JP2555147B2 - Tape loading mechanism - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention relates to, for example, a video tape recorder (hereinafter referred to as VTR).
The present invention relates to a device for recording or reproducing information by winding a tape at a predetermined angle (hereinafter referred to as loading) on a tape guide drum, and particularly to a tape loading mechanism suitable for cost reduction and size reduction.

[Conventional technology]

As an example of the structure of a conventional loading mechanism, see Japanese Patent Laid-Open No.
There is a structure described in No. 232750.

[Problems to be solved by the invention]

In the loading mechanism, downsizing of the mechanism of the entrance side driving member has been a problem.

An object of the present invention is to solve this problem, and to provide a mechanism for further miniaturization and cost reduction.

[Means for solving problems]

The above object is achieved by the following configurations. That is, a drum equipped with a rotary head that records and / or reproduces information on a tape, a tape guide group that winds the tape around the drum and forms a predetermined tape running path, and a tape guide group A guide base that is arranged, an attitude control member that is arranged along a movement path of the guide base and that engages with the guide base to control the attitude of the guide base during movement, and engages with the guide base. A driving member for driving, a positioning member for crimping and positioning the guide base when the tape guide group forms the predetermined tape traveling path, and a spring member, and using the spring member, A tape loader having a pressure-bonding force generating means for generating a pressure-bonding force for pressure-bonding the guide base to the positioning member; In the mechanism, the drive member includes a curved portion having a flat plate shape and a curved shape and having a gear portion, and an engaging portion formed integrally with the curved portion in a stepwise manner. And a slotted portion and a shaft portion that engage with each other are formed separately in the guide base and the engaging portion of the drive member, and the guide base and the drive member are rotatably engaged with each other. Wherein the crimping force generating means is connected to the gear portion of the curvature portion of the driving member to transmit the crimping force, and the spring member of the crimping force generating means has a curvature shape of the driving member. In the plane parallel to the flat plate-shaped surface of the section, the curved sections of the drive member are arranged so as not to overlap with each other and to be displaced from each other.

Further, the crimping force generating means is arranged at a height substantially equal to the curvature-shaped portion of the drive member in a height direction orthogonal to the flat plate surface of the curvature-shaped portion of the drive member.

[Action]

By forming the stepped engagement portion on the drive member and rotatably engaging the guide base, interference with other components during the loading operation can be avoided with a simple configuration.

Further, since the engaging portion is formed integrally and continuously with the curved portion of the driving member, the engaging portion is a component separate from the driving member, and the engaging portion is a component separate from the driving member. A step for integrating the unit and the driving member is unnecessary.
When the tape loading is completed, a large force is repeatedly applied to the drive member every time the tape is loaded, as a reaction force of the guide base pressure bonding for positioning the tape guide. Here, in the case of the joint portion in which the engaging portion and the driving member as separate parts are integrated, stress is concentrated and fatigue fracture is likely to occur under the large cyclic load as described above. Although there is a problem, the above configuration also eliminates such a problem.

Further, due to the simple structure that one of the engaging means has the shape of an elongated hole, the engaging guide base and the driving member do not restrain each other in the longitudinal direction of the elongated hole-shaped portion. This allows the guide base to be faithfully aligned with the catcher side without being obstructed by the driving member side when the guide base is pressure-bonded to the catcher or the like when the tape loading is completed. Posture and positioning are highly accurate at low cost.

Further, the crimping force generating means is connected to the gear portion of the curvature portion of the drive member to transmit the crimping force,
The structure of the engaging portion of the guide base and the drive member, which is poor in assemblability and tends to increase the cost, is simplified and the assemblability is improved. At this time, at the same time, the crimping force generating means is mounted on the drive member and integrally rotates, so that the crimping force generating means does not envelop and occupy a large space during the rotation. Further, the spring member of the crimping force generating means is arranged so as not to overlap with the curved portion of the driving member in a plane parallel to the flat plate surface of the curving portion of the driving member so as to generate the crimping force. The spring member of the means does not overlap with the curved portion of the drive member to increase the thickness of the tape loading mechanism. Further, in the height direction in which the crimping force generating means is orthogonal to the flat plate surface of the curved portion of the drive member,
The overall thickness of the tape loading mechanism is further reduced due to the arrangement at a height approximately equal to the curvature of the drive member.

