JP2006037246A - Apparatus for feeding warp of weaving machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To control fluctuation of warp tension, to prevent weaving bar, to reduce capacities of a rotation driving source and a transmission for driving the revolving shaft of a warp beam, to widen use condition ranges such as allowable warp tension, beating density range, etc., and to improve general purpose properties of a weaving machine in a warp feeding apparatus of a weaving machine. <P>SOLUTION: In the warp feeding apparatus 1 of a weaving machine, which is equipped with the driving gear 3 composed of the rotation driving force 4 and a transmission device 5 for transmitting the rotation of the driving force 4 to the warp beam 2 and in which the driving gear 3 rotates the warp beam 2 in the feed direction while applying damping force against warp tension to the warp beam 2, the apparatus is equipped with a damping device 10 for applying damping force to the warp beam 2 separately from the damping force of the driving gear 3 and damping force is applied to the warm beam 2 by the damping device 10. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

The present invention relates to a braking device for a warp beam for warp feeding in a warp feeding device of a loom.

The warp feeding device of the loom rotates a warp beam for warp feeding in the feeding direction in accordance with an increase in the tension of the warp while applying a predetermined tension to the sheet-like warp to send out the warp. For example, the warp feeding device disclosed in Patent Document 1 rotates the worm of the worm gear mechanism by a dedicated motor and drives the worm wheel while ensuring the braking force against the warp tension by the check function of the worm gear mechanism. The warp beam integrated with the worm wheel is rotated in the feeding direction, and the warp is fed under a predetermined tension.

In the weaving process of the loom, the warp tension fluctuates abruptly due to opening movement or beating, and this vibration occurs every pick (every cycle), so the tension fluctuation is transmitted to the warp beam around which the warp is wound. The fluctuation in tension becomes an exciting force, and the warp beam repeats fine rotation in the feed direction and rotation in the reverse feed direction (reverse rotation) due to torsional deformation of the shaft and backlash of the gear to induce so-called vibration rotation.

This vibration rotation changes the warp length between the weave and the warp beam, and a weaving step (uneven density) occurs. The larger the diameter of the warp beam, the greater the radius of the excitation force applied to the warp beam, so that the warp beam is more likely to vibrate and rotate, and the greater the weight of the warp beam, the greater the energy of vibration and rotation. The step tends to be large. Further, in weaving with a high-density woven fabric, a rapid warp tension fluctuation due to looseness especially at the time of hammering becomes a problem.
JP 2003-193355 A

Accordingly, an object of the present invention is to suppress warp tension fluctuations and prevent weaving steps in a warp feeding device of a loom. Another problem is that the capacity of the rotary drive source and transmission that drives the rotating shaft of the warp beam is reduced, and the range of use conditions such as allowable warp tension and driving density range is expanded to improve the versatility of the loom. It is to let you.

Based on the above problems, the present invention provides a driving device that transmits a rotation of a driving source to a warp beam by a transmission device while causing a braking force against warp tension to act on the warp beam, and rotates the warp beam in a delivery direction. The warp feeding device of the loom provided includes a braking device for applying a braking force to the warp beam, in addition to the braking force of the driving device.

Further, according to the present invention, the braking device is provided with braking force relaxation means for relaxing the braking force of the braking device when the warp beam rotates in the non-feeding direction. The braking force relaxation means is configured by a one-way rotation transmission device interposed between the braking device and the rotation axis of the warp beam in order to obtain a braking force 0 to a predetermined braking force value of the braking device. 3) or an actuator that reduces the contact pressure of the brake disc against the brake disc integrated with the brake shaft.

Note that the drive device is configured as an electric feeding device by an independent dedicated motor other than the loom motor, or the rotation of the loom motor is input, and the rotation is shifted to output the mechanical output. Configured as a delivery device. In addition, as a configuration that applies a braking force against warp tension in the drive unit, it consists of a dedicated motor, a drive shaft, and a reverse function of a worm gear mechanism that meshes with a warp beam gear (worm wheel) (a worm gear that can be self-locked). The worm gear is made up of a dedicated gear, which acts against the warp tension against the warp tension, or has a braking function, and a drive gear that meshes with the warp beam, and outputs a braking signal from the control device to the dedicated motor. A braking force against the warp tension is applied by a motor.

