CN105386219A - Batching tension adjusting device of loom - Google Patents

Abstract

The invention provides a fabric tension adjusting device for a loom. The fabric tension adjusting device of the loom includes a roll diameter following lever that rotates according to changes in the roll diameter of the fabric wound on the fabric roll, and a roll that adjusts the fabric winding torque according to the amount of rotation of the roll diameter following lever. The cloth torque adjustment device prevents wrinkles from being generated on the fabric by appropriately changing the cloth winding torque per unit winding diameter increase. The cloth winding tension adjustment device of the loom is equipped with a link mechanism, which is composed of a winding diameter following rod and a rotating rod connected to the cloth winding torque adjustment device, and the two link parts are directly connected. In the above, the initial arrangement of the two link members is set so that the amount of rotation of the rotation rod obtained by the rotation of the rotation of the rotation of the rotation of the rotation of the rotation of the rotation of the rotation of the rotation of the rotation of the rotation of the rotation of the rotation of the rotation of the winding diameter following the increase of the winding diameter accompanying the increase of the predetermined unit winding diameter with the increase of the predetermined unit winding diameter immediately after the winding is set. The rotation amount of the turning lever obtained by turning the winding diameter following lever around the increase of the winding diameter accompanying the increase of the unit winding diameter immediately before the end becomes smaller.

Description

Cloth tension adjustment device for loom

technical field

The present invention relates to a fabric tension adjusting device used in a loom, in particular to a fabric tension adjustment device that is rotatably supported on the frame of a loom and according to the roll diameter of the fabric (cloth) wound on the fabric roll (cloth roll plus The winding diameter following lever that rotates according to the change of the winding diameter) and the winding torque adjustment device that adjusts the driving torque (cloth winding torque) of the winding roller according to the rotation amount of the above winding diameter following lever Tension adjustment device.

Background technique

As the conventional technology of the above-mentioned web tension adjusting device, there is a technology disclosed in Patent Document 1. The fabric tension adjusting device disclosed in this patent document 1 includes: a detection rod as the above-mentioned winding diameter following rod; It is a friction transmission unit that rotates the rotary body and the shaft connected to the cloth roll, and changes the friction transmission according to the rotation amount of the detection rod accompanying the increase of the roll diameter of the cloth (hereinafter also simply referred to as "roll diameter"). The transmitted torque of the unit. In addition, according to the cloth tension adjusting device, the detection rod rotates as the winding diameter increases due to the progress of spinning, and the pressing force on the friction plate of the friction transmission unit of the cloth torque adjusting device is proportional to the rotation amount of the detection rod. As a result, the cloth winding torque is increased proportionally to the increase of the winding diameter (single-dot chain line I in Fig. 5(a)), and the tension of the winding cloth (cloth tension) can be adjusted.

In addition, the winding tension is calculated by dividing the winding torque by the winding diameter. That is, assuming that the winding tension is F, the winding torque is T, and the winding diameter is D, it can be obtained as F=T/D. In addition, in the loom, regarding the adjustment of the cloth tension accompanying the progress of weaving (the increase in the above-mentioned roll diameter), it is generally desired that the cloth tension be reduced in proportion, in other words, it is desired that the roll diameter increase per unit roll diameter. The degree of reduction of the winding tension due to the increase (hereinafter also simply referred to as "reduction degree") is fixed.

However, the "increase in the unit diameter of the coil" as used herein means a predetermined increase in the diameter of the coil. Therefore, the "increase in the coil diameter per unit coil diameter increase" means, for example, when the unit coil diameter increase is 100 mm, the coil diameter increases from 100 mm to 200 mm, or from 200 mm to 300 mm. situation etc. In addition, the "increase in coil diameter per unit coil diameter increase" is also simply referred to as "increase in unit coil diameter" hereinafter. In addition, "the degree of reduction of the fabric tension due to the increase in the roll diameter per unit roll diameter increase" means that the fabric tension at the last time (roll diameter at this time: De) during the increase of each unit roll diameter is The rate of change in the direction of decrease in the tension of the fabric tension with respect to the initial time (winding diameter at this time: Ds) (corresponds to the inclination of the graph in FIG. 5( b )). Specifically, it means that, for example, if the increment of the unit winding diameter is 100 mm, the ratio of change of the value of the winding tension at De=200 mm to the value of the winding tension at Ds=100 mm, or The change ratio of the value of the fabric tension at De=300 mm to the value of the fabric tension at Ds=200 mm, etc.

In addition, if the fabric tension at the first time (roll diameter: Ds) is Fs, and the fabric tension at the last time (roll diameter: De) is Fe, the degree of decrease (change ratio) Based on the difference between Fs and Fe (hereinafter also simply referred to as "tension difference"). On the other hand, if the relationship between Fe and Fs is taken into consideration, if the fabric winding torque at the first moment is Ts and the fabric winding torque at the last moment is Te, the fabric tension will pass as described above. The winding torque is calculated by dividing the winding diameter, so the ratio of the two: Fe/Fs becomes the ratio of Te to Ts: Te/Ts divided by the ratio of De to Ds: De/Ds. That is, it becomes Fe/Fs=(Te/Ts)/(De/Ds). Therefore, if the ratio of the above-mentioned winding torque is Tr (=Te/Ts), and the ratio of the winding diameter is Dr (=De/Ds), the relationship between Fs and Fe is Fe=Tr/Dr×Fs . And, if the above-mentioned tension difference, that is, Fs−Fe=(1−Tr/Dr)×Fs is constant when the winding diameter per unit increases, the above-mentioned degree of decrease is constant.

In addition, in the fabric tension adjusting device disclosed in Patent Document 1, in order to make the above-mentioned decrease degree closer to a constant state, that is, to reduce the above-mentioned tension difference per unit roll diameter increase as much as possible, the above-mentioned structure is adopted. . More details are as follows.

For example, in the case where the fabric winding torque is constant from the start of winding of the fabric to the end of winding, as shown by the two-dot chain line J1 shown in Fig. 5(a), the degree of reduction is as shown in Fig. 5(b) As the two-dot dash line J2, it gradually becomes smaller with the increase of the roll diameter. The reason is that, as mentioned above, the above-mentioned reduction degree is based on the above-mentioned tension difference, and the tension difference is obtained by multiplying Fs (=Ts/Ds) in the increase of each unit winding diameter by the above-mentioned (1-Tr/Dr) However, when the cloth winding torque is constant, the ratio of the cloth winding torque is constant (Tr=Te/Ts=1), so the tension difference is (1−1/Dr)×Fs.

And, since the ratio Dr (=De/Ds) of the above-mentioned coil diameter per unit coil diameter increases decreases in inverse proportion as the coil diameter becomes larger (for example, if the unit coil diameter increment is set to 100 mm, the above The ratio Dr of the roll diameter becomes 2 times when the roll diameter increases from 100mm to 200mm, and becomes 1.5 times when the roll diameter increases from 200mm to 300mm. In addition, when the roll diameter increases from 300mm to 400mm, it becomes approximately 1.33 times, and becomes 1.25 times when the roll diameter increases from 400mm to 500mm), so the above-mentioned (1-1/Dr) per unit roll diameter increases gradually decreases with the increase of the roll diameter, and Fs also It gradually becomes smaller with the increase of the coil diameter. Therefore, the above-mentioned tension difference per unit coil diameter increase gradually becomes smaller as the coil diameter becomes larger, and the above-mentioned reduction degree (change ratio) gradually becomes smaller as the coil diameter increases.

In this way, if the cloth winding torque is constant from the beginning of winding to the end of winding, the degree of decrease will gradually decrease with the increase of the winding diameter, and the winding tension will decrease inversely proportional to the increase of the winding diameter. And, as a result, wrinkles are generated in the fabric wound on the cloth roll, and the quality of the woven fabric deteriorates.

Therefore, in the fabric tension adjusting device disclosed in Patent Document 1, in order to reduce the change in the above-mentioned reduction degree when the coil diameter increases, the above-mentioned structure is adopted, and the fabric coil torque is increased by 10% according to the increase of the coil diameter. increase proportionally. In addition, according to this structure, compared with the case where the winding torque is constant, the ratio Dr of the winding diameter per unit winding diameter increases with the same change with the increase of the winding diameter, but the ratio Tr of the winding torque becomes It is a larger value than the case where the winding torque is constant when each unit winding diameter increases, so the above-mentioned tension difference becomes smaller when each unit winding diameter increases, as indicated by the single-dot dash line I in the graph of Fig. 5(b) It is shown that the degree of reduction mentioned above is alleviated.

prior art literature

patent documents

Patent Document 1: Japanese Mihiko 02-013503

Contents of the invention

The problem to be solved by the invention

However, even with the fabric tension adjusting device disclosed in Patent Document 1, although the above-mentioned reduction is reduced (decreased) compared with the case where the fabric winding torque is constant, it still gradually decreases as the winding diameter increases. , so the fabric wound on the fabric roll cannot be sufficiently prevented from wrinkling. More details are as follows.

In the fabric tension adjusting device disclosed in Patent Document 1, the fabric winding torque is changed in proportion to the amount of rotation of the rod in the fabric winding torque adjusting device that rotates with the rotation of the detection lever. In the adjusting device, the rod is configured to be rotated by a shaft to which the detection rod is fixed and which rotates with the rotation of the detection rod. Specifically, the rod is supported so as to be relatively non-rotatable with respect to the shaft to which the probe rod is fixed. Therefore, in this fabric tension adjusting device, the above-mentioned lever rotates by the same amount as the detection lever. On the other hand, the detection lever rotates by a predetermined amount in proportion to the increase in the winding diameter per unit. Therefore, the winding torque increase proportionally.

Here, regarding each section where the coil diameter increases per unit, for example, the increment of the unit coil diameter is set to 100 mm, the zone where the coil diameter is increased from 100 mm to 200 mm is set as the first zone, and the zone where the coil diameter is increased from 200 mm to 300 mm is Set the section as the second section, set the section where the roll diameter increases from 300mm to 400mm as the third section, set the section where the roll diameter increases from 400mm to 500mm as the fourth section, and set the winding start (the above-mentioned initial period of the first section) The time) of the cloth winding tension is set as F1, and the cloth winding torque is set as T1, after that, when the winding diameter per unit increases, the cloth winding torque increases in proportion to a, that is, the above-mentioned initial time of each interval If the winding torque is T1+a in the second interval, T1+2a in the third interval, and T1+3a in the fourth interval, the winding tension Fs at the first moment in each interval is the same as the last moment in the above interval. The tension difference R1, R2, R3, R4 of the fabric tension Fe in the first interval is R1=1/2×{(T1-a)/T1×F1}, in the second interval it is R2=1/6×{ (T1-a)/T1×F1}, in the third interval, it is R3=1/12×{(T1-a)/T1×F1}, in the fourth interval, it is R4=1/20×{(T1-a )/T1×F1}. Incidentally, when the cloth winding torque is constant, the above-mentioned a is 0.

From the above calculation formula, it is clear that the above-mentioned tension difference of the fabric tension corresponding to the degree of reduction of the fabric tension is constant when the above-mentioned a is constant, that is, when the fabric torque increases in proportion to the increase of the fabric diameter per unit. Next, {(T1-a)/T1×F1} becomes a constant and changes in a gradually decreasing manner. It is 1/2 of the constant in the first interval, 1/6 of the constant in the second interval, and 1/6 of the constant in the second interval. The third interval is 1/12 of the constant, and the fourth interval is 1/20 of the constant, and changes gradually. Therefore, in the configuration in which the fabric winding torque is increased in proportion to the increase in the winding diameter as in the fabric tension adjusting device of Patent Document 1, the fabric winding torque is constant from the start of winding to the end of winding. Similarly, the degree of reduction mentioned above does not become nearly constant, and the fabric tension decreases inversely proportional to the increase of the roll diameter. Therefore, even the fabric tension adjusting device according to Patent Document 1 cannot sufficiently prevent the fabric wound on the fabric roller from being wrinkled.

In addition, Patent Document 1 discloses a technique for increasing the winding torque quadratically (inversely proportional) as the winding diameter increases. Specifically, in the fabric tension adjustment device disclosed in Patent Document 1, the intersecting angle between the pressing arm that applies a pressing force to the friction plate of the friction transmission unit and the adjustment lever connected to the pressing arm is configured to be , and at each abutment position of the above-mentioned rod relative to the adjustment rod, the spring length of the spring biasing the above-mentioned rod to the adjustment rod side is changed, thereby changing the active force of the spring at the above-mentioned each abutment position, and then changing the pressing arm The pressing force of the friction plate acting on the friction transmission unit.

However, as described above, since the above-mentioned rod is supported so as to be relatively non-rotatable with respect to the above-mentioned shaft on which the detection rod is fixed, the movement of the spring due to the displacement of the contact position of the rod with respect to the adjustment rod as described above When the action force changes, the contact force of the probe rod to the fabric at the contact position of the probe rod and the fabric changes due to the reaction force of the spring, which may cause a change in the state of the wound fabric, which may affect the The quality of the fabric is adversely affected.

In view of the actual conditions of the existing cloth tension adjusting device as above, the object of the present invention is to provide a cloth tension adjusting device for a loom, which can properly adjust the tension of the cloth without changing the force acting on the rod by the spring. By changing the winding torque per unit winding diameter, the winding tension can be reduced approximately proportionally, and wrinkles can be prevented from being generated in the fabric wound on the winding roller.

Solution to the problem

The present invention presupposes a fabric tension adjusting device that is rotatably supported on the loom frame via a first support shaft and that adjusts according to changes in the roll diameter of the fabric wound on the fabric roll. A rolling diameter following lever that rotates; and a fabric winding torque adjusting device that adjusts the winding torque according to the amount of rotation of the rolling diameter following lever.

Furthermore, the fabric tension adjusting device of the present invention, which is based on the fabric tension adjusting device described above, is characterized in that it includes a link mechanism that includes, as a link member, the above-mentioned roll diameter following lever and a turning lever, and the turning The rod is rotatably supported on the loom frame via the second support shaft and connected to the cloth winding torque adjustment device, the winding diameter following rod and the rotation rod are directly connected, and the connecting portion can move toward the winding diameter following rod. And the extension direction displacement of one link member in the above-mentioned rotating rod, and, in the above-mentioned link mechanism, the initial arrangement of the above-mentioned link members is set so that, with respect to the specified unit winding diameter immediately after the start of winding The amount of rotation of the above-mentioned rotation lever obtained by the rotation of the above-mentioned winding diameter following the increase of the above-mentioned winding diameter of the increment, and the above-mentioned winding diameter following the above-mentioned winding diameter following the increase of the above-mentioned winding diameter with the above-mentioned unit winding diameter increase immediately before the end of winding The amount of rotation of the above-mentioned rotation lever obtained by the rotation becomes smaller.

In addition, the fabric tension adjusting device of the present invention is characterized in that, when the one link member is the winding diameter following lever, the initial arrangement of the link mechanism is set so that when the winding diameter following lever rotates, The range is such that the line segment connecting the second support shaft supporting the rotation lever and the connecting portion is on the side of the rotation direction of the winding diameter following rod relative to the line segment connecting the first supporting shaft supporting the rolling diameter following rod and the connecting portion. The formed angle satisfies any one of the following conditions (a) to (c):

(a) The angle range is between 90° and 195°, and the beginning of winding is closer to 90° than the end of winding;

(b) Angle range between -15° and 90°, and the beginning of winding is closer to 90° than the end of winding;

(c) It is included in the angular range of more than 270° and 375°, and the start of winding is closer to 270° than the end of winding.

In addition, the fabric tension adjusting device of the present invention is characterized in that, when the one link member is the rotation lever, the initial arrangement of the link mechanism is set such that, within the rotation range of the winding diameter following lever, The line segment that connects the second support shaft that supports the rotation lever and the connecting portion is formed on the side of the rotation direction of the roll diameter following rod with respect to the line segment that connects the first support shaft that supports the above-mentioned winding diameter following rod and the connecting portion. The angle satisfies any one of the following conditions (d) to (f):

(d) Angle range between 170° and 270°, and the end of winding is closer to 270° than the beginning of winding;

(e) included in the angular range exceeding 270° and less than 370°, and the end of winding is closer to 270° than the beginning of winding;

(f) The angular range is from -10° to 90°, and the angle at the end of winding is closer to 90° than at the start of winding.

Among them, in the above description, "initial configuration" means the initial state (the state at the start of winding, or the state in which the above-mentioned winding diameter following rod abuts against or approaches the cloth winding roller before the fabric starts to be wound and is still. (The two states are substantially the same)) the arrangement of the above-mentioned link members. In addition, regarding the above-mentioned initial configuration, it is not limited to the position of the first support shaft supporting the above-mentioned rolling diameter following rod or the position of the above-mentioned second supporting shaft supporting the above-mentioned rotating rod, but also includes the position of the above-mentioned winding diameter following rod and the above-mentioned rotating rod. The arrangement of the angle formed by one of the two link members relative to the other.