[Embodiment] An embodiment of the present invention will be described below with reference to FIGS. 1 to 14.

FIG. 1 is a plan view of a magnetic recording / reproducing apparatus using a tape loading mechanism according to the present invention, wherein 1 is a chassis, 2 is a tape guide drum on which a magnetic head is mounted, and 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 at the lower end, 8 a pinch roller, 10 a fixed width supporter 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 an audio signal and a control signal on the upper and lower ends of the tape 6, respectively. When the cassette 3 is mounted on the apparatus, the lid 12 on the front face of the cassette 3 is opened. 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 at 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 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 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. 2 (a), 26 is a guide base in which the guide roller 17 and the inclined pin 18 are planted, and the catcher 28 positions and holds them, and 27 is also the guide base in which the guide roller 19 and the inclined guide 20 are planted. , Is similarly positioned by the catcher 28. As shown in the figure, the tape guide on the output side of the tape guide drum 2 descends largely by the tape width as compared with the input 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 small and thin.

Next, the loading mechanism will be described in detail. FIG. 3 shows the guide moving member on the delivery side. As shown in FIG. 3, the guide roller 19 and the guide base 27 on which the inclined pins 20 are erected are connected with a connecting plate 29 with a large play.
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 entry side. Guide roller 17 and inclined pin
The guide base 26 on which the 18 is planted is rotatably supported around a shaft 33d that is planted on the entrance-side drive member 33. The entry-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 upper and lower two stages.
a, a cam portion 34d, and a lower surface on which 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 There is a cam portion 34e corresponding to the mode operation, and it has an arc shape as a whole. These are the entry side drive members 3 from the top.
3, 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. The bent upper surfaces 33e (see FIG. 4) of the cams 28j, 28k, 78a, 79b, which are the posture control members of the members 78, 79 and the guide base 26, are transparently shown. In addition, the height relationship of each part at the time of assembly completion is from the top to the V groove on the top of the catcher.
28a corresponds to the upper cylindrical portion 17a of the inlet side guide roller,
The entry-side guide base 26 is the cam portion 79 of the guide member 79.
b and the cam portion 28j of the catcher 28 correspond to each other, and the lower projection 26b of the entry-side guide base corresponds to the cam portion 78a of the guide member 78 and the lower U-groove 28b of the catcher 26, the cam portion 28k, and the entry-side driving member. The concave portion 33f (see FIG. 4) in the upper part of the bent portion of 33 corresponds.

FIG. 6A shows an unloading state.
The entry guide base 26 is rotatably held around a pin 33d planted on the entry drive member 33.
Rotation in the clockwise direction about 3d is restricted by the projection 26b of the entrance-side guide base and the cam portion 79b of the guide member 79 contacting each other. Further, the rotation in the counterclockwise direction described above causes the lower convex portion 26b of the entrance side guide base 26 and the guide member 78.
Is regulated by contact with the cam portion 78a. As described above, the position of the entry-side guide base 26 in the rotation direction is uniquely determined with respect to the degree of freedom in the rotation direction about the pin 33d.

As shown in FIG. 6 (b), the entry side guide base 26
Is the direction of clockwise rotation around the pin 33d,
By contact between the 6b and the concave portion 33f of the entry side drive member,
The counterclockwise direction is the lower convex portion 26b and the cam portion 7 of the guide member 78.
It is regulated by contact with 8a, and its rotation is also uniquely regulated.

Further, in the state of FIG. 6 (c), in the entry side guide base 26, the lower projection 26b and the depression 33f of the entry side drive member are brought into contact with each other in the clockwise direction, and in the counterclockwise direction. The left side surface portion 26e of the entrance side guide base 26 in the figure and the cam portion 28j of the catcher 28 are regulated by contact with each other, and the position in the rotation direction is also regulated uniquely.

