JPH11125317A - Eccentric driving device, and easing device for loom using it - Google Patents

Abstract

PROBLEM TO BE SOLVED: To adjust the easing amount of a tension roll by changing the eccentric amount of an output shaft during a loom is operated. SOLUTION: First and second shafts 11, 12 are combined with each other so as to be relatively rotated, and a displacement member 14 is rotatively mounted in the eccentric pin 12b of the second shaft 12. The displacement member 14 can make the output shaft 13 off-center from an axial center A by relatively rotating the first and second shafts 11, 12, and can make the output shaft 13 turn while retaining an eccentric amount constantly by synchronously rotating the first and second shafts 11, 12.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an eccentric drive device capable of freely adjusting the amount of eccentricity of an output shaft during operation, and to an easing device for a loom using the same.

[0002]

2. Description of the Related Art Conventional eccentric drive mechanism (crank mechanism)
It is known to use a screw shaft to change the amount of eccentricity of the output shaft (FIG. 12).

In this device, a disk 2 is fixed to a drive shaft 1,
A screw shaft 3 passing through the axis of the drive shaft 1 is horizontally mounted on the disk 2, and a screw member 5 for mounting an output shaft 4 is mounted on the screw shaft 3. The output shaft 4 is connected to a slide piece 7 via a connection rod 6, and the slide piece 7 is connected to a guide 8
Can reciprocate back and forth along.

In the slide piece 7, the drive shaft 1 has an arrow Ka.
When it rotates in the direction, it reciprocates in the direction of arrow Kb in the guide 8 via the connecting rod 6. The reciprocating stroke of the slide piece 7 can be adjusted by turning the screw shaft 3 to move the screw member 5 and changing the amount of eccentricity of the output shaft 4.

[0005]

According to the prior art, the amount of eccentricity of the output shaft 4 can be changed only when the drive shaft 1 is stopped. 7 cannot be adjusted at all.

Accordingly, an object of the present invention is to address the problems of the prior art by combining the first and second shafts and the displacement member so that even when the mechanical device is in operation,
An object of the present invention is to provide an eccentric drive device capable of freely adjusting an eccentric amount of an output shaft and an easing device for a loom using the same.

[0007]

Means for Solving the Problems To achieve the above object, a first invention according to the present application comprises a first shaft and a second shaft combined with the first shaft so as to be rotatable relative to the first shaft. And a displacement member having an output shaft. The gist of the displacement member is to change the amount of eccentricity of the output shaft by the relative rotation of the first and second shafts.

The displacement member may be a rotatable member rotatably mounted on the eccentric pin of the second shaft and rotating via the first shaft.

Further, the displacement member has a gear for setting the radius of the pitch circle to に 対 し て with respect to the internal gear attached to the first shaft, and the output shaft stands upright on the pitch circle of the gear. You may.

The displacement member can be a swing member that swings via the eccentric pins on the first and second shafts.

The first axis may move relative to the second axis by relatively moving in the axial direction of the second axis, and the second axis may move in the direction of movement of the output axis. May be provided.

The gist of the second invention is to provide an eccentric drive device according to the first invention, an interlocking mechanism connected to the eccentric drive device, and a tension roll attached to the interlocking mechanism.

[0013]

According to the first aspect of the present invention, the output shaft is provided on the displacement member, and the displacement member changes the amount of eccentricity of the output shaft by the relative rotation of the first and second shafts.
Therefore, even when both the first and second shafts are rotating, the eccentricity of the output shaft can be freely changed by rotating the output shaft relative to each other.

When the displacement member is a rotating member, the displacement member is rotated by the first and second shafts to rotate relative to each other.
, And can rotate around the eccentric pin of the second shaft to change the amount of eccentricity of the output shaft.

If the radius of the pitch circle of the gear of the displacement member is set to 1/2 of that of the internal gear on the first shaft side, and the output shaft is provided on the pitch circle of the gear, the output shaft will have an eccentric amount. Regardless of size,
Linearly moving in a specific radial direction of the first axis,
The relationship between the relative rotation angle of the shaft and the amount of eccentricity of the output shaft can be markedly simplified.

