US3483899A - Batten lifting mechanism for loom - Google Patents

Description

Dec. 16, 1969 P. A. WAGNER 3,483,399

BATTEN LIFTING MECHANISM FOR LOOM Filed May 7, 1968 5 Sheets-Sheet l 73 .QI." A i5 J --13 23 1 92 II l8 24 F.

I 1g. 2 9i m 7 a a A,

INVENTOR.

PAUL A. WAGNER WWW ATTORNEYS.

Dec. 16, 1969 P. A. WAGNER 3,433,899

BATTEN LIFTING MECHANISM FOR LOOM Filed May 7, 1968 5 Sheets-Sheet 2 L T 1 {a d 3 JE IQ INVENTOR.

PAUL. A. WAGNER ATTORNEYS.

Dec. 16, 11969 P. A. WAGNER 3,483,899

BATTEN LIFTING MECHANISM FOR LOOM Filed May '7, 1968 5 Sheets$heet 3 INVENTOR.

PAUL A WAGNER 01K MK ATTORNEYS.

Dec. 16, 1969 P. A. WAGNER 3,483,899

BATTEN LIFTING MECHANISM FOR LOOM Filed May 7, 1968 5 Sheets-Sheet 4 INVENTOR.

PAUL A. WAGNER ATTOR NEYS.

Dec. 16, 1969 P. A. WAGNER BATTEN LIFTING MECHANISM FOR LOOM 5 Sheets-Sheet 5 Filed May 7, 1968 INVENTOR. PAUL A. WAGNER lw 7 AYTORNEYS United States Patent US. Cl. 139171 26 Claims ABSTRACT OF THE DISCLOSURE The lifting mechanism of a loom is modified within the existing framework of the loom, to provide a clutchactuated four-position lifter in lieu of the standard gearoperated lifter. The modification includes the substitution of clutches and actuators, as well as cams, for the standard gears and mechanical linkages disposed on the frame of the loom. The power input shaft, the input control means for controlling the position of the batten, and the batten lifting arm linkage immediately connected to the batten remain the same as they were in the original machine. The new mechanism will be described in greater detail in the specification.

Background of the invention This invention relates to looms and mechanisms for positioning the battens in said looms, and more particularly to looms of the type which require their battens to be moved intermittently to four different positions.

This type of loom is very old in the art, and the mechanism for lifting the batten has remained substantially unchanged for years. See for example United States Patents 2,490,589 and 3,148,709 which describe this type of loom and disclosed control mechanisms for this type of loom.

The gear arrangements known in the prior art for lifting the batten suffer from the following defects among others: (1) they are noisy; (2) they are inefiicient; (3) they are limited in speed; and (4) their size and inertial forces at times result in breakage and costly downtime.

Summary of the invention My invention comprises a new and novel lifting mechanism which derives its power from an input shaft, and transmits said power intermittently in response to the existing control inputs to such a loom, through a controlled clutch means to eccentrically operated arms and thence to pivoted linkages connected to the batten lifter in the loom.

An object of this invention is to provide a new and novel clutch and cam system for use in an old apparatus,

to achieve higher performance at greater efiiciency with Brief description of the drawings FIG. 1 is a perspective view of a portion of a loom showing the overall arrangement and positioning of my invention;

FIG. 2 is a perspective view of a portion of the machinery shown in FIG. 1, taken from the reverse side in FIG. 1;

FIG. 3 is a plan view of a portion of the apparatus shown in FIG. 1;

FIG. 4 is a view of a portion of the apparatus shown in FIG. 3, taken as indicated by the lines and arrows IVIV;

FIG. 5 is a view of a portion of the apparatus shown in FIG. 3, taken as indicated by the lines and arrows VV;

FIG. 6 is a view of a portion of the apparatus shown in FIG. 3, taken as indicated by the lines and arrows VI-VI;

FIG. 7 is a view taken as indicated by the lines and arrows VIIVII in FIG. 6; and

FIGS. 8a, 8b, 8c, and 8d are simplified elevational views of a portion of the linkage in this apparatus showing the various parts in alternate positions.

