcher 2B and erasing 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 installed in the device, the lid 12 on the front of the cassette 3 is opened. Further, inside the opening 13, there are a tension bin 16 and a guide roller 17.
and the tilt pin 18 are inserted, the guide roller 19 and the tilt pin 20 are inserted into the opening 14, and the tilt pin 21 and the capstan 7 are inserted into the opening 15 at the positions shown by broken lines and solid lines, respectively.

At this time, the vinyl 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. The guide roller 17 and the tilt bin 18 move horizontally as a pair and are positioned near the tape guide drum 2. Guide roller 19 and inclined pin 20
They form a pair and move horizontally up to the vicinity of the audio head and control head 11, then diagonally downward and are positioned near the tape guide drum 2, winding the tape 6 around the tape guide drum 2 approximately 270 degrees. to wear. The tilting bin 21 is moved horizontally from behind the tilting bin 20 to a position 11K upstream of the audio head and control head 11.
The position of the tape 6 is corrected and the tape 6 is guided to the take-up reel 5. As a result, the tape 6 is ejected from the cassette 3, passes through the tension pin 16, the impedance roller 22, the full-width erasing head 10, the guide roller 17, and the inclined pin 1B, and is wound spirally around the tape guide drum 2 at a predetermined angle. 19, inclined pin 20, inclined pin 21, [i! After passing through the fixed guide 23, the audio head and control head 11, the height regulation guide 24, and the fixed guide 25, the capstan 7 and the pinch roller 8 are pressed against each other and driven, leading to winding-A/5.

Figure 2 (al is a side view when loading is completed, Figure 2 (
Al shows the side view when unloading is completed. In Figure 3 (α), 26 is the guide pace and the guide roller 1
7 and the inclined bin 18 are erected, positioned and held by the catcher 28, and the casing 27 is also erected with the guide roller 19 and the inclined guide 20 at the guide pace, 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 lowered by approximately the width of the tape compared to the tape guide on the input side. As a result, the inclination angle of the tape guide drum 2 is reduced, and by placing it at a position slightly lower than the cassette 3, the tape guide drum 2 can be placed under the lid 12 that opens in front of the cassette 3. We are trying to make it smaller and thinner. Next, we will explain the loading mechanism of the pancreas. Figure 3 shows the guide moving member on the exit side. Guide roller 19 and inclined bin 2
As shown in FIG. 3, the guide space 27 for planting 0 is connected to a connecting plate 29 with a large play. Similarly, the connecting plate 29 is connected to the exit drive member 31 with a large play. supported at one end.

The output side drive member 31 has an arc shape, and a gear portion 316 is provided on its outer periphery. Figure 4 shows the guide moving member on the entry side. Guide roller 17 and tilt bin 18
The guide pace 26 for planting is rotatably supported around a shaft 33d planted on the entry side drive member 33. The mosquito entry side drive member similarly has an arc shape, and a gear portion 33g is provided on its outer periphery. FIG. 5 shows the cam 34. The cam 34 consists of two stages, upper and lower. The upper stage has a gear part 54m and a cam part 54t from the right, and the lower stage has a stopper surface 64b that corresponds to the Zenepa gear (described later), and a cam that corresponds to the mode operation after loading. portion 54c, the cam portion 34 corresponding to the loading or unloading process;
f. There is a cam portion 34# corresponding to the mode operation after unloading, and the overall shape is an arc. These are arranged concentrically on the chassis in the order of the entry side drive member 33, the exit side drive member 31, and the cam 34 from the top.