In addition, in this application, "the line segment connecting the said 1st support shaft (the said 2nd support shaft) and the said connection part" means connecting the said 1st support shaft (the said 2nd support shaft) more specifically. The line segment between the axis center of the above-mentioned link and the center of the above-mentioned connecting part. In addition, a "connection part" is a part of the link mechanism in which the winding diameter tracking rod and the rotation rod are in a connected state, in other words, a part of the link mechanism in which the winding diameter following rod and the rotation rod intersect and overlap. In addition, "the above-mentioned winding diameter following lever and the above-mentioned rotation rod are directly connected" means that the above-mentioned winding diameter following rod and the above-mentioned rotation rod are connected without intervening other link members.

In addition, in the application, "-" in "-X°" (X: positive number) shown in the above-mentioned condition (b) [the above-mentioned condition (f)] such as "-15° [-10°]" means that the angle X formed by the line segment connecting the first support shaft supporting the winding diameter following rod and the connecting portion and the line segment connecting the second supporting shaft supporting the turning rod and the connecting portion The formed side is opposite to the rotation direction side of the above-mentioned winding diameter following lever. That is, regarding the above-mentioned condition (b) [the above-mentioned condition (f)], "the angle formed by the rotation direction side of the above-mentioned winding diameter following lever is -15° [-10°]" means "the angle between the above-mentioned winding diameter following lever The angle formed by the opposite sides of the rotation direction of the rod is 15° [10°]". Therefore, in the above-mentioned condition (b) [the above-mentioned condition (f)], "the angle range between -15° [-10°] and 90°" includes "the angle formed on the opposite side of the rotation direction of the above-mentioned winding diameter following lever." The angle is the angle range of 15° [10°] to 0°" and the angle range of "the angle formed by the rotation direction side of the above-mentioned rolling diameter following rod is 0° to 90°".

By the way, the relationship between the above-mentioned link members when the angle (hereinafter also referred to as "angle α") formed by the rotation direction side of the winding diameter following lever is 0° is, for example, like the long hand and short hand of a clock. Just overlap at twelve o'clock, and the above-mentioned two line segments are in a state of exactly overlapping. Therefore, the above-mentioned "angle range from -15° [-10°] to 90°" includes 0°, which is an angle at which the two line segments just overlap each other. In addition, when the above two line segments are exactly overlapping, the angle α can be regarded as 360°, so in this application, it is generally considered that “the angle α is 0°” = “the angle α is 360°”.

In addition, in the present application, "375° [370°]" shown in the above condition (c) [the above condition (e)] means that the angle α becomes "360°+15° [10°]" . Therefore, the "angle range exceeding 270° and 375° [370°]" in the above condition (c) [the above condition (e)] includes "the angle range of angle α from an angle exceeding 270° to 360°" and the angle range of "the angle range of angle α from 360° to 375° [370°]". In addition, as mentioned above, in this application, since "angle α is 0°" = "angle α is 360°", the above-mentioned "angle range exceeding 270° and below 375° [370°]" includes the above two The angle at which two line segments are exactly overlapped is 0° (360°). Therefore, the above-mentioned "angular range of angle α from 360° to 375° [370°]" can be said to be "angle range of angle α from 0° to 15° [10°], the above-mentioned condition (c) [the above-mentioned condition ( e)] in "the angle range exceeding 270° and below 375° [370°]" is generally considered to include "the angle α ranges from the angle exceeding 270° to 360°" and "the angle α ranges from 0° to 15° °[10°] angle range".

The effects of the present invention are as follows.

According to the present invention, in the winding cloth tension adjusting device as the above-mentioned premise, by using the above-mentioned link mechanism and setting the initial arrangement of the above-mentioned winding diameter following lever and the above-mentioned rotation lever as described above, the winding tension can be adjusted with respect to the winding start. The amount of rotation of the above-mentioned rotating lever obtained by the rotation of the above-mentioned rolling diameter following the increase of the winding diameter of the predetermined unit winding diameter increase after the winding can be reduced by the winding diameter of the above-mentioned unit winding diameter increase immediately before the end of winding. The amount of rotation of the above-mentioned rotating rod obtained by the rotation of the above-mentioned rolling diameter following the rod.

In addition, by changing the rotation amount of the above-mentioned rotation lever when the winding diameter per unit is increased in this way, it is not necessary to change the biasing force of the springs at the above-mentioned contact positions by adopting a structure that changes the length of the spring as disclosed in Patent Document 1. , the winding torque can be appropriately changed when the winding diameter increases per unit. Specifically, as shown by the solid line H1 in Fig. 5(a), the winding torque can be increased in inverse proportion, and as a result, the degree of reduction in the winding tension per unit winding diameter becomes substantially constant, as shown in As indicated by the solid line H2 shown in FIG. 5( b ), the fabric winding tension decreases substantially proportionally, so that wrinkles can be prevented from occurring in the fabric wound on the fabric fabric roller.

Description of drawings

Fig. 1 is a side view schematically showing main parts on the winding side of a loom equipped with a link mechanism 41 according to the first embodiment.

Fig. 2(a) and Fig. 2(b) are diagrams of the cloth winding torque adjusting device, wherein Fig. 2(a) is a top view including a part of a cross section along line AA, and Fig. 2(b) is a front view.

FIG. 3 is a diagram showing the movement trajectory of the link mechanism 41 from the start of winding to the end of winding in the first embodiment.

FIG. 4 is a reference diagram for setting the position of the support shaft 48 of the rotation lever 43 in the first embodiment.

FIG. 5( a ) is a graph showing changes in cloth winding torque with respect to the winding diameter, and FIG. 5( b ) is a graph showing changes in cloth winding tension with respect to the winding diameter.

6(A) and 6(B) show the characteristics of the link mechanism, FIG. 6(A) is a graph represented by a wave curve A, and FIG. 6(B) is a graph represented by a wave curve B.

FIG. 7 is a diagram showing an example of the link mechanism A corresponding to the waveform curve A. As shown in FIG.

FIG. 8 is a graph showing changes in follower displacement accompanying changes in the lever ratio in the link mechanism A of FIG. 7 .

FIG. 9 is a diagram showing an example of a link mechanism B corresponding to a waveform curve B. As shown in FIG.

FIG. 10 is a graph showing changes in the follower displacement amount accompanying changes in the lever ratio in the link mechanism B of FIG. 9 .

Fig. 11 is a side view schematically showing main parts on the winding side in the loom equipped with the link mechanism 59 in the second embodiment.

FIG. 12 is a diagram showing the movement trajectory of the link mechanism 59 from the start of winding to the end of winding in the second embodiment.

In the picture:

1—fabric (cloth roll), 2—fell, 3—yarn pressing roller, 4—cloth pressing roller, 5—yarn pressing roller, 6—cloth rolling roller, 6a—axis of cloth rolling roller 6, 7—axis Department, 8—bearing, 9—loom frame, 10—cloth winding torque adjustment device, 11—connecting shaft, 12—bearing, 13—sprocket, 14—friction transmission unit, 15—disc shell, 15a—connection Part, 15b—hollow portion, 16—friction transmission portion, 17—pressing force generating portion, 18—support pin, 19—rotating plate, 20—driven plate, 21—friction plate, 22—pressing plate, 23—pressing force Setting part, 24—Friction adjustment part, 25—Compression spring, 26—Adjusting nut, 27—Pressure rod, 27a—Abutment surface, 28—Follower rod, 29—Support shaft, 30—Pressure roller , 31—support rod, 32—abutment rod, 33—force setting part, 34—support shaft, 34a—axis center of support shaft 34, 35—bearing, 36—support shaft, 37—roller, 38— Guide shaft, 39—adjusting nut, 40—compression spring, 41—(in the first embodiment) linkage mechanism, 42—rolling diameter following rod, 42a—support portion, 42b—middle portion, 42c—contact portion, 42d—through hole, 42e—long hole, 43—rotating rod, 43a, 43b—through hole, 44—connecting pin, 44a—the axis of connecting pin 44 (the center of the connecting portion), 45—supporting shaft (the first support shaft), 45a—the axis of the support shaft 45 (the axis of the first support shaft), 46—the roller, 46a—the axis of the roller 46, 47—the joint, 48—the support shaft (the second support shaft) , 48a—the axis of the support shaft 48 (the axis of the second support shaft), 49, 50—the timing pulley, 51—the timing belt, 52—the rotation transmission mechanism, 53—the drive side link member, 53a—the drive side The center of rotation of the link member 53, 54—the driven side link member, 54a—the rotation center of the driven side link member 54, 55—the connecting portion of the two link members, 55a—the center of the connecting portion 55 (connection point ), 56—the driving side link member, 56a—the rotation center of the driving side link member 56, 57—the driven side link member, 57a—the rotation center of the driven side link member 57, 58—the two link members 58a—the center (connection point) of the connecting portion 58, 59—(in the second embodiment) linkage mechanism, 60—rolling diameter following rod, 60a—supporting portion, 60b—middle part, 60c—resisting Connecting portion, 60d, 60e—through hole, 61—rotating rod, 61a—through hole, 61b—long hole, 62—joint portion, 63—support shaft (second support shaft), 63a—the axis of support shaft 63 ( The axis of the second support shaft), 64—connection pin, 64a—the axis of the connection pin 64 (the center of the connection portion), X—rolling diameter following the rotation direction of the rod 42, Y—the rotation direction of the rotation rod 43, V - the direction of rotation of the drive side link member 53, W - the direction of rotation of the driven side link member 54, V' - the direction of rotation of the drive side link member 56 , W'—the direction of rotation of the driven side link member 57, X'—the direction of rotation of the rolling diameter following rod 60, Y'—the direction of rotation of the rotating rod 61.

detailed description

Hereinafter, a first embodiment of the present invention will be described based on FIGS. 1 to 10 .

In the loom, as shown in FIG. 1 , the woven fabric 1 is wound on the cloth roll 6 from the cloth fell 2 via the pressure roller 3, the pressure roller (cloth roll) 4, and the pressure roller 5. In addition, the cloth winding roller 6 is rotatably supported by the loom frame 9 via bearings 8 at shaft portions 7 provided at both ends thereof. In addition, the cloth winding roller 6 is connected to the main shaft of the loom (prime motor) not shown in the figure to be rotationally driven by the main shaft of the loom, and the cloth winding torque adjustment device interposed between the main shaft of the loom and the cloth winding roller 10 to adjust its rotation torque.

This cloth winding torque adjustment device 10 is, for example, the device shown in FIG. 2( a ) and FIG. 2( b ), but basically has the same configuration as the cloth winding torque adjustment device in Patent Document 1 described above. Specifically, as shown in FIG. 2( a ), the cloth winding torque adjustment device 10 includes: a connecting shaft 11 connected to the shaft portion 7 of the cloth winding roller 6 ; And the sprocket 13 driven by rotation of the main shaft of the loom;

In addition, in the present embodiment, the sprocket 13 is supported on the loom frame 9 so that its rotation axis coincides with the axis 6 a of the cloth winding roller 6 . On the other hand, the connecting shaft 11 is connected and fixed so that the axis thereof coincides with the shaft portion 7 of the cloth winding roller 6 . Therefore, the sprocket 13 and the connecting shaft 11 are arranged concentrically with each other. In addition, a through hole having a diameter larger than that of the connecting shaft 11 is formed at the center of the sprocket 13 , and the connecting shaft 11 passes through the through hole and extends toward the opposite side of the cloth winding roller 6 .

The friction transmission unit 14 includes: a disk-shaped casing 15 that is concentrically configured with the sprocket 13 and is relatively non-rotatably connected outside the loom frame 9; a friction transmission portion 16 that connects the disk-shaped casing 15 and the connection shaft 11; The pressing force acts on the pressing force generating portion 17 of the friction transmission portion 16 . Wherein, the disk-shaped housing 15 is a hollow cylindrical member, and has a connecting portion 15a for connecting with the sprocket 13 on one of the two side edges in the axial direction, and the connecting portion 15a has a through hole with the above-mentioned sprocket 13. A through hole with the same diameter as the hole. Furthermore, the friction transmission part 16 is provided in the hollow part 15b of the disk-shaped case 15. As shown in FIG.

The friction transmission part 16 includes a pair of support pins 18 extending parallel to the rotation axis of the disk housing 15 from the inner surface of the coupling part 15 a of the disk housing 15 and symmetrical across the rotation axis of the disk housing 15 . The position is installed on the connecting portion 15a of the disk-shaped casing 15; and a plurality of (two in the illustrated example) disk-shaped rotating plates 19, which penetrate a pair of support pins 18 in the hollow portion 15b of the disk-shaped casing 15 The snap fit is thus arranged coaxially with the disk-shaped housing 15 and relatively non-rotatable. In addition, this rotating plate 19 is not fixed with respect to each support pin 18, but can displace in the rotation axis direction of the disk-shaped housing 15. As shown in FIG. In addition, the rotating plate 19 has a through hole having a diameter larger than that of the connecting shaft 11 at its central portion, and the connecting shaft 11 is inserted into the through hole.

In addition, the friction transmission unit 16 includes a plurality of (two in the illustrated example) disks provided between adjacent rotating plates 19 and between the rotating plates 19 and the inner surface of the connecting portion 15 a of the disk housing 15 . and a plurality of disc-shaped friction plates 21 disposed between the rotating plate 19 and the driven plate 20 , and the inner surface of the connecting portion 15 a of the driven plate 20 and the disc-shaped housing 15 . Each driven plate 20 is fitted with the connecting shaft 11 at its central portion, and is attached so as to be displaceable in the axial direction with respect to the connecting shaft 11 and relatively non-rotatable. Wherein, the diameter of each driven plate 20 is smaller than that of the rotating plate 19 , and its outer peripheral edge is located inside the pair of supporting pins 18 . In addition, each friction plate 21 is an annular member having the same diameter as the driven plate 20 and having a through-hole inside that is larger than the through-hole of the above-mentioned rotating plate 19 . In addition, the part of each driven plate 20 that faces the friction plate 21 on the outer peripheral side is formed thinner, so that a stepped portion is formed on both surfaces, and each friction plate 21 adjacent to the driven plate 20 is engaged with the driven plate 20 . The stepped portion of the moving plate 20. Therefore, the friction plate 21 cannot be displaced relative to the driven plate 20 mounted on the connecting shaft 11 in the radial direction.

In addition, the friction transmission part 16 receives the pressing force in the direction of the rotation axis of the disc housing 15 acted by the pressing force generating part 17, so that the driven plate 20 becomes the rotating plate 19 supported by the disc housing 15 via the friction plate 21. And the state clamped by the disk-shaped housing 15, utilizing the frictional force (frictional resistance) generated between the rotating plate 19 and the friction plate 21 and between the friction plate 21 and the driven plate 20 accompanying the clamping, the disk-shaped housing 15 The rotation of (the sprocket 13 ) is transmitted to the connection shaft 11 connected to the cloth winding roller 6 via the driven plate 20 . Then, by adjusting the pressing force of the pressing force generating part 17, the magnitude of the above-mentioned frictional force is changed, thereby adjusting the rotational torque applied to the cloth winding roller 6 .

In the present embodiment, the pressing force generating part 17 includes: a pressing plate 22 fitted on the connecting shaft 11 on the outside of the rotating plate 19 on the outermost side (opposite to the cloth winding roller 6 ) of the friction transmission part 16; The pressing force setting part 23 related to the above-mentioned pressing force of the state; and the frictional force adjusting part 24 that adjusts the above-mentioned pressing force according to the increase of the roll diameter of the cloth winding roller 6 (bundling 1) accompanying the progress of weaving.

The pressing plate 22 is a disk-shaped member similar to the driven plate 20 of the above-mentioned friction transmission unit 16 , and is provided axially displaceable and non-rotatable with respect to the connecting shaft 11 similarly to the driven plate 20 .

In addition, the pressing force setting part 23 includes: a compression spring 25 inserted concentrically with the connecting shaft 11 on the outside of the pressing plate 22; An adjustment nut 26 is screwed to an external thread portion of the outer end portion of the connecting shaft 11 . Therefore, the pressing force setting portion 23 causes the urging force (pressing force) of the compression spring 25 to act on the friction transmission portion 16 via the pressing plate 22 . In addition, the distance between the pressing plate 22 and the adjusting nut 26 (compression amount of the compression spring 25) is adjusted by changing the screwing amount of the adjusting nut 26 relative to the external thread portion of the connecting shaft 11, thereby changing the force of the compression spring 25 on the The pressing force exerted by the friction transmission part 16 .

In addition, the frictional force adjustment unit 24 includes: a pressure lever 27 which is in contact with the pressing plate 22 at one end and is rotatably supported on the loom frame 9 at an intermediate portion; and a driven lever 28 which is rotatably supported at one end. It is supported on the loom frame 9 and abuts on the opposite end of the pressing rod 27 to the opposite side of the pressing plate 22 than the center of rotation of the pressing rod 27 in the front-rear direction, thereby urging the pressing rod 27 to the opposite side of the cloth winding roller 6 .

More specifically, the pressurizing rod 27 is formed in a fork shape with a pair of arm portions on one end side, and has an abutment surface 27a extending in the longitudinal direction on the other end side than the middle portion, And the abutting surface 27 a bears the acting force of the driven rod 28 . In addition, the pressurizing rod 27 is provided so as to extend in the front-rear direction of the loom, and is rotatably supported by a support shaft 29 at an intermediate portion. In addition, the supporting shaft 29 is supported by an unillustrated bracket shaft mounted on the loom frame 9, and is arranged so that one end side (two-fork side) end of the supporting pressing rod 27 is located in the pressing direction in the front-rear direction. Near the center of the plate 22.