According to the present invention, in the warp feeding device of the loom, the braking device that applies the braking force to the warp beam is provided separately from the braking force of the driving device, so that the braking force is applied to the warp beam during weaving. The vibration rotation of the warp beam can be suppressed, and the generation of the weaving step due to the vibration rotation of the warp beam can be effectively prevented (claim 1).

As described later in [Explanation of feed drive by worm gear (worm gear) mechanism], the torque of the drive device required for rotation in the reverse feed direction is larger than the torque of the drive device required for rotation in the feed direction. Since the braking force of the braking device is alleviated by the braking force relaxation means during rotation in the counter-feeding direction, the load on the driving device when the warp beam rotates in the counter-feeding direction can be reduced, and the load on the driving device is reduced. For this reason, even if the drive device has the same capacity, the use condition range such as the allowable warp tension and the driving density range is expanded, and the versatility of the loom is improved. Further, instead of widening the use condition range, a drive device having a capacity one rank smaller can be used, thereby reducing the cost (claim 2).

If the braking force relaxation means is a one-way rotation transmission device, a general-purpose one-way clutch, a coil spring, or the like can be used, so that the effect of claim 2 can be realized with a simple configuration. (Claim 3).

If the braking force relaxation means is constituted by an actuator for reducing the contact pressure, the contact pressure control can be easily changed, and the optimum contact pressure can be adjusted.

First, FIG. 1 shows a configuration of a part which is a premise of a warp feeding device 1 of a loom according to the present invention. In FIG. 1, a warp feeding device 1 of a loom includes a drive device 3 for driving a warp beam 2, and the drive device 3 rotates a dedicated motor 32 as a drive source 4 and the dedicated motor 32. It comprises a transmission device 5 that transmits to the warp beam 2. In this example, the transmission device 5 includes a worm 34 fixed to a drive shaft 33 that is integral with the output shaft of the dedicated motor 32, a gear 50 that meshes with the worm 34, a gear 50, and a gear 50. The gear 51 is supported by the rotating shaft 52 together, and the warp beam gear 35 meshes with the gear 51. The warp beam gear 35 is attached to the rotary shaft 21 for supporting the warp beam 2 and rotates together with the warp beam 2.

In this example, since the gear 50 is a worm wheel, the worm 34 and the gear 50 constitute a worm gear (worm gear) mechanism having a large reduction ratio, and have a check function (self-lock function). Therefore, the rotation of the dedicated motor 32 can be decelerated and transmitted to the warp beam gear 35, but the reverse, that is, the rotational force of the warp beam gear 35 is not transmitted to the worm 34.

The driving device 3 rotates the warp beam 2 while applying a braking force against the warp tension T to the warp beam 2 with respect to the warp 9 fed from the warp beam 2 to the pre-weave 8. The braking force against the warp tension T here is obtained by a non-return function (self-locking function) of the worm gear mechanism (the worm 34 and the gear 50 by the worm wheel meshing therewith). The warp 9 is drawn out as a sheet from the warp beam 2, guided by the guide roll 6 and the tension roll 7, and sent out in the direction of the pre-weaving 8. Further, the tension roll 7 is normally supported so as to be movable by a tension applying means (not shown), and applies a predetermined warp tension T to the warp 9.

The warp feeding device 1 of the loom of the present invention has a braking device 10 that applies a braking force to the warp beam 2 separately from the braking force of the driving device 3 as a characteristic configuration. This braking device 10 is embodied by the following embodiment. Except for the second embodiment, the unidirectional rotation transmission device 13 is used, and the second embodiment is an example in which the contact pressure against the brake disk 25 is decreased by the actuator 31.