Since the displacement member is a swinging member, the entire device can be reduced in size and weight, and can be adapted to high-speed rotation.

When the first shaft is relatively moved in the axial direction of the second shaft and relatively rotated, the first shaft may be driven linearly, and a simple linear drive source can be used. However, the first shaft at this time is driven to rotate integrally with the second shaft.

If a guide portion is provided on the second shaft, the guide portion regulates the moving direction of the output shaft, and the output shaft is restricted in the moving direction regardless of the magnitude of the eccentricity. The relationship between the relative rotation angle of the second shaft and the amount of eccentricity of the output shaft can be simplified.

According to the structure of the second invention, the tension roll can be caused to perform an easing movement by the eccentric drive device according to the first invention via the interlocking mechanism. Therefore, the tension roll can freely change the easing amount even during the operation of the loom. In addition, the easing amount at this time may be changed not only according to a decrease in the winding diameter of the warp beam, but also for each opening of the warp.

[0020]

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

The eccentric drive device 10 includes a first shaft 11, a second shaft 11,
And a displacement member 14 having an output shaft 13 (FIGS. 1 and 2). However, the eccentric drive device 10
Connected to the tension roll 41 via the interlocking mechanism 30,
It constitutes the easing device of the loom.

The first shaft 11 has an internal gear 11b having a pitch circle radius R at a large diameter portion on the distal end side, and a pulley 11c fixed to a small diameter portion on the base side. Also,
The first shaft 11 is connected to the motor 21 via a pulley 11c, a belt 21b, and a pulley 21a, and is rotatably supported on a frame of a loom (not shown) via a bracket (not shown).

The second shaft 12 is rotatably inserted through the axis A of the first shaft 11 to form a double shaft together with the first shaft 11. At the tip of the second shaft 12, the first shaft 11
A disk 12a to be stored in the large-diameter portion is attached,
The disk 12a has an eccentric pin 12 eccentric from the axis A.
b is erected. Also, at the base of the second shaft 12,
The pulley 12c is fixed. The second shaft 12 is connected to the motor 22 via a pulley 12c, a belt 22b, and a pulley 22a.

The displacement member 14 is rotatably mounted on the eccentric pin 12b of the second shaft 12. Displacement member 1
Reference numeral 4 denotes a gear 14a having a radius r of a pitch circle meshing with the internal gear 11b is formed on the disk 12a side, and an output shaft 13 parallel to the axis A stands on the pitch circle of the gear 14a. The radius r of the pitch circle of the gear 14a is set to r = R / 2 with respect to the radius R of the pitch circle of the internal gear 11b.

Now, the output shaft 13 of the displacement member 14 is
The upper position is defined as a reference position C (see FIG. 3).
(A)). At this time, the gear 14a meshes with the internal gear 11b at the mesh point Go, and the output shaft 13 has an eccentricity d = 0 from the shaft center A. Therefore, when the first and second shafts 11 and 12 rotate synchronously in the same direction (directions of arrows K1 and K2 in FIG. 1A), the displacement member 14 keeps the output shaft 13 on the axis A. , The eccentricity d = 0.

When the second shaft 12 is rapidly rotated with respect to the first shaft 11 to cause relative rotation of the first and second shafts 11 and 12, the eccentric pin 12b moves around the axis A. The gear 14 rotates (in the direction of arrow K3 in FIG. 3A, FIG. 3B).
a rotates around the eccentric pin 12b while meshing with the internal gear 11b (the direction of arrow K4 in FIG. 3A). Therefore, the output shaft 13 moves from the shaft center A by the rotation of the gear 14a (in the direction of the arrow K5 in FIG. 3B), and the shaft center A
Can be realized. However, FIG.
Shows only the relative rotation of the first and second shafts 11 and 12.