In addition, the pressing rod 27 is formed so that the abutting surface 27 a is substantially arc-shaped when viewed from the front in accordance with the rotation of the driven rod 28 which will be described later. Further, a pressure roller 30 is rotatably attached to each end portion of a pair of arm portions on the fork side of the pressure lever 27 . Therefore, it becomes a structure in which the contact surface 27a of the pressure lever 27 receives the acting force of the opposite side of the cloth winding roller 6 from the driven lever 28, so that the pressure lever 27 rotates around the support shaft 29, and is attached to the pressure lever. The pressing roller 30 on 27 acts on the pressing plate 22 with a pressing force toward the cloth winding roller 6 side.

The driven rod 28 includes: a support rod 31 rotatably supported on the loom frame 9 at one end; 32; and a force setting part 33 that makes one end of the abutting rod 32 apply force to the pressing rod 27.

More specifically, the support rod 31 is rotatably supported by the loom frame 9 via the support shaft 34 at one end thereof. In addition, in this embodiment, the support shaft 34 is arrange|positioned below the cloth fell 2 side rather than the fabric winding roller 6. As shown in FIG. Further, the support shaft 34 is rotatably supported by the loom frame 9 via a bearing 35 such that its axis is parallel to the axis of the cloth winding roller 6 , and is provided so as to protrude outward from the loom frame 9 . Further, the support rod 31 is relatively non-rotatably fixed to a portion of the support shaft 34 protruding outward from the loom frame 9 . Among them, the support rod 31 is arranged so as to be located between the loom frame 9 and the contact surface 27 a of the pressing rod 27 in the axial direction of the support shaft 34 . In addition, the support rod 31 supports the support shaft 36 at the other end thereof. Specifically, a pair of shaft support portions protruding outward in the thickness direction of the support rod 31 and separated in the width direction of the support rod 31 are provided at the other end of the support rod 31 , and the shaft 36 is supported so that its axis is aligned with the support rod 31 . The form perpendicular to the longitudinal direction is supported by a pair of shaft support parts.

The abutment rod 32 is rotatably supported relative to the support rod 31 via a support shaft 36 at its middle portion in such a manner that its longitudinal direction coincides with the longitudinal direction of the support rod 31 , and one end thereof is arranged to be larger than the above-mentioned other end of the support rod 31 . protrude. In addition, a roller 37 is rotatably attached to the above-mentioned one end of the contact lever 32 . In addition, the arrangement of the contact rod 32 in the axial direction of the support shaft 34 is also such that the roller 37 is located between the loom frame 9 and the contact surface 27 a of the pressing rod 27 . Further, the dimensions in the longitudinal direction of the support rod 31 and the contact rod 32 are set so that the roller 37 comes into contact with the pressure rod 27 in a state where the support rod 31 is supported by the support shaft 34 . Therefore, the driven rod 28 can be brought into contact with the contact surface 27a of the pressurizing rod 27 by the roller 37, and acts on the other end side of the contact rod 32 to the loom frame 9 side by the acting force setting part 33. The abutting rod 32 rotates around the support shaft 36 and the roller 37 presses the abutting surface 27 a of the pressing rod 27 .

The force setting part 33 includes: a guide shaft 38 protruding outward relative to the support rod 31 and penetrating the abutment rod 32 ; And the compression spring 40 is concentrically inserted into the guide shaft 38 and interposed between the contact rod 32 and the adjustment nut 39 . In addition, the guide shaft 38 is provided so as to pass through a through hole formed on the other end side of the abutment rod 32 , but the diameter of the through hole in the longitudinal direction of the abutment rod 32 is formed to be larger than the shaft diameter of the guide shaft 38 . The rotation of the post 32 around the support shaft 36 is not restricted by the guide shaft 38 . And, according to the urging force setting part 33 of such a structure, the above-mentioned urging force acts on the other end side of the abutment rod 32 by the compression spring 40, and the rotation of the adjusting nut 39 with respect to the external thread part of the guide shaft 38 is changed. The input amount is adjusted to adjust the distance between the abutment rod 32 and the adjustment nut 39 (compression amount of the compression spring 40 ), thereby changing the force exerted by the compression spring 40 on the abutment rod 32 .

According to the frictional force adjusting part 24 constituted as described above, since the driven lever 28 makes the urging force of the compression spring 40 act on the abutting surface 27a of the pressing rod 27 via the roller 37, the pressing rod 27 opposes each other in the front-rear direction. The pressing force toward the outside is received on the side opposite to the friction transmission part 16 from the center of rotation (support shaft 29 ), and as a result, the pressure rod 27 acts on the friction transmission part 16 by the pressure roller 30 via the pressure plate 22 . status. Therefore, in the friction transmission unit 14 , the friction transmission part 16 is in a state of receiving the pressing force applied by each part of the pressing force setting part 23 and the frictional force adjusting part 24 via the pressing plate 22 included in the pressing force generating part 17 .

In addition, in the frictional force adjustment part 24, the contact position of the roller 37 of the driven rod 28 with respect to the contact surface 27a of the pressure rod 27 is changed, in other words, the position of the roller 37 on the contact surface 27a of the pressure rod 27 is changed. The position where the pressing force applied by the moving rod 28 acts, thereby changing the pressing force that the pressing rod 27 acts on the friction transmission part 16 via the pressing roller 30 . That is, since the distance from the rotation center (fulcrum) of the pressing rod 27 to the position (action point) of the pressing roller 30 is constant, the pressing force on the contact surface 27a of the pressing rod 27 is changed as described above. According to the acting position (point of force) (changing the distance from the fulcrum to the point of force), according to the principle of leverage, the pressing force that the pressure roller 30 acts on the friction transmission part 16 changes. For example, at position S and position E shown in FIG. The pressing force exerted by the pressure roller 30 on the friction transmission portion 16 increases. That is, as the contact position of the roller 37 of the driven lever 28 with respect to the contact surface 27 a of the pressurizing rod 27 moves away from the rotation center of the pressurizing rod 27 , the pressurizing roller 30 acts on the pressurizing roller 30 in proportion to the distance. The pressing force of the friction transmission part 16 becomes larger.

Then, the pressing force applied to the friction transmission part 16 by the pressing force generating part 17 (frictional force adjusting part 24) is changed as described above, thereby changing the rotational torque applied to the cloth winding roller 6 (the cloth winding rotation of the cloth winding roller 6). Moment) changes in proportion to the change in the pressing force. In addition, as described above, the change in the contact position of the roller 37 of the driven rod 28 with respect to the contact surface 27 a of the pressurizing rod 27 is due to the fact that the driven rod 28 (support rod 31 ) supports the shaft center 34 a of the shaft 34 . Rotation of the driven lever 28 is generated by rotation of the support shaft 34 .

Moreover, in the present invention, in order to make the support shaft 34 rotate as the roll diameter of the fabric 1 wound on the cloth roll 6 increases, the roll diameter tracking lever 42 including the roll diameter follower lever 42 that is rotated in contact with the cloth roll 6 is rotated. The link mechanism 41 is connected to the support shaft 34 . Specifically, this link mechanism 41 has a structure like the example shown in FIG. 1 , and it will be described in more detail below.

In this embodiment, the link mechanism 41 is provided with a rotating rod 43 as a link member in addition to the above-mentioned coil diameter following rod 42, and the rotating rod 43 is connected to the above-mentioned frictional support via a rotation transmission mechanism 52 described later. The support shaft 34 of the support rod 31 of the transmission unit 14 is connected, that is, the driven rod 28 (support rod 31 ) of the cloth winding torque adjustment device 10 is connected via the rotation transmission mechanism 52 and the support shaft 34 . In addition, in this link mechanism 41 , the respective link members (winding diameter following rod 42 and rotation rod 43 ) are directly connected, and these connecting parts 47 are configured to be displaceable in the extending direction of winding diameter following rod 42 .

In the structure of this embodiment, the winding diameter following lever 42 has the support part 42a, the intermediate|middle part 42b, and the contact part 42c, and has the shape which these parts are integrally formed. Moreover, the support part 42a forms the through-hole 42d which penetrates in the board thickness direction at one end, and the intermediate part 42b continues at the other end side. In the illustrated example, the intermediate portion 42b is formed at an angle of approximately 45° with respect to the support portion 42a. Moreover, the abutting part 42c continues to the end part of the side opposite to the support part 42a of the intermediate|middle part 42b. And this contact part 42c is formed in the form extended substantially parallel to the support part 42a, and is continuous with the intermediate part 42b at one end side. Moreover, the roller 1 which abuts on the cloth 1 is rotatably attached to the other end side of the contact part 42c so that the axial direction may become parallel to the plate thickness direction.

The winding diameter following lever 42 having the above-mentioned structure is disposed between the loom frame 9 and the cloth winding roller 6 in the fabric width direction, and is rotatably supported via a support shaft 45 inserted into a through hole 42d of the support portion 42a. On the loom frame 9. Therefore, in this embodiment, the support shaft 45 that supports the winding diameter following rod 42 in this way becomes the "first support shaft" of the present invention. In addition, the support shaft 45 is pivotally supported by the loom frame 9 in a state in which the axis line is parallel to the axis line of the cloth winding roller 6 . Therefore, the rolling diameter following rod 42 is supported in a state in which its plate thickness direction coincides with the axial direction of the cloth rolling roller 6, and its rotational direction (corresponding to the dotted arrow X shown in FIG. 1 ) is consistent with the axial direction of the cloth rolling roller 6. Orthogonal.

In addition, the winding diameter following rod 42 is provided so that the roller 46 mounted on the abutting portion 42c and extending toward the cloth winding roller 6 is connected between the cloth fell side and the peripheral surface of the cloth winding roller 6 (the side wound on the cloth winding roller 6 ). Fabric 1) Butt. That is, the roll diameter following lever 42 is arranged so that the intermediate portion 42b is inclined toward the cloth fell 2 side with respect to the support portion 42a. Here, the support shaft 45 supporting the winding diameter following lever 42 is provided above the axis of the cloth winding roller 6 in the vertical direction. Therefore, the winding diameter following lever 42 is in a state where the contact state of the roller 46 to the fabric 1 wound on the cloth winding roller 6 can be maintained by its own weight. In detail, since the support shaft 45 is arranged above the axis of the cloth winding roller 6, the winding diameter following rod 42, which is suspended from the support shaft 45, is on the roller 46 and compared with the cloth winding in the front-rear direction. The axis center of the roller 6 (vertically below the support shaft 45) is in contact with the fabric roll 6 on the cloth fell 2 side, so that the center of gravity is closer to the cloth fall than the support position of the roll diameter following rod 42 (the position of the support shaft 45). 2 side displacement state. Therefore, the abutment state of the roller 46 to the fabric 1 wound on the fabric winding roller 6 can be maintained by the self-weight of the winding diameter following rod 42 .

The rotation lever 43 is a plate-shaped member in which a through-hole 43a and a through-hole 43b penetrating in the plate thickness direction are respectively formed at both ends. In addition, the rotation lever 43 is disposed between the loom frame 9 and the roll diameter following lever 42 in the fabric width direction, and is rotatably supported on the loom frame 9 via a support shaft 48 inserted in the through hole 43a at one end side. . Therefore, in the present embodiment, the support shaft 48 thus supporting the rotation lever 43 becomes the "second support shaft" in the present invention. In addition, the support shaft 48 is pivotally supported by the loom frame 9 in a state in which the axis line is parallel to the axis line of the cloth winding roller 6 . Therefore, the rotation lever 43 is supported in a state where its plate thickness direction coincides with the axial direction of the cloth winding roller 6 , and its rotational direction (corresponding to the dotted arrow Y shown in FIG. 1 ) is perpendicular to the axial direction of the cloth winding roller 6 .

In addition, in this embodiment, in addition to the rotating rod 43 installed on the supporting shaft 48, the supporting shaft 34 that supports the driven rod 28 (supporting rod 31) of the cloth winding torque adjustment device 10 is also connected with the rotating rod 43. The rotation mechanism (rotation transmission mechanism 52) of the rotation support shaft 48. More specifically, the support shaft 48 is rotatably supported by the loom frame 9 via a bearing (not shown), and protrudes toward the inside of the loom frame 9 . , a rotation lever 43 is installed relatively non-rotatably at the end, and a rotation transmission mechanism 52 is connected between the rotation lever 43 installed in this way and the loom frame 9 .

Incidentally, in the present embodiment, the rotation transmission mechanism 52 includes: a timing pulley 49 mounted on the support shaft 48 supporting the rotation rod 43; a timing belt mounted on the support shaft 34 supporting the support rod 31; a pulley 50; and a timing belt 51 connecting the above-mentioned timing pulleys 49 and 50. In addition, the timing pulley 49 is mounted relatively non-rotatably with respect to the support shaft 48 between the above-mentioned turning lever 43 and the loom frame 9 . In addition, the support shaft 34 protrudes toward the inside of the loom frame 9 in addition to protruding toward the outside of the loom frame 9 as described above, and the end portion of the support shaft 34 protruding inward is relatively non-rotatable. installed.

Therefore, the rotation of the support shaft 48 accompanied by the rotation of the rotation lever 43 is transmitted to the support shaft 34 through the timing pulley 49, the timing belt 51, and the timing pulley 50, so that the rotation of the support shaft 48 is transmitted to the support shaft 34, and the support The shaft 34 rotates. That is, the rotation lever 43 is connected to the support shaft 34 via the support shaft 48 and the rotation transmission mechanism 52 so that the support shaft 34 rotates with the rotation. In addition, the driven lever 28 in the cloth winding torque adjustment device 10 is supported by the support shaft 34 as described above. Therefore, the rotation lever 43 is connected to the driven lever 28 in the cloth winding torque adjustment device 10 via the support shaft 48 , the rotation transmission mechanism 52 , and the support shaft 34 .

In addition, on the other end side of the pivot lever 43 , a coupling pin 44 is inserted into and fixed to the through hole 43 b so as to protrude toward the opposite side of the loom frame 9 . And the rotation lever 43 is connected with the winding diameter following lever 42 via this connection pin 44. As shown in FIG.

More specifically, in the link mechanism 41, in addition to the above-mentioned through hole 42d, the winding diameter following rod 42 has an elongated hole 42e on the other end side of the support portion 42a, and the elongated hole 42e is formed so as to extend in the extending direction. Extend and penetrate in the thickness direction of the plate. Further, the winding diameter following lever 42 and the turning lever 43 are directly connected by inserting the connecting pin 44 fixed to the turning lever 43 into the elongated hole 42e of the supporting part 42a of the winding diameter following lever 42 as described above. In addition, in the link mechanism 41 in which the two link members are in a connected state, the "connecting part" in the present invention is a part where the winding diameter following rod 42 intersects and overlaps with the rotation rod 43 when viewed from the fabric width direction ( Hereinafter, it is also referred to as "connection part 47."), In this embodiment, the center of this connection part 47 becomes the axis|shaft 44a of the connection pin 44.

By the way, in the above-mentioned link mechanism 41, two link members (this embodiment: winding diameter following lever 42, rotation lever 43) each of which is rotatably supported on the support shaft at one end side are arranged at the other end side. In the link mechanism in which the sides are directly connected, the distance from at least one of the support shafts to the position where the two link members intersect changes with the rotation of the two link members. Therefore, in order to allow this change, in the link mechanism as described above, it is necessary to have a structure in which the position of the connecting portion of both link members changes in the direction in which at least one link member extends. Therefore, in the link mechanism 41 of the present embodiment, as described above, the long hole 42e that is long in the extending direction is formed in the support portion 42a of the winding diameter following rod 42, and the long hole 42e inserted through the long hole 42e The connecting pin 44 is used to connect the coil diameter following rod 42 and the rotating rod 43, so that the position of the connecting portion 47 (connecting pin 44) of the coil diameter following rod 42 and the rotating rod 43 is at the position of the coil diameter following rod 42 (support portion 42a). A structure capable of displacement in the direction of extension, thereby allowing the rotation of the two link parts.

In addition, the extension length of the elongated hole 42e is, of course, such that the rotation of the roll diameter following lever 42 is allowed from the start of winding of the fabric 1 to the cloth winding roller 6 to the end of winding. In addition, in the link mechanism 41 of this embodiment, as a result of setting the initial arrangement as described later, the position of the connecting pin 44 is in the direction in which the supporting portion 42a extends along with the rotation of the winding diameter following lever 42 during the above-mentioned period. The direction from the position near the boundary between the support portion 42a and the intermediate portion 42b toward the support shaft 45 changes within a range less than one-third of the extension length of the support portion 42a. Therefore, in the present embodiment, the elongated hole 42e of the support portion 42a of the roll diameter following lever 42 is formed such that its extension length is approximately one-third of the extension length of the support portion 42a in the direction from the vicinity of the above boundary toward the support shaft 45. within the extent. In addition, the width of the elongated hole 42e is, of course, a width at which the coupling pin 44 can slide in the elongated hole 42e.

In the loom of this embodiment including the link mechanism 41 having the above-mentioned structure, the winding diameter of the cloth 1 is 100 mm (≒ the diameter of the cloth winding roller 6) at the start of winding and 100 mm at the end of winding. 300mm. Therefore, in this embodiment, regarding the initial arrangement of each link member of the link mechanism 41, that is, the arrangement of each link member of the link mechanism 41 in the state (initial state) at the time when the winding starts, set In order to satisfy the following condition (a).