Description of the preferred embodiments Referring to FIGS. 1 and 2, a portion of the frame of a typical loom, which for purposes of describing the preferred embodiment of my invention is a narrow label loom, is shown. A main power source (not shown; any source as is known in the art being acceptable for purposes of this disclosure) drives a shaft 10 and a first set of gears designated 11, which drive a shaft 12 mounted in the frame 13. The shaft 12 transmits power through a second set of gears designated 14, to the power take-01f shaft 15 of the batten lifting mechanism designated 18; said mechanism being partially concealed within a portion of the frame 13.

In response to controlled input signals, the batten lift ing mechanism 18 positions the batten lifter lever arm 16 by pivoting it about the trunnion 17. Pivotally mounted about the trunnion 17 is batten lifter positioning arm 1611 which is connected at its pivotal mount to lever arm 16. Pivotal movement of the arm 16 about the trunnion 17 causes movement of the arm 16a about the trunnion 17. The arm 16a is pivotally engaged with the rod 90 which is slidably engaged at the reed beam 91 and fixedly connected at its other end to the batten 92. The batten can be moved to a plurality of positions, preferably four in a narrow label loom by the batten lifting mechanism 18 as will be more fully described.

Referring more particularly to FIGS. 3 through 7, I shall now describe the details of the lifting mechanism.

The power input shaft 15, FIG. 3 is journaled in bearings 20 in the frame 13, and is designed to be continuously rotating while the machine is in operation. This shaft supplies the power to drive a pair of eccentrics 22a and 22b, FIGS. 4 and 5, which in turn drive cranks 23a and 23b. It is in response to the motion of these cranks that the levers 24 and 25 and the connecting rod 26 position the batten lifter lever arm 16. Each eccentric is intermittently engaged by the shaft to be driven thereby independently by a separate spring clutch (which will be described more fully below). The clutches are controlled by a control mechanism designated 30.

For purposes of simplicity, I shall describe only one of the clutch mechanisms, it being understood that the other mechanism functions in a similar fashion, but that certain of the parts (as shown in the drawings) may assume a reverse position or a mirror image because of their disposition on the shaft 15. Referring then to FIG. 5, the clutch comprises a shaft adaptor 32 which is fixed to the shaft for rotation therewith by any suitable means, as for instance by key 33 and set screw 33a. A hearing 34 is disposed about a portion of the shaft adaptor, and is retained thereon by a retaining ring 35. Connected to the bearing 34 is a mounting hub 36 which in turn is fixedly 3 connected to eccentric 22b as by means of key 37. By this arrangement the shaft 15 and the adaptor 32 may be continuously rotated, even though the eccentric 22b and the mounting hub 36 are held in a fixed position.

In order to cause the mounting hub and the eccentric to rotate with the shaft and the shaft adaptor, a spring 38 is disposed about a portion of the mounting hub and shaft adaptor. The spring 38, as shown in its de-energized position, is spaced from the drum 32b of the shaft adaptor 32, said drum preferably being made by pressfitting a sleeve on the shoulder 32c of the adaptor 32. At one end of the spring 38, a tab 38a is disposed in a hole 39 in the drum 36a of the mounting hub 36 so that the spring normally follows the motion of the mounting hub 36.

Disposed about the spring in spaced relation thereto, is a release sleeve 40 which bears at one end on shoulder 32a of shaft adaptor 32, and at the other end on shoulder 36b of mounting hub 36. The release sleeve has a slot 41 therein in which is disposed a tab 38b which is the other end of the spring 38.

When shaft 15 is rotating as shown by the arrow FIG. and release sleeve 40 is restrained by actuator 50 (as will be more fully described), the mounting hub 36 and the spring 38 are stationary. In positioning the parts of this spring-actuated clutch on the shaft 15, it is necessary to adjust the parts so that the relationship just described will exist. To perform this adjustment I have provided a C-clamp adjusting ring 43 which is disposed about the release sleeve 40. As can be seen from FIG. 3, the adjusting ring 43 is slit, and a screw 43:: is provided to draw the ring tight on the release sleeve 40 when the ring has been rotated to the desired position. Referring again to FIG. 5, note that the ring has a slot 44 therein for reception of the tab 38b of the spring 38.

