JPH0766595B2 - Mechanism operation mechanism of magnetic recording / reproducing device - Google Patents

Description

The present invention relates to a mechanism structure in a magnetic recording / reproducing apparatus, and more particularly to a mechanism operating mechanism suitable for achieving a small size and light weight and high reliability.

[Conventional technology]

The reproducing function of the magnetic recording / reproducing apparatus is extremely diversified, and it is necessary to provide the operation modes of the mechanism according to them, and the number of operation modes increases. Further, the operation of the mechanism mode is generally not a drive by a plunger but an operation by a cam from the viewpoint of reduction in power consumption, weight reduction, cost reduction, and the like. In other words, by connecting the arms from the cam, the required operation in each part is obtained. An example of such a device is described in Japanese Patent Application Laid-Open No. 57-88558. In this case, in most cases, the tape loading mechanism is driven in addition to the braking of each reel stand, the pressing / releasing of the pinch roller, the position control of the tension arm, and the like.

These conventional systems employ a link mechanism with a plurality of arms because the positions of the cam and the member to be operated are distant from each other, and due to the small diameter of the cam, a variety of operating states can be obtained from the cam shape with little change amount. This is due to reasons such as what must be done.

[Problems to be solved by the invention]

However, the link mechanism generally has a low operation accuracy, and it is difficult to perform phase matching, and the number of parts increases. Also, when the driving force is transmitted to the above-mentioned cam mechanism and the like, the motor and the cam, which are the driving source, are often separated from each other due to the restrictions on the arrangement of the entire apparatus, and a rubber belt is used for transmitting the driving force. In addition, in a mechanism for driving a reel base as a tape drive mechanism, when a driving force is obtained from a capstan motor, it is possible that tape running performance is deteriorated due to torque unevenness due to gear drive. In order to avoid it, the driving force is transmitted by the rubber belt.However, the transmission by the belt has a problem that the loss of the lateral pressure of the bearing due to the belt tension and the change of the transmission rate due to the environmental change are large and the reliability of the device is deteriorated. Atsuta

The object of the present invention is to solve the above-mentioned problems of the prior art,
(EN) Provided is a mechanism operation mechanism of a magnetic recording / reproducing apparatus, which achieves a small size and a light weight by a simple mechanism, and further ensures a high reliability by surely transmitting a driving force. .

[Means for solving problems]

In order to achieve the above-mentioned object, the present invention comprises a ring having a gear portion and a cam portion for transmitting a rotational driving force to at least a part of a peripheral surface, and performs a rotary operation according to various modes such as recording and reproducing. And a first drive source for driving the capstan, a second drive source for driving the reel base, and a gear train, and are interlocked with the rotation operation of the mode operating mechanism. A first drive force transmission mechanism section for transmitting the drive force of the first drive source; a second drive force transmission mechanism section for transmitting the drive force of the second drive source; Of the idler mechanism section and the cam section of the mode operation mechanism section accompanying the rotation of the mode operation mechanism section, and operates the idler mechanism section of the first and second drive force transmission mechanism sections. It has a switching mechanism part for switching connection to either one,
The idler mechanism unit transmits the drive force to the take-up reel base or the supply reel base according to the direction of the drive force transmitted by the connected first or second drive force transmission mechanism unit. Constitute.

[Action]

As the mode operation mechanism unit rotates, the switching mechanism unit operates according to the cam unit, and connects the idler mechanism unit to either the first or second driving force transmission mechanism unit. Therefore, the driving force from the first driving source for driving the capstan or the driving force of the second driving source for driving the reel base is transmitted to the idler mechanism section. The idler mechanism transmits the driving force to the supply reel base or the take-up reel base.

In this way, the idler mechanism switches the driving force from the first and second driving sources and the transmission of the driving force to the supply reel base and the take-up reel base.

Here, since the first and second driving force transmission mechanism units are gear trains and the idler mechanism unit is also a gear train, switching and transmission of the driving forces are appropriately performed.

〔Example〕

 Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is an overall plan view showing an embodiment of a mechanism operating mechanism of a magnetic recording / reproducing apparatus according to the present invention.

The figure shows the magnetic tape cartridge indicated by the one-dot chain line in the figure.
It shows the unloading stop condition with 77 still attached. Inside the magnetic tape cartridge 77, a take-up reel 5 around which the magnetic tape 3 is wound and a supply reel 6 are housed, and a reel stand (not shown) rotatably supported on the shiyashi 1 respectively. No.) is mounted and engaged.

Further, on the palm 1, a cylindrical rotating cylinder 2 having a plurality of magnetic heads (not shown) mounted thereon, a loading ring 10, a capstan 14, a tension pin 16-a, a correction guide pin 82-a, a pinch roller. 15, guide roller 7,
8, 9, 11, loading mode motor 27, etc. are arranged as shown.

In this unloading stop state, when the loading ring 10 rotates in the direction of the arrow A ₁₀ , the guide rollers 7, 8, 9 and the guide roller 11 engaged with the tips of the guide arms 12 move, and these move the magnetic tape 3 Of the magnetic tape cartridge 77 is pulled out and wound around the rotary cylinder 2 in a spiral shape at a predetermined angle. As a result, the running path of the magnetic tape 3 as shown in FIG. 2 is formed. The device is operated while this traveling path is maintained.

The mechanism and operation of each part shown in FIGS. 1 and 2 will be described in detail below step by step.

FIG. 3 is a development view showing the mounting relationship between the rings and the shiyashi 1 that perform the main operation of this embodiment.

In the figure, there are three types of rings, a drive ring 32, a cam ring 38, and a loading ring 10. The cam ring 38 is at the closest height to the coconut 1, the drive ring 32 is above it, and is parallel to the upper surface of the coconut 1. The loading ring 10 is mounted above the drive ring 32 in an inclined state with respect to the coconut 1.