On the basis of the reference position C, the second shaft 12,
Relative rotation angle α of eccentric pin 12b, rotation angle β of gear 14a
And the mesh point G1 of the gear 14a with the internal gear 11b.
, The angle θ of the straight line AP1 with respect to the straight line AGo of the reference position C is θ = α +
(Π / 2−β / 2). The peripheral length of the internal gear 11b and the gear 14a between the meshing points Go and G1 is Rα = rβ, and the eccentricity d of the output shaft 13 is d = 2rsin (β /
2). On the other hand, since r = R / 2, β / 2 = R
α / (2r) = α holds, and θ = π / 2. That is, the output shaft 13 moves on the straight line AP1 perpendicular to the straight line AGo regardless of the relative rotation angle α of the second shaft 12 and the eccentric pin 12b. Can move linearly in a specific radial direction of the shaft 11.
The eccentricity d is d = 2r sin α, which is a sine function of the relative rotation angle α.

In this way, the output shaft 13 can arbitrarily change the eccentricity d by rotating the first and second shafts 11 and 12 relative to each other. The output shaft 13
Are eccentric by the amount of eccentricity d, then the first and second shafts 11,
By returning the rotation to the synchronous rotation, a turning movement with a radius d around the axis A can be performed (a dashed line in FIG. 3B). If the speed of the second shaft 12 is increased with respect to the first shaft 11, the output shaft 13 is eccentric in the direction of the arrow K5 in FIG. If the speed 12 is reduced, the eccentricity is opposite to the direction of the arrow K5.

However, the internal gear 11b and the gear 14a are
The radius of each pitch circle may be R ≠ 2r. At this time, the angle θ changes according to the relative rotation angle α and the eccentricity d. That is, the output shaft 13 does not move in a specific radial direction with respect to the first shaft 11, but can change the amount of eccentricity d according to the relative rotation angle α. When it is not necessary to set the amount of eccentricity d = 0, the output shaft 13 may be located at a position other than on the axis A at the reference position C. Conversely, by appropriately setting the eccentric position of the eccentric pin 12b from the axis A,
The amount of eccentricity d of the output shaft 13 irrespective of the radius r or R of the pitch circle
= 0 can be realized.

The interlocking mechanism 30 includes a rod 31 and a lever 3
2, 34, stud 33, arm 35, bracket 3
6. It has a tension rod 37 (FIGS. 1 and 4).

The lever 32 is connected to the output shaft 13 via a rod 31. The base of the rod 31 is connected to the output shaft 13 via a self-aligning bearing 31a and a bolt 13a. The connecting holes 31c, 31c... Are formed at the distal end of the rod 31, and the rod 31 can be connected to the distal end of the lever 32 via a pin 32c and a nut 32d by using an arbitrary hole 31c. Can be rotatably connected to The rod 31 is provided with the self-aligning bearing 3
The length can be freely adjusted by changing the screwing amount with respect to 1a and selecting the holes 31c.

The lever 32 is fixed to the distal end of a stud 33 attached to the distal end of the arm 35, and forms a swing member integrated with the arm 35. The arm 35 is provided with a support pin 36 of a bracket 36 fixed to a frame of a loom (not shown).
a swingably supported. Then, lever 32,
The arm 35 can swing back and forth integrally about the support pin 36a through the rod 31 in conjunction with the turning movement of the output shaft 13.

The lever 34 is rotatably supported at an intermediate portion of the stud 33. The lever 34 has a support hole 34b
The shaft 41a of the tension roll 41 is supported via the shaft. At the lower part of the lever 34, an arm 34a extending diagonally downward
The lower end of the tension rod 37 is rotatably connected to the tip of the arm 34a via a pin 34c. The upper end of the tension rod 37 with the load cell 37a is swingably supported by a support pin 36b of the bracket 36.

