JPH05303809A - Tape loading mechanism - Google Patents

Abstract

PURPOSE:To provide a tape loading mechanism in which a tape damage can be prevented without generating a twist, width directional bend, and height deviation or the like of the tape, even during loading the tape. CONSTITUTION:This mechanism is equipped with an inclined direction control means 21 which successively changes the inclined direction of a rotary drum 2. This control means 21 is constituted of a driving motor 32a which changes the inclined direction of the rotary drum 2, angle detector 34a which detects the angle of the inclined direction of the rotary drum 2, gear 37 provided at the outer periphery of a drum base 36 which mounts the rotary drum 2, and a pinion 38 fixed to the shaft of the driving motor 32g, and engaged with the gear 37. Also, the mechanism is equipped with an inclined angle control means 22 which successively changes the inclined angle of the rotary drum 2, and a tape guide control means which successively changes the position, inclined angle, and inclined direction of parts except of a tape pulling out body which pulls out the tape from a cassette.

Description

Detailed Description of the Invention

[0001]

This invention relates to a tape recorder, VT
The present invention relates to a tape loading mechanism of a magnetic recording / reproducing apparatus such as R.

[0002]

2. Description of the Related Art In a magnetic recording / reproducing apparatus using a rotary drum of this type, a tape is wound around the rotary drum to perform oblique scanning, and therefore a tape path system always requires an inclined tape guide. In the tape path including the rotating drum and the inclined tape guide, a so-called ideal tape path is formed in which the tape is not twisted, bent in the width direction, and displaced in height in the state where the recording and reproduction are completed. .. However, the ideal tape path system is not necessarily constructed in the state other than the completion of the loading, that is, in the unloading state in which the cassette is mounted or removed, or in the intermediate stage from the unloading state to the loading completed state. It was Therefore, there has been a problem that excessive stress is applied to the tape during loading to damage the tape.

Further, in recent years, miniaturization of magnetic recording / reproducing devices has been promoted,
Due to the trend of longer recordable time, thinner tapes are used. Since the strength of the tape is weakened accordingly, the permissible condition for not damaging the tape in the structure of the tape path and the tape loading is becoming severer year by year.

Therefore, for example, Japanese Unexamined Patent Application Publication No.
As disclosed in Japanese Patent Laid-Open No. 3-78150, a loading mechanism is disclosed which includes a tape guide control means for sequentially changing the tilt angle and the tilt direction angle of the tape guide according to the reciprocating movement.

FIG. 28 is a plan view showing an unloading state of this conventional loading mechanism, and FIG. 29 is a plan view showing a loading completed state. In the figure, reference numeral 1 is a deck base as a reference surface, and 2 is a rotary drum provided with a magnetic head 26 and arranged at a predetermined angle with respect to the reference surface. 3 is a cassette, 5 and 6 are supply side reels and take-up side reels which are pivotally supported inside the cassette 3, 4 is a tape wound around these reels, and the tape path is from the supply side reel 5 to the tape. It returns to the winding side reel 6 through the guide and is completed. 700 and 800 are tape drawers that are reciprocally arranged on the deck base 1, and 710 and 820 are guide bases that are the bases of the tape drawers 700 and 800, respectively.
70, 80, 770 and 780 are tape guides installed upright on the guide bases 710 and 820, of which 770 and
Reference numeral 780 is an inclined tape guide that is inclined with respect to the longitudinal direction of the tape to wind the tape 4 and guide the tape. 670, 68
Reference numeral 0 denotes a stopper which is provided on the deck base 1 and comes into contact with the tape drawers 700 and 800 when loading is completed. 671, 681, 767, and 768 are guide grooves provided on the deck base 1. The guide grooves 767 and 768 are set in such a shape that the directions of the tape drawers 700 and 800 are changed depending on the loading position. Drawer 700
, Guide the 800 round trips above. 764 and 765 are guides that are provided along the guide grooves 767 and 768 and that are configured so that the height from the deck base 1 changes sequentially,
790 and 791 are provided on the tape drawers 700 and 800, respectively.
0 is a means for controlling the inclination angle of the inclined tape guides 770 and 780 shown in detail in FIG. These, inclined tape guide 770, 780
Inclination angle control means 790, 791 and guide grooves 767, 768
And the guides 764 and 765 constitute tape guide control means 795 and 796.

FIG. 30 is a schematic view of a main part showing the tape guide control means 795 and the inclination angle control means 790 of the inclined tape guide 770. In the figure, 490 is a shaft set up on the back surface of the deck base 1, and 49 is a shaft. A gear pivotally supported by 490, 76 is a first arm that rotates integrally with the gear 49, 75 is a second arm swingably engaged with one end of the first arm 76, and 711 is a guide base 710. The first guide pin, 712, which is planted on the back surface of the guide arm, fits into the guide groove 767 with a predetermined clearance and fits into the hole provided at one end of the second arm 75. A second guide pin that is set up on the back surface and fits so that it can slide following the shape of the guide groove 671, 825 is a swing shaft provided on the guide base 710, and 830 holds the inclined tape guide 770. Tilt tape guide base that swings around swing shaft 825 It is axially supported, and its one end a is urged by an urging means (not shown) so as to abut the upper surface of the guide 764, so that the inclination angle η of the inclined tape guide 770 corresponds to the height change of the guide 764. Inclination angle control means 790 so that it can be changed
Is configured. The gear 48 in the tape guide control means 796 meshes with the gear 49, and the configuration thereof is arranged substantially symmetrically with the tape guide control means 795, so the description of the configuration will be omitted.

Next, the operation will be described. FIG. 28 shows an unloading state in which the cassette 3 is removable and the tape drawers 700 and 800 are inside the cassette 3. When the tape loading operation is started from here, drive means such as a motor is transmitted through transmission means (neither is shown),
The gear 49 rotates clockwise and the gear 48 rotates counterclockwise.
This allows the first arm 76, 86 and the second arm 7
The tape drawers 700 and 800 are guided through the guide grooves 6 and 5 respectively.
Start moving in the loading direction along 71, 681,
Tape guides 70, 80 and inclined tape guides 770, 780
Thus, the tape 4 is pulled out from the cassette 3 and is wound around the rotary drum 2. Below, the tape drawer 700
, 800, since the tape guide control means 795 and 796 perform the same operation, the operation of the tape guide control means 795 will be described.