As for the holding of these rings, with respect to the drive ring 32 and the cam ring 38, ring holders 33-a, 33-b, 34 of a two-stage structure rotatably supported on the side of the palm 1 are provided. −
a, 34-b, 35-a, 35-b are performed on the outer peripheral portions of these rings, and regarding the loading ring 10, the L ring holder 17 shown in FIG. 1 and the L ring holder shown in FIG. It will be held on the inner circumference of the loading ring 10 by 18,19.

These three types of rings are driven by a loading mode motor 27. That is, the ring drive mechanism for this is a reduction gear train that transmits the driving force of the loading mode motor 27 (hereinafter referred to as LM motor) LM motor 27 to the drive ring 32.

A transmission gear train that transmits the rotation of the drive ring 32 to the loading ring 10.

A transmission gear train that transmits the rotation of the drive ring 32 to the cam ring 38.

It is composed by. In addition, a switching mechanism using a Geneva gear is mounted in, and has a structure that cuts off the transmission of the driving force when the rotational force of the driving ring 32 is unnecessary.

Each ring 32, 38, 10 is rotated by the ring drive mechanism, and the loading ring 10 performs a loading operation of winding the magnetic tape 3 on the rotary cylinder 2 by a cam ring.
Reference numeral 38 denotes a concave / convex surface (cam surface) provided on the inner circumference, and performs a mode shifting operation for operating a mechanical element such as a brake.

In order to perform this loading operation, guide bases 29, 30 having guide rollers 7, 8, 9 mounted thereon are placed on the loading ring 10.

Further, in order to detect the rotation angle of the cam ring 38 in the mode transition operation, the cam ring 38 has two kinds of conductive patterns 38-b and 38-c (the pattern 38-b is continuous and the pattern 38c is intermittent). A brush 32-b is printed along the line 38 in a concentric arc shape, and a brush 32-b for short-circuiting these patterns 38-b and 38-c is attached to the lower surface of the drive ring 32. The pattern 38-b is connected to the ground side of the system control circuit (not shown), and the pattern 38-c is connected to the mode detection terminal side of this circuit.

Here, as will be described later, the rotation directions of the drive ring 32 and the cam ring 38 are opposite to each other, so that the relative angular relationship between the drive ring 32 and the cam ring 38 changes, so that the brush 32- The positional relationship between b and the patterns 38-b, 38-c is changed so that the different part of the pattern 38-c is short-circuited to the ground, and the system control circuit detects the angular relationship between the two rings 32, 38, which is desired. The transition position in the mode is detected.

The above ring drive mechanism, loading mechanism, and mode operation mechanism will be described in detail below.

FIG. 4 is a perspective view showing a reduction mechanism for transmitting the driving force of the LM motor 27 to the drive ring 32.

In the figure, an LM motor gear 50 is press-fitted to the end of the rotary shaft of the LM motor 27 that is screwed and fixed to the side wall of the LM motor holder 47. In addition, the LM motor gear 50 has a transmission gear.
The worm 40, which is rotatably held by the LM motor holder 47, is press-fitted to the other part of the rotary shaft 53 in which the transmission gear 39 is press-fitted. Furthermore, LM
The shafts 42, 44, 46, 51, 52 are press-fitted and fixed to the motor holder 47 from above, and each of these shafts has a reduction gear 41, 3, 45, 45 having a two-stage structure and a single-layer structure. The transmission gears 48 and 49 are rotatably supported by the shafts.

The upper stage 41-a of the reduction gear 41 is a worm wheel which meshes with the worm 40, and the lower stage 41-b and the upper stage of the reduction gear 43 thereof.
43-a, the lower stage 43-b of the reduction gear 43 and the upper stage 45-a of the reduction gear 45 mesh with each other, and the lower stage 45-b of the reduction gear is the drive gear 54 for driving the drive ring 32. Top 54
-It meshes with a. Therefore, it was pressed into the LM motor 27.
When the LM motor gear 50 rotates in the direction of the arrow A ₅₀ , the transmission gear 39M, the ohm 40, and the reduction gears ₄₁ , ₄₃ , ₄₅ which are meshed in sequence also move in the directions of the arrows A ₃₉ , A ₄₀ , A ₄₁ , A ₄₃ , A ₄₅ , respectively. The drive gear 54 rotates and rotates in the direction of arrow A ₅₄ . Conversely, when the LM motor gear 50 rotates in the direction of arrow B ₅₀ , each of the above gears also rotates in the directions of arrows B ₃₉ , B ₄₀ , B ₄₁ , B ₄₃ , B ₄₅ , and the drive gear 54 moves in the direction of arrow B 5 _54. Turn to.

The transmission gears 48, 49 have a role of transmitting the rotation of the switching gear 55 to the loading ring 10 as shown in FIG. 5 and specifically described in FIG. .

FIG. 5 is a plan view showing a power transmission mechanism from the drive ring 32 to the loading ring 10 or the cam ring 38.

In the figure, a gear portion provided on the inner circumference of the drive ring 32
On both sides of 32-a, fan-shaped 2 with a specified thickness
Two lock plates 58, 59 are attached and fixed to the upper surface of the drive ring 32. The radius of curvature of the inner peripheral surfaces of the lock plates 58 and 59 is set to be substantially equal to the radius of curvature of the addendum circle of the gear portion 32-a of the drive ring 32.

Further, as shown by the broken line in FIG. 5, the inner peripheral surface of the mounting portion of the lock plates 58, 59 in the drive ring 32 has a gear portion 32-
It is in a more depressed state than the root circle of a. The end surfaces of the lock plates 58, 59 close to the gear portion 32-a are chamfered as shown in the drawing.
The chamfered portion has the same shape as the tooth surface of the gear portion 32-a. That is, the continuous tooth surface of the gear portion 32-a in the drive ring 32 is set so that its end portion is connected to the end surfaces of the rock plates 58 and 59 obliquely above in the same tooth surface shape.