[Embodiment 1 (FIG. 2)]
As shown in FIG. 2, the first embodiment is an example in which a one-way rotation transmission device 13 is incorporated as a braking force relaxation means 12 between the brake gear 11 and the brake shaft 14 of the braking device 10. In FIG. 2, the braking device 10 includes a brake gear 11 that meshes with a warp beam gear 35, a brake disc 23 as a braking means that applies a braking force to the brake gear 11, a pair of brake disks 25, and a delivery of the warp beam 2. A braking force is applied to the rotation in the direction (hereinafter, the rotation in the feed direction is also referred to as normal rotation), and only the rotation in the counter feed direction (hereinafter, rotation in the counter feed direction is also referred to as reverse rotation) is controlled. It is comprised with the one-way rotation transmission device 13 which does not make power act. The one-way rotation transmission device 13 here is, for example, a one-way clutch. The warp beam gear 35 is concentrically attached to the rotary shaft 21 that supports the warp beam 2.

Both the brake gear 11 and the pair of brake disks 25 are supported by the brake shaft 14. The brake shaft 14 is rotatably supported with respect to the frame 17 by a ball bearing 15 and a bearing housing 16. The brake gear 11 is attached to the tip of the brake shaft 14 with the needle bearing 18, the one-way rotation transmission device (one-way clutch) 13, the sleeve 19, and the key 22 of the sleeve 19 being interposed at a position where the brake gear 11 meshes with the warp beam gear 35. Yes.

Next, the braking device 10 includes a plurality of struts 20 attached to the bearing housing 16, a brake disc 23 supported by these struts 20 in a non-rotating state, and a pair of opposing faces so as to sandwich the brake disc 23. A brake disk 25 and a brake spring 27 are included. The pair of brake discs 25 are prevented from rotating with respect to the brake shaft 14 by a spline or the like, are supported so as to be movable in the axial direction, and are brought into frictional contact with the surface of the brake disc 23 by the outer brake lining 24. Then, a braking force is applied to the brake shaft 14.

The brake spring 27 has a coil shape, is passed through the brake shaft 14, contacts the brake disk 25 on the brake spring 27 side at the tip, and contacts a spring receiver 28 inserted into the brake shaft 14 at the rear end. . The spring receiver 28 compresses the brake spring 27 by an adjustment nut 26 screwed into the male screw 29 of the brake shaft 14, and generates a frictional force corresponding to a necessary braking force between the brake disc 23 and the pair of brake linings 24. Let The brake disk 25 on the one-way rotation transmission device (one-way clutch) 13 side hits the ball bearing 15 by the receiving ring 30. Thus, the braking device 10 generates a necessary braking force by the frictional force between the brake disc 23 and the pair of brake linings 24.

With the above configuration, the brake gear 11 is rotatable with respect to the brake shaft 14 by the needle bearing 18, but because of the one-way rotation transmission function (one-way clutch) 13, the warp beam Although the rotation (reverse rotation) of the gear 35 in the reverse feeding direction is allowed, the braking force of the braking device 10 is rotated integrally with the brake shaft 14 against the rotation (forward rotation) in the feeding direction and resists the warp tension T. Act. As described above, the one-way rotation transmission device 13 is interposed between the rotating shaft 21 of the warp beam 2 and the braking force alleviating means 12 and applies the braking force of the braking device 10 to the rotation direction of the warp beam 2 being sent out. Thus, the braking force of the braking device 10 is not applied only to the rotation direction opposite to the feeding direction, that is, the rotation against the warp tension T.

As a result, even during weaving, the warp tension T fluctuates abruptly due to opening movement or beating, and even if this tension fluctuation causes a large excitation force to the warp beam 2, the warp beam 2 is rotated against the rotation in the delivery direction. The warp beam is generated by the braking force obtained by adding the braking force obtained by the non-return function (self-locking function) of the worm gear mechanism (the worm 34 and the warp beam gear 35 by the worm wheel meshing with the worm 34) and the braking force of the braking device 10. 2 does not induce vibration rotation. For this reason, generation of a weaving step can be prevented beforehand.