In its normal unfiexed position, the spring 38 has an inner diameter which is less than the diameter of the drums 32b and 36a, so that normally the spring would be in an interference fit with these drums, that is it would grip the drums. Therefore, in order to position the spring 38 so that there is a space between the spring 38 and the drum 32b, it is necessary to unwind the spring slightly, thereby expanding it radially. This can be done by turning the adjusting ring 43, and then clamping the adjusting ring 43 by means of the screw 43a in the desired position. Thus, the spring is normally held in such a position that it is disengaged from the shaft adaptor 32.

To maintain the spring 38 in its expanded condition, which is known as a de-energized condition, the release sleeve 40 is provided with a raised portion or detent 40a.

The end of an actuator 50 normally interferes with the detent 40a and thereby prevents rotation of the sleeve 40.

When the actuator 50 is moved to a position where it no longer interferes with the detent 4011, the clutch is energized, that is the spring 38 contracts in the radial direction and grips the hub 32b of the shaft adaptor 32. The driving torque from the shaft is immediately transmitted from the driving member 32 through the spring 38 to the driven members, that is the mounting hub 36 and those parts connected to it. This gripping action of the spring 38 is positive and provides a powerful snubbing action which virtually eliminates slippage. Thus, the driven member is accelerated to the speed of the driving member.

Inertial forces may cause the driven members to travel at a speed in excess of the shaft speed. To insure uniform, synchronous speed of both driven and driving members an anti-overrun spring 58 FIG. 5 is provided. This spring is wound so that in its normal condition its outer diameter is greater than the inner diameters of either drum 36a or 32b. Accordingly, to position it within the drums, it is necessary to wind the spring tighter, thereby contracting it radially. Once in position, the spring 58 exerts a force against the inner diameters of both drums; said inner diameters being preferably equal. Referring to FIG. 5, spring 58 is wound in the direction of the rotation of the shaft 15 as shown by the arrow when moving from left to right. Therefore, as long as the driving members 32, 3212 are rotating faster than the driven members 36, 36a the frictional forces will tend to compress the spring further, thereby permitting relatively free rotation. However, if the driven members attempt to exceed the speed of the driving members, the forces will tend to unwind the spring and expand it radially, causing it to grip both drums and maintain them at uniform speed.

The application of torque to the driven members will continue until the actuator 50 is again brought into interfering relation with a detent on the release sleeve 40, at which time the clutch will disconnect the mounting hub 36 from the power source. In the apparatus shown in FIG. 4, the actuator 50 would interfere with the detent b after a one-half revolution of the release sleeve 40. When this occurs, the spring 38 is again expanded so that it no longer grips the drum 32b.

The speed and inertia of the driven members causes them to remain in motion until friction, spring moment. and material elongations bring them to rest. I have provided a pair of lugs 45, extending from the release sleeve 40' as is best illustrated in FIGS. 6 and 7 which show the other clutch mechanism in operative relation to the eccentric 22a and crank 23a. These lugs 45 are disposed in slots 46 in eccentric 22a and exert a positive force to counteract the momentum of the driven parts.

In one embodiment of my invention, the reverse momentum of the crank and eccentric which occurs when these parts are suddenly stopped, is counteracted by a pawl 47 (shown best in FIGS. 3, 4, and 5) which is pivotally connected to the actuator 50 as by shoulder screw 48. The pawl 47 is maintained in its normal position by means of screw 49 and spring 51, which is disposed in compression about the screw 49 between one end of the pawl 47 and the actuator 50, as shown in FIG. 4. The hooked end of the pawl is normally engaged about the pin 52 when the crank is in the stationary position. Two pins 52 (FIG. 5 l are fixedly mounted to the ring 53 which in turn is fixedly attached to the eccentric 22b (FIG. 4) as by means of screws 54. The pins 52 are disposed at 180 from one another on the ring 53.

In operation, when the actuator 50 is moved vertically upward and pivots about the pin 55 (FIG. 4) attached to the frame 13, it raises the pawl 47, as well as the end of the actuator, so that the clutch mechanism is energized and rotates thereby rotating the eccentric. As the eccentric continues to rotate, the other pin 52 will contact the slanting surface 47a of the end of the pawl 47 and cam the pawl upwardly against the action of the spring 51. As the end of the actuator 50 engages the detent 4017 on the release sleeve 40, the pawl 47 engages the pin 52 and prevents the parts from sliding backward, due to reverse momentum.