The lower stage 54-b of the drive gear 54 meshes with the gear portion 32-a of the drive ring 32. As a result, the driving force of the LM motor 27 is transmitted to the drive ring 32.

FIG. 6 is an exploded perspective view showing the structure of the switching gear 55 in FIG.

In the figure, the switching gear 55 is a switching plate 55-b.
Has a three-layer structure in which two gears 55-a and 55-c are sandwiched. The outer peripheral surface of the switching plate 55-b has two cylindrical surfaces, a large diameter portion and a small diameter portion. The large diameter portion is the tip circle of the lower gear 55-c and the small diameter portion is the gear 55-c. The respective radii are set so as to substantially coincide with the root circle of the. The switching plate 55-b and the gears 55-a, 55-c are in a state in which the holes held by the switching plate 55-b and the gears 55-a and 55-c are aligned with each other, and then the pin 62 is pressed into the holes to fix the mutual phase relationship. Kept in. Then, as shown in FIG.
It is rotatably supported by a shaft 60 that is press-fitted into.

FIG. 7 shows this switching gear 55, drive ring 32, and cam ring.
FIG. 38 is a cross-sectional view showing a height relationship with 38.

In the figure, since the switching gear 55 is mounted on the boss portion on the shiyashi 1, it is located above the cam ring 38 and does not contact with it. However, the lowermost gear 55-c of the switching gear 55 meshes with the gear portion 32-a of the drive ring 32.

Further, the middle switching plate 55-b of the switching gear 55 is positioned at a height substantially opposite to the inner surface of the lock plate 58 on the drive ring 32 shown by the broken line in the figure.

The upper gear 55-a of the switching gear 55 meshes with the transmission gear 48 shown in FIGS. 4 and 5.

FIG. 8 is an exploded perspective view showing the structure of the switching gear 56 in FIG.

In the figure, the switching gear 56, like the switching gear 55, also has a three-layer structure of a switching plate 56-a and gears 56-b, 56-c.

However, in this case, the switching plate 56-a is located at the uppermost stage of the switching gear 56.

The phase relationship between these switching plates 56-a, gears 56-b, 56-c is the same as in the case of the switching gear 55, after the holes provided in the respective gears are aligned, the pin 63 is passed through these holes. Then, it is press-fitted and kept fixed.

The outer peripheral portion of the switching plate 56-a includes a large diameter portion and a small diameter portion. The large diameter portion is the tip circle of the middle gear 56-b, and the small diameter portion is the root circle of the gear 56-b. The respective radii are set so that they substantially match.

FIG. 9 shows this switching gear 56, drive ring 32, and cam ring 3.
FIG. 8 is a cross-sectional view showing a height relationship with FIG.

The switching gear 56 is a shaft press-fitted into the boss portion of the shiyashi 1.
A gear 56-b in the middle stage of the switching gear 56 is rotatably supported by 61, and is at a height that meshes with a gear portion 32-a of the drive ring 32, as shown by a broken line. Therefore, the upper switching plate 56-a is located at a height that substantially opposes the outer circumference of the lock plate 59 on the drive ring 32, and the lower gear 56-c connects the drive ring 32 and the cam ring 38. It is located between and meshes with the cam drive gear 57 shown in FIG.

The end faces connecting the large diameter portion and the small diameter portion of the outer circumferences of the switching plates 55-b, 56-a in the switching gears 55, 56 described above are similar to the tooth surfaces of the gears 55-c, 56-b, respectively. It has an involute curve, and is set so that the tooth surface and the end surface are planarly aligned when the pins 62 and 63 are press-fitted and the phase relationship between them is held fixed.

As shown in FIG. 3, FIG. 10 shows a cam drive gear that meshes with the second switching gear 56 below the drive ring 32.
The positional relationship between 57 and the cam ring 38 is shown.

As shown in the drawing, the cam drive gear 57 is configured so as to mesh with a gear portion 38-a provided on a part of the inner peripheral surface of the cam ring 38 and a lower gear 56-c of the switching gear 56 in a plan view. It is located in. Further, the upper surface of the cam drive gear 57 is located at a height shown by the one-dot chain line in FIG. 9 and at a height that does not contact the drive ring 32.

Due to this arrangement, when the switching gear 56 is rotated by the drive ring 32, the cam ring 38 is moved via the cam drive gear 57.
Is rotated.

FIG. 11 is a connection state of the reduction gear train from the LM motor 27 to the drive ring 32 and the transmission gear train from the drive ring 32 to the loading ring 10 and the guide arm 12 described in FIGS. 4, 5, 6 and 7. FIG.

In the figure, arrow A of the LM motor gear 50 shown in FIG.
By rotating in the ₅₀ direction, the worm 40, the reduction gears 41, 43, 45 and the drive gear 54, which are successively meshed, rotate in the directions of arrows A ₄₀ , A ₄₃ , A ₄₅ , A _{54 in} FIG. 11, respectively. The drive ring 32 is driven in the direction of arrow A ₃₂ by the lower stage 54-b of the drive gear 54. By this rotation, the gear portion of the drive ring 32
The lower gear 55-c of the switching gear 55 meshing with the 32-a rotates the upper gear 55-a in the direction of arrow A ₅₅ , and the transmission gear on the LM motor holder 47 meshes with the gear 55-a. 48,
Rotate _{49 in the} directions of arrows A ₄₈ and A ₄₉ , respectively, and rotate the loading ring 10 in the direction of arrow A ₁₀ .

Next, the operation of the transmission gear train arranged below in FIG. 11 will be described with reference to FIG. 12 showing a partial cross section of the portion of FIG. 11 when viewed from the right.