Further, when the warp beam 2 is reversely rotated (rotation in the counter-feeding direction), the one-way rotation transmission device (one-way clutch) 13 as the braking force relaxation means 12 allows the reverse of the warp beam 2 (rotation in the counter-feeding direction). The braking force of the braking device 10 does not act on the reverse rotation (rotation in the counter-feeding direction) of the warp beam 2 and is almost reduced to 0. For this reason, even if the braking device 10 is provided, the load on the driving device 3 at the time of reverse rotation of the warp beam 2 does not increase, but is reduced from the rotation load in the delivery direction.

As a result, as described later in [Explanation of feed drive by worm gear (worm gear) mechanism], even if the drive device 3 has the same capacity (same braking force), the braking device 10 transmits the one-way rotation as the braking force relaxation means 12. By incorporating the device (one-way clutch) 13, the required torque of the drive device 3 can be afforded, so that the range of use conditions such as the warp tension and the driving density range is widened with a simple configuration, and the versatility of the loom is improved. Further, instead of expanding the use condition range, the driving device 3 having a capacity (driving force) that is smaller by one rank can be adopted, thereby reducing the cost of the device.

According to the illustrated example, a one-way rotation transmission device (one-way clutch) 13 as a braking force relaxation means 12 is interposed between the braking device 10 and the rotary shaft 21, but a one-way rotation transmission device (one-way clutch). 13 can also be incorporated between the brake disc 25 and the brake shaft 14. Further, the one-way rotation transmission device 13 can also be configured as an electromagnetic clutch instead of a one-way clutch. When configured with an electromagnetic clutch, in conjunction with the control of the loom or artificially, excitation is required when braking is required, and excitation is canceled and set to a free state when it is not necessary such as reverse rotation. .

[Embodiment 2 (FIG. 3)]
In the second embodiment, as shown in FIG. 3, the braking force relaxation means 12 of the braking device 10 is configured by an actuator 31 that reduces the contact pressure of the pair of brake discs 25 with respect to the brake disc 23 integrated with the brake shaft 14, for example, an air cylinder. In this example, the pair of brake discs 25 are brought into contact with and separated from the brake disc 23 at the timing of switching between forward and reverse rotation of the warp beam 2. The brake gear 11 is directly fixed to the brake shaft 14 by a key 22.

In FIG. 3, the actuator 31 is attached to a support column 20 and a mounting plate 36 attached to the tip thereof, and the advance amount (advance output) of the actuator rod 37 is controlled by a pressure source 38, a valve 39 and a control device 40. It has become so. The actuator rod 37 penetrates the mounting plate 36 and abuts on one end of the brake spring 27 with a predetermined advance force by a spring receiver 28 at the tip. Therefore, when the brake shaft 14 rotates, a constant frictional force (braking force) acts between the brake disc 23 and the pair of brake discs 25.

When the warp beam 2 is rotated in the delivery direction (forward rotation), the control device 40 controls the valve 39, moves the actuator rod 37 in the advance direction, and applies a constant contact pressure to the pair of brake discs 25, thereby A braking force is applied to the beam 2. On the other hand, when the warp beam 2 is rotated (reversely rotated) in the counter-feeding direction, the control device 40 controls the valve 39 to move the actuator rod 37 in the backward direction so that the pair of brake discs 25 are removed from the brake disc 23. Release it so that it cannot be removed. As a result, the constant braking force between the brake disc 23 and the pair of brake discs 25 is reduced, or the braking force is hardly applied.

The actuator 31 may be a hydraulic air cylinder or an electromagnetic solenoid instead of an air cylinder, or may be configured by a combination mechanism of an electric motor, a hydraulic motor, and a rotation-linear motion conversion mechanism such as a screw mechanism. it can.