Specifically, the initial configuration is set as follows: The line segment connecting the support shaft 45 (first support shaft) supporting the winding diameter following rod 42 and the connecting portion 47, that is, the axis 45a (first support shaft) connecting the support shaft 45 is set. The axis of the support shaft) and the axis 44a of the connecting pin 44 (the center of the connecting portion 47) are set as a line segment N (single dotted line shown in FIGS. The line segment between the shaft 48 (second support shaft) and the connection portion 47, that is, the axis 48a (axis center of the second support shaft) connecting the support shaft 48 and the axis 44a (center of the connection portion 47 ) of the connection pin 44 The line segment is set as line segment K (two-dot chain line shown in Fig. 3), after setting the angle formed by line segment K relative to line segment N at the rotation direction side of roll diameter following lever 42 (line segment N) as angle α, in The rotation range of the winding diameter following lever 42 (the range in which the winding diameter following lever 42 rotates from the start of winding to the end of winding) and the angle α satisfy the following condition (a).

Condition (a): It is within an angle range of not less than 90° and not more than 195°, and the start of winding is closer to 90° than the end of winding.

By the way, in the structure of this embodiment, the length of the line segment N (the distance between the axis 45a of the support shaft 45 and the axis 44a of the connecting pin 44 ) is not constant, but changes with the rotation of the winding diameter following lever 42 . That is, in the link mechanism 41 of the present embodiment, when the winding diameter following lever 42 rotates, the connecting pin 44 slides in the direction of the support shaft 45 in the long hole 42e (upper end side in the long hole 42e ) accompanying the rotation. , In this way, the position of the connecting pin 44 changes, and as a result, the length of the line segment N gradually becomes shorter. Therefore, the length of the line segment N is at a maximum at the beginning of winding (initial configuration) and at a minimum at the end of winding.

Furthermore, in this embodiment, in order to satisfy the above-mentioned condition (a), the initial arrangement of each link member is set so that the angle α in the initial arrangement is 100°. In addition, in this embodiment, when setting the initial arrangement of each link member, first, the initial arrangement of the winding diameter following lever 42 is set on the premise of the following (1) and (2).

(1) As described above, in this embodiment, the roll diameter following lever 42 is in a state of maintaining the abutment state of the roller 46 on the fabric 1 wound on the fabric roll 6 by its own weight, so that the roll diameter is supported. The support shaft 45 (first support shaft) of the diameter following rod 42 is disposed above the cloth winding roller 6 .

(2) In addition, in this embodiment, the position of the support shaft 45 and the abutment position of the roller 46 to the fabric 1 wound on the fabric roll 6 are set within the rotation range of the roll diameter following lever 42 so that The amount of rotation of the roll diameter following rod 42 relative to the increment of the unit roll diameter is fixed. That is, as shown in FIG. 1, if the line segment connecting the shaft center 45a of the support shaft 45 and the shaft center 46a of the roller 46 is set as a line segment A, the shaft center 6a of the cloth winding roller 6 and the shaft center of the roller 46 are The line segment of 46a is set as line segment B, and the angle formed by line segment B relative to line segment A at the opposite side of the rotation direction of the rolling diameter following rod 42 (line segment A) is set as angle γ, then this angle γ is to follow the rolling diameter of the rod. 42 is affected by the amount of rotation relative to the increment of the unit roll diameter, by keeping the angle γ substantially constant during the increase of the roll diameter of the cloth 1, as described above, the roll diameter following rod 42 increases relative to the unit roll diameter. Since the amount of rotation is constant, the position of the support shaft 45 and the abutment position of the roller 46 are determined so that the angle γ is kept substantially constant within the rotation range of the winding diameter following lever 42 .

In addition, the position of the support shaft 45 and the above-mentioned abutment position of the roller 46 are determined so as to satisfy the prerequisites (1) and (2) above. However, the position of the support shaft 45 satisfying the above-mentioned (1) and (2) and the above-mentioned abutting position of the roller 46 are not a specific one, and there are ranges that can be set for each position. Therefore, regarding the respective positions, for example, the position of the support shaft 45 is determined within the range satisfying the above (1), and the contact position of the roller 46 is determined within the range satisfying the above (2). In addition, when the position of the support shaft 45 and the above-mentioned contact position of the roller 46 are determined, along with this, the arrangement angle of the line segment N in the initial arrangement of the roll diameter following rod 42 (relative to the cloth fell 2 side or the cloth fell 2) and the amount of rotation of the winding diameter following lever 42 from the start of winding to the end of winding (the total amount of rotation of the winding diameter following lever 42).

Incidentally, in the illustrated example, as a result of the premise of (1) and (2) above, with respect to the initial arrangement of the winding diameter following lever 42, the support position of the support shaft 45 (the position of the support shaft 45) is arranged The axis 6a of the cloth winding roller 6 is substantially above the vertical direction, and the line segment N (the extension direction of the supporting part 42a of the winding diameter following rod 42) is opposite to the rotation direction of the winding diameter following rod 42 relative to the vertical direction. The side slope is about 4°.

In addition, in this embodiment, the initial arrangement of the pivot lever 43 is set on the premise of the following (3) to (5).

(3) First, in this embodiment, the connecting pin 44 is positioned at the lower end (position near the boundary) in the elongated hole 42e of the supporting portion 42a of the coil diameter following lever 42 due to the own weight of the rotating lever 43 . That is, the position of the coupling pin 44 in the initial arrangement on the winding diameter following rod 42 (support portion 42a) is set to the lower end of the elongated hole 42e. In other words, the rotation lever 43 has a distance from the center of the through hole 43a in which the support shaft 48 is inserted to the center of the through hole 43b in which the coupling pin 44 is inserted, and a winding diameter from the axis 48a of the support shaft 48 to the initial configuration. The distance of the lower end part of the long hole 42e of the tracking rod 42 is substantially the same length dimension.

(4) Also, as described above, in the present embodiment, the initial arrangement is set so that the angle α is 100°. Therefore, the support shaft 48 (second support shaft) supporting the rotation lever 43 is provided so that the shaft center 48a ( The axis center of the second support shaft) is located at the line segment N passing through the axis 44a of the connecting pin 44 and in the state of initial configuration with the winding diameter following lever 42 to form a 100° line on the side of the rotation direction of the winding diameter following lever 42 ( The line indicated by the dashed-two dotted line in FIG. 4: hereinafter also referred to as "reference line L1".) above.

(5) Further, the support shaft 48 is provided at a position where the angle α formed between the line segment K and the line segment N at the position of the winding diameter following lever 42 at the end of winding is 195° or less based on the above condition (a). Specifically, for example, the position of the support shaft 48 is obtained based on the following, and according to the above (3), based on the position of the support shaft 48, the length dimension of the rotation rod 43 (from the center of the through hole 43a to the length of the through hole 43b) is determined. center distance).

First, the winding diameter at the end of winding is obtained from the arrangement angle of the line segment N in the initial arrangement (at the start of winding) of the winding diameter following lever 42 determined as described above and the total rotation amount of the winding diameter following lever 42. The arrangement angle of the support portion 42 a of the following rod 42 . Therefore, when a straight line parallel to the extending direction of the support portion 42a at the end of the winding is drawn through the axis 45a of the support shaft 45, it becomes a line L2 indicated by a dotted line in FIG. 4 . Incidentally, since the coupling pin 44 is located in the elongated hole 42e formed in the supporting portion 42a and is long (extending) in the extending direction of the supporting portion 42a, the axis 44a is positioned on the imaginary line L2 when the winding is completed. Therefore, the line segment N also lies on the dotted line L2. In addition, the position P1 where the dotted line L2 intersects the reference line L1 is a position where the angle α becomes 180° when the winding is completed because the support shaft 48 is provided at this position.

Then, the position of the support shaft 48 at which the angle α becomes 195° at the end of the winding is obtained. In addition, the angle α being 195° means that a straight line passing through the axis 48a of the support shaft 48 and the axis 44a of the coupling pin 44 at the position at the end of winding is on the opposite side to the rotation direction of the winding diameter following lever 42 with respect to the dotted line L2. An angle of 165° is formed, so in FIG. 4 , if an imaginary line forming an angle of 165° is drawn on the opposite side of the rotation direction of the winding diameter following lever 42 with respect to the imaginary line L2, the intersection point of the imaginary line and the reference line L1 becomes at The position of the shaft center 48a of the support shaft 48 at the angle α of 195° at the end of winding, and the intersection point of the imaginary line and the dotted line L2 is the position of the shaft center 44a of the connecting pin 44 at the end of winding.

Wherein, since the distance from the axis 48a of the support shaft 48 to the axis 44a of the connecting pin 44 is always constant, the imaginary line needs to be drawn as follows, that is, the distance on the reference line L1 obtained from the imaginary line The point and the point on the dotted line L2 are positions where the distance from the point on the reference line L1 to the axis 44a of the connecting pin 44 at the start of winding is equal to the distance from the point on the reference line L1 to the point on the dotted line L2. . Therefore, as a result of this imaginary line drawn based on this, this imaginary line becomes the line L3 shown by the solid line in FIG. 4 . And, the intersection point P2 of the solid line L3 and the reference line L1 is the position of the shaft center 48a of the support shaft 48 at which the angle α is 195° at the time of winding completion. Moreover, the intersection point P3 of the solid line L3 and the dotted line L2 becomes the position of the axial center 44a of the connection pin 44 at the time of completion|finish of winding.

In addition, as described above, when the axis 48a of the support shaft 48 is located on the reference line L1, the angle α at the end of winding becomes 180 by disposing the support shaft 48 so that the axis is located at the point P1 as described above. °, it can be seen from this that the support shaft 48 is provided in such a manner that the axis 48a is located on the side of the axis 44a of the connecting pin 44 at the start of winding from the point P2 obtained as described above, so that the angle α at the end of the winding smaller than 195°. In addition, the position of the support shaft 48 is set in consideration of design restrictions on the mechanical structure (position where the support shaft 48 can be arranged, etc.).

Based on the above (3) to (5), regarding the initial arrangement of the pivot lever 43, the position of the support shaft 48, the length of the line segment K (distance between the axis 48a of the support shaft 48 and the axis 44a of the connecting pin 44), And the arrangement angle of the rotation lever 43 (line segment K), thereby, the rotation amount of the rotation lever 43 (the total rotation amount of the rotation lever 43) during the period from the start of winding to the end of winding is determined.

Incidentally, in this embodiment, as a result of the premise based on the above (3) to (5), regarding the initial arrangement of the turning lever 43, the supporting position of the supporting shaft 48 (the position of the supporting shaft 48) as the winding end Among the positions where the angle α at the time is 195° or less, the position within the above-mentioned mechanical structural design constraints is arranged at the position where the angle α at the end of winding is 162°.

In addition, in the cloth winding torque adjusting device 10, according to the device structure, there is The desired total amount of rotation, so in this embodiment, the diameters of the timing pulleys 49, 50 in the rotation transmission mechanism 52 are set so that the driven lever 28 can The total rotation amount of the rotation lever 43 is the desired total rotation amount with respect to the total rotation amount of the rotation lever 43 .

As described above, in the loom including the fabric tension adjusting device 10, the fabric tension adjusting device 10 includes the link mechanism 41 in which the initial arrangement of each link member is set, and the The driven rod 28 connected by the rotating rod 43 of the spinning rod 43 starts to use the cloth winding roller 6 to wind the fabric 1 along with the beginning of spinning, and then, along with the progress of spinning, the roll diameter of the winding cloth 1 of the cloth winding roller 6 increases gradually. According to the increase of the roll diameter of the roll cloth 1, at the other end side of the abutting portion 42c, the roll diameter following rod 42 abutting the roll cloth 1 via the roller 46 follows the roll direction indicated by the dotted arrow X in FIG. 1 . The direction of rotation of the diameter following lever 42 is rotated toward the cloth fell 2 side.

By the way, in this embodiment, as described above, in the process of increasing the roll diameter of the roll cloth 1, the angle γ (the angle formed by the line segment B relative to the line segment A on the opposite side of the roll diameter following the rotation direction of the rod 42 : With reference to Fig. 1) be kept substantially fixed, thus the roll diameter follow-up lever 42 is relative to the increase of the roll diameter of the unit roll diameter increase amount when winding ends from the beginning of winding (in this embodiment, the unit roll diameter The increment is set to 50mm.) Always rotate with a fixed amount of rotation (5.5° in the example shown in Figure 3).

In addition, as described above, as the winding diameter following lever 42 rotates, the rotating lever 43 connected to the winding diameter following lever 42 via the connecting pin 44 is directed toward the cloth fell along the rotating direction of the rotating lever 43 indicated by the dotted arrow Y in FIG. 1 . 2 sides for turning. In addition, in this case, the change in the distance between the lower end of the long hole 42e of the support portion 42a of the support portion 42a of the roll diameter follower lever 42 and the change in the distance between the support shaft 48 due to the rotation of the roll diameter follower lever 42 is due to the coupling portion 47 of both link members. The connecting pin 44 is absorbed by displacement from the lower end to the upper end side in the elongated hole 42e, thereby allowing the rotation of both link members. Then, as the winding diameter following lever 42 rotates, the connection pin 44 is displaced from the lower end to the upper end side (support shaft 45 side) in the long hole 42e of the supporting portion 42a of the winding diameter following lever 42 .

In addition, in the rotation range of the winding diameter following lever 42 (the range in which the winding diameter following lever 42 rotates from the start of winding to the end of winding), an angle of 100° is set at the initial arrangement (at the beginning of winding) α (the angle formed by the line segment N on the winding diameter following lever 42 and the line segment K on the turning lever 43 on the side of the turning direction of the winding radius following lever 42 ) becomes 162° at the end of winding. That is, within the range of rotation of the roll diameter following rod 42, the line segment K connecting the second support shaft (support shaft 48) supporting the rotation rod 43 and the connecting portion 47 is relatively opposite to the first support shaft (support shaft 48) connecting and supporting the roll diameter following rod 42. The angle α formed by the line segment N of the axis 45) and the connecting portion 47 on the side of the rotation direction of the winding diameter following lever 42 is included in the angle range of 90° to 195°, and is closer to 90° at the start of winding than at the end of winding. .

As a result, as the winding diameter following lever 42 turns, the turning lever 43 turns while reducing the turning amount. That is, in the rotation range of the rotation lever 43 (the range in which the rotation lever 43 rotates with the rotation of the winding diameter following lever 42 from the start of the winding to the end of the winding), the rotation lever 43 rotates at a rate corresponding to the increase in the winding diameter per unit. The rotation amount of the rotation rod 43 obtained by the rotation of the winding diameter following the rotation of the rod 42 is rotated in a manner that gradually becomes smaller as the winding diameter increases.

Specifically, as described above, if the increment of the unit coil diameter is set to 50 mm, the increase in the unit coil diameter during the period from the start of coiling (100 mm of coil diameter) to the end of coiling (300 mm of coil diameter) is The rotation amount (rotation angle) of the rotation lever 43 relative to the rotation amount (rotation angle: 5.5°) of the rotation diameter following lever 42 for the increase of the winding diameter (increase of the unit winding diameter) changes as follows (1) to (4) ( Refer to Figure 3).

(1) When the winding diameter increases from 100 mm to 150 mm, the amount of rotation of the rotation lever 43 (immediately after winding start) becomes 19°.

(2) When the roll diameter increases from 150 mm to 200 mm, the amount of rotation of the rotation lever 43 becomes 9°.

(3) When the roll diameter increases from 200 mm to 250 mm, the amount of rotation of the rotation lever 43 becomes 7°.

(4) When the winding diameter increases from 250 mm to 300 mm, the amount of rotation of the rotation lever 43 (just before the end of winding) becomes 6°.

As described above, in this embodiment, the amount of rotation of the rotation lever 43 accompanying the increase in the unit winding diameter from the start of winding to the end of winding is relative to the increase in the unit winding diameter immediately after the start of winding. The rotation amount of the rotation lever 43 obtained by the rotation of the winding diameter following lever 42 (corresponding to the above (1)), and the rotation amount of the rotation lever 43 obtained by the rotation of the winding diameter following lever 42 with the increase of the unit winding diameter immediately before the end of winding. The amount of rotation (corresponding to (4) above) becomes a small value.

And, according to the rotation amount of the rotation lever 43 as described above (1) to (4), the increase amount of the cloth winding torque gradually decreases as indicated by the solid line H1 shown in FIG. 5( a ). More specifically, during the period from the start of winding to the end of winding, as the rotation lever 43 rotates according to the increase of the winding diameter, in the cloth winding torque adjustment device 10, the driven lever 28 is directed toward the driven lever. The contact position of the roller 37 of 28 with respect to the contact surface 27 a of the pressurizing rod 27 rotates in a direction away from the rotation center of the pressurizing rod 27 . As a result, the cloth winding torque gradually increases from the start of winding to the end of winding.