In pattern-controlled narrow labeled looms as heretofore constructed, it is customary to transmit indications from the pattern chain through a mechanical or electromechanical apparatus to one end of the loom, where the control mechanism 30, FIG. 1, controls the batten lifter and determines the position of the batten. Various attempts have been made in the art to automate or otherwise improve the input control signals to the control mechanism, as for example shown in the patents heretofore mentioned. However, for purposes of this invention, any suitable control input means, as is known in the art, will suffice. It is preferable however, to utilize a control input which intermittently moves the batten to one or another of four positions. For purposes of simplicity, I shall describe in detail, only that portion of the control mechanism 30 which is attendant to the clutch mechanism having the release sleeve 40, it being understood that the other'portion of the control mechanism attendant to the other clutch and release sleeve, as is illustrated in the drawings, functions in a similar fashion, but that certain of the parts may assume a reverse position or mirror image because of their disposition in the apparatus.

The control means (not shown) whether manual or automated such as any standard Jacquard, feeds its input signals to the control mechanism 30 of the batten lifter by means of applying tension to the rods 60a and 60b, FIGS. 1, 2, 3, 4, and 8, and moving the rods vertically upward or releasing the rods from their raised position so that they drop vertically downward. A typical rod arrangement is shown in FIG. 4 wherein the rod 60:: passes through a clearance hole 61 in the actuator 50. Disposed about the rod is a coiled spring 62, which in the relaxed position shown is fully extended and does not engage the actuator 50. This is the position where there is no positive input signal to the actuator from the control means (not shown). The spring is held in position on the rod by any suitable means such as the nut and washer 63, and may conveniently have a bearing plate such as the washer 64 resting on top of the spring to engage the actuator, and a weight 59 of several pounds attached to the bottom end to aid in returning the rod once it is released.

Upon an appropriate signal from the control means, tension is applied to the rod 60a in a direction of the arrow, and the rod is lifted so that the bearing plate 64 comes into contact with the bottom of the actuator 50. As the rod 60a is raised even further, the spring 62 is compressed, thereby exerting a force against the actuator 50. However, the actuator is prevented from being raised by the cam 65a and the follower 66a.

The follower is mounted for rotation to the actuator by means of the shoulder screw 67. The cam 65:: is fixedly mounted as by means of a key 68a and set screw 68b to a shaft 68 for rotation therewith; the shaft being journaled in bearings 69 in the frame 13. The cam is positively driven in synchronous rotational speed with the power input shaft 15, preferably by means of identical timing pulleys 72a and 72b connected to the shafts and 68 respectively and timing belt 73 connecting the pulleys.

As shown on FIG. 3, there are two cams 65a and 65b in the control mechanism 30. The cams are preferably identical, as is true of most of the parts in this apparatus, so that the parts are interchangeable, thus reducing the cost and inventory of parts. Each cam is essentially circular with the exception of a portion of one quadrant which has an indentation as at 70, FIG. 4.

As the cam 65a rotates in the direction of the arrow (FIG. 4) the actuator 50 is initially held in the position shown where it is in interfering relation with the detent 40a on the release sleeve 40. If, as has been previously described, a positive input signal to the rod 60a has caused the spring 62 to exert a force against the actuator 50, then as the cam continues to rotate, the follower 66:: will follow the surface of the cam into the indented portion 70, thereby pivoting the actuator 50 about the pin 55, and causing the end of the actuator 50 to move out of its interfering relation with the detent 400 on the release sleeve 40. As previously described, once the actuator is moved out of interfering relationship with the detent, there is nothing to prevent the spring 38 of the clutch from grabbing both the shaft adaptor and the mounting hub and transmitting a torque from the rotating shaft 15 to the eccentric 22b.