FIG. 6 sequentially shows the operating states of the entry guide pace 26 from the unloading state (.1 to the loading completion state II (1 l).
catcher 28, guide members 78, 79 involved in the operation of
, each cam portion 28 which is a posture control member of the guide base 26.
This is a perspective view of the bent upper surface 331 (see FIG. 4) of the drive member on the inlet side. In addition, the height relationship of each part when fully assembled is as follows:
corresponds to the upper cylindrical part 17a of the entrance guide roller,
Further, the cam portion 79k of the guide member 79 and the cam portion 28j of the catcher 28 correspond to the entrance guide base 26,
In addition, the lower protrusion 26b of the entry guide base (27) is the cam part 78g of the guide member 78, the U groove 28b of the lower part of the catcher 26, the cam part 28k, and the recess 33f (fourth (see figure) is supported. FIG. 8 shows the upper stage of the cam 34 and the drive system, (at shows unloading, (h) shows loading or in the middle of unloading, and (C) 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 54m.
As the cam 34 rotates, the gear 36 that meshes with the gear portion 346 rotates, and the output side drive member 31 engages with the gear 57.5.
The gear 39 rotates integrally with the gear 38 via the gear 8 and a compression spring (not shown), and is driven by meshing with the gear portion 316. Similarly, the entry side drive member 33 has a gear 40.
．． A gear 77 shown in FIG. 16, which inserts a crimping spring (not shown) through the gear 41, is driven by meshing with the gear portion 3i. When the loading is completed (, 1), the gear 360 rotation is stopped by the geneva gear, which will be described later, and the engagement between the ear 56 and the gear part 54 is released.
4 is engaged with the arm 42, and the arm 42 is connected to the shaft 43.
The arm 44 is rotated around a shaft 45. The arm 44 is engaged with the arm 480 and the shaft 49 by the arm 46 via the shaft 47, so that the pinch roller 8, which is pivotally supported by the arm 48, is moved in the loading position housing. Since the arm 48 is biased in the direction of arrow A by the spring, when the cam 54 and the arm 42 want to engage (.), the vinyl roller 8 is retracted to the unloading position. The cam 34 rotates further than the state in (b) (,
1, the arm 42 engages with the cam portion 54tL, and the toggle mechanism VC formed by the arms 44 and 46 presses the pinch roller 8 against the capstan 7. The shaft 45 is mounted on an arm 51 supported by a shaft 52, and the arm 51
Since the arm 42 is constantly pulled by the spring 53 and its position is regulated by the stopper 54, even after the movement of the vinyl roller 8 has stopped, the arm 42 rotates and the arm 51 moves away from the stopper 54 against the spring 53. ,
The pressure force between the Vinci roller and capstan is ensured.

7 to 9 show the lower stage of the cam 34 and the mode operation mechanism, FIG. 7 shows unloading, FIG. 8 shows the loading case or during unloading, and FIG. 9 shows the loading state. This is a Zenepa gear part that is provided integrally with the gear 36. The arm 55 has one end connected to the cam portion 5.
Spring 57 engaged with 4c or 341 and attached to one end
is biased counterclockwise around the shaft 56. 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 54a or 64- and has a spring 6 attached to one end.
1 in a clockwise direction around the shaft 62. Also, can the arm 65 engage with the shaft 60a on the arm 60? ! arm 6
It has a length of 5 m, and a spring 65 is attached to one end to bias it counterclockwise around a 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. Figure 7 shows the stopped state after unloading, and the arm 55 is engaged with the recessed portion of the cam portion 34-, 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 55
It is stable regardless of the stroke of 4e. 1 arm 60
engages with the convex portion of the cam portion 34-, and releases the engagement between the shaft 60g and the arm 651K 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- is It is stable regardless of the stroke, and the 8th
In the state shown, the arms 55 and 60 are engaged with the cam portion 54f, and only the brake 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 shown in FIG. 9 shows the recording and reproducing state, and a brake force is applied to the supply reel stand 59, but the arm 60 engages with the recess of the cam portion 54e and rotates due to the tensile force of the spring 61. 6oα engages arm 63α, rotates arm 63 against spring 65, and releases the braking force on drive disk 66.

At this time, the rotation of the gear 360 is stopped by the engagement between the Geneva gear portion 36m and the stopper surface 34A. ! The A moving members 31 and 33 stop, and the pressing force of each tape guide group to the positioning member is maintained.

