JP3494506B2 - Beating motion switching device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a beating motion switching device, and more particularly to a beating motion by transmitting the rotation of a main shaft to a rocking shaft via a crank, a cam or the like and swinging the rocking shaft. The present invention relates to an improvement in the technique of switching the rocking mode of a reed, and is applied to, for example, weaving of pile fabrics.

In this specification, the "oscillation pattern" means an oscillation amplitude, an oscillation phase, or a combination thereof.

[0003]

2. Description of the Related Art As a beating motion switching device of the above type, the one disclosed in Japanese Patent Laid-Open No. 4-352853 is known. In this prior art, the rotation of the main shaft is transmitted to the rocking shaft via a crank and one or more swing links. When switching the beating motion, the position of the pivot, which is the fulcrum of the swing link, is moved. When switching, fix the last retreat position of the reed,
The most advanced position is switched. That is, the rocking amplitude of the rocking shaft (and thus the reed) is switched.

[0004]

In the case of the prior art having the above-mentioned structure, one or more rocking links are interposed between the crank and the rocking shaft in addition to the commonly used intervening member. Because it is equipped, it is inevitable that it will be structurally complicated. In particular, since the motion converting mechanism is housed in the frame of the loom, such structurally complicated structure causes a space impossibility, and eventually the frame has to be increased in size.

Further, since the pivot shaft of the swing link is moved in order to switch the swing amplitude of the reed, the pivot shaft is easily vibrated and the possibility of mechanical damage is increased.

The most serious problem is that it is possible to switch between only two swing modes. That is, the degree of freedom in switching the swing mode is poor.

In view of the state of the art as described above, an object of the present invention is to provide a beating motion switching device which is structurally simple and rich in mechanical durability, and which has a large degree of freedom in swinging mode switching. It is to provide a conversion mechanism.

[0008]

For this reason, in the present invention, a pair of motion converting mechanisms for converting the rotational motion of the loom main shaft into the oscillating motions having different oscillating patterns are connected to both ends of the main shaft to form a reed. A gist is that a connecting member is interposed between a supporting rocking shaft and an output shaft of each motion converting mechanism, and the rocking shaft is set to be selectively connectable to an output shaft of any motion converting mechanism. .

[0009]

The reed supported by the rocking shaft swings in accordance with the set swing pattern of the motion converting mechanism on the selectively connected side to perform a repulsion movement.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIGS. In this embodiment, a crank mechanism is used as a motion converting mechanism. As shown in FIGS. 1 and 3, crank arms 7a and 7b are integrally formed at both ends of the main shaft 1 of the loom. , These crank arms have different predetermined lengths. Further, the main shaft 1 is connected to a drive motor of a loom (not shown) via a pulley 3 and a belt 5 at an end portion of one of the crank arms (right side in the illustrated example) side.

The crank arms 7a and 7b are respectively
The output shaft 31 is connected via the connecting rods 9a and 9b.
It is connected to sword levers 11a and 11b fixed to a and 31b. As described above, the pair of motion converting mechanisms are respectively configured by the crank arms 7a and 7b, the connecting rods 9a and 9b, the sword levers 11a and 11b, and the output shafts 31a and 31b. These output shafts 31a and 31b are connected to the locking shaft 13 via the left and right clutch units 30. These clutch units 30 are symmetrical with respect to an orthogonal plane passing through the center of the locking shaft 13 in the longitudinal direction, but have substantially the same configuration.
Only 0 will be described with reference to FIGS. 2 and 5.

In FIG. 2, the rocking shaft 13 is rotatably supported in its longitudinal direction by a plurality of bearings 15 on a beam 17 of the loom. An output shaft 31b is fixed to the end of the sword lever 11b. Therefore, the output shaft 31b serves as the output shaft of the motion converting mechanism. At the end of the output shaft 31b on the rocking shaft side, a plurality of meshing portions 311 formed of trapezoidal concavo-convex teeth are formed in the circumferential direction. Further, a through shaft hole is formed in the output shaft 31b, and a guide shaft 33 is slidably inserted in the longitudinal direction in the shaft hole. The guide shaft 33 is connected to the drive unit 37 at the end portion on the side opposite to the locking shaft, and is driven by the drive unit 37 to reciprocally slide in the shaft hole.