FIG. 6 (d) shows that the lower projection 26b is the catcher 2
It shows the state just before going into the U groove on the lower side of 8. Similarly, the counterclockwise direction is regulated by the contact between the lower convex portion 26b and the cam portion 28k of the catcher 28.
The clockwise direction is regulated by the contact of the rear left portion 26c of the entry-side guide base 26 with the cam portion 28j of the catcher 28 below the pin 33d in the drawing. This structure is characterized by this clockwise regulation.
That is, the position in the turning direction can be uniquely regulated by directly contacting only the surface on one side with respect to the traveling direction in front of and behind the turning shaft 33d. The reason for adopting such a method will be described below. That is, when shifting to the loading completed state shown in FIG. 6 (e), the entry side guide base largely rotates counterclockwise about the pin 33d. This time,
In FIG. 6 (d), in the structure in which a member for abutting against the right side portion of the entrance side guide base is provided on the front side in the traveling direction with respect to the pin 33d, when the state of FIG. It interferes with the guide base. In addition, FIG.
When the lower convex portion 26b and the concave portion 33f are restricted by direct contact as shown in (c), the entrance side driving member 33 has a smaller diameter due to the mechanism miniaturization, and its curvature separates from the lower convex portion 26b. There is play in the direction of rotation. Here, in the state shown in (d), the lower protrusion 26b moves toward the position where the loading is completed and the U groove 28b at the lower portion of the catcher.
Must be surely guided to. Therefore, clockwise play cannot be tolerated. Due to the direct contact between 26c and 28j, the operation shifts to the loading completed state reliably and without interference.

Then, as shown in FIG. 6 (e), the head portion 17a of the entrance side guide roller is moved to the entrance side V groove 28a of the catcher 28, and at the same time, the side portion 26a at the right rear part of the entrance side guide base is caught by the catcher 2.
The loading operation is completed with the pressing position determined on the inclined side portion 28d of 8.

 FIG. 7 shows details of the state shown in FIG. 6 (e).

Entry-side driving member 33 is reduced in diameter for mechanisms miniaturization, and an obtuse angle theta ₁ to the direction of pressing and the driving force F _L is the entry side guide roller head 17a to the catcher V groove 28a. Therefore, as it is, the force for pressing the 17a toward the 28a is not generated. Therefore, directly contacting the guide base 26 to the wall 28d at an acute angle theta ₂ with respect to the direction of the F _L. As a result, the guide base 26 receives a reaction force F _C from the wall 28d.
Receive. Wherein F _L to F _C of Toko, component F _LO rotating the guide base 26 around the 17a, F _CD and, component F _Lr towards the center of the 17a, F _CD and, component F towards the center of the 17a
_When divided into _Lr and F _Cr , the rotational force around 17a is F _LO
And F _CD are in balance. When the remaining F _Lr and F _Cr are compared, as shown in the figure, it is set that F _Cr > F _Lr.
It is possible to generate a component that presses a toward 28a. Then, the pin 33d is attached to the guide base 26 of the entrance side by the guide roller 1
Since it engages with the elongated hole 26g provided in the direction 7
It does not interfere with the force that pushes 17a toward 28a. With this component, as shown in the lower part of FIG. 7, it is possible to generate a force for rotating the guide base 26 counterclockwise around the center 17a in the figure, and to uniquely determine the height and posture of the guide base 26. Can be determined.

1) Here, in order to secure a sufficient tape winding angle with respect to the full width erasing head 10 in FIG. 7, the guide base 26 is rotated counterclockwise in FIG. It is effective to position the guide roller 17 on the left side when completed.

2) To reduce the size of the mechanism, a drive member
It is necessary to minimize the diameter of 33.

Both of the above 1) and 2) increase the angle θ ₁ in FIG. 7, but according to this embodiment, the guide roller head 17a can be surely pressed to the catcher V groove 28a.

Here, in the present embodiment, the inclined surface is formed on the catcher side and is brought into contact with the round portion on the guide base side. Conversely, the inclined surface is formed on the guide base side and directly contacts the catcher side. An arc-shaped portion may be provided.

Further, according to this structure, the guide members 78 and 79 do not need to be assembled in a form that meshes with the guide base 28, and each component can be sequentially stacked in one direction from above the mechanism, and the assembly workability is greatly improved. It is possible.

Further, as described with reference to FIG. 6 (d), when the guide base is largely rotated and loading is completed,
The predetermined loading operation can be surely completed without using the guide base and interfering with the guide member or the like.

Further, according to this structure, the tape wrap angle around the full width erasing head can be sufficiently secured and the full width erasing head can be fixed under the small and compact structure conditions as described above. The rigidity of the mechanical system that holds the tape is improved, and it is less likely to be affected by vibration and the like, so that the stability of the tape running performance can be improved. Further, because of the fixed structure of the full width erasing head, the number of parts for supporting the head can be reduced and the assembling accuracy can be easily obtained. For this reason, the tolerance of the component accuracy of each component can be relaxed, and the processing and assembly time can be shortened. Therefore, significant cost reduction can be realized.

