US3670978A

US3670978A - Compensator device

Info

Publication number: US3670978A
Application number: US77621A
Authority: US
Inventors: Myron Dragisich
Original assignee: Warner and Swasey Co
Current assignee: REED-CHATWOOD Inc
Priority date: 1970-10-02
Filing date: 1970-10-02
Publication date: 1972-06-20
Anticipated expiration: 1989-06-20

Abstract

An improved compensator device is provided to maintain a constant sliver path length between a pair of calender rolls and a reciprocable twister assembly of a balling mechanism. The compensator device includes a guide through which the sliver passes and a resilient link which carries the guide and flexes to enable the guide to move during reciprocation of the twister. The resilient link is formed by a plurality of flexible strips which extend between a universal joint mounted in a fixed relationship with the calender rolls and a second universal joint which is connected with the twister.

Description

United States Patent Dragisich COMPENSATOR DEVICE [21] App1.No.: 77,621

[56] References Cited UNlTED STATES PATENTS 8/1960 Rutgers ..242/43 Haug et a] ..242/54.4

[ 51 June 20, 1972 Primary ExaminerGeorge F. Mautz Assistant Examiner-Gregory A. Walters Auomey-Yount and Tarolli ABSTRACT An improved compensator device is provided to maintain a constant sliver path length between a pair of calender rolls and a reciprocable twister assembly of a balling mechanism. The compensator device includes a guide through which the sliver passes and a resilient link which carries the guide and flexes to enable the guide to move during reciprocation of the twister. The resilient link is formed by a plurality of flexible strips which extend between a universal joint mounted in a fixed relationship with the calender rolls and a second universal joint which is connected with the twister.

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M NW Q MW COMPENSATOR DEVICE This invention relates to a compensator device for maintaining a constant sliver path length between calender rolls and a twister assembly of a sliver balling mechanism.

Sliver is commonly fed at a constant rate from calender rolls to a false twister assembly in a balling mechanism. In the balling mechanism the sliver is wound at a constant rate in helical layers on a balling head. To form the helical layers on the balling head, the twister is reciprocated along a path extending parallel to the axis of rotation of the balling head. This reciprocating movement of the twister results in the distance between the calender rolls and twister being increased as the twister is moved away from acentral position and decreased as the twister is moved toward the central position.

The sliver is fed at a constant rate from the calender rolls and is wound at a constant rate by the balling mechanism. Therefore, compensator devices have been provided to maintain the sliver path length between the calender rolls and the twister constant even though the distance between the twister and calender rolls varies. Two known compensator devices are illustrated in U.S. Pat. Nos. 2,979,276 and 3,421,706. These compensator devices include a plurality of links and are relatively complicated in construction and require many parts. In addition these known compensator devices are relatively heavy and tend to hinder reciprocation of the twister.

Accordingly, it is an object of this invention to provide a relatively uncomplicated and light weight compensator device for maintaining a constant sliver path length between a source of the sliver and a twister assembly of a balling head mechanism;

' Another object of this invention is to provide a new and improved compensator assembly for maintaining a constant sliver path length between a sliver feeding means and a reciprocable delivery means which is moved along an elongated balling form so that sliver from the delivery means is wound in layers on the balling form, and wherein the comensator assembly includes flexible strip means for flexing to greater and lesser extents to move a sliver guide in such a manner as to maintain a constant sliver path length between the feed means and the delivery means as the delivery means is reciprocated along the balling form.

Another object of this invention is to provide a new and improved textile processing apparatus which includes a sliver feeding mechanism having an exit through which sliver is fed at a constant rate to a delivery means mounted on a carriage which is reciprocated in opposite directions from a central position as sliver is wound at a constant rate on a rotatable balling form, the distance between the delivery means and the sliver exit being shortest when the carriage is in the central position and variably greater as the carriage reciprocates from the central position, and wherein a resilient link having a curvature which constantly varies carries a guide through which the sliver passes and enables the guide to move in such a manner as to maintain a constant sliver path length between the sliver exit and the delivery means as the delivery means is reciprocated from the central position.