In addition, during the rotation of the driven lever 28 in this way, the amount of rotation of the driven lever 28 along with the amount of rotation of the rotation lever 43 changes as described in (1) to (4) above when the winding diameter per unit increases. gradually decreases as the diameter increases. That is, the amount of rotation of the driven lever 28 (the amount of increase in the cloth winding torque) changes so as to increase inversely proportional to the increase in the winding diameter from the start of winding to the end of winding. And, as a result, the degree of reduction of the fabric tension per unit diameter increases is substantially constant, and the fabric tension decreases approximately in proportion to the increase in the diameter as shown by the solid line H2 in FIG. 5( b ). In addition, since the fabric tension is substantially proportionally reduced in this way, it is possible to prevent the fabric 1 wound on the fabric roller 6 from being wrinkled.

In addition, the operation|movement of the rotation lever 43 as mentioned above is realized by the characteristic of the link mechanism demonstrated below.

That is, the characteristics of the link mechanism mean that the link mechanism is driven by a drive-side link member (hereinafter also referred to as a "drive-side link member") and directly connected to the drive-side link member. When the driven side link member (hereinafter also referred to as "driven side link member") is configured, the driven The side link members follow the waveform curves shown in the graphs of Fig. 6(A) and Fig. 6(B) (hereinafter, the waveform curve shown in the graph of Fig. 6(A) will also be referred to as "waveform curve A", and The waveform curve represented by the graph of FIG. 6(B) is referred to as "waveform curve B".) to perform rotational displacement (hereinafter also referred to as "driven displacement".).

In both the waveform curves A and B, the abscissa (x in the figure) is the rotation amount of the drive side link member accompanying the drive displacement of the drive side link member (hereinafter also referred to as "drive displacement amount"). The vertical axis (y in the figure) is the rotation amount of the driven side link member accompanying the driven displacement of the driven side link member (the rotation amount of the driven side link member relative to the driving displacement amount: hereinafter also referred to as "Slave Displacement".). In addition, the waveform curve A represents a link mechanism (hereinafter also referred to as "link mechanism A") in which the connecting portion of both link members is configured to be displaceable in the extending direction of the drive side link member as shown in FIG. 7 . The relationship between the driven displacement amount of the driven side link member and the driving displacement amount of the driving side link member. On the other hand, the waveform curve B represents a link mechanism (hereinafter also referred to as "link mechanism B") in which the connecting portion of both link members as shown in FIG. ".) The relationship between the driven displacement of the driven side link member and the driving displacement of the driving side link member.

In addition, in the link mechanisms A and B, the line segment connecting the center of rotation of the driving side link member and the center of the connecting portion and the line segment connecting the center of rotation and the center of the connecting portion of the driven side link member are driven After the angle formed by the side of the rotation direction of the side link member is set to "angle α", the waveform curve A is based on the driven displacement amount of the driven side link member when the angle α is 90° (270°) (0 ), and the waveform curve B is represented by taking the driven displacement amount of the driven side link member when the angle α is 0° (180°) as a reference (0). In addition, in the graphs of FIG. 6(A) and FIG. 6(B), the abscissa is divided and displayed by the angle range of every 90° of the angle α.

Among them, in the link mechanisms A and B, in the angle ranges of the above-mentioned angle α every 90°, due to the limitation of its mechanical structure, there are ranges of angle α that can be realized and ranges of angle α that cannot be realized. . Specifically, it is as follows.

＜About Link Mechanism A＞

Considering the structure of the link mechanism A in which the angle α changes in units of 90°, when the angle α changes in the angle range between 0° and 90°, the direction of change (change direction) changes from 90° to 90°. When starting from the ° side, a structure that changes from 90° to 0° can be realized, but when the direction of change starts from the 0° side, the structure that the angle α is 90° cannot be realized mechanically, only the angle A structure in which α changes within an angle range from 0° to less than 90° can be realized. In addition, regarding the case where the angle α changes in the angle range between 90° and 180°, in the case where the direction of change starts from the 90° side, a structure that changes from 90° to 180° can be realized, but when changing When the direction starts from the 180° side, that is, the structure in which the angle α changes from a state of 180° to a direction in which the angle α becomes smaller cannot be realized mechanically.

And, regarding the situation where the angle α changes in the angle range between 180° and 270°, in the case where the changing direction starts from the 180° side, a structure that changes from 180° to 270° can be realized, and in the changing direction From the 270° side, that is, the structure in which the angle α changes from the state of 270° to a direction in which the angle α becomes smaller cannot be realized mechanically. In addition, regarding the case where the angle α changes in the angle range between 270° and 360°, in the case where the change direction starts from the 360° side, the structure that changes from 360° to 270° can be realized, but in the change direction When starting from the 270° side, the structure in which the angle α changes from the state of 270° to 360° cannot be realized mechanically, and only the structure in which the angle α changes from an angle exceeding 270° to 360° Can be achieved.

To sum up, the waveform curve A in the graph of FIG. 6(A) represents the follower in the range (a1) to (a6) of the following angle α that can be realized mechanically with regard to the link mechanism A. The relationship of the driven displacement amount of the side link member with respect to the driving displacement amount of the drive side link member. More details are as follows.

Regarding the area of the graph between 0° and 90° of the angle α, the following relationship is shown: the angle α in the case where the change direction of the angle α starts from the 0° side is an angle range from 0° to less than 90° ( The relationship of the driven displacement amount of the driven side link member with respect to the driving displacement amount of the driving side link member of (a1) shown in the figure; and the angle in the case where the change direction of the angle α starts from the 90° side α is the relationship of the driven displacement amount of the driven side link member with respect to the driving displacement amount of the driving side link member in the angle range of 90° or less and 0° or more (shown (a2)).

In addition, regarding the area of the graph between 90° and 180° of the angle α, the following relationship is shown: the change direction of the angle α in the angle range ((a3) shown in the figure) where the angle α is 90° to 180° The relationship between the driven displacement amount of the driven side link member relative to the driving displacement amount of the driving side link member in the case of starting only from the 90° side, for the graph between 180° and 270° of the angle α The region represents the following relationship: in the case where the angle α changes in the angle range ((a4) shown in the figure) from 180° to 270° only from the 180° side, the driven side link member The relationship between the driven displacement amount and the driving displacement amount of the driving side link member.

In addition, the graph area between 270° and 360° of the angle α shows the relationship that the angle α is an angle exceeding 270° and not more than 360° when the direction of change of the angle α starts from the 270° side. The relationship of the driven displacement amount of the driven side link member with respect to the driving displacement amount of the driving side link member in the range (illustrated (a5)); and in the case where the change direction of the angle α starts from the 360° side The angle α is the relation of the driven displacement amount of the driven side link member with respect to the driving displacement amount of the driving side link member in the angle range ((a6) shown in the figure) of 360° or less and 270° or more.

＜About Link Mechanism B＞

Considering the structure of the link mechanism B where the angle α changes in units of 90°, when the angle α changes in an angle range between 0° and 90°, when the direction of change starts from the 0° side , the structure that changes from 0° to 90° can be realized, but in the case where the direction of change starts from the 90° side, the structure that the angle α changes from the state of 90° to 0° cannot be realized mechanically, only A configuration in which the angle α changes from an angle of less than 90° to an angle of 0° can be realized. In addition, regarding the case where the angle α changes in the angle range between 90° and 180°, in the case where the direction of change starts from the 90° side, a structure that changes from 90° to 180° can be realized, but when changing When the direction starts from the 180° side, that is, the structure in which the angle α changes from a state of 180° to a direction in which the angle α becomes smaller cannot be realized mechanically.

And, regarding the situation that angle α changes in the angular range between 180° and 270°, in the case where the direction of change starts from the 180° side, a structure that changes from 180° to 270° can be realized, but when changing When the direction starts from the 270° side, that is, the structure in which the angle α changes from a state of 270° to a direction in which the angle α becomes smaller cannot be realized mechanically. In addition, regarding the case where the angle α changes in the angle range between 270° and 360°, in the case where the direction of change starts from the 270° side, a structure that changes from 270° to 360° can be realized, but when changing When the direction starts from the 360° side, the structure that the angle α is 270° cannot be realized mechanically, and only the structure that the angle α changes from 360° to an angle larger than 270° can be realized.

To sum up, the waveform curve B in the graph of FIG. 6(B) represents the follower in the range (b1) to (b6) of the following angle α that can be realized mechanically with respect to the link mechanism B. The relationship of the driven displacement amount of the side link member with respect to the driving displacement amount of the drive side link member. More details are as follows.

Regarding the area of the graph between 0° and 90° of the angle α, the following relationship is shown: When the direction of change of the angle α starts from the 0° side, the angle α is an angle range of 0° to 90° (Fig. The relationship of the driven displacement amount of the driven side link member with respect to the driving displacement amount of the driving side link member of (b1)) shown in (b1)); and the angle α in the case where the change direction of the angle α starts from the 90° side It is the relation of the driven displacement amount of the driven side link member with respect to the driving displacement amount of the driving side link member in the angle range of less than 90° and 0° or more (shown (b2)).

In addition, regarding the area of the graph between 90° and 180° of the angle α, the following relationship is shown: the change direction of the angle α in the angle range ((b3) shown in the figure) where the angle α is between 90° and 180° The relationship between the driven displacement amount of the driven side link member relative to the driving displacement amount of the driving side link member in the case of starting only from the 90° side, for the graph between 180° and 270° of the angle α The region represents the relationship of the driven-side link member in the case where the angle α changes in the angle range ((b4) shown in the figure) from 180° to 270° (shown in the figure) only from the 180° side. The relationship between the driven displacement amount and the driving displacement amount of the driving side link member.

In addition, regarding the area of the graph between 270° and 360° of the angle α, the following relationship is shown: the angle α in the case where the direction of change of the angle α starts from the 270° side is an angle range of not less than 270° and not more than 360° ((b5) shown in the figure) the relationship of the driven displacement amount of the driven side link member with respect to the driving displacement amount of the driving side link member; and in the case where the change direction of the angle α starts from the 360° side The relationship between the driven displacement amount of the driven side link member and the driving displacement amount of the driving side link member in which the angle α is within an angle range of 360° or less and more than 270° ((b6) in the figure).

In addition, in the range of the angle α that can be realized in the link mechanisms A and B shown above, the tendency of the change of the driven displacement amount of the driven side link member with respect to the driving displacement amount of the driving side link member (hereinafter Also referred to simply as "change tendency".) The details are as follows.

＜About Link Mechanism A＞

First, the above-mentioned change tendency in the above-mentioned range (a3) will be described based on an example of the link mechanism A shown in FIG. 7 . In the illustrated example, the driving side link member 53 is indicated by a one-dot chain line, and the driven side link member 54 is indicated by a two-dot chain line, and the rotation direction of the driving side link member 53 is indicated by a dotted line. A line arrow V is indicated, and a rotational direction of the driven side link member 54 is indicated by a dashed arrow W. As shown in FIG. 7 shows a situation where the angle α changes in the range of 90° to 180°, and also shows a predetermined unit angle (unit drive displacement amount: in the example shown in the figure) for each rotation (drive displacement) of the drive side link member 53. is 3.4°). In addition, the driving displacement per unit driving displacement of the driving side link member 53 is also referred to as "unit driving displacement" below.

As can be understood from the figure, in the link mechanism A, when the driving side link member 53 is driven and displaced so that the angle α varies in the range of 90° to 180°, the driven side link The driven displacement of the member 54 relative to the driving displacement shows the following variation tendency: the driven displacement of the driven side link member 54 relative to the unit driving displacement (3.4°) becomes larger when the angle α approaches 90°, and increases as the angle α approaches 90°. It becomes smaller as it approaches 180°. Specifically, as shown in the figure, the driving displacement (unit driving displacement) of the driven displacement of the driven side link member 54 relative to the driving displacement of the driving side link member 53 starts from the side where the angle α approaches 90°. It gradually decreases to 37.8°→15.2°→12.3°→11.1°.

That is, in the link mechanism A, as shown in FIG. 7 , the rotation range of the driving side link member 53 in which the angle α changes in the range of 90° to 180° with the driving displacement of the driving side link member 53 is from The driven displacement of the driving side link member 54 relative to the driving displacement of the driving side link member 53 has a characteristic that the efficiency becomes better as the angle α approaches 90°, and the efficiency gradually decreases as the angle α approaches 180°.

Among them, in the link mechanism A, along with the rotation of the driving side link member 53, the rotation center 53a of the driving side link member 53 to the center of the connecting portion 55 of the two link members (hereinafter also referred to as "connection point") ) 55a (hereinafter also referred to as “driving side portion”) changes in length, and the length of the driving side portion is the same as the portion from the rotation center 54a of the driven side link member 54 to the connection point 55a (hereinafter also referred to as The ratio of the lengths of the "driven-side portion" to "the driven-side portion."), that is, the lever ratio changes, and this change in the lever ratio affects the driven displacement of the driven-side link member 54 .

In addition, in the case of the link mechanism A shown in FIG. 7, that is, as shown in FIG. In the case where the driving displacement is performed in the same way (hereinafter referred to as "link mechanism A of Fig. 7" in abbreviation), based on FIG. Changes in the driven displacement amount of the driven side link member 54 .

FIG. 8 shows the unit driving displacement of the driven side link member 54 with respect to the driving side link member 53 by aligning the rotational positions of the driving side link member 53 for each unit driving displacement of the link mechanism A in FIG. 7 . driven displacement. That is, in FIG. 8 , the driving displacement of the driving-side link member 53 in each unit driving displacement is shown in such a manner that the start positions thereof coincide. Here, in the link mechanism A, as described above, the length of the above-mentioned driving side portion of the driving side link member 53 changes in each unit driving displacement, and therefore, in FIG. 8 , for each unit driving displacement The length of the driving side portion of the driving side link member 53 is an average length obtained by averaging the lengths of the driving side portions in the unit driving displacement. On the other hand, since the length of the driven side portion of the driven side link member 54 does not change, the position of the rotation center 54a is shown differently in accordance with the change of the average length of the driving side portion.

In addition, the change in the driven displacement amount of the driven side portion in FIG. 8 is the driven displacement amount of the driven side link member 54 affected by the change in the lever ratio in the link mechanism A of FIG. 7 . The change. Specifically, as can be understood from FIG. 8 , in the link mechanism A of FIG. 7 , the shorter the average length of the driving side portion of the driving side link member 53 is, that is, the closer the angle α is to 180°. During the unit driving displacement, the smaller the driven displacement amount (rotation amount) of the driven side link member 54 (the above-mentioned driven side portion), the smaller the driven displacement amount is from the longer (angle) of the above-mentioned average length of the above-mentioned driving side portion. α close to 90°), the unit driving displacements are 13.1°, 11.8°, 11.4°, 11.2° in turn. And, the change in the driven displacement amount of the driven side link member 54 (the above-mentioned driven side portion) per unit driving displacement of the driving side link member 53 (the previous unit of the two consecutive unit driving displacements) The difference between the driven displacement of the driving displacement and the driven displacement of the subsequent unit driving displacement) is 1.3°, 0.4°, and 0.2° in turn.

To sum up, if the driven displacement of the driven side link member 54 (the above-mentioned driven side part) in the link mechanism A of FIG. 7 is considered, in the case of FIG. In the driving displacement per unit of the link member 53, the driven displacement amount of the driven side link member 54 gradually becomes smaller, and the change (decrease) of the driven displacement amount gradually becomes smaller as 22.6°, 2.9°, 1.2°. On the other hand, the driven displacement amount of the driven side link member 54 affected by the above-mentioned change in the lever ratio in the link mechanism A of FIG. Among them, they gradually decrease to 13.1°, 11.8°, 11.4°, and 11.2° in turn, and the change (decrease) of the driven displacement is 1.3°, 0.4°, and 0.2° in turn.

Thus, even under the influence of the change in the lever ratio described above, the driven displacement amount of the driven side link member 54 relative to the unit driving displacement of the driving side link member 53 changes as follows: The driving displacement per unit of the side link member 53 becomes gradually smaller and the amount of reduction thereof becomes gradually smaller. However, it can be seen from the above that the amount of decrease in the driven displacement amount is smaller than the amount of decrease in the driven displacement amount of the driven side link member 54 obtained in FIG. 7 . It can be understood that the change in the driven displacement amount of the driven side link member 54 in the case of FIG. 7 is not affected only by the above-mentioned change in the lever ratio. In addition, in the link mechanism A, there is an angle α as a variable factor other than the above-mentioned lever ratio. Therefore, the change in the driven displacement amount (the driven displacement amount of the driven side link member 54 obtained in FIG. 7 The remainder of the reduction) can be said to be affected by changes in the angle α.

By the way, the amount of reduction in the driven displacement of the driven side link member 54 affected by the change in angle α can be obtained by subtracting the amount shown in FIG. 8 from the reduced amount of driven displacement obtained in FIG. 7 . Calculate the amount of reduction in the follower displacement amount affected by the above-mentioned change in the lever ratio. Specifically, the difference between the two is 21.3°, 2.5°, and 1.0° from the side where the angle α approaches 90°. Therefore, in the link mechanism A in FIG. The second unit driving displacement The driven displacement in is 21.3° smaller than the driven displacement in the initial unit driving displacement, and then changes to 2.5° and 1.0° smaller in turn.

Therefore, the link mechanism A can also be said to have the following characteristics: even if the influence of the above-mentioned lever ratio is removed, the driven displacement amount of the driven side link member 54 is reduced with a change in the angle α in the range of 90° to 180°. It becomes gradually smaller in per unit driving displacement of the driving side link member 53 .