In FIG. 11 and FIG. 12, the connecting gear 62 is pivotally supported by the shaft 65 press-fitted from above the chassis 1, the lower gear 62-a is connected to the lower gear 55-c of the switching gear 55, and
The upper gear 62-b meshes with the upper gear 61-a of the two-stage gear 61, respectively. The gears 61, 63, 64 are rotatably supported by shafts 66, 67, 68 which are press-fitted and fixed to a gear holder 69 screwed to the side surface of the chassis 1 from below, and a retaining ring 70 engaged from below, It is axially positioned by 71 and 72.

In addition, the boss portion 13-c of the pinch roller arm 13 is held by the center of rotation of the guide arm 12 having a U-shaped cross section through the spacers 73 and 74, and the shaft 22 is planted in the chassis 1. Further, it is rotatably supported together with the guide arm 12 and the fan-shaped gear 28. As shown in FIG. 11, the pin 75 is press-fitted into the protruding portion 13-a of the pinch roller arm 13 in a state of protruding in the upward direction of the shiyashi 1, and is in contact with the side surface of the sector gear 28. .

As shown in FIG. 11, the boss 13- of the pinch roller arm 13
A return spring 76 is mounted on the cylindrical surface of the outer periphery of c with a margin. One end 76-a of the return spring 76 is locked to the projection 13-a of the pinch roller arm 13 and the other end 76-b thereof is the guide arm 12. Is connected to the connecting portion 12-a having a U-shaped cross section and connects the protruding portion 13-a of the pinch lower arm 13 to the guide arm 12.
12-a is urged in the direction away from each other.

Therefore, when the drive ring 32 is rotated in the direction of arrow A ₃₂ ,
Via the lower gear 55-c of the switching gear 55, the gears 62-a, 62
-B, 61-a, 61-b, 63-a, 63-b are the arrows A ₆₂ , A ₆₁ ,
The fan gear 28 is rotated in the A ₆₃ direction, and is rotated in the arrow A ₂₈ direction. As a result, the pin 75 on the pinch roller arm 13 is pressed by the side surface of the sector gear 28, and the pinch roller arm 13 is pressed.
13 is rotated in the direction of arrow A ₁₃ and, further, the guide arm 12 is rotated in the direction of arrow A ₁₂ via the elastic reaction force of the return spring 76 that abuts against the pinch roller arm 13.

In this way, the rotation of the LM motor 27 is transmitted to the loading ring 10 and the guide arm 12 via the drive ring 32, so that the loading operation is performed.

Next, the loading mechanism and its operation are shown in Figs.
A detailed description will be given with reference to FIG.

First, in FIG. 13, on the loading ring 10,
Pins 10-a and 10-b are press-fitted. These pins 10-a,
10-b is engaged with the long holes provided in the guide bases 29, 30 with a predetermined gap. Further, these base guides 29, 30 are provided with projections 29-b, 30-b, and projections 10-e, 10 fixed on these and the loading ring 10 are provided.
Springs 10-c and 10-d are independently hung between -f and -f, and the positions of the guide bases 29 and 30 with respect to the loading ring 10 are restricted. Since the loading ring 10 and the guide bases 29, 30 have the above-described mounting relationship, the loading ring 10 rotates from the state shown in FIG. 1 in the direction of arrow A ₁₀ as described above. Then, the base guides 29 and 30 also move. By this operation, the magnetic tape 3 is gradually wound around the rotary cylinder 2 from the state in which it is stretched over the front surface of the magnetic tape cartridge 77, as shown in FIG.

FIG. 14 shows a state in which the guide base 29 has entered the U-shaped groove 20-c of the cache 20 and is in contact therewith by the rotation of the loading ring 10 in this manner.
FIG. 15 is a plan view seen from above, and FIG. 15 is a side view seen from the direction of arrow A in FIG.

In FIGS. 14 and 15, a positioning pin 29-a is press-fitted into the base guide 29, and when approaching the catcher 20, a U-shaped groove 20-a and a V-shaped groove 20 are provided above and below the catcher 20, respectively. Move along the -b and U-shaped groove 20-c while correcting the traveling direction. At the same time, as shown in FIG. 15, the upper surface 29-c of the tip end portion of the guide base 29 comes into contact with the lower surface 20-d of the chatter 20, and the tilting of the guide base 29 back and forth is also corrected. . Even after the horizontal and vertical positions are corrected and positioned as described above, the loading ring 10 further rotates to give the spring 10-c a predetermined extension, whereby the guide base 29 with respect to the chatter 20. And is crimped with a predetermined crimping force.

16 is a plan view showing a state in which the base guide 30 is moved in the direction of the carrier 21 by the loading ring 10 in the same manner as above, and FIG. 17 is a side view seen from the direction B of the arrow in FIG. Figures 18 and 19 show the guide base 30.
FIG. 3A is a plan view and a side view showing a state in which is pressed to the carrier 21.

First, referring to FIGS. 16 and 17, the loading ring 10
By the rotation of the base guide 30, the base guide 30 comes close to the catcher 21, and the pin 30-a provided on the base guide 30 is guided to the groove 21-b of the catcher 21 through the path shown by the broken line.
A V-shaped notch 21-a provided above the groove 20-b
The direction of travel is corrected toward.

Then, as shown in FIG. 18 and FIG. 19 when viewed from the arrow C side, the pin 30-a abuts on the V-shaped notch 21-a, and the bottom surface of the base guide 30 is the surface 21 of the chatter 21. Even after contacting −c, the loading ring 10 further rotates in the direction of arrow A ₁₀ and extends the spring 10-d by a predetermined amount. As a result, the base guide 30 is pressure-bonded to the carrier 21, and the position on the plane and the tilted state in the vertical direction are determined.

FIG. 20 shows that the driving ring 32 causes the loading ring 10
FIG. 21 is a plan view showing the positional relationship between the guide arm 12 and the cache 31 that are rotated in conjunction with the, and FIG. 21 is a side view thereof.