These and other objects and features of the present invention will become more apparent upon a consideration of the following description taken in connection with the accompanying drawings wherein:

FIG. 1 is a schematic illustration depicting the relationship between a pair of calender rolls, a balling mechanism for winding sliver from the calender rolls in a ball, and a compensator device for maintaining a constant sliver path length between the calender rolls and a delivery assemblyin the form of a twister of the balling mechanism as the delivery assembly is reciprocated;

FIG. 2 is an enlarged schematic illustration taken generally along the line 2-2 of FIG. I, further depicting the operation of the compensator device;

FIG. 3 is an enlarged fragmentary sectional view of a portion of a flexible link forming a part of the compensator device; and

FIG. 4 is an enlarged fragmentary illustration of a universal joint of the compensator device.

Textile processing apparatus 10 constructed in accordance with the present invention includes a pair of calender rolls I2 and 14 which pull sliver 16 from a gill box (not shown). The sliver passes from the calender rolls 12 and 14 through a guide 20 of a compensator device 22 to a delivery assembly or twister 26 in a balling mechanism 28. The sliver 16 is fed at a constant rate from the calender rolls l2 and 14 to the balling mechanism 28 where it is wound, at the same rate, in helical layers on a balling head 30.

The balling head 30 includes an elongated cylindrical balling form 32 which is mounted on a rotatable balling shaft 34. A drive cylinder 38 engages an outer layer 42 of sliver on the balling head 28 and is rotated at a constant rate in the direction of the arrow 44 by a drive shaft 46 to thereby effect rotation of a ball 48 of sliver on the balling head 30 at a constant rate. As the sliver is wound on the balling head 30, the shaft 34 is pivoted away from the drive cylinder 38 in a counterclockvvise direction (as viewed in FIG. 1) by the accumulation of sliver on the balling head 30. It should be noted that the rate at which the sliver is wound on the balling head 30 remains constant as the diameter of the ball 48 of sliver increases since the ball of sliver is driven at a constant peripheral speed by the drive cylinder 38. The rate at which the sliver is wound on the balling head 30 is equal to the rate at which the sliver is fed from the calender rolls l2 and 14.

In accordance with well known operating procedures, the delivery assembly 26 is mounted on a carriage 50 and is reciprocated along a support shaft 52 by a drive mechanism 54 so that the sliver 16 is wound in helical layers on the elongated cylindrical balling form 32 as the balling form is rotated by the drive cylinder 38. As the delivery mechanism or twister 26 is reciprocated, a stationary rack 56 imparts rotational movement to a pinion or ring gear 58 on a twister tube 60 through which the sliver passes. Rotation of the twister tube 60 imparts a twist to the sliver immediately before it is wound on the balling head 30. Since reciprocation of the twister tube 60 will result in the twister tube being rotated in opposite directions by the rack gear 56, the twists imparted to the sliver are false twists, that is the twists are in opposite directions and will disappear upon an unwinding of the sliver from the balling form 32. Although many different types of delivery assemblies could be used, the delivery assembly 26 is advantageously constructed as shown in copending U. S. Pat. application Ser. No. 71,974 filed on Sept. I4, 1970 by M. Dragisich.

The drive mechanism 54 includes a drive arm 64 having a slot 66 which engages a follower 70 on the carriage 50. Reciprocation or oscillation of the drive arm 64 moves the carriage along the shaft 52 which extends parallel to the shaft 20 of the balling head 30. The general construction and mode of operation of the balling mechanism 28 and its relationship to the calender rolls l2 and I4 is similar to that described in U.S. Pat. No. 3,042,330 to Haug et al. and, to avoid prolixity of description, will not be further described herein.