8A and 8B show the upper stage of the cam 34 and the drive system. FIG. 8A shows the state of unloading, FIG. 8B shows the state of loading or unloading, and FIG. 8C shows the state of loading. 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 meshing with the gear portion 34a rotates, and the output side driving member 31 rotates integrally with the gear 38 via the gears 37 and 38 via a crimping spring (not shown). The gear 39 is driven by meshing 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. 14 that incorporates a 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 shown in FIG.
The tip of the arm 34 and the arm 42 are engaged, and the arm 42 rotates around the shaft 43 and the arm 44 around 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 arm 44 moves the pinch roller 8 supported by the arm 48 to the loading position. Since the arm 48 is urged in the direction of arrow A by a spring, the cam 34 and the arm 42
Are not engaged (a), 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 pinch roller 8 is moved to the capstan 7 by the toggle mechanism formed by the arms 44 and 46. Crimp.
The shaft 45 is erected on an arm 51 supported by the shaft 52,
Is constantly 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 is rotated and the arm 51 moves away from the stopper 54 against the spring 53. , The pressure force between the pinch roller and capstan is secured.

FIG. 9 shows the lower stage of the cam 34 and the mode operating mechanism,
(A) shows the state of unloading, (b) shows the state of loading or unloading, and (c) shows the state of loading. 36a is a Geneva gear portion provided integrally with the gear 36. One end of the arm 55 is engaged with the cam portion 34c or 34e, and is biased counterclockwise around the shaft 56 by the spring 57 attached to one end. A brake member 58 is attached to the other end of the arm 55, and applies a braking force to the supply reel base 59. The arm 60 is engaged with the cam portion 34c or 34e, and is urged clockwise around a shaft 62 by a spring 61 attached to one end. Further, the arm 63 is an arm 6 that can be engaged with the shaft 60a on the arm 60.
A spring 65 is attached to one end and biased around the shaft 62 in a counterclockwise direction. Further, a brake member 64 is mounted on the other end, and applies a braking force to the drive disk 66 engaged with the take-up reel 5. (A) shows a stopped state after unloading, in which the arm 55 is engaged with the concave portion of the cam portion 34e and a braking force is applied to the supply reel table 59. At this time, since the concave portion and the arm 55 are not directly engaged with each other, the braking force is determined only by the force of the spring 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. It is stably secured regardless of the stroke of 34e, and in the state of (b), the arms 55 and 60 are engaged with the cam portion 34f, and only the braking force to the supply reel base 59 is released. Therefore, at the time of loading, the tape 6 is basically delivered from the supply reel side. The state of (c) is recorded.
The state of reproduction is shown, and the 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 61
The shaft 60a engages with the arm 63a and is rotated by the pulling force of the arm 63a.
Is rotated against the spring 65 to release the braking force on the drive disc 66. At this time, the engagement of the Geneva gear portion 36a and the stopper surface 34b stops the rotation of the gear 36, stops the driving members 31 and 33, and holds the pressure force of each tape guide group to the positioning member. 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 three driving members 31 and 33 and the cam 34 described above.
(A) is for ejection, (e) is for loading completion, and (f) is for mode operation such as recording or reproduction. Each member is shown in an arc shape in a simplified form. As shown in FIG. 8, the incoming drive member 33 rotates at substantially the same speed in the opposite direction to the movement of the cam 34, and the outgoing drive member 31 rotates at almost twice the speed in the same direction.

FIG. 11 is a perspective view of the catcher 28. The tape guide drum 2 has an integral structure for positioning the tape guide groups on the entrance side and the exit side. Regarding the tape guide group on the entrance side, the shaft above the guide roller 17 shown in FIG.
Positioning is performed by the groove 28a, and the lower part is regulated by the U groove 28b to prevent the guide roller 17 from falling in a direction perpendicular to the approach 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 being in 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 V groove 28e and the U groove 28f, and the height is determined by the stopper surface 28g. Also tilt pin 20
Is regulated by the wall 28h. Further, a notch 28i is provided between the V groove 28e and the U groove 28f of the catcher 28.
In the unloading state shown in FIG.
One end of the cam 34 and one end of the output side driving member
However, these members escape from the notches 28i by the loading operation, so that the guide roller 19 and the inclined pin 20 can be held at predetermined positions in the loading operation completed state.