A connecting member 35 is fixed to the end of the guide shaft 33 on the rocking shaft side adjacent to the meshing portion 311 of the output shaft 31b. An example of the structure of the connecting member 35 is shown in FIG. That is, the connecting member 35 includes the meshing portion 351 on the side facing the meshing portion 311 of the output shaft 31b. The meshing portion 351 is the meshing portion 3 of the output shaft 31b.
The concave and convex teeth are similar to those of No. 11 and can mesh with the latter. A large number of projections 352 are formed along the circumference of the connecting member 35 on the side facing the locking shaft.

On the other hand, a large number of grooves 131 are formed along the circumference on the outer peripheral surface of the end of the locking shaft 13 facing the output shaft 35, and these grooves 131 are formed on the connecting member 35. The protrusion 352 has a shape that can be engaged with the protrusion 352. Further, a blind shaft hole 132 is formed in the end portion of the locking shaft 13, and the blind shaft hole 132 is formed.
2 can accommodate the end of the guide shaft 33 on the locking shaft side.

In the above structure, when the main shaft 1 makes one revolution as shown in FIG. 3, the output shaft 31 is correspondingly rotated.
a and 31b swing by angles θY1 and θY2, respectively. In the case of the present embodiment, this swing amplitude is determined by the length of the crank arm 7 connecting the main shaft 1 and the output shaft 31. The relationship between these swing amplitudes is shown in FIG. ΘM in the figure is one rotation angle of the spindle 1, and θM = 3
60 degrees corresponds to the rotation angle at the time of beating. In this way, a pair of motion conversion mechanism composed of crank mechanism,
Rotational motions of the main shaft are converted into oscillating motions having different oscillating patterns, specifically, oscillating amplitudes.

As described above, in this embodiment, the crank mechanism is used as the motion converting mechanism, and the crank arms 7a and 7b of the crank mechanism have different lengths.
Therefore, as shown in FIG. 4, when the spindle 1 rotates,
The output shaft 31a on the crank arm 7a side swings by an angle θY1, and the output shaft 31b on the crank arm 7b side rotates by an angle θ.
Swing Y1 only. These swing amplitudes correspond to the lengths of both crank arms 7a and 7b.

When there is no drive by the drive unit 37, the connecting member 35 is urged toward the output shaft via the guide shaft 33 by the spring built in the drive unit 37. Therefore, the meshing portion 311 of the output shaft 31 meshes with the meshing portion 351 of the connecting member 35, and at this time, the projection 352 of the connecting member 35 maintains the meshing engagement with the groove 131 of the locking shaft 13. The clutch unit 30 is set to do so.

The clutch unit 30 having the above structure
2, the drive unit 37 on the side of the crank arm 7a is not driven in the state shown in FIG.
3 is pulled out to the side opposite to the locking shaft (right side in the figure), and the connecting member 35 also moves to the same side. As a result, the meshing portion 311 of the output shaft 31 a is changed to the meshing portion 35 of the connecting member 35.
1, the projection 352 of the connecting member 35 maintains the meshing engagement with the groove 131 of the locking shaft 13. Since the drive unit 37 on the crank arm 7b side is being driven at this time, the clutch unit 3 on the same side is
At 0, the guide shaft 33 is pushed to the locking shaft side, and the connecting member 35 also moves to the same side. As a result, the meshing portion 311 of the output shaft 31b is disengaged from the meshing engagement with the meshing portion 351 of the connecting member 35. The protrusion 352 of the connecting member 35 meshes with and engages with the groove 131 of the locking shaft 13. Therefore, since the rocking shaft 13 is connected to the output shaft 31a of the motion converting mechanism on the right side in FIG. 1, the swing amplitude of the reed 19 during one rotation of the main shaft 1 becomes θY1 (see FIG. 4).