When the delivery assembly 26 is reciprocated along the shaft 52 by operation of the drive mechanism 54, the delivery assembly is moved in opposite directions from a central position which is directly beneath and closest to a sliver exit from the calender rolls l2 and I4. As the delivery assembly 26 moves to either side of the central position, the distance between the delivery assembly and the sliver exit from the calender rolls l2 and 14 increases. Thus, when the delivery assembly 26 is in the central position, the carriage 50 (see Fig. 2) is located in a position directly beneath the sliver exit from the calender rolls l2 and 14. At this time the straight line distance between the sliver exit from calender rolls I2 and 14 and the delivery assembly 26 is a minimum.

When the carriage 50 is moved from the central position the distance between the delivery assembly 26 and sliver exit from the calender rolls l2 and 14 increases. Thus, when the carriage 50 is moved toward the right from the central position (shown in solid lines in Fig. 2) to the position shown in dashed lines in FIG. 2, the distance between the sliver exit from the calender rolls I2 and I4 to the delivery assembly 26 is somewhat greater than when the carriage 50 lllltl delivery as sembly are in the central position. When the carriage 50 is moved to the left of the central position, the distance between delivery assembly 26 and sliver exit from the

calender rolls

12 and 14 increases in a similar manner.

The sliver comes out of the sliver exit from the

calender rolls

12 and 14 at a constant rate and is drawn through the twister tube 60 to the balling head 30 at the same rate. Therefore if the sliver is placed under proper tension at the shortest distance between the delivery assembly 26 and the sliver exit from the

calender rolls

12 and 14, that is when the delivery assembly 26 is in a central position, then as the distance increases the sliver tension will increase and could result in a slight but definite and undesirable drafting of the sliver. Conversely, if the sliver tension is properly adjusted for the larger distance between the exit from the calender rolls 12 and 14 and the delivery assembly 26 at the opposite ends of the reciprocating stroke of the delivery assembly, there will be slack in the sliver which will interfere with proper forming of the ball 48 on the balling head 30 when the delivery assembly 26 is in the central position. The problem of maintaining proper tension in the sliver 16 as it passes from the calender rolls l2 and 14 to the balling head 30 is accentuated by increased angularity produced by longer balling forms 32 with the resulting longer traverse distances and by bringing the

calender rolls

12 and 14 closer to the balling mechanism to make the textile processing apparatus smaller and more compact.

In the past, the problem of maintaining the proper tension in the sliver 16 with changes in the distance between the sliver exit from the calender rolls l2 and 14 and the delivery assembly 26 has been solved by providing compensator devices which maintain the sliver path length between theexit from the

calender rolls

12 and 14 and the delivery assembly 26 a constant as the delivery assembly is reciprocated. These known compensator devices have been somewhat unsatisfactory in that-they are relatively complicated in their construction and include a number of pivotally interconnected links and other components which are relatively expensive to manufacture'and difficult to maintain. In addition, these complicated known compensator devices are relatively heavy and have a relatively large inertia which must be overcome to reciprocate the delivery mechanism 26 at high speeds along the shaft 52. The improved compensator device. 22 con--.

structed in accordance with the present invention is relatively uncomplicated in construction and is relatively light in weight. The compensator device 22 includes a resilient link 80 which carries guide and flexes to enable the guide 20 to move in such a manner as to maintain the sliver path length between the exit from the calender rolls l2 and 14 and the delivery assembly 26 constant as the delivery assembly 26 is reciprocated along the shaft 52. When the delivery assembly 26 is in the central position, the resilient link 80 will be deflected so that it has a relatively small radius of curvature, as shown in solid lines in FIG. 1. One end of the flexible link 80 is mounted in a fixed relationship with the sliver exit from the calender rolls l2 and 14 while the other end of the link 80 is connected with the delivery assembly 26.