FIG. 12 is a perspective view showing a guide member 68 of the tape guide group and a method of supporting the guide base 27 on the output side by the guide member 68. The guide member 68 has a T-shaped cross section, and the claw portions 27a and 27b of the guide base 27 engage so as to hold the T-shaped portion, thereby restricting the movement path of the guide base 27.
As shown in FIG. 1, the moving path of the guide base 26 on the entrance side is the wall of the guide member 78 and the shaft portion under the guide roller 17.
78a, 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 moving away from 69c, the pressing force of the inclined pin 21 to the catcher 73 is ensured. By driving the inclined pin 21 at the above timing, the inclined pin 21 is loaded from behind 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. Accordingly, since the movement of the arm 72 is controlled by the movement of the cam 34, there is no interference at the overlapping portion.

As described above, the loading mechanism and the mode operation in this apparatus are performed centering on the entrance side drive member 33, the exit side drive member 31, and the cam 34. FIG. 14 is a perspective view showing an assembling structure of the above-mentioned three arc-shaped members. Cam 34
The guide pins 74a to 74e implanted in the chassis 1 engage with the grooves 34g formed on the entire lower periphery of the cam 34, so that the chassis 1 is rotatably guided on the chassis 1. Guide pins 74a to 74e are
In the rotation range of the cam 34 shown in FIG. 11, three or more are always arranged so as to engage with the groove 34g of the cam 34. The delivery side drive member 31 is rotatably sandwiched between the cams 34 by the guide pins 76a and 76b, and the guide pins 76a and 76b and the delivery side drive member elongated holes 31b and 31c are set in the lower portion of the delivery side drive member 31. By engaging the pin 30 and the elongated hole portion 34h of the cam 34, the pin 30 can be rotated concentrically with the cam 34. The entrance side drive member 33 has a small rotation angle as shown in FIG. 10, and gears 75 and 77 are held on the outer periphery by constantly meshing with the entrance side drive member gear portion 33a. The delivery drive member 31 and the cam 34
As shown in the figure, it rotates in the same direction at an angle of about 180 degrees or more. Therefore, as shown in FIG. 1, by replacing the substrate that holds the rotation of the output side driving member 31 with the cam 34, a slot formed in the output side driving member 31 is formed.
The angles of 31b and 31c can be calculated as the relative rotation angle difference between the output side driving member 31 and the cam 34. That is, 180
In the case of holding a ring that rotates more than 180 degrees on the substrate, the angle of the long hole can be reduced according to the present embodiment, as compared with the case where the long hole of the ring requires 180 degrees or more. , Problems such as strength can be minimized. Guide members 78, 79, 81 are screws 88, 89, 80, 82, respectively.
As a result, the cam 34 is screwed on the chassis 1 to suppress the vertical play of the cam 34. The holder 83 is interposed between the entrance drive member 33 and the exit drive member 31, and the integrally formed boss 83a engages with the long groove 33b of the entrance drive member 33 to engage the entrance drive member 33.
And is screwed to the chassis 1 with screws 84. The holder 85 is screwed to the chassis 1 with a screw 86 to suppress the play of the entry side driving member 33 in the vertical direction.

The entrance drive member 33 having a small rotation angle is always guided by the boss 83a of the holder 83, and rotates on the holder 83. In the section such as (b) and (c) of FIG. 10, the holder 83 may not be engaged with the end 31 d of the outlet drive member 31 in the outlet drive member 31. Out-loading drive member after unloading
When the end portion 31d of 31 and the holder 83 are engaged with each other, even if the end portion 31d is slightly bent or warped, the holder 83 has a tapered surface 83b that engages with each other, so that the end portion 31d is reliably projected. Side drive member 3
1 can be guided below the holder 83. The end portions 31d and 31e of the output drive member 31 engaged with the holder 83 are larger than the diameter of the gear portion 31a, and the input and output drive members having the same diameter.
The gear portions 33a, 31a of the gears 33, 31 are prevented from engaging with the tapered surface 83b of the holder 83, and the distance between the drive members 33, 31 on the inlet side and the outlet side is minimized to miniaturize the device. When the loading is completed, as shown in FIG.
It engages with the end portion 31e of the delivery side drive member 31, and prevents the delivery side drive member 31 from floating by receiving a reaction force when the guide base 27 presses the catcher 28. With the above-described configuration, even when the entrance side and the exit side drive members 33 and 31 intersect in a plane, the ends 33c and 31d are reliably separated from each other, and no interference occurs.