[Embodiment 3 (FIG. 4)]
The third embodiment is an example in which the braking device 10 and the braking force relaxation means 12 are incorporated at the position of the rotating shaft 21 that supports the warp beam 2 as shown in FIG. In FIG. 4, the one-way rotation transmission device (one-way clutch) 13 as the braking force alleviating means 12 is inserted in the outer diameter portion of the rotating shaft 21 and rotates idly when the rotating shaft 21 rotates in the reverse direction. The sliding bearing 41 as the braking device 10 is provided between the one-way rotation transmission device (one-way clutch) 13 and the loom frame 42, and friction between the sliding bearing inner ring 43 and the sliding bearing outer ring 45 (sliding). Resistance) generates braking force. In this case, the larger the diameter of the rotating shaft 21, the higher the frictional force, and the stronger the braking force.

When the warp beam 2 is rotated in the delivery direction (forward rotation), the rotary shaft 21 and the sliding bearing inner ring 43 rotate together, and a braking force acts on the warp beam 2 by the sliding bearing 41. On the other hand, when the warp beam 2 rotates (reversely) in the counter-feeding direction, only the rotating shaft 21 rotates, so that no braking force acts on the warp beam 2.

[Embodiment 4 (FIG. 5)]
In the fourth embodiment, instead of using a one-way clutch as the one-way rotation transmission device 13 in the first embodiment (FIG. 2), the brake shaft 14 between the pair of brake disks 25 and the brake gear 11 is used as shown in FIG. In this example, a torsion coil spring 45 is interposed. The torsion coil spring 45 is wound along the outer peripheral surface of the brake shaft 14, fixed to the brake shaft 14 at one end, and fixed to the boss portion of the brake gear 11 at the other end.

When the warp beam 2 rotates in the delivery direction, the brake gear 11 rotates in the direction of twisting the torsion coil spring 45. Therefore, when the torsion coil spring 45 is fully twisted or rotated by a predetermined amount of rotation, the brake gear 11 rotates. This is transmitted to the brake shaft 14. As a result, the braking force of the braking device 10 acts on the warp beam 2 when the warp beam 2 rotates in the delivery direction.

On the other hand, when the warp beam 2 rotates in the counter-feeding direction, the brake gear 11 rotates in the direction of returning (opening) the torsion coil spring 45, so that the torsion coil spring 45 applies its urging force to the brake gear 11. Rotates while acting. At this time, since the rotation of the brake gear 11 is not transmitted to the brake disc 25, the braking force of the braking device 10 is not applied to the warp beam 2. It should be noted that the amount of rotation at the time of reverse rotation is set so as not to exceed the braking force (ie, the brake disk 25 does not rotate in reverse rotation), or the amount of twisting does not exceed the braking force, that is, a sufficient amount of twist corresponding to the reverse rotation amount. Thus, the spring constant of the torsion coil spring 45 is determined.

[Embodiment 5 (FIGS. 6 and 7)]
In the fifth embodiment, instead of using the torsion coil spring 45 in the fourth embodiment (FIG. 5), the compression coil spring 46, the brake side connecting member 47, and the gear side connecting member 48 are used as shown in FIGS. It is an example. The brake side connecting member 47 is fixed to the brake shaft 14, and the gear side connecting member 48 is fixed to the brake gear 11. The brake side connecting member 47 and the gear side connecting member 48 are connected to each other via a compression coil spring 46.

For forward rotation of the warp beam 2, the brake gear 11 rotates in a direction in which the compression coil spring 46 is compressed. When the brake gear 11 rotates and the compression coil spring 46 is completely compressed, or when the compression force of the compression coil spring 46 reaches a compression amount corresponding to the braking force of the braking device 10, the rotation of the brake gear 11 is transmitted to the brake disc 25. The braking force of the braking device 10 acts on the warp beam 2.

During the reverse rotation of the warp beam 2, the brake gear 11 rotates in a direction to release the compression coil spring 46. As a result, the compression coil spring 46 rotates while applying a biasing force to the brake gear 11. At this time, since the rotation of the brake gear 11 is not transmitted to the brake disc 25, the braking force of the braking device 10 is not applied to the brake gear 11. It should be noted that the amount of rotation at the time of reverse rotation does not exceed the braking force (the brake disk 25 does not rotate in reverse rotation), or does not exceed the braking force, that is, has a sufficient amount of twist corresponding to the amount of reverse rotation. The spring constant of the compression coil spring 46 is determined.