Drive unit 37 on the crank arm 7b side
Is stopped and the guide shaft 33 is pulled out to the side opposite to the locking shaft (left side in the drawing), the connecting member 35 also moves to the same side. As a result, the meshing portion 31 of the output shaft 31b
1 engages with the engaging portion 351 of the connecting member 13, and at this time, the projection 352 of the connecting member 35 maintains the engaging engagement with the groove 131 of the locking shaft 13. Since the drive unit 37 on the crank arm 7a side is driven at the same time as the drive of the drive unit 37 on the crank arm b side is stopped, in the clutch unit 30 on the same side,
The meshing engagement between the meshing portion 311 and the meshing portion 351 as described above is released. Therefore, the swing amplitude of the reed 19 is θY2 (see FIG. 4).

The swing amplitude can be changed by changing the length of the crankshafts of the left and right motion converting mechanisms. In addition to this, the timing at which one of the left and right drive units 37 is driven and at the same time the other drive is stopped, that is,
By adjusting the switching timing of a and 31b, it is possible to freely set the rocking position of the reed, that is, the rocking phase. For example, from the output shaft 31a to the output shaft 3
When switching to 1b, by changing and adjusting the switching timing, the swing range of the reed after switching is θY2
Even if it is the same as, the rocking phase of the reed will be changed. The drive control of the left and right drive units 37 is performed by a control device (not shown). The control device inputs the rotation angle signal from the rotation angle detector of the main shaft 1 during the operation of the loom, and based on the order of the fabric structure or the multicolor weft insertion,
The left and right drive units 37 are driven and stopped at a predetermined rotation angle (predetermined timing) in a predetermined loom cycle.

The swing patterns shown in FIGS. 6 to 9 will be described below with reference to FIGS. 10 to 12 showing changes in swing amplitude. 10 to 12, the horizontal axis represents the crank angle.

In the examples shown in FIGS. 6 and 10, the most advanced position is changed by fixing the last retreat position of the reed and switching the swing amplitude. In this case, at the timing when the reed reaches the final retreat position, the drive unit 37
The guide shaft 33 is driven by, that is, the connection is switched. As a result, the most advanced position of the reed is changed by an amount corresponding to Δθ (= θY2-θY1). Although the maximum amount of change in the most advanced position of the reed is Δθ, the amount of change can be freely set by changing the connection switching timing (crank angle). However, at this time, the final retreat position of the reed will also change.

In FIG. 10, the crank angle of 180 degrees corresponds to the rearmost retracted position, and the crank angle of 360 degrees (0 degree) corresponds to the most advanced position. Therefore, the swing amplitude is switched at a crank angle of 180 degrees (indicated by A in the figure). For example, in the configuration shown in FIG. 1, the curve indicated by a in FIG. 10 corresponds to the crank arm 7a side, and the curve indicated by b corresponds to the crank arm 7b side.

Changing the most advanced position of the reed in this way is necessary in the case of pile weaving. That is, in the loose pick loom cycle, the reed is driven by the output shaft 31b on the angle θY2 (curve b) side, and in the fast pick loom cycle, the output shaft 31a on the angle θY1 (curve a) side.
This drives the reed.

In the example shown in FIG. 7, the most advanced position of the reed is fixed and the swing amplitude is switched to change the last retracted position. In this case, at the timing when the reed reaches the most forward position, the driving and stopping of the driving of the left and right drive units 37, that is, the switching of the connection is performed. However, the timing when the reed is in the most forward position is the timing of the beating. At the time of beating, the impact due to beating acts on the entire system. It is not practically preferable to switch the swing amplitude at such timing. Therefore, when adopting such a swing pattern, consideration is actually given to the switching timing as shown in FIGS. 9 and 12. This point will be described later in detail.

It is necessary in multicolor weft insertion to change the last retreat position of the reed in this way. That is, it is assumed that there are wefts a of a type that can generate a high flight speed by a jet fluid for weft insertion and wefts b of a type that hardly generate a high flight speed. In the loom cycle in which the weft yarn a is inserted, the reed is driven by the output shaft 31b, and in the loom cycle in which the weft yarn b is inserted, the reed is driven by the output shaft 31a.