In this way, in the link mechanism A of FIG. 7 , the driven displacement amount of the driven side link member 54 becomes gradually smaller per unit driving displacement of the driving side link member 53 due to the influence of the change of the angle α. Such a quadratic manner changes. Therefore, even if only the influence by the change of the angle α is grasped, the rotation amount in the driven displacement of the driven side link member 54 is as shown in the waveform curve A shown in FIG. 6(A) in the range (a3). This shows the change tendency (characteristic) of the quadratic curve. That is, the above-mentioned change tendency in the range (a3) gradually becomes smaller per unit driving displacement of the driving side link member as the driving side link member is driven and displaced so that the angle α changes from 90° to 180°. .

In addition, based on the above idea, in the waveform curve A shown in the graph of FIG. The above-mentioned tendency of change in a1), (a2), (a4), (a5), and (a6) can also be obtained in the same manner. In addition, the change tendency of the driven displacement amount of the driven side link member as a result of this calculation is as follows.

Regarding the area of the graph between 0° and 90° of the angle α, the range (a1), that is, the angle α in the case where the angle α changes from the 0° side, is an angle between 0° and less than 90° Range, the above-mentioned change tendency is opposite to the above-mentioned change tendency in the above-mentioned range (a3). That is, in the range (a1), the change tends to be a quadratic curve that gradually becomes larger per unit driving displacement of the driving side link member. On the other hand, in the range (a2), that is, when the angle α changes from the 90° side, the angle α is 90° or less and 0° or more, the above-mentioned change tendency is the same as that in the above-mentioned range (a3). The above changes tend to be the same.

In addition, regarding the area of the graph between 180° and 270° of the angle α, the angle α in the range (a4), that is, when the angle α changes from the 180° side, is 180° to 270°. For the angle range, the above-mentioned tendency of change is opposite to the above-mentioned tendency of change in the range (a3) (same as the above-mentioned tendency of change in the range (a1)).

And, regarding the region of the graph where the angle α is between 270° and 360°, the angle α in the range (a5), that is, when the angle α changes from the 270° side, is more than 270° and not more than 360°. The above-mentioned change tendency is the same as the above-mentioned change tendency in the range (a3). On the other hand, in the range (a6), that is, when the angle α changes from the 360° side, the angle α is in the range of 360° or less and 270° or more, the above-mentioned change tendency is the same as the above-mentioned change in the range (a3) The tendency is opposite (same as the above-mentioned change tendency in the ranges (a1) and (a4)).

＜About Link Mechanism B＞

In addition, regarding the above-mentioned tendency of change in the range of the achievable angle α in the link mechanism B, first, based on an example of the link mechanism B shown in FIG. illustrate. In the illustrated example, the driving side link member 56 is indicated by a one-dot chain line, and the driven side link member 57 is indicated by a two-dot chain line, and the rotation direction of the driving side link member 56 is indicated by a dotted line. A line arrow V' is indicated, and a rotational direction of the driven side link member 57 is indicated by a dotted line arrow W'. 9 shows the situation where the angle α changes in the range of 180° to 270°, and also shows that the drive side link member 56 is rotated (drive displacement) per unit drive displacement (11.25° in the illustrated example). state.

As can be understood from the figure, in the link mechanism B, when the driving side link member 56 is driven and displaced so that the angle α varies in the range of 180° to 270°, the driven side link The driven displacement of the member 57 with respect to the driving displacement shows a change tendency as follows: the driven displacement of the driven side link member 57 with respect to the unit driving displacement (11.25°) becomes larger as the angle α approaches 180°, and increases with time as the angle α approaches 180°. becomes smaller as it approaches 270°. Specifically, as shown in the figure, the driving displacement (unit driving displacement) of the driven side link member 57 relative to the driving displacement of the driving side link member 56 starts from the side where the angle α approaches 180°. It gradually decreases to 24.3°→13.7°→5.6°→1.4°.

That is, in the link mechanism B, as shown in FIG. The driven displacement of the driving side link member 57 relative to the driving displacement of the driving side link member 56 has a characteristic that the efficiency becomes better as the angle α approaches 180°, and gradually deteriorates as the angle α approaches 270°.

Among them, in the link mechanism B, along with the rotation of the drive side link member 56, the portion from the rotation center 57a of the driven side link member 57 to the center (connection point) 58a of the connecting portion 58 of both link members ( The length of the driven side portion) changes, and the ratio of the length of the driven side portion to the length of the portion (driving side portion) from the rotation center 56a of the driving side link member 56 to the connection point 58a, that is, the lever ratio changes. , the change in the lever ratio affects the driven displacement of the driven side link member 57 .

In addition, in the case of the link mechanism B shown in FIG. 9, that is, as shown in FIG. In the case of driving displacement in the same way (hereinafter abbreviated as "link mechanism B in Fig. 9"), the driven side link member 57 per unit driving displacement of the driving side link member 56 caused by the change of the lever ratio The change in the driven displacement amount of can be obtained based on FIG. 10 .

FIG. 10 shows the unit driving displacement of the driven side link member 57 with respect to the driving side link member 56 by aligning the rotational positions of the driving side link member 56 for each unit driving displacement of the link mechanism B in FIG. 9 . driven displacement. That is, in FIG. 10 , the driving displacement of the driving-side link member 56 in each unit of driving displacement is shown in a form in which the start positions coincide. Here, in the link mechanism B, as described above, the length of the above-mentioned driven side portion of the driven side link member 57 changes in each unit driving displacement. Therefore, in FIG. 10 , for each unit driving displacement The length of the driven side portion of the driven side link member 57 is an average length obtained by averaging the lengths of the driven side portion in the unit driving displacement. On the other hand, since the length of the above-mentioned driving side portion of the driving side link member 56 does not change, the above-mentioned driven side portion of the driven side link member 57 is adapted to the change in the above-mentioned average length of the above-mentioned driven side portion. , the position of the rotation center 57a is displayed differently.

In addition, the change in the driven displacement amount of the driven side portion in FIG. 10 is the driven displacement amount of the driven side link member 57 affected by the change in the lever ratio in the link mechanism B in FIG. 9 . The change. Specifically, as can be understood from FIG. 10 , in the link mechanism B in FIG. 9 , the longer the average length of the driven side portion of the driven side link member 57 is, that is, the closer the angle α is to 270 ° unit driving displacement, the smaller the driven displacement amount (rotation amount) of the driven side link member 57 (the above-mentioned driven side part), the smaller the driven displacement amount is from the above-mentioned average length of the above-mentioned driven side part ( The unit driving displacement of the angle α is close to 180° is 26.1°, 20.9°, 15.9°, 12.5° in turn. In addition, changes in the driven displacement amount of the driven side link member 57 (the above-mentioned driven side portion) per unit driving displacement of the driving side link member 56 are 5.2°, 5.0°, and 3.4° in order.

To sum up, considering the driven displacement of the driven side link member 57 (the above-mentioned driven side part) in the link mechanism B of FIG. 9, in the case of FIG. In the driving displacement per unit of the rod member 56, the driven displacement amount of the driven-side link member 57 gradually becomes smaller, and the change (decrease) of the driven displacement amount gradually becomes smaller in order of 10.6°, 8.1°, 4.2° °. On the other hand, the driven displacement amount of the driven side link member 57 affected by the above-mentioned change in the lever ratio in the link mechanism B of FIG. In the displacement, it decreases gradually to 26.1°, 20.9°, 15.9°, and 12.5° in sequence, and the change (decrease) of the driven displacement amount is 5.2°, 5.0°, and 3.4° in sequence.

In this way, even under the influence of the above-mentioned change in the lever ratio, the driven displacement amount of the driven side link member 57 relative to the driving side link member 56 per unit driving displacement changes in the following manner: The driving displacement per unit of the side link member 56 becomes gradually smaller and the amount of reduction becomes gradually smaller. However, it is clear from the above that the amount of decrease in the amount of driven displacement is smaller than the amount of decrease in the amount of driven displacement of the driven side link member 57 obtained in FIG. 9 . From this, it can be understood that the change in the driven displacement amount of the driven side link member 57 in the case of FIG. 9 is not only affected by the change in the lever ratio described above. In addition, in the link mechanism B, there is an angle α as a variable factor other than the above-mentioned lever ratio, so the change in the driven displacement amount (the driven displacement of the driven side link member 57 obtained in FIG. 9 The remainder of the amount of reduction), can be said to be affected by changes in the angle α.

By the way, the amount of reduction in the driven displacement of the driven side link member 57 affected by the change in angle α can be obtained by subtracting the amount of decrease in the driven displacement obtained in FIG. 9 from that shown in FIG. 10 . Calculate the amount of reduction in the follower displacement amount affected by the above-mentioned change in the lever ratio. Specifically, the difference between the two is 5.4°, 3.1°, and 0.8° from the side where the angle α approaches 180°. Therefore, in the link mechanism B in FIG. Among the driven displacement amounts of the driven side link member 57 in each unit driving displacement of the four unit driving displacements of the driving side link member 56 from the state of 180°, in the second unit driving displacement The driven displacement amount is 5.4° smaller than the driven displacement amount in the initial unit driving displacement, and then changed to 3.1° and 0.8° smaller in turn.

Therefore, the link mechanism B can be said to have the following characteristics: In addition to the influence of the above-mentioned lever ratio, the driven displacement amount of the driven side link member 57 varies with the change of the angle α in the range of 180° to 270°. The driving displacement per unit of the side link member 56 becomes gradually smaller.

In this way, in the link mechanism B of FIG. 9 , the driven displacement amount of the driven side link member 57 gradually changes per unit driving displacement of the driving side link member 56 due to the influence of the change of the angle α. Small changes in the way of such a quadratic curve. Therefore, even if the influence of only the change of the angle α is grasped, the rotation amount in the driven displacement of the driven side link member 57 is expressed as shown in the waveform curve B shown in FIG. 6(B) in the range (b4). The change tendency (characteristic) of the quadratic curve. That is, the above-mentioned change tendency in the range (b4) gradually becomes smaller per unit driving displacement of the driving side link member as the driving side link member is driven and displaced so that the angle α changes from 180° to 270°. .

In addition, based on the above idea, in the waveform curve B shown in the graph of FIG. The above-mentioned tendency of change in b1), (b2), (b3), (b5), and (b6) can also be obtained in the same manner. In addition, the change tendency of the driven displacement amount of the driven side link member as a result of this calculation is as follows.

Regarding the area of the graph between 0° and 90° of the angle α, the range (b1), that is, the angle α in the case where the angle α changes from the 0° side, is an angle range of not less than 0° and not more than 90° , the above-mentioned change tendency is the same as the above-mentioned change tendency in the above-mentioned range (b4). On the other hand, in the range (b2), that is, the angle range in which the angle α is less than 90° and greater than 0° when the angle α changes from the 90° side, the above-mentioned change tendency is the same as that in the above-mentioned range (b4). The above changes tend to be opposite. That is, in the range (b2), the above-mentioned change tendency is a quadratic tendency that gradually increases per unit driving displacement of the driving side link member.

In addition, regarding the area of the graph between 90° and 180° of the angle α, the angle α in the range (b3), that is, when the angle α changes from the 90° side, is 90° to 180°. Angle range, the above-mentioned change tendency is opposite to the above-mentioned change tendency in the range (b4) (the above-mentioned change tendency in the range (b2) is the same.

In addition, regarding the region of the graph between 270° and 360° of the angle α, the angle α in the range (b5), that is, when the angle α changes from the 270° side, is 270° to 360°. Angle range, the above-mentioned tendency of change is opposite to the above-mentioned tendency of change in the range (b4) (same as the above-mentioned tendency of change in the ranges (b2), (b3)). On the other hand, in the range (b6), that is, the angular range in which the angle α is 360° or less and exceeds 270° when the angle α changes from the 360° side, the above-mentioned change tendency is the same as that of the above-mentioned range (b4) The tendency to change is the same.

In addition, in the above, with regard to the link mechanisms A and B, the range of the angle α that can be realized in the structure of the link mechanisms A and B when the angle α changes within the angle range of 90° or approximately 90° (range ( The above-mentioned change tendencies in a1) to (a6), (b1) to (b6)) have been explained, and within each of the above-mentioned ranges, even if the angle range in which the angle α changes is smaller than the above-mentioned 90° or approximately 90° range, the above-mentioned change tendency in this small range is also the same tendency as the above-mentioned change tendency in the above-mentioned range including this range.

And, as explained above, with regard to the link mechanism A, B, the range of the angle α that the above-mentioned change tendency can realize in its structure becomes the graph shown in FIG. 6(A) or FIG. 6(B). The trend shown by the waveform curves A and B. That is, the link mechanisms A, B have the characteristic that the driven side link member is driven to be displaced according to the waveform curves A, B accompanying the driving displacement of the driving side link member.

In summary, if the link mechanism 41 in the above-mentioned embodiment is considered, the link mechanism 41 is a link mechanism configured as follows, as described above, as the winding diameter of the driving side link member. The connecting portion 47 of the rod 42 and the rotating rod 43 as a driven side link member is displaced in the extending direction of the winding diameter following rod 42 (the support portion 42a thereof) along with the rotation of the winding diameter following rod 42, so the link mechanism 41 corresponds to the link mechanism A described above. Therefore, in the link mechanism 41, along with the rotation (drive displacement) of the roll diameter following lever 42, the rotation lever 43 rotates according to the above-mentioned change tendency represented by the waveform curve A in the graph of FIG. 6(A) (driven displacement).

Furthermore, as described above, in the link mechanism 41 of the present embodiment, the angle α changes within an angular range of 100° to 162° from the start of winding of the fabric 1 to the end of winding. In addition, this angle range corresponds to the range indicated by (z) within the above-mentioned range (a3) in the graph of FIG. 6(A). Therefore, the above-mentioned change tendency of the pivot lever 43 in the above-mentioned angle range in the link mechanism 41 is the same tendency as the above-mentioned change tendency of the driven-side link member in the above-mentioned range (a3). That is, the link mechanism 41 plays the role (hereinafter also simply referred to as "this role") as the object of the present invention in the above-mentioned angle range, that is, due to the influence of the change of the angle α along with the driving displacement of the winding diameter following lever 42, , the driven displacement amount of the rotating rod 43 changes in a quadratic curve so as to gradually decrease per unit driving displacement of the winding diameter following rod 42 . In other words, the link mechanism 41 plays the following role: During the period from the start of winding to the end of winding, due to the influence of the change of angle α, the winding diameter with respect to the increase in the unit winding diameter immediately after the winding starts The amount of rotation of the rotation lever 43 obtained by following the rotation of the lever 42 and the amount of rotation of the rotation lever 43 obtained by the rotation of the winding diameter following lever 42 accompanying the increase of the unit winding diameter immediately before the end of winding is small.

In addition, in the link mechanism 41, similar to the link mechanism A of FIG. 7 , as the winding diameter following rod 42 is driven and displaced, the rotation center of the winding diameter following rod 42 (support portion 42a) (the axis of the supporting shaft 45) 45a) to the center of the connecting portion 47 of the two link members (the axis 44a of the connecting pin 44) (corresponding to the above-mentioned "driving side part") changes in a gradually shortened manner, and the rotating rod 43 The ratio of the length of the portion from the center of rotation (the position of the axis 48a of the support shaft 48) to the axis 44a of the connecting pin 44 (corresponding to the above-mentioned "driven side portion") to the length of the driving side portion is also That is, the lever ratio changes in a gradually increasing manner. Therefore, also due to the influence of the change in the lever ratio, the driven displacement amount of the rotating rod 43 also changes in a gradually decreasing manner in the per unit driving displacement of the winding diameter following rod 42. . That is, the above-mentioned main action is also manifested by the influence of the above-mentioned change in the lever ratio. Therefore, in the link mechanism 41 of this embodiment, the above-mentioned main action caused by the influence of the change of the angle α can be multiplied and added to the above-mentioned main action caused by the influence of the change of the lever ratio to obtain a larger main action. To achieve the above effect.

In addition, the first embodiment is not limited to the configuration described above, and may be implemented in a modified form as in the following (1) and (2).

(1) In the above-mentioned first embodiment, the initial arrangement of each link member in the link mechanism 41 is set so that, within the rotation range of the winding diameter following lever 42 (from the start of winding to the end of winding), The rolling diameter follows the range of rotation of the rod 42), and the angle α satisfies the above-mentioned condition (a) and changes in the angle range of 100 ° to 162 ° (the range (z) represented by the graph of Fig. 6 (A)), but this The invention is not limited to the case where the initial arrangement of each link member is set so that the angle α changes within the angle range as in the first embodiment described above, and the initial arrangement of each link member is set so that the angle α satisfies the above-mentioned condition (a ), that is, the angle α in the range of 90° to 195° may be changed in the direction of increasing the angle along with the rotation of the winding diameter following lever in the above-mentioned rotation range.

In addition, the "angle range of not less than 90° and not more than 195°" in the above condition (a) is 180° to 195° of the angle α in the range (a3) plus the range (a4) in the graph of FIG. 6(A). The angle range in the range of ° is a range beyond the range (a3) (90° to 180°) that functions as described above, and the details of the angle range are as follows.