The tape drawer 700 has a first guide pin.
711 in the guide groove 767 and the second guide pin 712 in the guide groove 67.
Since it moves on the deck base 1 while being engaged with 1, the inclination direction of the inclined tape guide 770 is determined by the shape and relative positional relationship of the two guide grooves 767 and 671. Further, as the tape drawer 700 moves, the inclination angle η of the inclined tape guide 770 changes according to the height of the guide 764. By satisfying the relations shown below with respect to the changes in the inclination direction, inclination angle, and movement trajectory of these inclined tape guides 770, the tape path formed in the momentary loading process is regarded as an ideal tape path so that no stress is generated on the tape. To configure.

When the conditional expression shown in Japanese Patent Laid-Open No. 3-78150 is cited,

[0010]

[Equation 1]

Here, a) parallel condition: inclined tape guide 770 and tape guide 70
The center line direction of the tape 4 stretched between and is parallel to the deck base 1. b) Height conditions: inclined tape guide 770 and tape guide 70
The center height of the tape 4 stretched over the tape is the same as the center height of the tape 4 in the cassette 3. c) Untwisted condition: The tape 4 is not twisted at any part. Each symbol is shown below. D: Diameter of rotating drum 2 r: Radius of inclined tape guide 770 A: D / (2r) L: Tape length from tape separation point of inclined tape guide 770 to entry point of rotating drum B B: L / r S: Angle of tape incident on the rotating drum 2 β: Angle of tape winding on the rotating drum 2 (one side) γ: Inclination direction of the inclined tape guide 770 (angle from the X axis) η: Inclined tape with respect to an axis perpendicular to the deck base surface Inclination angle of guide 770 α: Inclination angle of rotating drum 2 ξ: Inclination angle of inclination tape guide 770 in the direction parallel to the tape between rotating drum 2 and inclination tape guide 770 (= tape incident angle to inclination tape guide 770 ) Θ: Angle of tape winding around the inclined tape guide 770. Each inclination direction ψ of the rotary drum 2 is fixed to the negative direction of the X axis in the conventional example. Here, among the variables of the equations (1) to (3), D, r, and α are constants, β and L are constants determined by the loading path of the inclined tape guide 770, and γ, η, and ξ. Are in a relationship satisfying the following relational expressions (4) and (5). Therefore, (1) ~
In equation (3), there are three unknowns, S, θ, and ξ, and since there are three conditional expressions, S, θ, and ξ can be uniquely determined if other constants are determined. .. cos η = -sin αcos βsin ξ + cos αcos ξ ---------- (4) sin γ = (sin ξsin β) / sin η ----- (5) As a result, the tape incident angle S to the rotary drum 2 and the inclination Tape incident angle ξ on tape guide 770,
The tape winding angle θ is obtained, and the tape guide control means 795 is set so as to satisfy the above-mentioned specifications of the inclined tape guide 770 during loading.

When the tape loading operation is completed, as shown in FIG. 29, the tape drawers 700, 800 are stopped by the stopper 670,
When it reaches 680 and is positioned, the tape 4 is completely wound around the rotary drum 2 and the driving means is stopped to complete the tape loading operation.

In an actual magnetic recording / reproducing apparatus, a tape path is formed in cooperation with a tape driving capstan, a pinch roller, etc. in addition to the above-mentioned rotary drum and tape guide, but these are omitted in this figure. I am doing it.

The unloading operation is the reverse of the loading operation, and the tape guide control means 795,
Tape 4 while forming an ideal tape path with 796
Are stored in the cassette 3.

The improvement effect of the conventional device obtained by FIGS. 28 to 30 is shown in FIG. This figure shows the relationship between the tape winding angle on the rotary drum 2 and the magnitude of the tape twist during loading. When the tape twist increases, the distance between the tape center line and the upper and lower ends in the tape width direction differs. For this reason, the stress distribution is different in the width direction of the tape 4 and unilateral stretching may occur,
May be pressed against a flange provided on the upper or lower end of the tape guide 70 or 80, and the tape edge may be damaged. As shown in FIG. 31A, in the case of the normal loading mechanism, the tape twist is 0 because the ideal tape path is formed in the loading completed state, but the tape twist increases toward the unloading state, Unnecessary stress is likely to occur. On the other hand, in the case of Japanese Patent Laid-Open No. 3-78150 cited as a conventional example as shown in FIG. 31B, the tape twist is maintained at 0 because the tape is always loaded while forming the ideal tape path. It has been shown that

[0016]

In Japanese Patent Laid-Open No. 3-78150, the tape guide adjacent to the rotary drum 2 is an inclined tape guide 770, and the tape to the inclined tape guide 770 is calculated in calculating the ideal tape path during loading. The incident angle ξ of 4 is an unknown number, that is, a value that changes momentarily during loading. However, in the tape path in which the winding angle of the tape 4 on the rotary drum 2 is larger than 190 ° disclosed in Japanese Patent Laid-Open No. 3-78150, for example, 250 °, in order to reduce the tape running load, The inclined tape guide adjacent to the rotary drum 2 may be a roller type. At this time, if the incident angle ξ is generated with respect to the roller, the tape 4 moves upward and downward with respect to the roller, and the flange may damage the tape edge. Therefore, in the case of a roller, the incident angle should be a constant of ξ = 0 and cannot be a value that changes momentarily during loading.

Further, when the tape winding angle on the rotary drum 2 is small at the initial stage of tape loading, the tape winding angle of the entire tape drawer becomes small. In some cases, the angles obtained by the equations (1) to (3) cannot be satisfied, and in this case, the ideal tape path cannot be formed, and there is a risk of tape twisting.

The present invention has been made to solve the above-mentioned problems, and can be applied to various tape path systems such as a tape guide having a roller guide adjacent to the rotary drum, and a tape for the rotary drum. It is an object of the present invention to provide a tape loading mechanism capable of preventing tape damage without causing twisting of the tape, bending in the width direction, height deviation, etc. even in the entire tape loading process including when the winding angle of the tape is small. To do.