The tension roll 41 is rotatably supported by a shaft 41a, and has warps W, W,. In addition, the warp W,
W ... are unwound from the warp beam B, pulled out through a tension roll 41 to a heald (not shown) and a weave, and wound up as a woven fabric. Also, the load cell 37a
The tension of the warps W, W ... can be detected electrically.
However, FIG. 1 shows only the shaft 41 a on one side of the tension roll 41, the eccentric drive device 10, and the interlocking mechanism 30. That is, the interlocking mechanism 30 is provided on both sides of the tension roll 41, and the eccentric drive device 10 is provided on one or both sides of the tension roll 41.

When the output shaft 13 of the eccentric drive device 10 makes an orbital movement about the axis A by the amount of eccentricity d (arrow K in FIG. 4).
6 direction), the lever 32 and the arm 35 swing back and forth through the rod 31 (in the direction of arrow K7 in FIG.
3. The tension roll 41 can be reciprocated back and forth by the easing amount q via the lever 34 (solid line and two-dot chain line in the figure). At this time, the tension rod 37
Swings back and forth through the arm 34a of the lever 34 (in the direction of the arrow K8 in the figure), and prevents the lever 34 from rotating around the stud 33. Therefore, the interlocking mechanism 30
When the output shaft 13 rotates in synchronization with the rotation of the loom, the tension roll 41 is reciprocated by the easing amount q in accordance with the opening movement of the warps W, W. , And warp W, W ... can be maintained at a constant tension.

The interlocking mechanism 30 includes a control device 50 shown in FIG.
, The eccentricity d of the output shaft 13 can be controlled, and the easing amount q can be set optimally. The control device 50
Is a frequency divider 52, a driving unit 53, and a relative rotation control unit 5.
6, a driving means 57 is provided. The control device 50 receives a pulse signal So from an encoder EN connected to the main shaft MS of the loom.

The output of the encoder EN is connected to the addition terminal U of the counter 53a of the driving means 53 via the frequency divider 52, and the output of the counter 53a is connected to the driver 53b.
Is connected to the motor 21 via the. The motor 2
1, a pulse generator 21c is connected, and an output of the pulse generator 21c is connected to a subtraction terminal D of a counter 53a.

The output of the encoder EN is supplied to an arithmetic controller 56a of the relative rotation control means 56, frequency dividers 56c1, 56c2.
, 56c3. Arithmetic controller 56
The output of a is connected to the computing unit 56b,
The outputs of 6c1, 56c2 and 56c3 are connected to a switch 56d.
Connected individually.

The winding diameter Db of the warp beam B detected by a winding diameter sensor (not shown) is input to the calculator 56b. The output of the arithmetic unit 56b is provided by a switch 56d,
It is individually connected to one contact of the changeover switch 56e. The output of the switch 56d is connected to the addition terminal U of the counter 57a of the driving means 57 via another contact of the changeover switch 56e, and the output of the counter 57a is connected to the motor 22 via the driver 57b. I have. A pulse generator 22c is connected to the motor 22, and an output of the pulse generator 22c is connected to a subtraction terminal D of a counter 57a. An operation signal Sd from a loom control circuit (not shown) is input to the relative rotation control means 56.

When the loom is operating in a steady state, the encoder EN outputs a pulse signal So of a predetermined pulse rate as the main shaft MS rotates (FIG. 6A). The frequency divider 52 outputs a pulse signal S from the encoder EN.
The command signal Sa is generated by dividing o by 作 り,
Output to the addition terminal U of the counter 53a. Therefore,
The motor 21 can rotate completely synchronously with the spindle MS via the counter 53a and the driver 53b.
However, the pulse generator 21c connected to the motor 21 is
When the motor 21 rotates, the pulse signal So becomes 1
/ 2 pulse rate is generated, and the counter 53a
Feedback.

The frequency divider 56c1 converts the pulse signal So into 1 /
The frequency is divided by 1 and the same pulse signal S1 as the pulse signal So is output to the switch 56d. The frequency dividers 56c2, 56c
3 can divide the pulse signal So by １ ／ and １ ／, respectively, and output pulse signals S2 and S3.
On the other hand, at the time of steady state, the switch 56d
2 can be selected and output as a command signal Sb to the driving means 57 via the changeover switch 56e (time t <t1 in FIG. 6A). However, it is assumed that the changeover switch 56e has been switched to the switch 56d through the operation signal Sd because the loom is in a steady operation.