In the description related to the characteristics of the link mechanism using FIG. 7 in the above-mentioned first embodiment, in order to explain the characteristics of the link mechanism A every 90° of the angle α, in FIG. 7 , as the angle α at 90° The range from 180° to 180° is shown for the link mechanism A. In the illustrated structure, the link mechanism A is not only able to make the driving side link member 53 change from the state of 90° to the angle α. The driving displacement is performed in a manner of 180°, and the driving displacement of the driving-side link member 53 can be varied in a manner exceeding 180° to 270°. That is, the link mechanism A is configured to be variable in the angle range (range (a3)+(a4)) where the angle α is 90° to 270°.

In addition, when the link mechanism A changes in the range (a3)+(a4) of the angle α in this way, it is clear from the above description that this function is performed while the angle α is changed in the range (a3). When the angle α changes in the range (a4), it acts opposite to this action, that is, the driven displacement of the driven side link member gradually increases with the driving displacement of the driving side link member (hereinafter also referred to as referred to as "opposite effect".).

Wherein, regarding the driven displacement amount of the driven side link member in this range (a4), it can also be seen from the graph of FIG. Angle range of 195°: the range (p) shown in the figure), the change of the driven displacement is very small. Therefore, even if the final unit driving displacement in the rotational range of the driving side link member is changed such that the angle α exceeds (over) 180°, if the angle α at the time of completion of the rotation in the final unit driving displacement is 195° or less, the driven displacement amount of the driven side link member in the last unit driving displacement is smaller than the driven displacement amount of the driven side link member in the preceding unit driving displacement.

In this way, in the link mechanism A, the range (a4) is a range that has the opposite effect, but if the angle α at the time of the end of the rotation in the above-mentioned last unit driving displacement is within the range (p) in the range (a4), Then, the link mechanism A may play this role within the rotation range of the drive side link member. Therefore, in the present invention, regarding the link mechanism configured such that the connecting portion of the two link members can be displaced in the direction in which the drive-side link member extends, like the link mechanism A, in order to achieve this function, each link member The initial configuration is set so that the angle α satisfies the above condition (a).

In the range (p) of the range (a3) and the range (a4), as described above, the closer the angle α is to 180°, the greater the driven displacement of the driven side link member relative to the unit driving displacement of the driving side link member. The smaller the amount of displacement is, therefore, the closer the angle α is to 180° at the start of winding, the smaller this effect can be obtained. Therefore, it is preferable to set the initial arrangement of each link member so that the angle α at the start of winding is 150° or less.

(2) In the above-mentioned first embodiment and above-mentioned (1), regarding the initial arrangement of each link member in the link mechanism A, the angle α is set so that the above-mentioned condition (a) is satisfied, but the present invention is not limited thereto The above-mentioned initial configuration of the link mechanism A may also be set such that the angle α satisfies the following condition (b) or condition (c) within the rotation range of the winding diameter following rod.

Condition (b): It is included in the angle range of -15° to 90°, and the winding start time is closer to 90° than the winding end time.

Condition (c): It is included in the angular range exceeding 270° and not more than 375°, and the winding start time is closer to 270° than the winding end time.

Regarding the conditions (b) and (c), in more detail, first of all, regarding the condition (b), the angle range, as explained above, includes "the angle formed on the opposite side of the rotation direction of the winding diameter following lever." Angle range from 15° to 0°" and "angle range from 0° to 90° on the side of the rotation direction of the roll diameter following lever". Among them, regarding "the angle formed by the rotation direction side of the winding diameter following lever is an angle range of 0° to 90°", because of the condition that "the start of winding is closer to 90° than the end of winding", at this angle The angle α of the range varies from 90° to 0°, and its angular range according to its changing direction (angle: large → small) corresponds to the range (a2) in the graph of FIG. 6(A) described above. In addition, regarding "the angle range of 15° to 0° formed by the opposite side of the rotation direction of the winding diameter following lever", in other words, the angle range is "the angle range of 345° to 360° of the angle α", According to the above variation tendency, the angle range is a part of the range (a6) in the above-mentioned graph of FIG. 6(A), and is an angle range from 360° (=0°) to 345°.

That is, condition (b) is a condition that also includes the following cases, that is, adding a part of the range (a6) that has the opposite effect (360° (0°) below 345° In the angle range above), the angle α changes to a smaller direction, and the angle α at the end of the winding is in the range of more than 0° (360°) to -15° (345°) (the range that plays the opposite effect ( a6)) within. In addition, the "angle range from 0° (360°) to -15° (345°)" is the same as the angle range from 180° to 195° in the condition (a) described in (1) above, It is a range in which the driven displacement of the driven side link member varies very little with respect to the driving displacement of the driving side link member, so it is also included in the range that acts oppositely, as in condition (a). the condition. Furthermore, even when the initial arrangement of each link member is set so as to satisfy the condition (b), the link mechanism A can function within the rotation range of the drive side link member.

Among them, regarding the angular range of condition (b), the closer the angle α is to 0° (360°), the smaller the driven displacement amount of the driven side link member relative to the driving side link member per unit driving displacement. At the beginning, the closer the angle α is to 0° (360°), the smaller the obtained effect. Therefore, it is the same as the setting of the initial arrangement of each link member described in (1) above. When the initial arrangement of the link members is set so as to satisfy the condition (b), it is preferable to set the angle α at the start of winding to be 30° or more.

In addition, regarding the condition (c), as explained above, the angle range includes "angle α from an angle exceeding 270° to 360°" and "angle α from 0° (360°) to 15° (375°) angle range". Among them, regarding the "angle α from an angle exceeding 270° to 360°", because of the condition that "the start of winding is closer to 270° than the end of winding", the angle α in this angle range varies from more than 270° to 360°. The angle of 270° reaches 360°, and its angular range according to its changing direction (angle: small→large) corresponds to the range (a5) in the graph of FIG. 6(A) described above. In addition, regarding "the angle range of angle α from 0° to 15°", according to the above-mentioned change tendency, this angle range corresponds to a part of the range (a1) in the above-mentioned graph of FIG. 6(A) (0°( = 360°) to 15°) angle range.

That is, the condition (c) is a condition that also includes the case where the angle α changes to There is a large change in direction, and the angle α at the end of the winding is in the range of over 360° (0°) to 375° (15°) (the range (a1) that plays the opposite role). In addition, the "angle range from 360° (0°) to 375° (15°)" is the same as the angle range from 180° to 195° in the condition (a) described in (1) above, and is derived from The range in which the driven displacement of the driven-side link member varies very little with respect to the driving displacement of the drive-side link member. Therefore, it is the same as condition (a), and even a part of the range that has the opposite effect is included in this condition. . Furthermore, even when the initial arrangement of each link member is set so as to satisfy the condition (c), the link mechanism A can function within the rotation range of the drive side link member.

Among them, regarding the angle range of the condition (c), the closer the angle α is to 360° (0°), the smaller the driven displacement amount of the driven side link member relative to the unit driving displacement of the driving side link member. At the beginning, the closer the angle α is to 360° (0°), the smaller the obtained effect. Therefore, it is the same as the setting of the initial arrangement of each link member described in (1) above. When the initial arrangement of the rod member is set so as to satisfy the condition (c), it is preferably set so that the angle α at the start of winding is 330° or less.

In addition, in the above-mentioned first embodiment, with regard to the structure of the link mechanism, the connecting portion configured so that the driving side link member (winding diameter following rod) and the driven side link member (rotation rod) can follow the winding diameter. The case of displacement in the extension direction of the rod has been described, but the link mechanism of the present invention is not limited to the above-mentioned configuration as long as the above-mentioned connecting portion can be displaced in the extension direction of one of the link members among the winding diameter following rod and the rotation rod. In the case of the configuration as in the first embodiment (where the one link member is a winding diameter following rod), the one link member may be used as a turning lever, and the connecting portion may be displaced in the extending direction of the turning lever.

Therefore, as the second embodiment of the present invention, based on FIG. 5(a), FIG. 5(b), FIG. 6(A), FIG. 6(B), FIG. 11, and FIG. An example of a web tension adjusting device of a link mechanism capable of displacing in the extending direction of the rotating rod will be described. In addition, in this second embodiment, the cloth winding torque adjustment device as a premise has the same configuration as that of the above-mentioned first embodiment. In addition, the link mechanism 59 in this second embodiment is omitted from the illustration in FIG. The structure in which the driven rod 28 in the torque adjustment device 10 is connected. And, as shown in FIG. 11 , in this link mechanism 59 , each link member (rolling diameter following lever 60 and turning lever 61 ) is directly connected so that their connecting portion 62 can displace in the direction in which the turning lever 61 extends. structure.

The rolling diameter following rod 60 has the same structure as the rolling diameter following rod 42 in the above-mentioned first embodiment. A through hole 60d is formed at one end of the support portion 60a, and a through hole 60e is formed at the center of the boundary portion between the support portion 60a and the intermediate portion 60b, and the roller 46 is attached to the contact portion 60c. In addition, the winding diameter following rod 60 is disposed between the loom frame 9 and the cloth winding roller 6 in the fabric width direction, and is rotatably supported on the loom frame 9 via a support shaft 45 inserted into the loom frame 9 . In the through hole 60d of the support part 60a, it is arranged above the axis 6a of the cloth winding roller 6 in the up-down direction, and the winding diameter following rod 60 is arranged so that, due to its own weight, it will be wound relative to the cloth winding roller 6. The fabric 1 maintains the contact state of the roller 46 on the cloth fell 2 side.

In addition, the appearance shape of the turning lever 61 is the same as that of the turning lever 43 in the above-mentioned first embodiment, and a through-hole 61 a is formed in the same manner as the turning lever 43 at one end thereof. Among them, the rotation rod 61 has an elongated hole 61b extending in the extending direction and penetrating in the plate thickness direction at the other end side thereof. In addition, the rotation lever 61 is arranged between the loom frame 9 and the winding diameter follower lever 60 in the fabric width direction similarly to the above-mentioned first embodiment, and the support shaft 63 inserted into the through hole 61a is passed on one end side. And can be rotatably supported on the loom frame 9 . In addition, the support shaft 63 is equipped with the timing pulley in the above-mentioned rotation transmission mechanism similarly to the support shaft 48 of the above-mentioned first embodiment. Therefore, as described above, the turning lever 61 (the link mechanism 59 having the turning lever 61 ) is connected to the driven lever 28 in the cloth winding torque adjustment device 10 via the rotation transmission mechanism and the support shaft 63 .

Moreover, the winding diameter following lever 60 and the rotation lever 61 are connected via the connection pin 64 similarly to the said 1st Example. Among them, in this second embodiment, as mentioned above, a long hole is formed on the side of the rotating rod 61, and the connecting pin 64 fixedly arranged on the winding diameter following rod 60 is inserted through the long hole 61b of the rotating rod 61, so that the two can be directly connected to each other. link. More specifically, the connecting pin 64 is inserted into and fixed to the through hole 60e of the roll diameter following rod 60 in a form protruding toward the loom frame 9 side, and the connecting pin 64 is in the form of being inserted into the elongated hole 61b of the rotating rod 61. Therefore, the winding diameter following rod 60 is directly connected to the rotating rod 61 . In addition, in such a link mechanism 59, when viewed from the width direction of the fabric, the connecting portion 62 is a portion where the winding diameter following rod 60 intersects and overlaps with the turning rod 61, and the center of the connecting portion 62 becomes the axis 64a of the connecting pin 64. .

In addition, in the link mechanism 59 in the second embodiment, since the position of the connecting portion 62 (connecting pin 64) is configured to be displaced in the direction in which the rotating rod 61 extends along with the rotation of the winding diameter following rod 60, Rotation of the two linkage members is permitted. In addition, the extension length of the elongated hole 61b allows, of course, the displacement of the coupling pin 64 accompanying the rotation of the winding diameter following lever 60 from the winding start time to the winding end time. By the way, in the link mechanism 59 in the second embodiment, as will be described later, as a result of setting the initial arrangement, the position of the link pin 64 is changed according to the rotation of the winding diameter following lever 60 during the above-mentioned period. In the direction in which the rotation rod 61 extends from the vicinity of the center of the rotation rod 61 toward the other end side (the side opposite to the support shaft 63 supporting the rotation rod 61 ), approximately two-fifths of the extension length of the rotation rod 61 change.

In the loom of the second embodiment including the link mechanism 59 configured as above, the roll diameter of the rolled cloth 1 is 100 mm at the start of winding and 300 mm at the end of winding. Furthermore, in the present second embodiment, the initial arrangement of each link member in the link mechanism 59 is set to satisfy the following condition (d).

In detail, let the line segment connecting the support shaft 45 (its axis 45a) supporting the roll diameter following rod 60 and the connecting portion 62 (its center: the axis 64a of the connecting pin 64) be a line segment N' (shown in FIG. 12 ). The single dotted line shown), linking the supporting shaft 63 (its axis 63a) of the rotating rod 61 and the line segment of the connecting part 62 (axis 64a) is set as a line segment K' (the double point shown in Figure 12 dashed line), after setting the angle formed by the line segment K' relative to the line segment N' on the side of the rotation direction of the roll diameter following lever 60 (line segment N') as angle α, in the rotation range of the roll diameter following lever 60, the initial configuration The angle α is set to satisfy the following condition (d).

Condition (d): It is included in the angular range of 170° to 270°, and the end of winding is closer to 270° than the start of winding.

Wherein, in the structure of the second embodiment, the length of the line segment K' (the distance between the axis 63a of the support shaft 63 and the axis 64a of the connecting pin 64) is not fixed, but changes with the rotation of the winding diameter following lever 60. Variety. That is, in the link mechanism 59 of the second embodiment, if the roll diameter following lever 60 rotates, the connecting pin 64 faces the other end side of the rotating rod 61 in the elongated hole 61b (towards the inside of the elongated hole 61b) along with the rotation. The upper end side of the connecting pin 64) slides, so as a result of the position change of the connecting pin 64, the length of the line segment K' gradually becomes longer. Therefore, the length of the line segment K' is minimum at the start of winding (initial arrangement), and becomes maximum at the end of winding.

Also, in the present second embodiment, in order to satisfy the condition (d), the initial arrangement of each link member is set so that the angle α in the initial arrangement is 180°. Moreover, in this second embodiment, when setting the initial arrangement of each link member, first, regarding the initial arrangement of the winding diameter following rod 60, it is different from the initial arrangement of the winding diameter following rod 42 in the above-mentioned first embodiment. Set the same as the setting of . And, accompanying this, the arrangement angle of the support portion 60a (line segment N') of the winding diameter following lever 60 and the total rotation amount of the winding diameter following lever 60 are determined.

In addition, the initial arrangement of the rotation lever 61 is set according to the following circumstances and considering the design restrictions on the mechanical structure in the second embodiment, that is, according to the arrangement angle of the support part 60a in the initial arrangement and The angle of arrangement of the support portion 60a at the end of winding is determined by the total rotation amount of the winding diameter following lever 60, the distance from the axis 45a of the support shaft 45 to the axis 64a of the connecting pin 64 is always fixed, and the support shaft 63 is installed It is set at a position where the angle α in the initial arrangement is 180° as described above and a position where the angle α at the end of winding based on the condition (d) is 270° or less. And, as a result, the position of the support shaft 63, the arrangement angle of the rotation lever 61 in the initial arrangement, and the total rotation amount of the rotation lever 61 are determined. Incidentally, in this second embodiment, the position of the support shaft 63 is arranged at a position where the angle α at the end of winding is 245°.

As described above, in the loom including the link mechanism 59 in which the initial arrangement of each link member is set, the roll diameter following lever 60 moves in the direction indicated by the dotted arrow X in FIG. 11 as the roll diameter increases. During the rotation toward the cloth fell 2 side, as in the above-mentioned first embodiment, the rotation is always performed by a constant rotation amount with respect to the increase in the unit winding diameter from the start of winding to the end of winding. In addition, as the winding diameter following lever 60 rotates in this way, the rotating lever 61 connected to the winding diameter following lever 60 via the connecting pin 64 rotates toward the cloth fell 2 side in the direction indicated by the dotted arrow Y' in FIG. 11 .

In addition, the angle α set to 180° in the initial arrangement (at the start of winding) becomes 245° at the end of winding as described above. That is, the line segment K′ connecting the second support shaft (support shaft 63 ) supporting the rotation lever 61 and the connection portion 62 is relative to the line segment connecting the first support shaft (support shaft 45 ) supporting the winding diameter following rod 60 and the connection portion 62 The angle α formed by N' on the side of the rotation direction of the winding diameter following lever 60 is included in the angular range of 170° to 270° in the rotating range of the winding diameter following lever 60, and is closer to 270° at the end of winding than at the beginning of winding. °.

In addition, it is clear from this structure that the link mechanism 59 in the second embodiment corresponds to the above-mentioned link mechanism B shown in FIG. 9 . Therefore, in the link mechanism 59, the change tendency of the driven displacement of the rotation rod 61 as the driven side link member with respect to the driving displacement of the winding diameter following rod 60 as the driving side link member becomes as shown in FIG. 6(B ) shows the changing tendency of the waveform curve B. Furthermore, in the link mechanism 59, as described above, the angle α changes from 180° to 245° in the rotation range of the coil diameter following lever 60, so that the rotation lever 61 follows the curve shown in the graph of FIG. 6(B). In the above-mentioned change tendency in the range (b4), the driven displacement (rotation amount) per unit driving displacement of the winding diameter following rod 60 gradually decreases and the driven displacement (rotation) proceeds.