[0019]

In the tape loading mechanism according to the present invention, instead of the incident angle of the tape to the tape guide adjacent to the rotating drum, the inclination direction angle or inclination of the rotating drum set as a constant in the conventional example. The angle is an unknown value and is a value that changes every moment. That is, it is provided with tilt direction control means for sequentially changing the tilt direction angle of the rotary drum in response to a tape loading operation in the same rotation direction as the advancing direction of the tape drawer on the supply side with respect to the rotary drum. is there.

In addition, there is provided tilt angle control means for sequentially changing the tilt angle of the rotary drum in the direction in which the tilt angle of the rotary drum decreases at the time of loading in response to the tape loading operation.

Further, in response to the tape loading operation, a tape guide other than the tape drawer, which abuts the tape from the outside of the tape path, that is, a so-called external tape guide is intervened from the outside in the tape path from the beginning of loading. Increase the winding angle of this tape guide and the tape guides before and after it. That is, the tape guide control means for sequentially changing the position, the inclination angle, and the inclination direction angle of the externally applied tape guide is provided.

[0022]

The tape loading mechanism of the present invention is
In the course of tape loading, the tape is loaded in the same rotation direction as the tape drawer on the supply side with respect to the rotary drum, that is, clockwise during loading and counterclockwise during unloading. It changes sequentially in response to movements.

Further, the inclination angle of the rotary drum is gradually changed in response to the tape loading operation from a state in which the inclination angle of the rotary drum is larger than that at the completion of loading at the time of unloading to a direction decreasing at the time of loading. When the loading is completed, the tilt angle is set to a predetermined value.

Further, in the course of loading, the position, tilt angle and tilt direction of the external tape guide are sequentially changed in response to the tape loading operation.

[0025]

【Example】

Example 1. Embodiments of the present invention will be described below with reference to the drawings. 1 to 7 show an embodiment of a VTR tape loading mechanism in the present invention. 1 to 3 are views of the deck as seen from the front side, in which 1 is a deck base as a reference surface, 2 is a magnetic head 26, and a rotary drum is arranged at a predetermined angle with respect to the reference surface. Reference numeral 21 is a tilt direction control means for the rotary drum 2, the details of which are shown in FIGS. 3 is a cassette, 5 and 6 are supply side reels and take-up side reels which are pivotally supported inside the cassette 3, 4 is a tape wound around these reels, and the tape path is from the supply side reel 5 to the tape. Take-up reel 6 via guide
Return to and complete. Reference numerals 7, 8 and 9 denote tape drawers arranged on the deck base 1 so as to be reciprocally movable, 71,
82 and 91 are guide bases which are the bases of the tape drawers 7, 8 and 9, and 70, 80, 81 and 90 are guide bases 71 and 8 respectively.
The tape guides 67, 68, 69 provided upright on the 2, 91 are guide grooves provided as guide means on the deck base 1,
The above-mentioned reciprocating movements of the tape drawers 7, 8 and 9 are guided respectively. 670, 680 and 690 are installed on the deck base 1,
These stoppers are in contact with the tape drawers 7, 8 and 9 when loading is completed. 11 and 12 are each deck base 1
Unlike the tape guide on the tape drawer, these are fixed tape guides that are erected upright, and are always fixed at the same position on the deck base 1.

Here, ψ1, ψ2,
ψ3 indicates the tilt direction angle of each rotary drum 2. That is, the angle formed by the arrow from the X-axis in the figure in the counterclockwise direction to the arrow indicating the tilt direction of the rotary drum 2 is the tilt direction angle.

FIG. 4 is a view of the deck as seen from the back side, in which 43 is a loading motor as a tape loading driving means, and 44 is this loading motor.
A worm gear supported on 43, 45 pivoted on shaft 450,
A gear that meshes with the worm gear 44, 46 is pivotally supported by the shaft 460, a main gear that meshes with the gear 45, 47 is pivotally supported by a shaft 470, and a gear that meshes with the main gear 46, 48 is a shaft 48.
A gear that is pivoted at 0 and also meshes with the main gear 46, 49
Is a gear that is pivotally supported by a shaft 490 and meshes with the gear 48, and 44 to 49 form a gear train. 76 is a first arm that rotates integrally with the gear 49, 75 is a second arm that swingably engages one end of the first arm 76, and 86 is a first arm that rotates integrally with the gear 48. One arm, 85 is a second arm swingably engaged with one end of the first arm 86, and 96 is a gear.
The first arm that rotates together with 47, 95 is the first arm 96
Is a second arm swingably engaged with one end of the. the above
The drive force of the loading motor 43 is applied to the tape pull-out member 7, by the gear trains of 44 to 49 and the arms of 75, 76, 85, 86, 95, 96.
It constitutes a transmission means for transmitting to 8 and 9.

FIGS. 5 and 6 are schematic views showing the main part of the inclination direction control means 21 of the rotary drum 2. In the figures, 39 is a guide ring provided on the deck base 1, and 36 is a rotatable guide ring. A drum base 37 supported by the gear base 37, a gear formed on the outer circumference of the drum base 36, a drive motor 32a provided on the deck base 1, and a pinion 38 fixed to the output shaft meshes with the gear 37. ing. 34a is an angle detector installed on the deck base 1, the shaft 370, the coupling
The rotation angle of the drum base 36 can be detected by being connected to the drum base 36 via 35a. Again 56
Is an angle detector coupled to the main gear 46 via the coupling 56a, and can detect the rotation angle of the main gear 46. Since the detection angle of the angle detector 56 and the loading position of the tape drawers 7, 8 and 9 have a one-to-one correspondence, they function as a loading position detector. 57
Is electrically connected to the two angle detectors 34a and 56,
This is a comparator that compares and calculates these detected angles. Also,
Reference numeral 24 is a lower drum provided on the drum base 36, and 25 is a step provided for the tape 4 to be wound around the rotary drum 2 at a predetermined angle for running, which is called a lead. 23 is the lower drum above
The upper drum is rotatably supported by 24, and 26 is this upper drum.
23 is a magnetic head fixed on top.