The following effects can be obtained by changing the rocking mode of the reed as described above. It is advantageous to increase the rotation speed of the loom by driving the reed by the output shaft 31b to reduce the swing range of the reed. Therefore, the rotation speed of the loom is increased at this time. When the reed is driven by the output shaft 31a to increase the swing range, the weft insertion period can be lengthened, so that stable weft insertion can be performed at this time.

In the example shown in FIGS. 8 and 11, the swing amplitude is not changed and only the swing phase is switched. That is, in the configuration shown in FIG. 1, the left and right crank arms 7
By making the lengths a and 7b equal and making the formation positions of the crank arms 7a and 7b in the circumferential direction of the main shaft 1 different from each other, the output shafts 31a and 31b are
It is set so as to perform oscillating motions having the same amplitude and different phases. The left and right drive units 37 are driven and stopped at a predetermined crank angle for each predetermined loom cycle.

In the loom cycle shown in FIG. 11, the swing amplitude of the reed is switched by a crank angle of 180 degrees (C in the figure).
(Indicated by).

Such a swing pattern is adopted in the case of pile weaving by utilizing the fact that the most advanced position of the reed is changed. Since the rocking range of the reed after switching does not change, the retreat position of the reed also inevitably changes, but such a change does not affect weft insertion, so there is no particular problem. .

The swing pattern of FIG. 9 as an alternative to the swing pattern of FIG. 7 described above in practice will be described below with reference to FIG. Since it is not practically preferable to switch the connection at the beating timing as described above, as shown in FIG. 12, the connection is switched at the timing without this, that is, at the crank angle θM1. The movement switching mechanism is constructed by shifting the phase. More specifically, in FIG. 1, by forming the crank arms 7a and 7b in the circumferential direction of the main shaft 1 at different positions, the output shafts 31a and 31b are formed.
Swing b in different phases.

As for the switching timing, even if the output shaft 31 connected to the locking shaft is switched from the curve a side to the curve b side or from the curve b side to the curve a side at this timing, the reed is most advanced. The timing, that is, the crank angle θM1, is set so that the position becomes the same as the most advanced position before switching.

In other words, the position of the reed connected to the curve b side output shaft 31 when the curve b side output shaft 31 reaches the swing position S1 and the reed position when the curve b side output shaft 31 reaches the swing position S6. The switching timing is set so that the positions of the reeds that are connected are the same. Specifically, the crank angle θM1 such that (θY1-θ1) is equal to (θY2-θ2) may be set as the switching timing.

The switching operation will be described below by taking the case where the connection state is switched from the curve b side output shaft 31b to the curve a side output shaft 31a as an example. In response to the swing position of the output shaft 31b on the side of the curve b changing from S1 → S2 → S1 (FIG. 12), the reed performs a swing motion of positions P1 → P2 → P1 (FIG. 9). .

When the output shaft 31b on the curve b side moves from the swing position S1 to S3, the connection is switched to the output shaft 31a on the curve a side. At this time, the reed position is P3, and the swing position of the output shaft 31a on the curve a side is S4. When the output shaft 31a on the side of the curve a reaches the swing position S5, the position of the reed is P4.
Becomes

After that, when the output shaft 31a on the side of the curve a reaches the swing position S6, the reed is at the most forward position. However, since the switching timing is set as described above, the most advanced position of the reed at this time coincides with P1. Thereafter, the reed oscillates in the positions P1 → P4 → P1 in response to the swing change S6 → S5 → S6 of the output shaft 31a on the side of the curve a.

Although the crank mechanism is used as the motion converting mechanism in the above-described embodiments, a cam mechanism may be used instead of the crank mechanism. An example thereof is shown in FIGS. 13 and 14. That is, the loom main shaft 1 is mediated by the positive cam mechanism 40.
And the locking shaft 13 are connected. This positive cam mechanism 40, as shown in FIG.
And a pair of cams 43a and 43b fixed to the output shaft 31
It is constituted by a pair of cam balls 42a, 42b which are supported by a pair of cam levers 41a, 41b fixed to and are in rolling contact with the respective cams 43a, 43b.