Specifically, if the increment of the unit winding diameter is set to 50 mm, and the winding diameter following rod 60 accompanying the increase of the unit winding diameter during the period from the beginning of winding (rolling diameter 100 mm) to the end of winding (rolling diameter 300 mm) The amount of rotation (unit driving displacement) shown in Figure 12 is 5.5°, then the amount of rotation of the rotating rod 61 relative to the unit driving displacement gradually decreases from the side where the angle α approaches 180° to 16°→13°→9 °→6°. That is, in the second embodiment, the amount of rotation of the rotation lever 61 accompanying the increase in the unit winding diameter from the start of winding to the end of winding is the same as in the above-mentioned first embodiment. The rotation amount of the rotation lever 61 obtained by the rotation of the winding diameter following lever 60 accompanying the increase of the unit winding diameter immediately after the start of winding, and the rotation amount of the rotation lever 61 obtained by the rotation of the winding diameter following lever 60 accompanying the increase of the unit winding diameter immediately before the end of winding. The amount of rotation becomes a small value.

Therefore, in the second embodiment, as described above, according to the change in the rotation amount of the rotation lever 61, the increase amount of the cloth winding torque gradually becomes smaller as shown by the solid line H1 in FIG. Here, the degree of reduction of the fabric tension per unit diameter increases is substantially constant, and the fabric tension decreases approximately in proportion to the increase in the diameter of the fabric as shown by the solid line H2 in FIG. 5( b ).

In addition, 2nd Example is not limited to the structure demonstrated above, It can also implement in the form deform|transformed into the following (1), (2).

(1) In the above-mentioned second embodiment, the initial arrangement of each link member in the link mechanism 59 is set to be within the rotation range of the winding diameter following rod 60, and the angle α satisfies the condition (d) and is between 180° and The angle range of 245° changes, but the present invention is not limited to the case where the initial arrangement of each link member is set so that the angle α changes within the angle range of the above-mentioned second embodiment, it may also be that each link member The initial configuration is set so that the angle α satisfies the condition (d), that is, the angle α can be changed to a larger angle in the angle range of 170° to 270° with the rotation of the winding diameter following rod in the above-mentioned rotation range.

In addition, the "angle range of not less than 170° and not more than 270°" in the condition (d) is the range of 170° to 180° of the angle α in the range (b3) represented by the graph of FIG. 6(B) plus The angle range of the range (b4) is larger than the above-mentioned range (b4) (180° to 270°) that functions. The details of this angle range are as follows.

First, the link mechanism B shown in FIG. 9 is the same as the above-mentioned link mechanism A, and is a structure that can change the angle α in the angle range (range (b3)+(b4)) of 90° to 270°. In addition, in the link mechanism B, when the angle α changes in the range (b3)+(b4) in this way, it is clear from the above description that while the angle α changes in the range (b3), the opposite effect occurs. It plays this role when the angle α changes in the range (b4).

Here, regarding the driven displacement amount of the driven side link member in this range (b3), it can be seen from the graph of FIG. (q)), the amount of driven displacement is equivalent to the angular range of 180° to 190° in the range (b4), which becomes a very large amount of displacement. Therefore, if the initial unit driving displacement in the rotational range of the driving side link member is a unit driving displacement in which the angle α changes over (over) 180° and the rotation start time in the initial unit driving displacement is If the angle α is 170° or more, the driven displacement amount of the driven side link member in the initial unit driving displacement is larger than the driven displacement amount of the driven side link member in the next unit driving displacement. .

In this way, in the link mechanism B, the range (b3) is a range that has the opposite effect, but if the angle α at the time of the start of the rotation in the above-mentioned initial unit driving displacement is within the range (q) in the range (b3), Then, the link mechanism B may function within the rotation range of the drive-side link member. Therefore, in the present invention, regarding the link mechanism configured such that the connecting portion of the two link members can be displaced in the extending direction of the driven side link member like the link mechanism B, in order to achieve this function, each link member The initial configuration of is set so that the angle α satisfies the condition (d).

(2) In the above-mentioned second embodiment and above-mentioned (1), regarding the initial arrangement of each link member in the link mechanism B, it is set so that the angle α satisfies the condition (d), but the present invention is not limited thereto, The above-mentioned initial arrangement of the link mechanism B may be set so that the angle α satisfies the following condition (e) or condition (f) within the rotation range of the winding diameter following lever.

Condition (e): In the angular range of more than 270° and not more than 370°, the winding end is closer to 270° than the winding start time.

Condition (f): In an angle range including -10° to 90°, the winding end is closer to 90° than the winding start time.

Regarding the conditions (e) and (f), in more detail, first, regarding the condition (e), as explained above, the angle range is an angle range including "angle α exceeding 270° to 360°." " and "angular range of angle α from 0° (360°) to 10° (370°)". And, regarding these two angle ranges, according to the change direction (angle: large → small) of the angle α based on "the winding end is closer to 270° than the winding start", it can be said that the former corresponds to the above-mentioned Fig. 6 ( The range (b6) in the graph of B) (below 360° and over 270°), the latter corresponds to an angle range of a part (below 10° and 0° or more) of the range (b2) in the graph.

Therefore, the condition (e) is a condition that also includes the case where the angle α changes to The direction change is small, and the angle α at the start of winding is in the range (the range (b2) that plays the opposite role) greater than 360° to 370° (the angle from 360°(0°)+10°). In addition, the "angle range of 10° (370°) or less and 0° (360°) or more" is the same as the angle range of 170° to 180° in the condition (d) described in (1) above. Since the driven displacement amount of the driven-side link member is in a very large range, it is also included in the condition (e) even if it is a part of the range that acts oppositely, as in the condition (d). Furthermore, even when the initial arrangement of each link member is set so as to satisfy the condition (e), the link mechanism B can function within the rotation range of the drive side link member.

In addition, regarding the condition (f), as explained above, the angle range includes "the angle range between 10° and 0° formed on the opposite side to the rotation direction of the winding radius following lever" and "the The angle formed by the rotation direction side of the following rod is an angle range from 0° to 90°. In addition, the former angle range among them is, in other words, "the angle range of 350° to 360° of the angle α" or "the angle range of -10° to 0° of the angle α". And, regarding the above-mentioned two angle ranges, according to the change direction (angle: small → large) of the angle α based on "the winding end is closer to 90° than the winding start", it can be said that the former corresponds to the above-mentioned Fig. 6 ( Part of the range (b5) in the graph of B) (350° to 360°), which corresponds to the range (b1) (0° to 90°) in the graph.

Therefore, the condition (f) is based on the condition that the angle α is in the angle range including the above-mentioned part of the range (b5) that plays the opposite role and the range (b1) that plays the role. The larger direction changes, and the angle α at the start of winding is in the range of less than 0° and up to 350° (the angle from 360° (0°) to -10°) (the range that plays the opposite role (b5) )Inside. In addition, the "angle range from 350° (-10°) to 360° (0°)" is the same as the angle range from 170° to 180° in the condition (d) described in (1) above, and is The range in which the driven displacement amount of the driven side link member is very large is the same as condition (d), and even a part of the range in which it acts oppositely is included in condition (f). In addition, when the initial arrangement of each link member is set so as to satisfy the condition (f), the link mechanism B can also function within the rotation range of the drive side link member.

In addition, this invention is not limited to the structure demonstrated in the said 1st, 2nd Example (above-mentioned each Example), It is also possible to implement in the aspect modified|transformed into the following (1)-(5).

(1) In each of the above-mentioned embodiments, the winding diameter following rod and the rotating rod as the link members constituting the link mechanism are all plate-shaped members, but the link members in the link mechanism of the present invention are not It is not limited to members of this shape, and any link member may have a shape as long as it has a function as a link member of a link mechanism. The rod member is made into a rod-shaped member.

(2) In each of the above-mentioned embodiments, in the link mechanism, the winding diameter following rod and the rotation rod are directly connected by inserting the connecting pin fixed to the other link member through the elongated hole formed in one link member. , but the connecting structure of the winding diameter following rod and the rotating rod of the link mechanism of the present invention is not limited to the connecting structure obtained by such a long hole and a connecting pin, as long as the two connecting rod parts are directly connected into two connecting rod parts A structure in which the position of the linking portion of one link member changes in the extending direction of one link member may be used. A sliding coupling connects the two link parts.

(3) In each of the above-mentioned embodiments, the roll diameter following rod includes: a support portion and an abutment portion that exist in the same direction, and a middle portion that connects the support portion and the abutment portion and forms an angle with respect to the support portion and the abutment portion. portion, but the structure of the roll diameter following rod of the present invention is not limited to such a structure, and the intermediate portion may be removed, and only a linear rod consisting of a support portion and an abutting portion extending in the same direction may be used.

In addition, in the above-mentioned embodiments, the winding diameter following lever is composed of a single member, but the winding diameter following lever is not limited to being composed of such a single member, and may be formed by combining two or more members. That is, with regard to the roll diameter following rod of each of the above-mentioned embodiments, what functions as a link member of the link mechanism is the support portion, and the intermediate portion and the abutting portion are used as the support portion to follow the increase in the roll diameter of the cloth 1 . And the rotating part is the functional part. Therefore, regarding the structure of the rolling diameter following rod of the present invention, it is also possible to use the components corresponding to the supporting part of the rolling diameter following rod in the above-mentioned embodiments and the components corresponding to the intermediate part and the abutting part as different components, and A structure in which the above two components are combined in such a way that they cannot be rotated relative to each other.

(4) In each of the above-described embodiments, the supporting shaft supporting the rotating rod and the supporting shaft supporting the driven rod 28 are connected via a rotation transmission mechanism composed of a timing pulley and a timing belt, so that the wound cloth rotates. The driven lever 28 of the moment adjusting device 10 rotates with the rotation of the turning lever, but in the present invention, when the supporting shaft of the turning lever and the supporting shaft of the driven lever are arranged so that their centers of rotation are different, Instead of the above-mentioned timing pulley and timing belt, a rotation transmission mechanism using a gear, a chain, or the like may be employed. In addition, it is not limited to the structure in which the supporting shaft of the rotating rod and the supporting shaft of the driven rod 28 are connected by the above-mentioned rotation transmission mechanism, and the rotating rod or the driven rod 28 (cloth winding torque adjustment device 10) can In the case where the center of rotation of the drive rod 28 is configured in the same manner as the center of rotation of the driven rod 28, the supporting shaft of the rotating rod and the supporting shaft of the driven rod 28 may be connected by a shaft joint or the like, or it may be made into a rotating rod A structure supported by the same support shaft as the driven rod 28.

(5) In each of the above-mentioned embodiments, the rolling diameter following rod is based on the premise that the contact state of the roller 46 relative to the cloth 1 is maintained by its own weight. In order to meet this premise, the support shaft 45 supporting the rolling diameter following rod The position of is set above the axis 6a of the cloth winding roller 6 . However, regarding the arrangement of the winding diameter following lever in the present invention, the support shaft supporting the winding diameter following lever may be arranged at any position around the cloth winding roller. However, due to the relationship between the position of the support shaft and the contact position with respect to the cloth, the abutment state of the roller with respect to the cloth may not be maintained by the weight of the diameter following rod. Therefore, in this case, for example, a configuration may be adopted in which a biasing means such as a spring is used to apply an urging force to the roll diameter following lever to maintain the contact state of the roller with respect to the roll.

In addition, in each of the above-mentioned embodiments, it is assumed that the amount of rotation of the winding diameter following rod relative to the increase in the unit winding diameter of the cloth 1 is fixed, and the position of the support shaft 45 and the rollers are set so as to satisfy this premise. 46 is the abutting position relative to the roll cloth 1 . However, in the present invention, the arrangement of the winding diameter following lever is not limited to satisfying such a premise, and the rotation amount of the winding diameter following lever per unit winding diameter increase may not be fixed. The details are as follows.

For example, it may be configured such that the winding diameter increases per unit winding diameter depending on the arrangement of the winding diameter following rod (the position of the support shaft supporting the winding diameter following rod and the setting of the contact position of the roller with respect to the cloth). The amount of rotation of the following rod gradually decreases with the increase of the roll diameter. Specifically, as described above, the angle γ (the line segment connecting the axis of the support shaft supporting the winding diameter following rod and the axis of the roller, and the line segment connecting the axis of the cloth winding roller and the axis of the roller are in the winding The angle formed by the opposite sides of the rotation direction of the diameter following lever) is an angle that affects the amount of rotation of the winding diameter following lever relative to the increment of the unit winding diameter. In addition, by setting the position of the support shaft supporting the winding diameter following rod and the contact position of the roller with respect to the winding cloth so that the angle γ in the initial configuration becomes an angle close to 180°, the winding diameter per unit The amount of rotation of the winding diameter following lever when the winding diameter increases becomes gradually smaller as the winding diameter increases. In addition, in this case, a greater present effect can be obtained by synergistic effect with the effect obtained by the structure (link mechanism) of the present invention.

In addition, according to the configuration of the roll diameter following rod, contrary to the above, when the rotation amount of the roll diameter following rod per unit roll diameter increases gradually increases with the increase of the roll diameter, or according to the size of the unit roll diameter increase And from the beginning of winding to the end of winding, when setting the increase of the winding diameter of more than three unit winding diameters, there is also a difference between the winding diameter following the lever after the winding is just started and before the winding is about to end. With respect to the rotation amount of the unit winding diameter increase, the rotation amount of the middle winding diameter following lever relative to the unit winding diameter increase becomes large, etc. However, even in these cases, if the relationship with the effect obtained by the structure (link mechanism) of the present invention is used, the rotation of the rotating rod as a result plays the role of this effect, and the arrangement of the winding diameter following rod may also be configuration as above.

In addition, this invention is not limited to embodiment demonstrated above, Unless it deviates from the summary of this invention, various changes are possible.

Claims (3)

1. a cloth winding tension regulator for loom, possesses: can be supported in the coil diameter of carrying out rotating on loom frame and according to the change of the coil diameter of the fabric be wound on cloth beam rotationally via the first back shaft and follow bar; And the batching torque adjustment arrangement of batching torque is adjusted according to the amount of spin that above-mentioned coil diameter follows bar, the feature of the cloth winding tension regulator of above-mentioned loom is,

Possesses linkage, this linkage is configured to, comprise above-mentioned coil diameter as linkage component follow bar and comprise dwang, above-mentioned dwang can be supported in rotationally on above-mentioned loom frame via the second back shaft and to link with above-mentioned batching torque adjustment arrangement, above-mentioned coil diameter follows bar and above-mentioned dwang directly links, and linking part can follow the bearing of trend displacement of the side's linkage component in bar and above-mentioned dwang to above-mentioned coil diameter

In aforementioned link mechanism, the initial configuration of above-mentioned each linkage component is set as, the amount of spin of the above-mentioned dwang that the rotation that the above-mentioned coil diameter of increase of the above-mentioned coil diameter of the unit coil diameter recruitment with regulation after just starting relative to winding follows bar obtains, the amount of spin of the above-mentioned dwang that the rotation that the above-mentioned coil diameter of the increase of the above-mentioned coil diameter of the adjoint above-mentioned unit coil diameter recruitment before winding closes to an end follows bar obtains diminishes.

2. the cloth winding tension regulator of loom according to claim 1, is characterized in that,

One side linkage component is that above-mentioned coil diameter follows bar,

The above-mentioned initial configuration of aforementioned link mechanism is set as, follow the slewing area of bar in above-mentioned coil diameter, link and support above-mentioned second back shaft of above-mentioned dwang and the line segment of above-mentioned linking part relative to linking and support above-mentioned coil diameter and follow above-mentioned first back shaft of bar and the line segment of above-mentioned linking part to meet following (a) ~ (c) any one condition at the rotation direction side angulation that above-mentioned coil diameter follows bar:

A () is contained in the angular range of more than 90 ° less than 195 °, and close to 90 ° at the end of comparing winding when winding starts;

B () is contained in the angular range of more than-15 ° less than 90 °, and close to 90 ° at the end of comparing winding when winding starts;

C () is contained in more than 270 ° and the angular range of less than 375 °, and close to 270 ° at the end of comparing winding when winding starts.

3. the cloth winding tension regulator of loom according to claim 1, is characterized in that,

One side linkage component is above-mentioned dwang,

The above-mentioned initial configuration of aforementioned link mechanism is set as, follow the slewing area of bar in above-mentioned coil diameter, link and support above-mentioned second back shaft of above-mentioned dwang and the line segment of above-mentioned linking part relative to linking and support above-mentioned coil diameter and follow above-mentioned first back shaft of bar and the line segment of above-mentioned linking part to meet following (d) ~ (f) any one condition at the rotation direction side angulation that above-mentioned coil diameter follows bar:

D () is contained in the angular range of more than 170 ° less than 270 °, and close to 270 ° when starting than winding at the end of winding;

E () is contained in more than 270 ° and the angular range of less than 370 °, and close to 270 ° when starting than winding at the end of winding;

F () is contained in the angular range of more than-10 ° less than 90 °, and close to 90 ° when starting than winding at the end of winding.