The main specifications of the deck here are that the diameter of the rotary drum 2 is 20 mm, the angle of inclination of the rotary drum 2 when loading is completed, that is, ψ3 in FIG. 6.8 °, tape winding angle on rotary drum 2 250 °, tape guide with flange 7
The diameter of 0, 80, 81, 90 is 3.5mm, and the width of tape 4 is 3.65m.
m, thickness 8 μm, Young's modulus in the width direction and Young's modulus in the longitudinal direction are 600 kg / mm ² , and the tape tension at the entrance of the rotary drum 2 is 10 g.

Next, the operation will be described. FIG. 1 shows an unloading state in which the cassette 3 is removable and the tape drawers 7, 8 and 9 are inside the cassette 3. In this state, the inclination angle ψ1 of the rotary drum 2 is about 190 °. When the tape loading operation is started from this state, the loading motor 43 causes the transmission means 44 to 49, 75, 7
6, 85, 86, 95, 96 through the tape drawer 7,8,
9 starts moving in the loading direction along the guide grooves 67, 68 and 69, respectively, and the tape 4 is moved by the tape guides 70, 80 and 90.
Is pulled out of the cassette 3.

In response to the tape loading operation described above, the tilt direction control means 21 operates as follows. First, the drive motor 32a is rotated counterclockwise in FIG. 6 to drive the gear 37, and the drum base 36 is guided by the guide ring 39.
The rotation direction of the rotary drum 2 changes in the clockwise direction. This tilt direction angle is detected by the angle detector 34a. On the other hand, the loading position is also detected by the angle detector 56 as the rotation angle of the main gear 46.

FIG. 7 shows a loading motor 43 and a drive motor.
The drive control block diagram of 32a is shown. In the figure, an output signal a1 of an angle detector 56 as a loading position detector and an angle detector as a rotary drum tilt direction angle detector
The output signal b1 of 34a is compared and calculated by the comparator 57, and the result is input as the input signal b2 to the drive motor 32a.

At this time, in order to form an ideal tape path even during loading, the relations between the loading position and the inclination direction angle of the rotary drum 2 are satisfied by the equations (1) to (5) shown in the conventional example. It has to be something that does. Here, in the above equations (1) to (5), instead of setting the incident angle of the inclined tape guide to be a ξ = 0 constant, the inclination direction angle ψ of the rotary drum 2 is set as an unknown value and the solution (coordinate conversion according to the inclination direction angle is performed. Do). FIG. 8 shows the inclination angle ψ of the rotary drum 2 and the drive motor 32a with respect to the winding angle of the tape 4 on the rotary drum 2 in the specifications of this deck.
It is a figure which showed the relationship with the rotation angle of [compared with the tape drawer body 7]. In the figure, with respect to the winding angle of the tape 4 on the rotary drum 2, (a) is the loading position of the tape drawer 7, (b) is the rotation angle of the drive motor 32a, and (c) is the same.
Indicates the tilt direction angle ψ of the rotary drum 2. The loading position (a) of the tape withdrawing body 7 changes in proportion to the winding angle, and the solution of the inclination direction angle ψ of the rotary drum 2 is obtained from the above equations (1) to (5). The approximate curve (c) is fitted so as to draw a smooth change locus that can be controlled by the tilt direction control means 21 in this embodiment. To achieve this, the rotation angle (b) of the drive motor 32a is set as shown in the figure. In this embodiment, the changing speed of the rotation angle of the drive motor 32a is reduced in the first half and the latter half of the tape loading. It will be set so as to allow. In the comparator 57, the output signals a1 and b1 of the two angle detectors 56 and 34a are compared and calculated as the input signal b2 to the drive motor 32a so as to realize the relationship between (a) and (b).

Subsequently, after the intermediate loading stage of FIG. 2, the tape drawers 7, 8, 9 are stopped by the stoppers 670, 680 ,.
When the tape 4 reaches 690 and the winding of the tape 4 onto the rotary drum 2 is completed, the inclination angle ψ3 of the rotary drum 2 is 11 as shown in FIG.
Set to 0 ° to form a given tape path. Then, the loading motor 43 is stopped to complete the tape loading operation.

On the contrary, when performing the unloading operation from the loading state, the operation opposite to the above-mentioned tape loading operation is performed. That is, the tape drawer 7,
In response to the movement of 8 and 9 in the direction of the cassette, the rotating drum 2 on the drum base 36 is changed in the counterclockwise direction by the inclination direction control means 21. That is, the inclination direction angle of the rotary drum 2 is sequentially changed in the same rotation direction as the traveling direction of the tape pull-out body 7 on the supply side with respect to the rotary drum 2.

In an actual magnetic recording / reproducing apparatus, a tape path is constructed in cooperation with a tape driving capstan, a pinch roller, etc. in addition to the above-mentioned rotary drum and tape guide, but these are omitted in this figure. I am doing it.

In the structure of the above embodiment, in this embodiment, the flange reaction force acting on the tape at the flange portion of the tape guide is calculated and used as an index corresponding to the stress acting on the tape. In general, the tape tension during loading tends to be higher near the tape guide closer to the reel on the winding side, but the flange reaction force has a similar tendency correspondingly. Therefore, the flange reaction force of the tape guide 90 of the tape pull-out body 9 located closest to the winding side in the tape path of FIG. 3 may be examined.

FIG. 9 shows the tape guide 90 at the four stages during loading according to the deck specifications in this embodiment.
Is a simulation of the flange reaction force acting on the tape at the flange portion of. This simulation
The tape path from the supply-side reel 5 to the winding-side reel 6 is developed, the shape of the tape path is replaced with a model with fixed beams at both ends, and the flange reaction force generated by the displacement amount at each flange is calculated. is there. Originally, the flange reaction force should be 0 in the ideal tape path, but it does not become 0 completely due to the fact that the angle in the inclination direction of the rotary drum 2 is changed by an approximate curve and the mechanical convenience.
However, according to this embodiment, the effect of reducing the flange reaction force by 1/5 to 1/10 can be seen as compared with the case of the normal tape loading mechanism in which the rotary drum 2 is fixed.