In FIGS. 20 and 21, a lever 79 engaged with the guide base 25 is provided as a return spring at the tip portion of the guide arm 12.
They are connected by 78 by being urged counterclockwise. The lever 79 is provided with a claw-shaped protrusion 79-a so as to engage with the side wall of the guide guide 81. The side wall of the guide guide 81 extends linearly toward the cache 31 and regulates the postures of the lever 79 and the guide base 25 during the loading operation.

The rotation of the guide arm 12 causes the guide base 25 to move and come into contact with the carrier 31. 22 and 23 show the contact state. At this time, the positioning pin 25-a provided on the guide base 25 is attached to the V pin provided on the chuck 31.
It abuts the letter-shaped notch 31-a. The lower surface 25-b of the base guide 25 is in contact with the locally projected surface 81-a of the tip of the guide guide 81.

After the contact state, the fan gear 28 further rotates by a predetermined angle to press the one end 76-a of the return spring 76, and the base guide 25 is pressure-bonded to the catcher 31 to be positioned.

The mechanism and operation of the loading mechanism have been described above. Next, the tension pin 16 and the correction guide 82 will be described with reference to FIGS. 24 and 25.

FIG. 24 is a plan view showing the positional relationship between the tension arm 16 and the correction guide arm 82 in the unloading state shown in FIG.

In the figure, the tension arm 16 and the correction guide arm
Both 82 are rotatably supported by a shaft 83 press-fitted in the palm 1. In the unloaded state, the tension pin 16-pressed into the tips of the tension arm 16 and the correction guide arm 82 respectively.
The correction guide pin 82-a is housed behind the magnetic tape 3 stretched over the opening of the magnetic tape cartridge 77.

Notch 16 provided at one end of this tension arm 16
A spring 85 is stretched between b and the shaft 84 planted on the palm 1 so that the tension arm 16 is urged in the direction of arrow A ₁₆ . Further, the projection 82-b provided on the correction guide arm 82 and the palm 1
A spring 88 is stretched between the protrusion 87 provided on the outer peripheral side surface of the and the correction guide arm.
82 is biased in the direction of arrow B ₈₂ . A projection 82-c is provided near the tip of the correction guide arm 82, and the projection 82-c is in contact with the side surface of the tension arm 16. For this reason, the spring 85 tension arm
The rotation of 16 is blocked by a correction guide arm 82 which is biased by a spring 88.

The projection armature 16-c of the tension arm 16 has the other end of the band brake 86 fixed to the palm 1 with a screw 89. In the unloading state, the band brake 86 is mounted in a loose state on the supply reel stand 37 as shown in the figure.

The end portion of the tension arm 16 provided with the cutout 16-b, the end portion 82-d of the correction guide arm 82, and the springs 85 and 88 are shown in FIG. As shown, it is located sufficiently above the drive ring 32, and there is no concern about contact with the drive ring 32.

This Ann Rohde queuing state, in the course of transition to the loading state, when the driving ring 32 is rotated in the arrow A ₃₂ direction, the projections provided on the drive ring 32 32
-C contacts the end portion 82-d of the correction guide arm 82, and moves the correction guide arm 82 against the reaction force of the spring 88 by the arrow A _82.
Rotate in the direction. When the angle of this rotation exceeds a certain value, the action point of the force of the spring 88 is the shaft 83 and the palm 1.
To the left with respect to the straight line connecting the protrusions 87 on the side surface of the. Therefore, the correction guide arm 82 is urged by the spring 88 in the direction of arrow A ₈₂ , which is opposite to the unloaded state.

FIG. 25 is a plan view showing an arrangement state of the tension arm 16 and the correction guide arm 82 at the time when the loading operation is completed.

In the figure, the correction guide arm 82 and tension arm 16 urged by springs 88 and 85 pull out the magnetic tape 3 from the base surface side, and the magnetic tape cartridge
A predetermined tape running path is formed on the exit side of 77. At this time, the correction guide arm 82 comes into contact with the protruding portion 150-a of the guide plate 150 to define the planar position.

In addition, the protrusion 16-c on the tension arm 16 also has an arrow A ₁₆
Since it is rotated in the direction, the band brake 86 contacts the supply reel stand 37 with a predetermined tension. As a result, a predetermined braking torque is generated on the supply-side reel stand 37,
Appropriate tension is applied to the magnetic tape 3 drawn from the supply reel 6 during recording and reproduction.

When performing Ann Rohde queuing operation from the state of the the loading completion, first, the protrusion 82 of the protrusion 32-C on the drive ring 32 is rotated in the arrow B ₃₂ direction correction guide arm 82
By pressing -e, the correction guide arm 82 is rotated in the direction of arrow B ₈₂ against the biasing force of the spring 88. Then, the tension arm 16 also has a protrusion 82-c on the correction guide arm 82.
It is pressed by and is rotated in the direction of arrow B ₁₆ . When this rotation angle exceeds a certain value, the correction guide arm 82 is biased by the spring 88 in the direction of arrow B ₈₂ , contrary to the loading operation, as shown in FIG. 24. , The tip portion of the magnetic tape cartridge 77 is returned to the state of being housed in the opening of the magnetic tape cartridge 77.

The tape running path shown in FIG. 2 is formed by the loading operation, pressure bonding, and positioning operation by the rotation of the drive ring 32 described above. Operations such as recording (playback), rewinding, and fast-forwarding are performed on the tape running path. Next, a mechanism for maintaining the tape traveling path will be described.

During the loading operation, in FIG. 5, the lock plate 58 on the drive ring 32 moves in the direction of the arrow A ₃₂ together with the drive ring 32 to approach the switching gear 55. Switching gear 5
As described with reference to FIG. 6, reference numeral 5 has a three-stage structure, and since the intermediate switching plate 55-b is located at the height described with reference to FIG. Gear unit 32-a
During the loading operation in which the lower gear 55-c of the switching gear 55 meshes with the lower gear 55-c, it idles above it.