When the delivery assembly 26 is moved along the shaft 5 from the central position, the straight line distance between the two ends of the flexible link 80 increases. This increase in the distance between the ends of the flexible link 80 decreases the deflection of the link and increases its radius of curvature. Thus, when the carriage 50 moves from the central position shown in solid lines in FIG. 2 to the position shown in dashed lines shown in FIG. 2, the deflection of the link 80 decreases. As the link 80 tends to straighten, the radius of curvature of the link increases from that shown in solid lines in FIG. 1 to the radius of curvature shown in dashed lines in FIG. 1. It should be noted that the radius of curvature of the flexible link 80 increases in direct proportion to an increase in the distance between the delivery assembly 26 and the sliver exit from the calender rolls l2 and 14 and decreases in direct proportion to reductions in this distance.

The guide 20 is mounted on the flexible link midway between its ends. Therefore changing the radius of curvature of the link 80 moves the guide 20 relative to the sliver exit from the calender rolls l2 and 14. When the delivery assembly 26 is in the central position and the straight line distance between the delivery assembly and the sliver exit from the calender rolls 12 and 14 is relatively small, the flexible link 80 is deflected to a relatively large extent. The relatively large deflection of the link 80 results in the guide 20 being located a relatively large distance away from a direct path between the sliver exit from the calender rolls 12 and 14 and the delivery assembly 26. Therefore, the path which the sliver 16 follows in moving from the calender rolls 12 and 14 through the guide 20 to the delivery assembly 26 is longer than the relatively short straight line distance between the delivery assembly and calender rolls.

When the delivery assembly 26 is moved away from the central position, the straight line distance between it and the sliver exit from the calender rolls 12 and 14 increases and the deflection of the resilient link 80 decreases. Decreasing the deflection of the link 80 increases its radius of curvature so that the guide 20 moves toward the position shown in dashed lines in FIG. 1. As the radius of curvature of the flexible link 80 increases, the straight line distance between the delivery assembly 26 and sliver exit from the calender rolls 12 and 14 more closely approaches the length of the path along which the sliver must travel in moving from the sliver exit from the calender rolls, through the guide 20, to the delivery assembly 26. I

In passing from the sliver exit of the calender rolls 12 and 14 to the delivery assembly 26, the sliver travels through a substantially constant distance -even though the straight line distance between the sliver exit and delivery assembly varies. This is because the guide 20 varies the path along which the sliver travels as the straight line distance between the sliver exit from the calender rolls l2 and 14 and the delivery assembly 26 changes. Thus, even though the straight line distance between the delivery assembly 26 and sliver exit from the calender rolls l2 and 14 varies as the delivery assembly is reciprocated along the shaft 52, the 'sliver path length between the sliver exit and the delivery assembly is maintained constant by varyingthe extent to which the resilient link 80 is deflected. r

The resilient link 80 must be deflected in a direction transverse to the longitudinal axis of the shaft 52 and path of reciprocation of the delivery assembly 26 to move the guide 20 from the position shown in solid lines inFlG. 1 to the position shown in dashed lines shown in FIG. 1 as the delivery'as sembly is reciprocated along the shaft. However, the resilient link 80 need not be deflected in a direction extending parallel to the shaft as the delivery mechanism 26 is reciprocated. To prevent unnecessary flexing of the resilient link 80 during movement of the delivery assembly 26, the opposite ends of the resilient link 80 are connected to the carriage 50 and a frame 84 of the textile apparatus 10 by a pair of universal

joint assemblies

86 and 88.

The universal

joint assemblies

86 and 88 cooperate with each other and the resilient link 80 to enable the resilient link tor'nove either direction from the central position (shown in solid lines in FIG. 2), without flexing in a direction extending parallel to the longitudinal axis of the shaft 52. Thus, when the carriage 50 is moved to the right (as viewed in FIG. 2) from the central position, the

universal joints

86 and 88 enable the link 80 to move without flexing in a direction parallel to the longitudinal axis of the shaft 52. The universal joint 86-includes a base 90 (FIG. 4) having a pair of upstanding arms or posts 92 and 94 (see FIG. 1). A connector member or link 96 is pivotally connected with the