Example 2. In the first embodiment, the rotary drum 2
The drive in the tilt direction is performed by using the dedicated motor 32a, and this drive circuit is electrically controlled in the configuration of FIG. 7, but the drive circuit is not necessarily limited to such a configuration. 10 and 11
FIG. 10 shows another embodiment of the present invention. FIG. 10 is a view of the deck as seen from the back side, and FIG. 11 is a schematic view of the main part of the inclination direction control means 211. In the figure, those parts which are the same as or correspond to those of the first embodiment are designated by the same reference numerals, and a description thereof will be omitted. 501 is a gear that is pivotally supported by the shaft 500 and meshes with the gear 48, and 51 is a cam groove formed in the gear 501. Reference numeral 52 is a gear that engages with the cam groove 51 by a pin 521 and rotates about a shaft 520, 38b is a pinion that meshes with the gear 52, and 37 is a gear formed on the outer periphery of the drum base 36. The cam groove 51
Is formed in such a shape that the rotation of the pinion 38b with respect to the rotation angle of the main gear 46 is the same as the rotation angle (b) of the drive motor 32a shown in FIG.

The operation will be described. The process from the unloading state to the loading state of the tape drawers 7, 8 and 9 is the same as in the first embodiment. Gear train at this time
By rotating 44 to 49, the gear 501 also rotates counterclockwise in FIG. This causes the gear 52 to move into the cam groove 51.
In accordance with the shape of the rotary drum 2, it rotates counterclockwise, and the angle of inclination of the rotary drum 2 changes via the pinion 38b and the gear 37. FIG. 10 shows a state in which the above operation is almost completed. At this time, as in FIG. 8 in the first embodiment, the inclination direction angle (c) of the rotating drum 2 is set as an approximate solution to the loading position (a) of the tape drawer 7, and this is set as the shape of the cam groove 51. Realized by.

With the above configuration, as in the first embodiment,
Since the tilt direction angle of the rotary drum 2 changes in response to the tape loading operation of the tape drawers 7, 8, and 9, the stress acting on the tape is significantly reduced, and the effect of preventing the tape damage is obtained.

Example 3. In the first and second embodiments, the tilt direction of the rotary drum 2 is variable, but it is also possible to configure the tape path by changing the tilt angle of the rotary drum 2 by the tilt angle control means. 12 to 14 show another embodiment of the present invention. FIG. 12 is a view showing an unloading state of a tape loading mechanism including the tilt angle control means, and FIGS. 13 and 14 are tilt angle control means 22. FIG. In the figure, those parts which are the same as or correspond to those of the first and second embodiments are designated by the same reference numerals, and a description thereof will be omitted. In the figure, 27 is a pair of support stands erected on the deck base 1, 28 is a bearing member provided on the support base 27, 29 is fixed to the side surface of the lower drum 24, and is rotatable by the bearing member 28. A swing shaft 30 supported coaxially with the swing shaft 29, a swing shaft 30 provided coaxially with the swing shaft 29 at a position facing the center of the lower drum, and a gear 31 fixed coaxially with the swing shaft 29. , 32b
Is a drive motor installed on the deck base 1, and a worm gear 33 coaxially fixed to the output shaft meshes with the gear 31. An angle detector 34b is installed on the deck base 1, and can detect the inclination angle of the rotary drum 2 via the coupling 35b and the swing shaft 30. Reference numeral 56 denotes an angle detector coupled to the main gear 46 via a coupling 56a, which detects the rotation angle of the main gear 46 and acts as a loading position detector. 57 is the above two angle detectors 34
It is a comparator electrically connected to b and 56 for comparing and calculating the detected angles.

Next, the operation of the tilt angle control means 22 will be described with reference to FIG. First, in the unloading state shown in FIG. 14A, the deck base 1 of the rotating drum 2 is
The inclination angle α1 with respect to is larger than that when the loading is completed, and is set to 25 °, for example. Then, in response to the tape loading operation of the tape drawers 7, 8 and 9, the worm gear 33,
The rotary drum 2 swings via the gear 31 and the swing shaft 29, and the inclination angle with respect to the deck base 1 changes in a direction that decreases.

At this time, in order to form an ideal tape path even during loading, the relationship between the loading position and the inclination angle of the rotary drum 2 satisfies the expressions (1) to (5) shown in the conventional example. I have to make one. Here, instead of setting the incident angle of the inclined tape guide to the ξ = 0 constant in the above equations (1) to (5), the inclination angle α of the rotating drum 2 is used as an unknown value to obtain the solution. Figure 15
Is tape 4 to rotating drum 2 in the specifications of this deck
6 is a diagram showing the relationship between the winding angle of the rotary drum 2 and the rotation angle of the drive motor 32b with respect to the winding angle of the tape drawing body 7 in comparison. In the figure, with respect to the winding angle of the tape 4 on the rotary drum 2, (a) is the loading position of the tape drawer 7, (b) is the rotation angle of the drive motor 32b, and (c) is the rotary drum 2. The inclination angle α is shown.
The loading position (a) of the tape drawer 7 changes in proportion to the winding angle.
The solution of the inclination angle α of the rotary drum 2 is obtained from the equation (5), and the approximate curve (c) is fitted so as to draw a smooth change locus controllable by the inclination angle control means 22 in this embodiment. In order to achieve this, the rotation angle (b) of the drive motor 32b is set as shown in the figure. In this embodiment, the changing speed of the rotation angle of the drive motor 32b is reduced in the first half and the latter half of the tape loading. It will be set so as to allow. The tilt angle of the rotary drum 2 is detected by the angle detector 34b. The loading position of the tape drawer 7 is the main gear
The angle detector 56 detects the rotation angle of 46. These are compared and calculated by the comparator 57, and the relationship between (a) and (b) of FIG. 15 is realized. As a result, the tilt angle of the rotary drum 2 is controlled to a value most suitable for each position during loading.

When the loading is completed, the inclination angle of the rotary drum 2 is simultaneously set to a predetermined value α as shown in FIG. 14 (b).
2. For example, 6.8 ° is reached, and the rotation of the drive motor 32b is stopped.