As the eccentric 22b rotates with the mounting hub, it turns along it outer, circumferential surface within the crank 23b where it is keyed by the key 27b FIG. 5. Since the eccentric is rotating about a fixed point which is offcenter, it will be understood that the crank 23b will be caused to move upwardly, thereby changing the position of the lever FIG. 4 as will be more fully explained hereinafter. As the release sleeve 40 continues to rotate, so does the cam 65a The outer peripheral surface of the release sleeve 40, which rises along a curve to form the detent 40a, is so designed that as the cam follower 66a follows the surface of the cam indentation 70 until it reaches the maximum radial surface of the cam 65a, the actuator 50 will again approach the surface of the release sleeve 40, before the sleeve has rotated 180. Thus, the actuator 50 will be in position to engage the detent 4%.

To adjust the lower limit of the vertical position of the actuator 50, one adjusting screw and nut designated 56 FIG. 4 is mounted beneath the actuator 50 on a flange extending from the frame 13 to bear against the lower surface of the actuator. The actuator is preferably positioned so that it just clears the circular portion of the release sleeve 40.

Since the shaft speeds are the same, it is apparent that the cam will have to make one complete revolution for every time the clutch mechanism rotates one-half of a revolution. Thus, it would be impossible for the clutch mechanism and eccentric to rotate continuously. Rather, their motion would have to be intermittent since there are two detents on each release sleeve.

Each crank can be mowed to one of two vertical positions, and at each position it must dwell for the time it takes the cam to rotate another 180 before it can be moved to the other position. The effect of this motion on the position of the batten will now be described with the aid of the motion drawings, FIGS. 8a, 8b, 8c and 8d. The cranks 23a and 23b are connected to the levers, 24 and 25 respectively by means of shoulder screws 28 which provide for pivotal action therebetween. The shorter lever 24 which may be referred to as a pivot lever for convenience in distinguishing it from the longer lever 25, is pivotally mounted to the frame 13 by means of a heavy stud shaft 29. Lever 25 is pivotally connected to lever 24 by means of the stud 21. Lever 25 is pivotally connected at the end thereof to connecting rod 26 by means of the stud 31.

Referring now to the motion diagrams, note that the pivot point at stud 29 is fixed, while the pivot point at stud 21 is floating. Referring to FIG. 8b, the cranks, eccentrics, and clutches are disposed in the position shown throughout the detail, FIGS. 3, 4, 5, 6, and 7, as previously described. At the instant shown, the cam 65a has reached the point where the actuator 50 has been raised out of interfering relation with the detent a by the spring 62 in response to a positive input signal. The catch mechanism is about to be rotated about the shaft 15 in the direction of the arrow which will cause the crank 23b to be raised. Since the crank 23a remains stationary, the pivot lever 24 will likewise be stationary, and the pivot point 21 will remain fixed. Therefore, as the crank 23b rises, it will pivot the crank 25 about the stud 21, so that the end of the crank 25, which is connected to the connecting rod 26, will be moved from the position shown in full lines to the position shown in phantom. The crank 23b will be moved to the limit of its upward vertical travel where it will be stopped by the engagement of the actuator with the detent 40b. This motion is caused by an input signal to the rod a while no input signal has been transmitted to the rod 60b.

Both cranks 23a and 23b would now be at the upper limit of their vertical travel. The connecting rod 26 on the other band would be at the lowest point in its vertical travel, thereby causing the batten lifter lever arm 16 and positioning arm 16a to lift the batten to its highest position where it will remain for at least 180 of travel of the cam a.

If the positive input signal to the rod 60a, which has caused the rod to move vertically upwardly, is no longer applied to the rod 60a, it will drop down to its original position as shown in FIG. 4, and until another input sig nal is transmitted to either rod 60a or 60b, the batten will remain in a fixed position. If, however, the positive input signal transmitted through the rod 60a remains positive, the actuator 50 will be moved out of interference with the detent 40b when the cam 65a once again rotates to a position where the follower 66a rolls into the indentation 70,

and the eccentric 22b would again make one-half of a revolution. The crank 23b would be driven downward, thereby causing the stud 31 to move upwardly to its original position shown in FIG. 8b. This position is the next to the lowest vertical position which the pivot point at stud 31 can assume, and in this position, the batten isin the next to the highest position which it can assume.