posts

92 and 94 for pivotal movement relative to the base 90. A bifurcated connector section 100 is fixedly connected to the link 80 and includes a pair of arms I04 and 106 (FIG. 4) which are pivotally connected with the member 96. The end of the flexible link 80 is received in a slot 80b in the member 100 and is secured thereto by a suitable threaded fastener 80a The axis of the pivot connection between the

arms

92 and 94 and the member 96 is perpendicular to the axis of the pivot connection between the

arms

104 and 106 of the connector section 100. Therefore, the connector section 100 and the end portion of the link 80 to which it is connected are freely pivotal in all directions relative to the carriage 50.

The universal joint 88 is constructed in the same manner as the universal joint 86 so that the opposite end of the resilient link 80 is freely movable when the carriage 50 is reciprocated along the shaft 52. Since the construction and mode of operation of the

universal joints

86 and 88 is well known they will not be further described herein. However, it should be noted that the

universal joints

86 and 88 prevent the resilient link 80 from being deflected in a direction parallel to the path of movement of the carriage 50 (FIG. 2) while enabling the link 80 to be freely deflected in a direction extending transverse to the path of movement of the carriage 50, that is between the positions shown in solid and dashed lines in FIG. 1.

The flexible link 80, in the specific embodiment of the present invention illustrated herein, is formed by a plurality of

resilient strips

110, 112 and 114 (see FIG. 3) made of suitable spring steel and having face surfaces disposed in abutting engagement. By constructing the flexible link 80 of a plurality of resilient strips, the failure of any one of the strips during operation of the textile processing apparatus will not result in a complete failure or breaking of the link 80. In addition, the provision of the

flexible strips

110, 112 and 114 increases the service life of the flexible link 80 by decreasing wear on the link as it is flexed between the positions shown in solid and dashed lines in FIG. 1.

The guide is supported at the center of the link 80 on a mounting bracket 120. The mounting bracket 120 is connected directly to the link 80 and includes a pair of upstanding arms 122 and 124 (FIG. 2) which engage opposite sides of an annular groove 126 formed in the guide ring 20. The

arms

122 and 124 securely grip the guide ring 20 to mount it on the flexible link 80.

In view of the foregoing description it can be seen that compensator device 22 maintains a constant sliver path length between the sliver exit from the calender rolls l2 and 14 and the delivery assembly 26 in the balling mechanism 28. The compensator device 22 includes a single resilient link 80 which is flexed to greater and lesser extents when the delivery assembly 20 is reciprocated relative to the balling head 30. As the resilient link 80 is flexed, its radius of curvature varies to move the guide 20 and maintain tension in the sliver 16. The flexible link 80 is relatively simple in construction and dependable in its operation. In addition, it is relatively light in weight so that the inertia of the compensator device 22 is relatively low to enable the delivery assembly 26 to be reciprocated at high speeds along the shaft 52.

Having described a specific preferred embodiment of the invention, the following is claimed:

1. An assembly for use in a balling apparatus wherein sliver froma feeding means passes through a guide to a delivery means which is mounted on a reciprocable carriage and is moved along an elongated balling form so that the straight line distance between said feeding means and said delivery means varies as sliver from the delivery means is wound in layers on the balling form as it is rotated, said assembly comprising flexible link means having a constant overall length for carrying said guide and for flexing in a direction transverse to the direction of reciprocation of the delivery means as the delivery means is reciprocated along the balling forms, first connection means disposed in a fixed position adjacent to the feed means for operatively connecting one end portion of said flexible link means with the feed means, and second connection means for operatively connecting a second end portion of said flexible link means with the delivery means for movement therewith so that said flexible link means is flexed by reciprocating movement of the link means is flexed by reciprocating movement of the carriage along the balling form as the straight line distance between said feeding means and said delivery means varies, and the guide is moved transversely to the direction of reciprocation of the delivery means to maintain a constant sliver path length between the feed means and delivery means.