On the contrary, when performing the unloading operation from the loading state, the tilt angle control means 22 performs the reverse operation. That is, the inclination angle of the rotary drum 2 changes in the increasing direction.

Similar to FIG. 9 in the first embodiment, FIG. 16 is a simulation of the flange reaction force acting on the tape at the flange portion of the tape guide 90 in the four stages of loading in the specifications of this deck. is there.
Originally, the flange reaction force should be zero in the ideal tape path, but it is completely zero due to the fact that the inclination angle of the rotating drum 2 is changed with an approximate curve and the mechanism is convenient.
Does not mean However, according to the third embodiment, similar to FIG. 9, the effect of reducing the flange reaction force can be seen as compared with the case of the normal tape loading mechanism in which the rotary drum 2 is fixed.

With the above construction, the inclination angle of the rotary drum 2 changes in response to the tape loading operation of the tape drawers 7, 8 and 9, so that the first and second embodiments can be performed.
Similarly, the stress acting on the tape is greatly reduced, and the effect of preventing the tape damage is obtained.

Example 4. In the third embodiment, the rotary drum 2
The tilt angle drive is performed by using the dedicated motor 32b, and this drive is electrically controlled, but the drive is not necessarily limited to such a configuration. 17 and 18 show another embodiment of the present invention. FIG. 17 is a view of the deck as seen from the back side, and FIG. 18 is a schematic view of the main part of the tilt angle control means 221. In the figure, those parts which are the same as or correspond to those of the first to third embodiments are designated by the same reference numerals, and a description thereof will be omitted. In the figure,
Reference numeral 491 is a gear that is pivotally supported by the shaft 490 and meshes with the gear 48, and 492 is a cam groove formed on the side surface of a cylindrical member 493 coaxial with the gear 491. Reference numeral 27 denotes a pair of support bases provided upright on the deck base 1, 28 denotes a bearing member provided on the support base 27, 29 is fixed to a side surface of the lower drum 24, and is rotatably supported by the bearing member 28. An oscillating shaft, 55 is an arm having one end fixed to the oscillating shaft 29, and 551 is a pin erected on the other end of the arm 55, which engages with the cam groove 492. The cam groove 49
The shape of 2 is formed such that the rotation of the swing shaft 29 with respect to the rotation angle of the main gear 46 becomes the same as the rotation angle of the drive motor 32b of FIG. 15 in the third embodiment.

The operation will be described. In the unloading state, the inclination angle α1 of the rotary drum 2 is larger than that at the completion of loading, and is set to 25 °, for example. The history of the tape drawers 7, 8, 9 from the unloading state to the loading state is described in Examples 1 to 3
Is the same as. At this time, the rotation of the gear 491 causes the cam groove 49
2 rotates, and the arm 55 rotates clockwise in FIG. As a result, the rotary drum 2 also rotates clockwise and the inclination angle becomes smaller. At this time, FIG.
Similar to the above, the loading position of the tape drawer 7 (a)
As an approximate solution to, the inclination angle (c) of the rotating drum 2
Is set and this is realized by the shape of the cam groove 492. When the loading is completed, the inclination angle α2 of the rotary drum 2 also reaches a predetermined value, for example, 6.8 °.

With the above configuration, as in the third embodiment,
Since the inclination angle of the rotary drum 2 changes in response to the tape loading operation of the tape drawers 7, 8, and 9, the stress acting on the tape is significantly reduced, and the effect of preventing the tape damage is obtained.

Example 5. Also, from the initial stage of loading, a so-called external tape guide that contacts the tape from outside the tape path other than the tape drawer is made to act as a tape guide that constitutes the tape path. By using a control means that is variable during loading, it is possible to realize tape loading with less tape damage as in the first to fourth embodiments.

19 to 26 show an embodiment of the tape guide control means for changing the position, the inclination angle and the inclination direction of the tape guide 12, for example. 150 in FIGS.
Is the tape guide control means. 22 is a schematic view of the main parts of the tape guide control means 150, and FIG. 23 is an exploded perspective view thereof. In the figure, 16 is a fulcrum shaft erected on the deck base 1, 17 is a first arm whose one end is rotatably supported by the fulcrum shaft 16, and 170 is a shaft 173 at the other end of the first arm 17.
Is a pivotally supported guide base, 175 is a spring which is engaged between the first arm 17 and the guide base 170 and biases the guide base 170 in the counterclockwise direction in the figure, and 120 is a guide. A second arm rotatably supported by a shaft 172 on the base 170, 12 is a tape guide erected on the second arm 120, and 125 is between the guide base 170 and the second arm 120. Is a spring that is engaged with and biases in the direction of increasing the inclination angle η in the figure. 18 is the arm 17 deck base 1
These are guide pins implanted on the side, and the tape guide 12 and the guide pin 18 rotate around the fulcrum shaft 16. These fulcrum axes
16, first arm 17, guide base 170, second arm
120 and the tape guide 12 are collectively referred to as tape guide changing means 15. Reference numeral 155 is a guide member provided on the deck base 1, 151 is in contact with the contact portion 121 of the second arm 120, and the inclination angle of the tape guide 12 erected on the second arm 120 is changed depending on the loading position. The contact surface 152 whose height is set so that it contacts the contact portion 122 of the second arm 120, and the tape guide 12 that stands on the second arm 120
Is a contact surface whose shape is set so that the angle of the tilting direction of is changed depending on the loading position. 1a is deck base 1
The guide pin 18 rotates in the hole 1a by the hole formed in the hole. 69 is a guide groove and 4 is a tape. In this embodiment, the rotary drum 2 is fixed to the deck base 1 with a predetermined angle.