27 and 28 are plan views showing the positional relationship between the drive ring 32 and the lock plate 58 and the switching plate 55-b of the switching gear 55 before and after the completion of the loading operation.

As described in FIG. 5, the gear portion 32 of the drive ring 32
The gear surface of -a switches at both ends to the end surface of the lock plate 58 above the drive ring 32. Therefore, until the lock plate 58 reaches the switching gear 55, the switching gear 55 is in the direction of the arrow A ₅₅ because the lower gear 55-c meshes with the gear portion 32-a of the drive ring 32. However, at the end of the gear portion 32-a, the engagement with the lower gear 55-c is released. However, the toothed end of the lock plate 58 has a switching plate 55-b.
By pressing the boundary between the large-diameter portion and the small-diameter portion forming the tooth surface of the switching gear 55, the switching gear 55 is further rotated to the state shown in FIG. 28 (in this case, the gear portion 32-a and the gear portion 32-a). The phase of meshing of 55-c is set so that the tooth surfaces of the lock plate 58 and the switching plate 55-b engage at this end).

In this state, the two boundary portions of the large diameter portion and the small diameter portion of the switching plate 55-b are both lock plates.
It is locked and held by the inner peripheral surface of 58.

Since the gears 55-a, 55-c and the switching plate 55-, which form the switching gear 55, have a fixed phase relationship with each other as described with reference to FIG. 6, the switching plate 55-b is locked by the locking plate 58. When locked to, the rotation of the gear 55-a is also blocked,
Transmission gears 48, 48 that mesh with this, loading ring 1
The rotation of 0 and the guide arm 12 is also prevented. When the switching gear 55 is locked, the loading ring described above is used.
The base guides 29, 30 on the 10 and the base guide 25 on the guide arm 12 are set to be approximately equal to the timings when they are crimped to the respective catches 20, 21, 31 with a predetermined force.

By the above switching operation, the positioning of the guide rollers provided on the guide bases 29, 30, 25 is maintained, and the tape running path is reliably held.

Further, in FIGS. 29 and 30, during the loading operation period, the lock plate 59 and the lock plate 59 are also rotated in the direction of arrow A ₃₂ . During this rotation period, the inner peripheral surface of the lock plate 59 is in sliding contact with the two boundary portions of the large diameter portion and the small diameter portion of the upper switching plate 56-a (FIG. 8) of the switching gear 56.

Since the switching gear 56 and the drive ring 32 have the mounting relationship described with reference to FIG. 8, during the period in which the lock plate 59 is in sliding contact with the switching plate 56-a, switching is performed as shown in FIG. The rotation of the gear 56 is blocked. Therefore, the cam ring 38 does not rotate during this period.

Then, as described above, after the locking of the switching gear 55 by the lock plate 58 is completed, the gear portion 32-a of the drive ring 32 that moves in the direction of the arrow A ₃₂ and the lock plate 59.
As shown in FIG. 30, the boundary portion forming the tooth surface of the switching gear 56
The boundary portion forming the tooth surface of the upper switching plate 56-a starts to be pressed, and by further movement, the gear portion 32-a starts to mesh with the middle gear 56-b of the switching gear 56, As a result, the cam ring 38 below the drive ring 32 starts to rotate via the cam drive gear 57 that meshes with the gear 56-c in the lower stage.

Next, the cam ring 38 constitutes a mode operation mechanism portion, and the mode operation performed by its rotation will be described.

FIG. 31 is a plan view showing an arrangement state of the reel base braking members and the driving members before the cam ring 38 is rotated.

In the figure, the take-up reel stand 36 and the supply-side reel stand 37
Gears for driving these are arranged as shown in the figure in the vicinity of, and a braking member for braking the take-up reel stand 36 and the supply reel stand 37 between the gears and the shiyashi 1. The kind is arranged.

FIG. 32 shows a planar arrangement of the brakes located below the gears.

In the figure, on the uneven surface of the cam provided on the inner circumference of the cam ring 38, a main brake operation lever 91-a, a supply side reel base sub brake operation arm 92-a, a winding side reel base brake operation arm 94- a, take-up reel stand sub brake 9
5, The operating end of the pinch roller operating lever 96-a is in contact.

These cam surfaces provided on the inner circumference of the cam ring 38 have two
It is mainly configured by two arc surfaces having different radii of curvature and a taper surface connecting them. By rotating the cam ring 38, the operated members are rotated around the shafts 91-S, 92-S, 94-S, 95-S, 96-S press-fitted onto the shiyashi 1 and wound. The braking torque is applied to the take-up reel stand 36 and the supply-side reel stand 37, and the pinch roller 15 is pressed against the capstan 14 and the like. The operation end of the operated members is in the H position when it is in contact with the arc surface having a small radius of curvature of the cam ring 38, and is in the L position when it is in contact with the arc surface having a large radius of curvature. , I will call each one.

The idler gear operation slider 93 uses the torsion spring 110 to
The cam ring 38 is urged and abutted against the inner peripheral surface of the cam ring 38. Only the cam surface of the cam ring 38 for operating the idler gear operating slider 93 is composed of three circular arc surfaces having different radii of curvature, whereby the idler gear operating slider 93 can take three positions. Hereinafter, these three positions will be referred to as H, M, and L in ascending order of the radius of the cam surface.

In the state during the loading operation described in FIG. 23, the main brake 91 is in a position where it does not contact the take-up reel stand 36, the supply-side reel stand 37, and the supply-side reel stand sub-brake 92, the take-up side. Only the reel stand sub-brake 95 is in contact with the supply reel stand 37 and the take-up reel stand 36, respectively.