2. An assembly as set forth in claim 1 wherein said first and second connection means each include universal joint means for enabling said flexible link means to flex in the direction transverse to the direction of reciprocating movement of the delivery means and for preventing said flexible link means from being flexed in the direction of reciprocating movement of the carriage and delivery means.

3. An assembly as set forth in claim 1 wherein said flexible link means includes a plurality of flexible strips which are disposed with flat face surfaces in an abutting relationship.

4. An assembly as set forth in claim 1 further including connector means secured to said flexible link means for supporting the guide.

5. Textile processing apparatus comprising a sliver feeding mechanism having a sliver exit means through which sliver is fed at a constant rate, a balling mechanism operatively associated with the sliver feeding mechanism and including an elongated rotatable balling form upon which sliver received from said sliver exit means is wound at a constant rate, a carriage supported for reciprocation longitudinally of said balling form and in opposite directions from a central position to either one of two end positions, delivery means mounted on said carriage for movement therewith and through which the sliver passes immediately before it is wound on said balling form, the distance between said delivery means and said sliver exit means being shortest when said carriage is in the central position and variably greater as said carriage reciprocates from the central position toward one of the end positions, and compensating means operatively connected with said sliver exit means and said delivery means for maintaining a constant sliver path length between said sliver exit means and said delivery means as said delivery means reciprocates with said carriage from the central position toward one of the end positions and the distance between said delivery means and said sliver exit means varies, said compensating means including a guide through which the sliver passes in moving from said sliver exit means to said delivery means and a resilient link means disposed in a fixed position adjacent to the feed mechanism for connecting one end of said link to said feed mechanism, and means connecting the other end of said link with the delivery means, whereby said link will have a radius of curvature which constantly varies from a relatively small radius of curvature when said carriage is in the central position toward a relatively large radius of curvature as the carriage is moved from the central position toward one of the end positions, and means for operatively connecting said guide to said resilient link to effect movement of said guide as the radius of curvature of said link changes to maintain a constant sliver path length between said sliver exit means and said delivery means as said carriage and said delivery means are reciprocated from the central position.

6. Textile processing apparatus as set forth in claim 5 wherein said resilient link includes a strip of flexible material which is deflected so as to have a relatively small radius of curvature when said carriage is in the central position and a relatively large radius of curvature when said carriage has been moved through an outward stroke from the central position.

7. Textile processing apparatus as set forth in claim 6 wherein said compensating means further includes a first universal joint at an end of said flexible link which is operatively connected with said sliver exit means and a second universal joint at an end of said flexible link which is connected with said sliver exit means, said first and second universal joints cooperating with each other and said flexible link to prevent deflection of said flexible link in a direction parallel to the direction of reciprocation of said carriage.

8. Textile processing apparatus as set forth in claim 5 wherein said connecting means includes means for mounting said guide on said flexible link at a location which is midway between opposite ends of said flexible link.

Claims

1. An assembly for use in a balling apparatus wherein sliver from a feeding means passes through a guide to a delivery means which is mounted on a reciprocable carriage and is moved along an elongated balling form so that the straight line distance between said feeding means and said delivery means varies as sliver from the delivery means is wound in layers on the balling form as it is rotated, said assembly comprising flexible link means having a constant overall length for carrying said guide and for flexing in a direction transverse to the direction of reciprocation of the delivery means as the delivery means is reciprocated along the balling forms, first connection means disposed in a fixed position adjacent to the feed means for operatively connecting one end portion of said flexible link means with the feed means, and second connection means for operatively connecting a second end portion of said flexible link means with the delivery means for movement therewith so that said flexible link means is flexed by reciprocating movement of the link means is flexed by reciprocating movement of the carriage along the balling form as the straight line distance between said feeding means and said delivery means varies, and the guide is moved transversely to the direction of reciprocation of the delivery means to maintain a constant sliver path length between the feed means and delivery means.