The motor 22 can rotate in synchronization with the spindle MS and the motor 21 via the counter 57a and the driver 57b of the driving means 57. That is, the eccentric drive device 10 turns the output shaft 13 while keeping the eccentricity d constant (the dashed line in FIG. 3B), and realizes the constant easing amount q of the tension roll 41 via the interlocking mechanism 30. be able to. The pulse generator 22c connected to the motor 22 generates a pulse having a pulse rate 1/2 of the pulse signal So with the rotation of the motor 22, similarly to the pulse generator 21c connected to the motor 21. I do.

The arithmetic controller 56a counts the pulse signal So from the encoder EN, and activates the arithmetic unit 56b every time the rotation amount of the main shaft MS reaches a predetermined value. Then, the arithmetic unit 56b reads the winding diameter Db of the warp beam B, and when it detects that the reduction amount of the winding diameter Db exceeds a value necessary for correcting the easing amount q (at time t = FIG. 6A). t1),
The switch 56d is switched from the frequency divider 56c2 to the frequency divider 56c3 only for a predetermined time Δt = t2−t1. Therefore, the command signal Sb to the driving means 57 is switched to the pulse signal S3 from the frequency divider 56c3 instead of the pulse signal S2 from the frequency divider 56c2 during this time.
The motor 22 has a speed of 1 to the spindle MS and the speed of the motor 21.
/ 2 speed. Therefore, the output shaft 13 of the eccentric drive device 10 can continuously decrease the eccentric amount d during the time Δt, and can reduce the easing amount q of the tension roll 41.

The arithmetic unit 56b switches the switch 56d to the frequency divider 56c2 after the lapse of the time Δt (time t = t2).
Side, and the subsequent eccentricity d and easing q are kept constant. Thereafter, the same operation is repeated as the weaving time elapses.

When the winding diameter Db of the warp beam B decreases with the progress of weaving, the computing unit 56b finds the optimum easing amount q for the winding diameter Db, and outputs necessary to realize the easing amount q. After the amount of eccentricity d of the shaft 13 is determined, the time Δt required to realize a new amount of eccentricity d is determined. Here, the relationship between the winding diameter Db and the easing amount q is determined by the specifications of the woven fabric during weaving, including the properties of the warps W, W... And may be set in advance in the calculator 56b. Further, the relationship between the easing amount q and the eccentricity d is uniformly determined by the specifications of the related members of the interlocking mechanism 30,
The time Δt for realizing the new eccentricity d is equal to the spindle M
S, the rotation speed of the motor 21 and the frequency dividers 56c2, 56c
3 and the specifications of the eccentric drive device 10. That is, the computing unit 56b can execute a series of necessary computations by finding the rotation speed of the spindle MS based on, for example, the pulse signal So input to the computation controller 56a.

When increasing the eccentricity d of the output shaft 13,
The controller 50 only needs to rotate the motor 22 at a high speed from the motor 21 for a predetermined time Δt = t4−t3 (FIG. 6B). That is, the switch 56d is connected to the arithmetic unit 5
6b, the pulse signal S1 from the frequency divider 56c1 may be output to the drive means 57 as the command signal Sb for a predetermined time Δt instead of the pulse signal S2 from the frequency divider 56c2. .

When the weaving progresses and the warps W, W... Wound on the warp beam B are completed and the warp beam B is replaced, the loom is stopped. Even when the second shafts 11 and 12 are stopped, the eccentricity d of the output shaft 13 can be changed. At this time, since the loom is stopped, the operation signal Sd
Does not exist, and the changeover switch 56e is switched to the computing unit 56b side. When the calculator 56b detects that the warp beam B has been replaced and the winding diameter Db has increased,
A predetermined number of pulses are output directly to the counter 57a as a command signal Sb via a built-in pulse generator (not shown), and the motor 22 can be rotated by a predetermined rotation angle. That is, the motor 22 relatively rotates the second shaft 12 by a predetermined angle with respect to the stopped first shaft 11, and outputs the output shaft 13.
Can be increased. The computing unit 56b at this time designates the rotation direction of the motor 22 by switching the output side of the driver 57b, for example.