FIG. 33 shows the idler gear operating slider 93, the idler gear support plate 97 and the idler gear 9 located above the idler gear operating slider 93.
FIG. 34 is a plan view showing the positional relationship with 8, the winding gear 99, and the FR gear 100, and FIG. 34 is a sectional view taken along the line XX ′. However, these Fig. 33 and Fig. 34 show the idler gear operating slider.
93 is in the H position.

In FIGS. 33 and 34, the idler gear operating slider 93 is held by the holder 101 so that it can be slid on the surface of the palm 1 in the arrow direction.

At one end of the idler gear operating slider 93, there is a side wall forming a substantially elliptical concave portion, and as shown in FIG. The idler gear support plate 97 is placed on the upper surface of this protruding portion,
On the other hand, since the FR gear 100 and the take-up gear 99 are rotatably arranged around the shafts 100-s and 99-s press-fitted into the shiyashi 1 above them, the vertical position is restricted. A boss 102 is caulked in the center of the idler gear support plate 97, and a shaft 103 penetrates and is press-fitted into a hole of the boss 102. And Idler Gear 98, Shaft 10
It is rotatably supported by 3 and the felt 104
Is pressed against the idler gear support plate 97 by this, and thus a predetermined rotational drive load is applied.

Further, the lower end of the shaft 103 which is extended and pressed into the lower portion of the idler gear support plate 97 is engaged with the elliptical hole portion 93-a of the idler gear operating slider 93.

Therefore, as the idler gear operating slider 93 slides to the L, M, and H positions by the cam ring 38, the shaft 103 is pressed and the idler gear supporting plate 97,
Also, the idler gear 98 pivotally supported on the idler gear 98 also moves in the L or H direction. And this idler gear 98 is indicated by the arrow H.
When it moves in the direction of arrow M, it meshes with the FR gear 100, when it moves in the direction of the arrow L, it meshes with the take-up gear 99, and when it is located in the position M, it does not mesh with either of them. In this way, the idler gear operating slider 93 interlocks with the rotation of the cam ring 38 to move the idler gear 98 to the FR gear 100,
A switching mechanism portion for switching and engaging with the winding gear 99 is formed.

Therefore, when the cam ring 38 is rotated in the direction of the arrow A ₃₈ from the arrangement state shown in FIGS. 31 and 32, each input end of the operated members is fast-forwarded during the loading operation period by the cam surface. / Rewind (FF / Rew), loading stop (stop while loading), recording (/ playback /
It is shifted by a predetermined amount for each mode of fast-forward reproduction. The rotation angle of the cam ring 38 is detected by the print patterns 38-b, 38 on the cam ring 38 described with reference to FIG.
-C.

Hereinafter, the state of the operated member and the rotation state of each motor in each mode will be described.

FIG. 35 shows the arrangement of the operated members when the cam ring 38 is rotated in the direction of arrow A ₃₈ from the state during the loading operation shown in FIGS. 31 and 32 to enter the loading stop mode. Is shown.

In this loading stop mode, only the main brake operating lever 91-a is rotated to the L side, and the brake portion at the output end thereof is the take-up reel stand 36, the supply reel stand 3
It blocks the rotation of 7. Further, the idler gear operation slider 93 is at the position M, and the idler gear 98 is the take-up gear.
It does not mesh with 99 or FR gear 100.

FIG. 36 shows a state in which the cam ring 38 is further rotated in the direction of arrow A ₃₈ from the loading stop mode shown in FIG. 35, and the brakes are in the recording (playback, fast-forward playback) mode. ing.

In the figure, the pinch roller operating lever 96 is rotated in the H direction to engage with the output end of the pinch roller arm 13
Is rotated, and the pinch roller 15 is pressed against the capstan 14. Each brake operating lever is rotated in the H direction to release the engagement with the take-up reel stand 36 and the supply reel stand 37. However, the band brake 86 shown in FIG. 25 is in contact with the outer peripheral surface of the supply-side reel stand 37 and applies a predetermined tension to the running magnetic tape.

Further, the idler gear operating slider 93 moves to the position L, and the idler gear 98 moves the take-up gear 98 as shown in FIG.
Bite into 39. The winding gear 99, together with the gears 179 and 178, forms a mechanism portion that transmits the driving force from the reel motor 105. The winding gear 99 is rotated in the direction of arrow T ₉₉ by the reel motor 105. As a result, the idler gear 98 that has been bitten into the take-up gear 99 is also bited into the gear 106 on the outer peripheral portion of the take-up reel stand 36, and rotates the take-up reel stand 36 in the direction of arrow T ₃₆ . Then, by rotating the capstan 14 and the cylinder 2 in the counterclockwise direction, the magnetic tape 3 runs and scans.

38 and 39 show the cam ring during fast forward or rewind.
Position 38 is shown.

In this figure, in this case, the supply side reel base 36 and the winding side reel base 37 are in contact with the sub-brakes 92 and 95, respectively, and
The pinch roller 15 is no longer pressed against the capstan 14. Then, the idler gear operating slider 93 moves to the arrow H side, whereby the idler gear 98 causes the FR gear 10 to move.
Bite into 0. The FR gear 100 forms a mechanism portion that transmits the driving force of the capstan 14, together with the gear 109 and the gears 171-175 that bit the gear 108 of the capstan 14 in conjunction with the rotation of the pinch roller arm 13. It rotates with the rotation of the capstan 14.

Therefore, at the time of fast-forwarding, the capstan 14 rotates clockwise in the drawing to rotate the FR gear 100 counterclockwise, and the idler gear 98 bitten in the FR gear 100 is urged rightward to wind the reel base 36. It meshes with the transmission gears 106, 107 for rotating the reel reel 36 and rotates the reel reel base 36 in the clockwise direction. Further, in the case of rewinding, the capstan 14 is reversely rotated and the adler gear 98 is fed through the transmission gears 111 and 112 to the supply side reel stand 37.
And transmits the counterclockwise rotational force to it.