When such a cam mechanism is used as the motion converting mechanism, the amplitude of the swing motion of the loom with respect to the main shaft 1 can be made different by making the lifts of the cams of the motion converting mechanisms different from each other. Further, by changing the mounting phase of the cam on the main shaft 1 of the loom, the phase of the swinging motion relative to the rotating motion of the loom can be different. Further, by making the lift and the mounting phase different, it is possible to make the amplitude and the phase of the swing motion different.

The meshing portion 311 of the output shaft 31 and the connecting member 3
The shape of the meshing portion 351 of No. 5 may be changed to that shown in FIG. 2 and may be as shown in FIG. As a result, the rotational force can be received on the surface perpendicular to the circumferential direction.

When the specifications of the fabric to be woven are changed,
The connection state may be switched before the loom is started (that is, while the loom is stopped), and the connection state may be fixed during operation of the loom. That is, in the case of weaving a fabric using a weft yarn that tends to have a high flight speed, the rocking shaft 13 is connected to the output shaft 31b so that the swing range of the reed is set to be small. Settings can be enabled. Further, when weaving a woven fabric using a weft yarn having a high flight speed, by connecting the output shaft 31a so as to set the rocking range of the reed to a large range, the weft inserting period is extended and the weft inserting failure is prevented. Occurrence can be reduced.

The pair of motion conversion mechanisms may be set so that the lengths of the link members are made different from each other so that the swing motions having different phases are switched.

[0042]

Since the intermediary swing link is not used, the structure is simple. Further, for the same reason, since the pivot shaft does not move, the mechanical durability as a whole is improved. Furthermore, the swing phase of the reed after switching can be freely set only by appropriately changing the switching timing during the operation of the loom.

[Brief description of drawings]

FIG. 1 is a front view showing the overall configuration of a first embodiment of a beating motion switching device of the present invention.

FIG. 2 is also a partial cross-sectional overall view showing the configuration around the clutch unit.

FIG. 3 is a side view showing the relationship between the swing amplitude of the loom main shaft and the rocking shaft.

FIG. 4 is a perspective view showing the relationship of the swing amplitude of the output shaft of the motion switching mechanism.

FIG. 5 is a perspective view showing an example of a connecting member of the clutch unit.

FIG. 6 is a side view showing an example of a swing pattern.

FIG. 7 is a side view showing another example of the swing pattern.

FIG. 8 is a side view showing another example of the swing pattern.

9 is a side view showing another example of a swing pattern that replaces the swing pattern shown in FIG. 7. FIG.

FIG. 10 is a graph showing changes in swing amplitude in the swing pattern shown in FIG.

11 is a graph showing changes in swing amplitude in the swing pattern shown in FIG.

12 is a graph showing changes in swing amplitude in the swing pattern shown in FIG.

FIG. 13 is a front view showing another example of the motion switching mechanism.

FIG. 14 is a side view showing the main part thereof.

FIG. 15 is a partially enlarged view showing another example of the engagement mode between the locking shaft and the connecting member.

[Explanation of symbols]

1: Loom spindle 7: Crank arm 9: Connecting rod 13: Rocking shaft 19: Reed 30: Clutch unit 31: Output shaft 33: Guide shaft 35; Connection member 37: Drive unit 40: Positive cam mechanism 43: Cam

Claims (3)

(57) [Claims] 1. A pair of motion converting mechanisms for converting the rotation of a loom main shaft into rocking having different rocking patterns, which are connected to both ends of the main shaft, and a rocking shaft for supporting a reed and outputs of the motion converting mechanisms. A beating motion switching device, wherein a connecting member is interposed between the shaft and the rocking shaft, and the rocking shaft is set to be selectively connectable to an output shaft of one of the motion converting mechanisms. 2. The device according to claim 1, wherein the motion conversion mechanism is a crank mechanism. 3. The apparatus according to claim 1, wherein the motion converting mechanism is a cam mechanism.