In the above description, the eccentric drive device 10
The second shaft 12 may be synchronized with the main shaft MS instead of synchronizing the first shaft 11 with the main shaft MS. Further, a relative rotation control means 5 is provided between the encoder EN and the driving means 53.
6 are additionally provided, so that the motors 21, 2
The rotation of both can be controlled simultaneously.

The frequency dividers 52, 56c1, 56c2,
56c3 indicates that each division ratio is 1/2, 1/1, 1
Instead of setting to, 、, another arbitrary dividing ratio may be set. The eccentricity d of the output shaft 13 can be changed more quickly by making the frequency division ratios of the frequency dividers 56c1 and 56c3 largely different from the reference frequency division ratios of the frequency dividers 52 and 56c2.

Instead of using the motors 21 and 22 as the respective driving sources, one of the first and second shafts 11 and 12 is connected to the main shaft MS or a shaft rotating synchronously with the main shaft MS, and the other is connected to the other. May be driven by a motor. The first and second shafts 11 and 12 have one shaft connected to the main shaft MS or a shaft rotating synchronously with the main shaft MS, and the other shaft is connected to the one shaft via a transmission. May be connected, and the eccentricity d at this time can be controlled by temporarily changing the speed ratio of the transmission.

Further, the eccentric drive device 10 controls the output shaft 1 by stopping the first and second shafts 11 and 12 simultaneously.
3 can be stationary and the first and second shafts 11, 12
By changing the synchronous rotation speed, the drive cycle of the drive target connected to the output shaft 13 can be changed.

[0052]

[Other Embodiments] The displacement member 14 may be formed as a plate-like swinging member (FIGS. 7 and 8).

At both ends of the displacement member 14, an eccentric pin 14b and an output shaft 13 are erected in directions opposite to each other. An elongated hole 14c is formed in an intermediate portion of the displacement member 14, and an eccentric pin 12b provided on the disk 12a of the second shaft 12 is slidably engaged with the elongated hole 14c. I have. The second shaft 12 is rotatably inserted through a shaft hole of the first shaft 11 via a bearing 11e, and a large-diameter portion of the first shaft 11 has a gear 11 formed on the outer periphery.
d and a gear 21d that meshes with the gear 11d. The large diameter portion of the first shaft 11 is formed with a hole 11f into which the eccentric pin 14b of the displacement member 14 is rotatably inserted.

When the second shaft 12 is rotated faster than the first shaft 11 via the motor 22 (see arrow K1 in FIG. 8A).
K2 direction), the displacement member 14 includes eccentric pins 14b, 12b
Relative to each other (in the direction of arrow K12 in the figure), the output shaft 13 can be eccentric from the axis A by swinging around the eccentric pin 14b (in the direction of arrow K13 in FIG. FIG. In addition, the displacement member 14 is an eccentric pin 1.
The positions of the eccentric pins 2b and 14b may be switched, the eccentric pin 12b on the first shaft 11 side may be engaged with the elongated hole 14c, and may be swung around the eccentric pin 14b on the second shaft 12 side.

The first shaft 11 may be moved relative to the second shaft 12 in the axial direction (FIG. 9).