Having described the two vertical positions which the crank 23b can assume, I will now describe the two positions which the crank 23a can assume. Accordingly, refer to FIG. 80 wherein once again the cranks are in the position of the machinery previously described with respect to the detailed drawings. At this point, an input signal is given to actuator 50a through rod 60b, and as cam 65b rotates, the follower 66b moves into the indentation 70a, and the actuator 50a is lifted by means of the spring, so that it is no longer in engagement with the detent on the clutch mechanism associated with crank 23a, and the crank is turned 180 by the energized spring clutch, thereby driving the crank to its lowest point of travel in the vertical direction. When this occurs, the pivot lever 24, pivots about the fixed pivot point 29 thereby moving the floating pivot point at stud 21 from its original position to the position shown in phantom. Although the crank 23b does not rotate with the shaft 15, nevertheless, the action of the floating pivot point 21 causes the lever 25 to move from the position shown in full lines to the position shown in phantom, thereby raising the connecting rod 26 from the position shown in full lines to the position shown in phantom. In this position it is at its highest point of vertical travel and, therefore, the batten is at its lowest point of vertical travel.

When the cranks stop moving, the batten dwells for at least 180 of rotation of the cams. If the input signal through rod 60b remained positive so that the spring continued to exert a force against the actuator 50a, then the next time thecam indentations 70a reach the follower 66b, the actuator again would be lifted out of contact with the detent on the clutch mechanism, and the crank 23a would be moved verticallly upward to its highest position, and the parts again would assume the original position shown in FIG. 80.

Referring to FIG. 8a wherein the parts are initially in the position shown in FIG. 8c, I have illustrated the condition wherein a positive input signal is transmitted through both rods (60a and 60b) at the same time so that as the cams rotate together, both Will reach the point at which the actuators will be released preferably at the same time. Crank 23a will be moved vertically downward, and crank 23b will be moved vertically upward. Lever 24 will therefore assume the position shown in phantom wherein it has rotated the floating pivot point at stud 21 about the fixed pivot point 29 to the position shown in phantom. Simultaneously, lever 25 has been rotated by crank 23b about stud 21 so that lever 25 is now in the position shown in phantom. This combination of the movements results in the movement of the pivot point at stud 31 to the position shown in phantom wherein the connecting rod 26 is moved to the next to the highest vertical position of its travel, with the corresponding movement of the batten to the next to the lowest vertical position in its travel. All four positions of the batten mechanism have now been illustrated, and it should be apparent that various combinations or moves in steps from one position to another are possible, depending on the input signals. For example, as shown in FIG. 8, if both of the cranks 23a and 23b are in the lowest vertical position and input signals are provided through rods 60a and 60b at the same time to the actuators 50 and 50a, then both cranks will move to the highest vertical position, and the connecting rod 26 will be shifted from its highest vertical position to its lowest vertical position, shown in phantom. As in the previously described cases, the movement of the connecting rod 26 causes a pivotal movement of the batten arms 16 and 16a about the trunnion 17, shown in'FIG. 1, so that the movement of the batten corresponding to the movement of the connecting rod just described, would be from its lowest position to its highest position. If the positive signal was maintained on both actuators, the cranks, after a dwell period, would be rotated to their lowest position, thereby shifting the connecting rod 26 to its highest position, as shown in full lines.

It should further be apparent that it is not necessary that a positive input signal be transmitted to an actuating arm at the exact instant when the arm is to be lifted. Rather, it is only necessary that a positive input signal be applied at some point in time before the cam has rotated to the position where the follower can move into the indentation and raise the arm.

Likewise, my invention could readily be used on multishuttle broad looms or on looms having various numbers of positions, by the addition of more clutches and the changing of cams, release sleeves, cranks and their related parts.

What is claimed is:

1. In a loom having a power input shaft for driving a mechanism for positioning the batten in said loom, and control means for applying signals to actuate the batten positioning mechanism, the improvement comprising:

(a) a drive shaft mounted for rotation in said loom and connected to said power input shaft;

(b) clutch means positioned about said drive shaft for intermittent engagement and rotation therewith;

(c) eccentric means engaged with said clutch means for movement therewith;

(d) linkage means connecting said eccentric means to said batten for positioning said batten in response to the movement of said eccentric means; and

(e) a control mechanism engagement with said control means and said clutch means for controlling the engagement and rotation of said clutch means with said shaft.