With the above operation, the state as a normal recording / reproducing apparatus is satisfied.

〔The invention's effect〕

As described above, according to the present invention, all the operations of the mechanism can be performed by gear drive, so that
The reliability of the device can be ensured by increasing the certainty of operation against environmental changes, a low load mechanism with high transmission efficiency can be obtained, and the assemblability can be improved.

[Brief description of drawings]

1 to 39 show an embodiment of a mechanism operating mechanism of a magnetic recording / reproducing apparatus according to the present invention. FIG. 1 is an overall plan view showing a state at the time of unloading, and FIG. 2 is a loading. FIG. 3 is a plan view showing a state at the time, FIG. 3 is a development view showing the mounting relationship of the rings to the shiyashi, and FIG. 4 is a perspective view showing a speed reducing mechanism for transmitting the driving force of the loading mode motor to the drive ring. FIG. 5 is a plan view showing a power transmission mechanism from a drive ring to a loading ring or a cam ring, FIG. 6 is a development view showing a structure of a first switching gear in FIG. 5, and FIG. FIG. 8 is a sectional view showing the height relationship between the switching gear, the drive ring and the cam ring, FIG. 8 is a development view showing the structure of the second switching gear in FIG. 5, and FIG. 9 is the second switching gear and the driving ring. ， Height relationship with cam ring FIG. 10 is a plan view showing the positional relationship between the cam drive gear meshing with the second switching gear and the cam ring, and FIG. 11 is a view showing between the loading mode motor, drive ring, loading ring, and guide arm. FIG. 12 is a plan view showing a connected state of the transmission gear train, FIG. 12 is a partial sectional view thereof, FIG. 13 is an overall plan view of a loading mechanism, and FIG. 14 is a first guide base in FIG. FIG. 15 is a plan view showing a state of being abutted against, FIG. 15 is a side view thereof,
FIG. 16 is a plan view showing a state where the second guide base in FIG. 13 is rotated by a loading ring,
FIG. 17 is a side view thereof, and FIG. 18 is a plan view showing a state in which the second guide base is in contact with the second carriage, and FIG.
Figure is its side view, Figure 20 is a plan view showing the positional relationship between the guide arm rotated by the guide arm and the third carriage, Figure 21 is its side view, and Figure 22 is the third base guide. FIG. 23 is a plan view showing a state in which the abutment is in contact with the third carrier.
Figure is its side view, Figure 24 is a plan view showing the positional relationship between the tension arm and correction guide arm during unloading, and Figure 25 is a cross section showing the positional relationship between the tension arm and correction guide during loading. FIG. 26 is a sectional view showing the height relationship between the tension arm and the correction guide,
27 and 28 are plan views showing the positional relationship between the first locking plate of the drive ring and the switching plate of the first switching gear before and after the completion of the loading operation, and FIGS. 29 and 30 are respectively loading. FIG. 31 is a plan view showing the positional relationship between the second lock plate of the drive ring and the switching plate of the second switching gear during operation. FIG. 31 is a plan view showing the arrangement state of the reel base braking members and the driving members with respect to the cam ring. 32 and FIG. 32 are plan views showing the arrangement of brakes with respect to the cam ring, FIG. 33 is a plan view showing a mechanism for transmitting and switching the driving force to the reel stand, FIG. 34 is FIG. Fig. 35 is a cross-sectional view taken along the line X ', Fig. 35 is a plan view showing the layout of the operated members shown in Fig. 32 in the loading stop mode, and Fig. 36 is the layout of the same during recording, playback and fast-forward playback. Show FIG. 37 is a plan view showing the state of the driving force transmission mechanism to the reel base during recording, reproduction and fast-forward reproduction, and FIG. 38 is the operated members shown in FIG. 32 during fast-forward or rewind. And FIG. 39 is a plan view showing the state of the driving force transmission mechanism to the reel stand. 1 ... Sheath, 2 ... Rotating cylinder, 3 ... Magnetic tape, 5 ... Take-up reel, 6 ... Supply reel, 7,8,9,11 ...
… Guide rollers, 10 …… Loading ring, 27 …… Loading mode motor, 32 …… Drive ring, 38 …… Cam ring, 55 …… First change gear, 56 …… Second change gear, 58… … First lock plate, 59 …… Second lock plate.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Takashi Sasaki 292 Yoshida-cho, Totsuka-ku, Yokohama-shi, Kanagawa, Ltd. Home Appliances Research Laboratory, Hitachi, Ltd. (72) Inventor Kohei Takita 292 Yoshida-cho, Totsuka-ku, Yokohama-shi, Kanagawa Ceremony Company Home Appliance Research Laboratory, Hitachi, Ltd.

Claims (1)

[Claims] 1. A magnetic recording / reproducing apparatus in which a magnetic tape is wound around a tape guide drum having a magnetic head at a predetermined angle to form a predetermined tape running path, and a rotational driving force is transmitted to at least a part of a peripheral surface. It consists of a ring with a gear part and a cam part, and has a mode operation mechanism part that performs a rotational operation according to various modes such as recording and reproduction, a first drive source for driving a capstan, and a reel base drive. A first drive force transmission mechanism section for transmitting the drive force of the first drive source in conjunction with the rotation operation of the mode operation mechanism section, and a gear train The second drive force transmission mechanism section for transmitting the drive force of the second drive source, the idler mechanism section including a gear, and the mode operation mechanism section associated with the rotation of the mode operation mechanism section. It operates according to the cam, Hydra mechanism part
A switching mechanism part for switching and connecting to either one of the second driving force transmitting mechanism parts, wherein the idler mechanism part is driven by the connected first or second driving force transmitting mechanism parts. A mechanism operating mechanism for a magnetic recording / reproducing apparatus, which transmits the driving force to a take-up reel base or a supply reel base according to a direction of force.