The second shaft 12 has spiral cam grooves 12e1 and 12e formed on the outer peripheral portion of a thick disk 12a fixed to the tip.
e2 is formed. However, the cam grooves 12e1, 12e
It is assumed that e2 is formed at a sufficiently large lead angle irrespective of the illustration. The first shaft 11 is formed in a cylindrical shape, and is provided with rollers 11g1 and 1g which engage with the cam grooves 12e1 and 12e2.
1g2 is mounted on the inner circumference. Also, the first shaft 11
Is rotatably housed in the moving member 15 via the bearings 15a, 15a. The first shaft 11 is formed with a hole 11f for rotatably and slidably inserting an eccentric pin 14b erected on the displacement member 14, and the movable member 15
The screw shaft 21e connected to the motor 21 is screwed into a projecting portion 15b projecting from the outer periphery.

Therefore, the first shaft 11 is provided with a cam groove 12e1.
, 12e2 and the second through rollers 11g1, 11g2.
Can be rotated integrally with the shaft 12 of the first embodiment. When the moving member 15 is moved along the axis A via the motor 21 (in the direction of the arrow K14 in FIG. 9A), the first shaft 11 is moved relative to the second shaft 12 by rollers 11g1 and 11g1. 11g2 and relative rotation via the cam grooves 12e1 and 12e2 (FIG. 3B), and the displacement member 1 via the eccentric pins 14b and 12b.
The output shaft 13 can be decentered from the axis A by swinging the output shaft 4. The cam grooves 12e1 and 12e2 may be formed in any number other than two. The moving member 15
May be driven linearly by a linear motor in addition to the combination of the motor 21 and the screw shaft 21e, or any other linear indexing mechanism may be used.

In FIG. 9, the displacement member 14 swings around an eccentric pin 12 b erected on the disk 12 a on the second shaft 12 side, and the eccentric pin 14 b erected on the first shaft 11.
However, it may be slidably and rotatably engaged via the long hole 14c. That is, the displacement member 14 includes the first and second
It is sufficient to swing around the other by engaging one of the eccentric pins 12b and 14b on the shafts 11 and 12 side.

A guide portion 12f may be formed on the disk 12a of the second shaft 12 (FIGS. 10 and 11). The guide portion 12f is arranged so that the axis A
Is formed in a groove shape passing through. The output shaft 13 penetrates the displacement member 14, and the base of the output shaft 13 is
It is rotatably inserted into a sliding block 13b slidably engaging with 2f. The displacement member 14 has
An elongated hole 14c is formed at one end thereof, and the eccentric pin 11 erected on the first and second shafts 11 and 12 is formed in the elongated hole 14c.
h and 12b are slidably engaged in common.

Therefore, when the first shaft 11 rotates relative to the second shaft 12 (in the direction of the arrow K15 in FIG. 11), the displacement member 14 is connected to the output shaft 1 via the eccentric pins 11h and 12b.
3 to move the output shaft 13 to the axis A.
(In the direction of arrow K16 in the figure).
At this time, the output shaft 13 can linearly move along the guide portion 12f via the sliding block 13b moving along the guide portion 12f. The guide section 12
f may be changed so as to guide the output shaft 13 so as to move on a straight line passing through the axis A, and may be changed to any other shape other than the illustrated one. It may be replaced.

In the above description, the eccentric driving device 10
Can be used as a drive source of a loosing machine, a crank opening device, a beating device, a weaving device of a pile loom, and the like.

In the crank opening device, the heald may be reciprocated up and down once every two rotations of the loom. Therefore, the eccentric drive device 10 realizes an arbitrary opening curve including the dwell period by rotating the output shaft 13 once every two rotations of the loom and smoothly increasing or decreasing the eccentricity d of the output shaft 13 during the rotation. be able to. Further, by increasing or decreasing the amount of eccentricity d so as to eliminate the turning motion of the output shaft 13, it is possible to stop the heald at the maximum opening position of the warps W, W.

In the case of a beating device, the eccentric drive device 10 can be used to prevent a weaving step caused by a weak beating force when the loom is started. That is, the eccentric drive device 10 increases the eccentric amount d of the output shaft 13 when the loom is started, advances the beating position, compensates for the lack of the beating force, prevents the weaving step, and keeps the rotation of the loom in a steady state. And the eccentricity d may be controlled to return to the steady value.