2. The invention in claim 1 wherein said clutch means comprises at least one spring-actuated clutch having a first portion fixedly connected to said drive shaft for rotation therewith and a second portion positioned about said first portion and engaging said eccentric means, first spring means engaging said second portion for gripping said first portion, release means engaging said first spring means for permitting and preventing the gripping of said first portion by said first spring means, said release means engaging said control mechanism to normally prevent said first spring means from gripping said first portion while said drive shaft is rotating, and to permit said first spring means to grip said first portion when said release means is disengaged from said control mechanism.

3. The invention of claim 2 wherein second spring means is positioned about said drive shaft between said drive shaft and a portion of said first and second portions of said clutch in engagement therewith, said second spring means permitting rotation of said first portion independently of said second portion and preventing said second portion from rotating at a faster speed than said first portion.

4. The invention of claim 1 wherein said eccentric means comprises at least one eccentric mounted about said clutch means and fixedly connected thereto for rotation therewith, and a crank mounted about said eccentric for translation in response to rotation of said eccentric.

5. The invention of claim 1 wherein said eccentric means comprises a plurality of eccentrics each having a crank engaged therewith for translation in response to rotation of said eccentric, and said linkage means comprises a first lever pivotally connected at one end to one of said cranks and pivotally connected between its ends to a fixed portion of said apparatus, a second lever pivotally connected at one end to another of said cranks and pivotally connected between the ends thereof to the other end of said first lever, and means connecting the other end of said second lever to said batten.

6. The invention of claim 1 wherein said control mechanism comprises lever means pivotally mounted in said apparatus releasably engaged to said clutch means, signal input means connecting said control means with said lever means to pivot said lever means in response to signals from said control means, and cam and follower means connected to said drive shaft and said lever means to predetermine the pivoted position of said lever means whereby the cam and follower means determines the engagement or non-engagement of said lever means with said clutch means upon appropriate input signal from said control means.

7. The invention of claim 2 wherein said eccentric means has a slot means therein, and lug means are fixedly connected to said release means to engage said slot means to exert a positive force to counteract the momentum of the parts being driven by said drive shaft.

8. The invention of claim 6 wherein said lever means comprises at least one lever, and said signal input means comprises at least one rod slidably mounted through said lever and a spring positioned between the end of said rod and said lever, said spring being normally in an unfiexed condition when there is no input signal from said control means, said rod responding to an input signal from said control means by sliding to a position wherein said spring is compressed against said lever and thereby urges said lever to disengage from said clutch means.

9. The invention of claim 8 wherein said cam and follower means comprises a follower mounted on said lever, a cam mounted for rotation to a cam shaft, and timing means connecting said cam shaft to said drive shaft.

10. The invention of claim 8 wherein adjustable positioning means are disposed in said apparatus in engagement with said lever to limit the pivotal movement of said lever in one direction.

11. The invention of claim 9 wherein pawl means are connected to said lever for intermittently engaging said eccentric means to prevent reverse movement of said eccentric means when said eccentric means are brought to a stop.

12. The invention of claim 11 wherein said pawl means comprises a pawl pivotally mounted to the free end of said lever and a spring engaging said pawl and said lever and urging said pawl to engage said eccentric means.

13. The invention of claim 12 wherein projection means are connected to said eccentric means to engage said pawl.

14. The invention of claim 1 wherein said clutch means comprises a plurality of spring actuated clutches each of said clutches having a first portion fixedly connected to said drive shaft for rotation therewith and a second portion positioned about said first portion and engaging said eccentric means, first spring means engaging said second portion for gripping said first portion, release means engaging said first spring means for permitting and preventing the gripping of said first portion by said first spring means, said release means engaging said control mechanism to normally prevent said first spring means from gripping said first portion While said drive shaft is rotating and to permit said first spring means to grip said first portion when said release means is disengaged from said control mechanism.

15. The invention of claim 14 wherein each clutch has a second spring means positioned about said drive shaft between the drive shaft and a portion of the first and second portions of said clutch in engagement therewith, said second spring means permitting rotation of said first portion independently of said second portion, and preventing said second portion from rotating at a faster speed than said first portion.