In this way, by transmitting the movement of the cam 34 to the drive member via a switching mechanism such as a geneva gear, it is possible to easily cope with an increase in the number of operation modes. FIG. 10 shows the movements of the three drive members 31 and 33 and the cam 34 described above, in which (A) is when ejecting, (E) is when loading is completed, and (F) is when the mode is in the recording case or playback mode. During operation. The shape of each member is simplified and shown as an arc. As shown in FIG. 8, in response to the movement of the cam 34, the inlet drive member 53 rotates in the opposite direction 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 integrated structure that positions the tape guide groups on the entrance and exit sides of the tape guide drum 2. The tape guide group on the entrance side is positioned by the shaft part F W 28g on the upper part of the guide roller 17 shown in FIG. to prevent it from falling over. 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 28a. The inclination of the slanted bin 18 is determined by which side of the guide base 27 comes into contact with the wall 28d. The same applies to the tape guide group on the exit side, the position and angle of the guide roller 19 are determined by the R groove 28 and the U groove 28, and the height is determined by the stopper surface 28F. The inclination of the housing inclined pin 20 is regulated by the wall 28A. Furthermore, the r groove 2 of the catcher 28
A notch 28i is provided between 8# and the U groove 28f. In the unloading state shown in FIG. 2 (bl), one end of the cam 34 and one end of the exit drive member pass through the notch 28i, but due to the loading operation, these members escape from the notch 28i. Therefore, when the loading operation is completed, the guide roller 19 and the inclined bin 20 can be held at predetermined positions.

FIG. 12 is a perspective view showing the guide member 68 of the tape guide group and how the guide base 27 on the exit side is supported by the guide member 68. The guide member 68 has a Z-shaped cross section, and the claw portions 27a and 27b of the guide base 27 engage with the Z-shaped portion to restrict the movement path of the guide base 27. This will be explained in detail later. As shown in FIG. 1, the movement path of the guide base 26 on the entry side is such that the lower part of the guide roller 17 and the wall 78g of the guide member 7B are moved, and the end face 261 of the guide base 26 and the guide member 79 are This is regulated by engagement with the wall 79g.

FIG. 13 shows a mechanism for moving the inclined bin 21 placed on the outlet side. Figure 13 (6) is a state corresponding to the unloading state shown in Figure 8g9 (.1).The ear 69, which is rotatably supported coaxially with the arm 48, is The right end 48 of the arm 48 is biased by the spring 70 hooked on the bent portion 69k and the left end 48m of the arm 48.
h and the bent portion 69a of the gear 69 are in contact with each other.

When the mode shifts from this state to the state shown in FIG. 13(b), which corresponds to FIG.
The arm 7 has a gear portion 72α that meshes with the gear portion 696 of
2 rotates, and the inclined pin 2 is implanted at the tip of the arm 72.
1 is positioned at a predetermined position using the character 73.

After positioning, the arm 48 further rotates to move to the first position.
As shown in FIG. 3 (Al), the arm 48 moves away from the bent portion 690 of the gear 69 against the spring 70, thereby ensuring the pressing force of the inclined pin 21 against the catcher 73. By driving the tilting pin 21, the tilting pin 21 is loaded from behind the guide pace 27.In other words, since the movement loci of the tilting pin 21 and the guide base 27 partially overlap, the guide pace 27 is in the lead. The position of the arm 42 and the reduction ratio of the arm 72 drive system are set so that the cam 34 and the arm 42 engage with each other and drive the tilting bin 21 when the cam 54 passes through the overlap area. Since the movement of the arm 72 is controlled by the movement, there is no interference at the overlapping portion.Next, details of the engagement state and structure of the guide base 27 and the guide member 68 shown in FIG. 12 described above will be described. .