FIG. 24 is a view of the deck as seen from the back side. In the figure, the same or corresponding parts as those of the above-mentioned first to third embodiments are designated by the same reference numerals and the description thereof will be omitted. In the figure,
Reference numeral 461 denotes a main gear that is pivotally supported by the shaft 460 and meshes with the gear 45. Reference numeral 46a denotes a cam groove formed in the main gear 461, which engages with the guide pin 18 of the tape guide changing means 15. Position of the tape guide 12 in the loading process,
The tilt angle and the tilt direction angle are obtained as follows. That is, in the tape path from the rotary drum 2 to the tape drawer body 8, the position of the tape drawer body 8 is set so as to satisfy the conditional expressions (3), (4), and (5) that are not twisted in the conventional example. , The inclination angle and the inclination direction angle are calculated, and in the tape path from the tape drawer 8 to the tape guide 12, the tape drawer 8 is replaced with the rotary drum 2 and the specifications are applied to the above (1) to (5). ) The position, tilt angle, and tilt direction angle of the tape guide 12 are determined so as to satisfy the equation. Then, based on these results, the shapes of the two contact surfaces 151, 152 of the guide member 155 and the shape of the cam groove 46a are set. The tape guide changing means 15, the guide member 155, the hole 1a, and the cam groove 46a constitute the tape guide control means 150.

The main specification of the tape guide control means 15 here is that the distance between the fulcrum shaft 16 and the tape guide 12 is 5.5 mm.
, The diameter of the tape guide 12 is 2 mm, the inclination angle of the tape guide 12 is 25.2 ° when the loading is completed, and the inclination direction (Example 1
The angle formed by the arrow from the X-axis in the drawing to the arrow indicating the inclination direction of the tape guide 12 is 57.5 ° similarly to the inclination angle of the drum 2).

The operation will be described. FIG. 19 shows an unloading state in which the cassette 3 is removable and the tape drawers 7, 8 and 9 are inside the cassette. At this time, the tape guide control changing means 15 is at the most rotated position in the clockwise direction in the figure as shown in FIG. When the tape loading operation is started via the loading motor 43 from this state, the tape pull-out bodies 7, 8, 9 start moving, and the tape guides 70, 80, 90 pull out the tape 4 from the cassette 3.

Next, when the tape 4 is pulled out, the tape 4 reaches a state where it is also in contact with the tape guide control means 15 as shown in FIG. At this time, tape guide 12
The inclination angle and the inclination direction angle are set to 8 ° and −7 °, respectively. FIG. 22 shows the tape guide control means at this time.
It shows around 15. As the loading progresses further, the tape guide control means 15 will move to the cam groove of the main gear 461.
It rotates counterclockwise according to the shapes of 46a and the guide member 155.

FIG. 25 shows the tape guide with respect to the winding angle of the tape 4 on the rotary drum 2 in the specifications of this deck.
12 tilt angles η, tilt direction angles γ and tape guide variable means
It is the figure which showed the relationship with the rotation angle of 15 in contrast with the tape drawer 7. In the figure, tape 4 to rotating drum 2
(A) is the loading position of the tape drawer 9, (b) is the rotation angle of the tape guide changing means 15, and (c) is the inclination angle η and inclination angle γ of the tape guide 12. Is shown. The loading position (a) of the tape drawer 9 changes in proportion to the winding angle. On the other hand, from the equations (1) to (5) shown in the conventional example, the tape guide is shown.
The solution of the tilt angle η and the tilt direction angle γ of 12 is obtained, and the approximate curve (c) is fitted so as to draw a smooth change locus that can be controlled by the tape guide control means 150 in this embodiment, and the tape is applied to this. Guide changing means 15 is cam groove 46
Rotate as shown in (b) by a. That is, this rotation and the two contact surfaces 151 and 152 of the guide member 155 interact with each other, and the tape guide 12 that substantially satisfies the above equations (1) to (5) as shown by the curve (c). Inclination angle η and inclination direction angle γ
You will get

Further, the tape loading operation progresses, the tape drawers 7, 8, 9 reach the stoppers 670, 680, 690, the tape 4 is completely wound around the rotary drum 2, and the rotary drum 2 and the tape guide 70, A predetermined tape path is formed at 80, 81, 11, 12, 90. Where the loading motor
43 stops and completes the tape loading operation. Figure 2
1 indicates this state. In the unloading operation, the reverse operation to the above operation is performed as in the first to fourth embodiments.

With such a structure, the external tape guide 12 can obtain a large winding angle from the initial stage of loading, and further, by changing the position, the inclination angle, and the inclination direction angle, the ideal tape path can be formed. The configuration can be facilitated.

Further, FIG. 26 is a simulation of the flange reaction force acting on the tape at the flange portion of the tape guide 90 in the four stages of loading in the specification of this deck, as in FIG. 9 in the first embodiment. is there.
Originally, the flange reaction force should be 0 in the ideal tape path, but it does not become 0 completely due to the fact that the tape guide 12 is changed by an approximate curve and the mechanical convenience. However, according to the fifth embodiment, as shown in the figure, the effect of reducing the flange reaction force can be seen as compared with the case of the normal tape loading mechanism in which the tape guide 12 is fixed.

Example 6. The above-mentioned Examples 1 to 5 are examples in which each is carried out independently, but it is clear that even if a plurality of these are carried out in combination, it is further effective in preventing tape damage.

For example, in the above-described first to fourth embodiments, one of the tilt direction angle and the tilt angle of the rotary drum 2 is changed during the loading, but the tilt direction angle and the tilt angle are combined together. FIG. 27 shows an embodiment in which both the angles are changed. If both the inclination direction angle ψ and the inclination angle α of the rotating drum 2 are values that change sequentially as unknowns, the rotating drum 2 in the above equations (1) to (5)
The incident angle of the tape guide adjacent to the can be ξ = 0, and the incident angle S of the rotating drum 2 can be a constant. Therefore, the tape 4 can be always wound along the lead 25 of the rotary drum 2. In the figure,
The tilt angle control means 22 is mounted on the tilt direction control means 21.
Drive motors 32a, 32b supported by 27 and independent of each other
And angle detectors 34a and 34b, and a comparator 57
The tilt angle and the tilt direction angle are controlled as in the first and third embodiments.

In the sixth embodiment, the drive motor 32a independently drives the rotary drum 2 in the tilt direction and tilt angle.
, 32b, for example, Example 2 and Example 4
Similarly to the above, the gear 52 and the gear 491 may be included.