16. The invention of claim 14 wherein said eccentric means comprises a plurality of eccentrics, a separate eccentric being fixedly engaged with a separate second portion of a separate clutch for rotation therewith, and a plurality of cranks, a separate crank being disposed about a separate eccentric and in sliding engagement therewith for translation in response to the rotation of said eccentric, and said linkage means comprises a first lever pivotally connected at one end to one of said cranks and pivotally connected between its ends to a fixed portion of said apparatus, a second lever pivotally connected at one end to another of said cranks and pivotally connected between the ends thereof to the other end of said first lever, and means connecting the other end of said second lever to said batten.

17. The invention of claim 16 wherein said last-mentioned means comprises a rod pivotally connected at one end through the free end of said second lever, a batten lifter lever arm pivotally mounted in said apparatus and pivotally connected at its free end with said rod, a batten lifter positioning arm pivotally mounted in said apparatus and connected at its pivot to said batten lifter lever arm for rotation therewith and a second rod connected at one end to said batten and pivotally connected at the other end to the free end of said batten lifter positioning arm.

18. The invention of claim 14 wherein said control mechanism comprises lever means mounted in said apparatus releasably engaged to said clutch means, signal input means connecting said control means with said lever means to pivot said lever means in response to signals from said control means, and cam and follower means connected to said drive shaft and said lever means to determine the pivoted position of said lever means whereby the cam and follower means determines the engagement or non-engagement of said lever means with said clutch means upon appropriate input signal from said control means.

19. The invention of claim 18 wherein said lever means comprises a plurality of levers, each pivotally mounted in said apparatus and positioned to engage a separate release means on a separate clutch.

20. The invention of claim 19 wherein said signal input means comprises a plurality of rods eachf rod being slidably mounted through a separate lever, and a plurality of springs, each spring being positioned between the end of one of said rods and the lever through which said rod is slidably mounted, said springs being so disposed with respect to said levers that they are normally in an unflexed condition when there is no input signal from said control means, each of said rods responding to a separate input signal from said control means by sliding to a position wherein the spring associated with said rod is compressed against the lever through which said rod passes and thereby urges said lever to disengage from the release means on said clutch.

21. The invention of claim 20 wherein said cam and follower means comprises a plurality of followers, each of said followers being mounted on a separate lever, a cam shaft mounted for rotation in said apparatus, a plurality of cams mounted for rotation on said cam shaft, each of said cams being positioned to engage a separate follower, and timing means connecting said cam shaft to said drive shaft.

22. The invention of claim 21 wherein said timing means comprises a timing pulley mounted to one end of said cam shaft, a second timing pulley mounted to said drive shaft and a timing belt disposed about each of said pulleys and connecting said pulleys to positively drive said cam shaft from said drive shaft.

23. The invention of claim 19 wherein each of said release means comprises a release sleeve mounted on a separate second portion in a separate clutch, and connected to said first spring means for movement therewith, each of said release sleeves having at least one detent thereon positioned to engage a separate free end of one of said levers. V L 24. The invention of claim 23 wherein the total number of clutches is twoand each of said release sleeves has two detents thereon positioned 180 apart.

t 25. The invention of claim 23 wherein adjustable positioning means are disposedin said apparatus to engage each of said levers independently and limit the pivotal movement of said levers in one direction so that said levers engage only detents on said release sleeves and do notengage the surfaces of said release sleeves.

v 2,6. The invention of claim 1'9 .wherein said eccentric means comprises a plurality'of eccentrics, each fixedly connected to a separate second portion of said clutches for movement therewith and a plurality of cranks, each crank disposed about a separate eccentric in engagement 12 therewith for translation in response to rotation of said eccentric, each of'saideccentrics having at least one pin protruding therefrom and pawl means are connected to each of said levers for intermittently engaging said eccentrics to preventtreyerse movement of said eccentrics when said eccentrics are brought to a stop References Cited UNITED STATES PATENTS 3,148,709 9/1964 Gage 139- 171 3,190,517 6 /1965 P1031101 139 179 3,192,957 7/1965 oN6i11 r ,139-55 3,403,707

10/1968 Schedin 13917l HENRY S.VJAUDON, Primary Examiner i

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