FIG. 15 shows a cross-sectional view of a conventionally used guide member 90 having a T-shaped cross section and a guide base 27 in an engaged state. In accordance with this, FIG. 16 shows a guide member 68 having a double-shaped cross section and a guide base 27 according to the present invention.
FIG. In FIG. 15, 90m, 90k, and 90c indicate position regulating parts of the guide member 90 with respect to the guide pace 27. The position is regulated by 90g in the vertical direction, and by 2 points 90&, 90e in the horizontal direction. 1. Direction of position regulating force at the time of octopus! ，
, FB, FC. In FIG. 15, the urging direction of the guide base 27 is indicated by arrow A in the figure. Indicated by B. The position regulating portion 90k between the guide member 90 and the guide base 27 is determined by the direction A or B indicated by the arrow in the figure. 90e is 90k',
90c', there is a backlash in the left and right direction, and the positioning in the rotational moment direction is difficult due to the guide member 9.
It changes depending on the clearance between 0 and guide pace 27. Separately, in the case of the embodiment according to the present invention shown in FIG. 16, by biasing the guide base 27 as shown by arrow C, the vertical direction is 68 k and the horizontal direction is 68 k in the figure.
Since the position regulating part in the left and right direction is determined by 68- and the cutting surface 68e, there is no play in the left and right direction, and the position in the rotational moment direction is also determined. Furthermore, in pursuit of miniaturization of the mechanism, it is necessary to place the aforementioned tape guide drum 2 and guide base 27 as close as possible. 1st
In the case of the guide member 90 having a T-shaped cross section as shown in FIG. As shown in FIG. 16, the amount by which the claw portion 27h of the guide base protrudes toward the tape guide drum 2 side can be reduced. For this reason, generally, the guide members 68 and 90 are brought closer to the guide base 27 side when the guide members 68 and 90 are installed upward from the chassis 1 side. In other words, the guide base 27 can be positioned close to the tape guide drum 2, which is advantageous for downsizing the mechanism. Figure 17. Figure 18 is the same as Figure 15 in the explanation. This figure shows a wobbling state of the guide base 27 when an urging force is not applied to the guide base 27 in the anchored state of the guide pace 27 shown in FIG. 16. FIG. 17 shows a conventional structure having a T-shaped cross-section, and FIG. 18 shows an embodiment according to the present invention having a Z-shaped cross-section. @ in the diagram indicates guide pace 27
This is the angle of the wobbling range. If the clearance of parts is designed so that the total wobbling angle of the guide member is almost the same for the T-shaped cross-sectional shape and the double-shaped cross-sectional shape, the conventional cross-sectional shape shown in Fig. 17 becomes T-shaped. In the case of a letter-shaped cross-sectional shape, wobbling occurs below the reference position, whereas the cross-sectional shape according to the present invention shown in FIG.

With the Z-shaped one, there is no wobbling downward, only upward wobbling. Miniaturization of mechanism. In pursuit of thinning, each part of the mechanism has a laminated structure, and in particular, the driving member of the guide pace 27 is arranged on the lower side of the guide base 27, making the clearance extremely tight. In this case as well, the cross-sectional shape of the guide member 68 is made into a two-character shape as in the present invention.
By eliminating most of the downward wobbling of the guide base 27, it is possible to make the mechanism thinner.

〔Effect of the invention〕

According to the present invention, it is ideal for stable tape rotation because it is difficult to shape the guide member in the past. jIt is possible to realize a device that cannot take a movement guide route at a low cost, and the mechanism can be made smaller. Simplification can be further promoted.

[Brief explanation of drawings]

Figure 1 is a plan view showing the entire mechanism of the recording/reproducing device.
Figure 2 is a side sectional view showing the exit guide pace part, Figure 3.4
．． FIG. 5 is a perspective view showing the driving member, FIG. 6 is a plan view showing the movement of the guide base (27) during the loading operation,
Figure 7.8.9 is a plan view showing the mode operation mechanism, gg1
1 is a perspective view showing the catcher, FIG. 12 is a perspective view showing the guide mechanism of the exit guide base, FIG. 13 is a plan view of the tape pull-out mechanism, and FIG. 14 is a perspective view showing the drive member holding mechanism. Fig. 15 is a sectional view showing a conventional guide base guide mechanism, Fig. 16 is a sectional view showing a guide base (27) guide mechanism according to the present invention, and Fig. 17 is a sectional view showing the wobbling state of Fig. 15. , FIG. 18 is a sectional view showing the loose state of FIG. 16.

Claims (1)

[Claims] 1. A tape guide drum (2) equipped with a rotary head for recording or reproducing information on the tape (6), and a tape guide drum (2) for pulling out the tape (6) from the cassette (3). (2) a guide base (27) on which a group of tape guides for winding and forming a predetermined tape running path is placed, and which moves freely back and forth between a loading position and an unloading position; , a magnetic recording and reproducing device comprising: a driving member (31) that is connected to and moves the guide base (27); and a guide member (68) that guides the movement path when the guide base (27) moves. , the cross-sectional shape of the engaging portion of the guide member with the guide base (27) is approximately Z-shaped, and the position of the guide base is restricted in the vertical direction with respect to the moving direction of the guide base at the tape loading reference height position. a first guide surface (68(a)), a second guide surface (68(b)) that regulates the position in the left-right direction, and a second guide surface (68 (b)) that faces the second guide surface and regulates the position in the left-right direction. 3. A tape loading mechanism for a magnetic recording/reproducing device, comprising: a guide surface (68(c)).