〔The invention's effect〕

According to the present invention, the stepped engagement portion is formed on the drive member, and the guide base is rotatably engaged with the drive member, so that interference with other components during the loading operation can be avoided with a simple configuration. Therefore, it is possible to obtain the effect of size reduction as well as cost reduction.

Further, since the engaging portion is formed integrally and continuously with the curved portion of the driving member, the engaging portion is a component separate from the driving member, and the engaging portion is a component separate from the driving member. The process for integrating the drive unit and the drive unit is not necessary, and it is possible to endure repeated loads each time the tape is loaded, and the cost is reduced and the reliability is improved. Further, due to the simple structure that one of the engaging means is in the shape of an elongated hole, the engaging guide base and the driving member do not restrain each other in the longitudinal direction of the elongated hole portion, and the performance is improved at low cost. The effect of is obtained.

Further, the crimping force generating means is connected to the gear portion of the curvature portion of the drive member to transmit the crimping force,
The structure of the engaging portion between the guide base and the drive member, which is poor in assemblability and is likely to cause a cost increase, is simplified, the assemblability is improved, and the cost is reduced. At this time, at the same time, the crimping force generating means is not mounted on the driving member and integrally rotated so that the crimping force generating means does not envelop and occupy a large space, and the spring member of the crimping force generating means is driven by the driving member. The thinning effect can also be obtained by the configuration in which the curved portions are arranged so as not to overlap each other and to be displaced from each other.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a plan view showing the entire mechanism of a 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, FIG. 7 is a plan view showing the action of the pressing force, and FIG. 8 shows the pinch roller pressing mechanism. FIG. 9 is a plan view showing a mode operation mechanism, FIG. 10 is a plan view showing a phase relationship of a driving member, FIG. 11 is a perspective view showing a catcher, and FIG. 12 is a guide mechanism of a delivery guide base. 13 is a plan view of a tape pull-out mechanism, and FIG. 14 is a perspective view showing a holding mechanism of a driving member. 1 …… Chassis 2 …… Tape guide guide 10 …… Full width erasing head, 17 …… Tape guide 26 …… Inlet side guide base, 28 …… Catcher

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yoshiyuki Tanaka 1410 Inada, Katsuta City, Ibaraki Prefecture Incorporated company Tokai Plant, Hitachi, Ltd. Co., Ltd. (56) References: 61-105938 (JP, U) JP 59-48461 (JP, B2)

Claims (2)

(57) [Claims] 1. A drum having a rotary head for recording and / or reproducing information on and from the tape, a tape guide group for winding the tape around the drum and forming a predetermined tape running path, and the tape. A guide base in which a guide group is arranged; an attitude control member arranged along a movement path of the guide base to control the attitude of the guide base during movement by engaging with the guide base; A driving member that engages and drives, a positioning member for pressing and positioning the guide base when the tape guide group forms the predetermined tape running path, and a spring member. A tape loader that uses a pressure-bonding force generating unit that generates a pressure-bonding force for pressure-bonding the guide base to the positioning member using the tape loader. In the driving mechanism, the driving member has a curved portion having a flat plate shape and a curved shape and having a gear portion, and an engaging portion formed integrally with the curved portion in a stepwise manner. An elongated hole-shaped portion and a shaft-shaped portion that engage with each other are formed separately in the guide base and the engagement portion of the drive member, and the guide base and the drive member are rotatably engaged with each other. Wherein the crimping force generating means is connected to the gear portion of the curvature portion of the driving member to transmit the crimping force, and the spring member of the crimping force generating means has a curvature of the driving member. A tape loading mechanism, wherein the curved portion of the drive member is arranged in a plane parallel to the flat plate-like surface of the drive member so as not to overlap with each other and offset from each other. 2. The pressing force generating means is arranged at a height substantially equal to that of the curved portion of the drive member in a height direction orthogonal to the flat plate surface of the curved portion of the drive member. The tape loading mechanism according to claim 1, which is characterized in that.