[Embodiment 6 (FIG. 8)]
In the sixth embodiment, instead of using the one-way clutch as the one-way rotation transmission device 13 in the first embodiment (FIG. 2), a brake disc sandwiched between a pair of brake disks 25 as shown in FIG. This is an example in which 23 can be rotated within a predetermined range. In FIG. 8, the brake disc 23 is inserted into and supported by the support column 20 through a mounting hole 49 that is a long hole in the circumferential direction. Therefore, together with the pair of brake disks 25 only within the range of the long hole as the mounting hole 49. It can be rotated.

During the forward rotation of the warp beam 2, the brake shaft 14 rotates, so that the pair of brake discs 25 and the brake disc 23 sandwiched between them rotate together. When one end of the brake disc hits the support column 20, the brake disc 23 stops, and the pair of brake discs 25 rotate with the frictional force acting on the brake disc 23. Therefore, the braking device 10 applies the braking force to the warp beam 2. .

During the reverse rotation of the warp beam 2, the brake shaft 14 is rotated, but the pair of brake discs 25 and the brake disc 23 sandwiched between them rotate together, and other than the mounting hole 49 of the brake disc 23, that is, a long hole. When the end hits the column 20, the brake disc 23 stops. In this manner, the braking force is not applied to the braking device 10 until the mounting hole (long hole) 49 of the brake disk 23 and the support column 20 come into contact with each other. The amount of rotation of the warp beam 2 at the time of reverse rotation is set until the mounting hole 49 of the brake disk 23 hits the support column 20 (to the extent that no braking force is applied to the reverse rotation), and no further reverse rotation is performed. Therefore, the sixth embodiment is applied to a mechanical drive device 3, for example, a mechanical drive device 3 including a transmission that changes a gear ratio according to warp tension T. Since the electric drive device 3 may be reversed many times by the dedicated motor 32, it is applied by limiting the amount of reverse rotation in the drive device 3 or widening the formation range of the mounting hole 49.

[Description of feed drive by worm gear mechanism]
As described above, the rotation (forward rotation) drive in the delivery direction of the warp beam 2 causes the braking force against the warp tension T to act, so that the load is relaxed with respect to the warp tension T in which the rotation direction is the same. Driven. For this reason, in general, a worm gear is often used for the feeding drive. The worm gear (the worm 34 and the warp beam gear 35 of the worm wheel) always applies a braking force to the warp beam 2 so that the warp beam 2 does not idle when the warp 9 is fed. The torque required for the drive device 3 during the forward rotation of the warp beam 2 depends on the magnitude of the braking force by the worm gear (the worm 34 and the warp beam gear 35 of the worm wheel), that is, the magnitude of the warp tension T.

In general, in the case of delivery using a worm gear, the necessary motor torque TF during forward rotation and the necessary motor torque TR during reverse rotation with respect to the warp tension T of the dedicated motor 32 connected to the worm gear have a relationship of TF <TR. Further, the ratio TR / TF = 3 to 4 (when the advance angle is 10 ° or less). This indicates that the motor torque TR at the time of reverse rotation is required to be 3 to 4 times that at the time of forward rotation without the braking device 10, and it becomes a problem to reduce the motor torque TR required at the time of reverse rotation.

Conventionally, the reduction ratio of the dedicated motor 32 is increased in order to increase the motor torque TR at the time of reverse rotation. However, if the reduction ratio is large as an adverse effect, the maximum rotational speed of the warp beam 2 is lowered and cannot be used for coarse density weaving. . Further, when trying to cope with the coarse density, it becomes impossible to cope with the high warp tension T. Further, when the outer diameter of the warp beam 2 is large or when the warp tension T is high, the required torque of the drive device 3 of the warp beam 2 increases, but the warp feeding device 1 of the loom using the worm gear is braked. When the device 10 is provided, the worm gear braking force is partially borne by the braking force of the braking device 10 (hereinafter referred to as the warp beam braking force) during the normal rotation of the warp beam 2. The required torque of the driving device 3 at that time is a torque corresponding to (warp tension T) − (warp beam braking force B).