[0065]

As described above, according to the present invention, even in the magnetic recording / reproducing apparatus having the tape path in which the tape guide adjacent to the rotary drum is the roller type, the tape guide is always brought close to the ideal tape path even during the loading process. Since the rotary drum and the tape guide are moved, the tape is prevented from being damaged without undue stress being applied to the tape.

[Brief description of drawings]

FIG. 1 is a plan view showing an unloading state of a tape loading mechanism according to a first embodiment of the present invention.

FIG. 2 is a plan view showing an intermediate stage of loading of the tape loading mechanism according to the first embodiment of the present invention.

FIG. 3 is a plan view showing a loading completion state of the tape loading mechanism according to the first embodiment of the present invention.

FIG. 4 is a view of the tape loading mechanism as seen from the back surface of the deck according to the first embodiment of the present invention.

FIG. 5 is a schematic view of a main portion showing a tilt direction control unit of the rotary drum according to the first embodiment of the present invention.

FIG. 6 is a perspective view showing the operation of the inclination direction control means of the rotary drum in the first embodiment of the present invention.

FIG. 7 is a drive control block diagram of a loading motor 43 and a drive motor 32a according to the first embodiment of the present invention.

FIG. 8 is a diagram showing a first embodiment of the present invention, the loading position and the drive motor 32 with respect to the tape winding angle of the rotary drum.
It is a figure which shows the relationship between the rotation angle of a, and the inclination direction angle of a rotating drum.

FIG. 9 is a diagram showing the relationship between the flange reaction force acting on the tape at the flange portion of the tape guide 90 during loading and the tape winding angle of the rotary drum in Embodiment 1 of the present invention.

FIG. 10 is a view of the tape loading mechanism as seen from the back surface of the deck according to the second embodiment of the present invention.

FIG. 11 is a schematic view of a main part showing a tilt direction control unit of a rotary drum according to a second embodiment of the present invention.

FIG. 12 is a plan view showing an unloading state of the tape loading mechanism according to the third embodiment of the present invention.

FIG. 13 is a schematic view of a main part showing a tilt angle control means of a rotary drum in a third embodiment of the present invention.

FIG. 14 is a perspective view showing the operation of the tilt angle control means for the rotary drum in the third embodiment of the present invention.

FIG. 15 is a loading position and drive motor with respect to the tape winding angle of the rotary drum in the third embodiment of the present invention.
It is a figure which shows the relationship between the rotation angle of 32b, and the inclination angle of a rotating drum.

FIG. 16 is a diagram showing the relationship between the flange reaction force acting on the tape at the flange portion of the tape guide 90 during loading and the tape winding angle of the rotary drum in Embodiment 3 of the present invention.

FIG. 17 is a diagram of the tape loading mechanism as seen from the back surface of the deck in Embodiment 4 of the present invention.

FIG. 18 is a schematic view of a main portion showing a tilt angle control means for a rotary drum in Embodiment 4 of the present invention.

FIG. 19 is a plan view showing an unloading state of the tape loading mechanism including the tape guide control means according to the fifth embodiment of the present invention.

FIG. 20 is a plan view showing an intermediate stage of loading of the tape loading mechanism including the tape guide control means in the fifth embodiment of the present invention.

FIG. 21 is a plan view showing a loading completion state of the tape loading mechanism including the tape guide control means in the fifth embodiment of the present invention.

FIG. 22 is a schematic view of a main part showing a tape guide control means in a fifth embodiment of the present invention.

FIG. 23 is an exploded perspective view of the tape guide control means according to the fifth embodiment of the present invention.

FIG. 24 is a diagram of the tape guide control means as seen from the back surface of the deck according to the fifth embodiment of the present invention.

FIG. 25 is a diagram showing a relationship among a tape winding angle of a rotary drum, a loading position, a rotation angle of a tape guide changing unit 15, an inclination angle of a tape guide 12, and an inclination direction angle in Example 5 of the invention. is there.

FIG. 26 is a diagram showing the relationship between the flange reaction force acting on the tape at the flange portion of the tape guide 90 during loading and the tape winding angle of the rotary drum in Embodiment 5 of the present invention.

FIG. 27 is a schematic view of a main portion showing a tilt direction and a tilt angle control means of a rotary drum according to a sixth embodiment of the present invention.

FIG. 28 is a plan view showing an unloading state of the conventional tape loading mechanism.

FIG. 29 is a plan view showing a loading completion state of the conventional tape loading mechanism.

FIG. 30 is a main part schematic diagram showing a tape guide control means in a conventional tape loading mechanism.

FIG. 31 is a diagram showing a relationship between a tape twist during loading and a tape winding angle of a rotary drum in a conventional tape loading mechanism.

[Explanation of symbols]

 1 Deck Base 2 Rotating Drum 3 Cassette 4 Tape 7, 8, 9 Tape Drawer 11, 12, 70, 80, 81, 90 Tape Guide 67, 68, 69 Guide Means 43 Drive Means 21 Tilt Direction Control Means 22 Tilt Angle Control Means 150 Tape guide control means

Claims (3)

[Claims] 1. A rotating drum provided with a magnetic head is arranged at a predetermined angle with respect to a reference surface, and a tape drawer is arranged to wind a tape around the rotating drum in a spiral shape over a predetermined angle. The tape drawer moves back and forth along a predetermined path to pull out the tape from the cassette, wind the tape around the rotary drum, and guide means and driving means for storing the tape in the cassette. In the tape loading mechanism, in response to the tape loading operation, a tilt direction in which the tilt direction angle of the rotary drum is sequentially changed in the same rotation direction as the moving direction of the tape drawer on the supply side with respect to the rotary drum. A tape loading mechanism comprising a control means. 2. A tape loading mechanism comprising tilt angle control means for sequentially changing the tilt angle of the rotary drum in a direction of decreasing at the time of loading in response to the tape loading operation. 3. In response to the tape loading operation, a tape guide other than the drawer body that comes into contact with the tape from the outside of the tape path sequentially changes the position, tilt angle, and tilt direction angle while intervening in the tape loading operation. The tape loading mechanism according to claim 1, further comprising tape guide control means.