The pile loom for weaving the pile fabric simultaneously moves the tension roll and the take-up roll back and forth by the same amount, thereby moving the position of the weaving mouth relative to the beating position. Therefore, the eccentric drive device 10 can be used as a drive source of such a cloth moving device.

Further, the eccentric drive device 10 can be used as a drive source of a beating device of a pile loom for changing a beating amount and changing a beating position. That is, the eccentric drive device 10 can change the beating amount by controlling the eccentric amount d of the output shaft 13 and can change the pile height.

The eccentric drive device 10 according to the present invention
Can be widely applied to any mechanical device that changes the eccentricity d of the output shaft 13 and changes the drive stroke of the drive target.

[0067]

As described above, according to the first aspect of the present invention, by displacing the output shaft of the displacement member via the first and second shafts rotatably combined with each other, the displacement member is displaced. Changes the eccentricity of the output shaft by rotating the first and second shafts relative to each other even when the first and second shafts are rotating, and synchronously rotating the first and second shafts. Since the eccentricity of the output shaft can be kept constant, the eccentricity of the output shaft can be adjusted steplessly even during operation of the mechanical device, and the driving stroke of the driven object can be freely adjusted. effective.

According to the second aspect of the present invention, by using the eccentric drive device for the easing device of the loom, the winding diameter of the warp beam changes with the progress of weaving, and it becomes necessary to change the easing amount. Since the easing amount can be set optimally without stopping the loom,
It is possible to improve the quality of the woven fabric.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view of the entire configuration.

FIG. 2 is a sectional view of a main part configuration.

FIG. 3 is an explanatory diagram of an operation (1).

FIG. 4 is an operation explanatory view (2).

FIG. 5 is a control block diagram.

FIG. 6 is an operation explanatory diagram.

FIG. 7 is a diagram (1) corresponding to FIG. 2, showing another embodiment.

FIG. 8 is an operation explanatory diagram of FIG. 7;

FIG. 9 is a view (2) corresponding to FIG. 2, showing another embodiment.

FIG. 10 is a view (3) corresponding to FIG. 2, showing another embodiment.

FIG. 11 is an operation explanatory diagram of FIG. 10;

FIG. 12 is an operation explanatory diagram showing a conventional technique.

[Explanation of symbols]

 A: shaft center d: eccentric amount R, r: radius of pitch circle 10: eccentric drive device 11: first shaft 11b: internal gear 11h: eccentric pin 12: second shaft 12b: eccentric pin 12f: guide portion DESCRIPTION OF SYMBOLS 13 ... Output shaft 14 ... Displacement member 14a ... Gear 14b ... Eccentric pin 30 ... Interlocking mechanism 41 ... Tension roll

Claims (7)

[Claims] A first shaft, a second shaft combined with the first shaft so as to be rotatable relative to the first shaft, and a displacement member having an output shaft. An eccentric driving device for changing the amount of eccentricity of the output shaft by relative rotation of a second shaft. 2. The eccentric member according to claim 1, wherein the displacement member is a rotatable member that is rotatably mounted on an eccentric pin of the second shaft and that rotates through the first shaft. Drive. 3. The displacement member has a gear that sets a radius of a pitch circle to a half of an internal gear attached to the first shaft, and moves the output shaft on a pitch circle of the gear. The eccentric drive device according to claim 2, wherein the eccentric drive device is provided upright. 4. The eccentric drive device according to claim 1, wherein the displacement member is a swing member that swings through each of the eccentric pins on the first and second shafts. 5. The eccentric drive according to claim 4, wherein the first shaft relatively rotates with respect to the second shaft by relatively moving in the axial direction of the second shaft. apparatus. 6. The apparatus according to claim 4, wherein the second shaft has a guide portion for regulating a moving direction of the output shaft.
Or the eccentric drive device according to claim 5. 7. An easing device for a loom, comprising: the eccentric drive device according to claim 1; an interlocking mechanism connected to the eccentricity drive device; and a tension roll attached to the interlocking mechanism. .