However, when the warp beam 2 is reversely rotated, the warp beam 2 must be rotated by a torque that overcomes (warp tension T) + (warp beam braking force B) as opposed to forward rotation. Therefore, the required torque for reversing the warp beam 2 is a torque corresponding to (warp tension T) + (warp beam braking force B). For this reason, the capacity of the drive device 3 is determined by the required torque at the time of reverse rotation of the warp beam 2. Must be selected. In addition, for this reason, without using the original torque, allowable warp tension and driving density range (the number of weft insertions per inch, the smaller (coarse), the faster the warp beam needs to be rotated), etc. The range is limited.

As described above, the present invention can be applied not only to the electric drive device 3 but also to the mechanical drive device 3. Further, the braking means 10 may apply braking over the entire sending-out period, and in a weaving machine that changes the weaving conditions during weaving, the weaving condition is likely to occur or the warp beam 2 is likely to vibrate. Only the braking device 10 may apply braking. Further, control by the braking device 10 may be applied to the transmission device 5. Specifically, a braking force may be applied between the drive shafts 33 by the drive device 10 connected to the one-way clutch. However, this case can be applied when a dedicated motor having a braking function is used without using a worm gear.

It is a side view of the warp delivery apparatus 1 of a loom. 1 is a cross-sectional view of a main part of a warp feeding device 1 for a loom according to Embodiment 1. FIG. 6 is a cross-sectional view of a main part of a warp feeding device 1 for a loom according to Embodiment 2. FIG. It is a model explanatory drawing of the principal part of the warp delivery apparatus 1 of the loom by Embodiment 3. It is a model explanatory drawing of the principal part of the warp delivery apparatus 1 of the loom by Embodiment 4. FIG. 10 is a schematic explanatory diagram of a main part of a warp feeding device 1 of a loom according to a fifth embodiment. It is explanatory drawing of the principal part seen from the arrow direction of A in FIG. It is a model explanatory drawing of the principal part (brake disc 23) of the warp sending apparatus 1 of the loom by Embodiment 6.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Warp delivery device 2 of a loom 2 Warp beam 3 Drive device 4 Drive source 5 Transmission device 10 Braking device 11 Brake gear 12 Braking force relaxation means 13 Unidirectional rotation transmission device 14 Brake shaft 21 Rotating shaft 23 Brake disc 25 Brake disc 27 Brake Spring 31 Actuator 32 Dedicated motor 33 Drive shaft 34 Warm 35 Warp beam gear 45 Torsion coil spring 46 Compression coil spring 47 Mounting hole 50 Gear 51 Gear 52 Rotating shaft

Claims (4)

A drive device (3) comprising a rotation drive source (4) and a transmission device (5) for transmitting the rotation of the drive source (4) to the warp beam (2) is provided. In a warp feeding device (1) of a weaving machine that rotates the warp beam (2) in the feeding direction while acting a counteracting braking force on the warp beam (2),
In addition to the braking force of the drive device (3), a warp feeding device (1) for a loom is provided, which is provided with a braking device (10) for applying a braking force to the warp beam (2). The warp feeding device (1) is also rotatable in the counter-feeding direction, and includes a braking force relaxation means (12) for relaxing the braking force of the braking device (10) when the warp beam (2) rotates in the counter-feeding direction. The warp feeding device (1) for a loom according to claim 1, characterized in that it is provided in a braking device (10). The braking force relaxation means (12) comprises a one-way rotation transmission device (13) interposed between the braking device (10) and the rotating shaft (21) of the warp beam (2). The warp feeding device (1) of the loom described. The braking force relaxation means (12) comprises an actuator (31) for reducing the contact pressure of the brake disc (25) against the brake disc (23) integral with the brake shaft (14). Warp feeding device (1) of the loom.

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