US2507904A - Constant tension speed-varying control for spinning frames or the like - Google Patents

Description

May 16, 1950 G. M. HELLER ETAL 2,507,904

CONSTANT TENSION SPEED-VARYING CONTROL FOR SPINNING FRAMES OR THE LIKE 3 SheetsSheet 1 Filed Oct- 6, 1948 INVENTOR. GEOFGZ'MHELLE')? and E4011 3. Elvis,

ATTORNEY:

May 16, 1950 G. M. HELLER ETAL 2,507,904

CONSTANT TENSION SPEED-VARYING CONTROL FOR SPINNING FRAMES OR THE LIKE 5 Sheets-Sheet 2 Filed Oct. 6, 1948 @M MZL i QE Q May 16, 1950 -G. M. HELLER ETAL 2,507,904

CONSTANT TENSION SPEED-VARYING CONTROL FOR SPINNING FRAMES OR THE LIKE 3 Sheets-Sheet 3 Filed 001.. 6, 1948 W 5 3 ME HW a MF {A Z I m? w Patented May is, 1950 UNITED CONSTANT TENSION SPElD-VARYING GON- TBOL FOB SPINNING FRAMES OR THE George M. Heller and Paul B. Reeves, Columbus,

Ind., assignors to Reeves Pulley Company, j lumbus, Ind, a corporation of Indiana Application October-6, 1.48, Serial N0. 53,1

17 Claims.

The present invention relates to control means interposed in the driving train. for a spinning frame, or the like, and intended to improve the eiiiciency and speed of such a machine by maintaining optimum speed of the machine at all es. possible speed, at each given instant during the cycle of operation of the machine, which will permit continuous operation without an excessive number of "ends down" or breaks in the various strands being wound.

A given set of strands will, of course, withstand Optimum speed, of course, is the highest a predetermined degree of tension. It has been 7 ascertained that the tension existing in the portion of each strand extending between the guiding eyelet on the thread board and the bobbin, varies in accordance with three primary factors; viz., the currently existing angle at which the strand meets the effective periphery of the bobbin, the lineal distance between the traveler and the effective surface of the bobbin, and the lineal distance between the guiding eyelet and the traveler; these factors being here listed in descending order of importance. Each of these factors varies continuously during the operation of a spinning frame. In some types of operations, all three factors vary oppositely a great number of times during a cycle of operation. In another type of operation, the last factor varies oppositelywhile the other two factors vary progressively inone direction only.

It has been determined that tension in the critical portion of the strand decreases as each of the above factors decreases, and increases as each of the above factors increases; and that variation in the mentioned angle has the greatest effect upon tension, variation in the distance between the guiding eyelet on the thread board and the corresponding traveler on the ring rail has the least effect upon tension, and variation in the distance between the traveler and the currents effective surface of the bobbin has an intermediate effect upon tension. It follows that, in order to maintain maximum feasible operating speed, the speed of operation of the machine should be reduced as the weighted algebraic sum of the three factors increases, and should be increased as the weighted algebraic sum of those factors decreases.

In a few spinning frames which have recentl become available, the thread board reciprocates with the ring rail, thereby eliminating thelineal distance between the guiding eyelet and the traveler as a variable factor.

It is a primary object of the present invention, then, to provide means for controlling the speed at which a spinning frame or the like will be operated by a constant speed power source, in response to variations in those variable factors. According to the present invention, a speed controlling means which is highly sensitive to movements of a control element, is associated with the ring rail of a spinning frame, or the like, the con- 1 trol element following the movements of the ring rail. and further being affected as theeflective diameter of'the bobbin is increased by the addie tion thereto of successive layers of the strand being wound. A further object of the invention is to provide an arrangement whereby the control mechanism may be made properly responsive to the movements of a spinning frame ring rail, whether that frame is being used to perform a filling wind, a warp wind, or a combination wind.

Further objects of the invention will appear as the description proceeds. To the accomplish ment of the above and related objects, our invention may be embodied in the forms illustrated in the accompanying drawings, attention being called to the fact, however, that the drawings are illustrative only, and that change may be made in the specific constructions illustrated and described, so long as the scope of the appended claims is not violated.

Fig. '1- is a perspective view of a fragment of a spinning frame of conventional construction having associated therewith a drive train including a speed-varying mechanism and control mechanism for actuating the speed-varying mechanism in response to changes in the defined dominating factors! Fig. 2 is a fragmentary end elevation of portions of the drive train;

Fig. 3 is an enlarged fragmentary illustration of a fluid motor used in the organization of Fig. 4 is a perspective view of a control mechanism used in filling winding operations, and the panel upon which it is mounted;

Fig. 5 is a fragmentary perspective view of a; portion of 1 the control mechanism in a different position of adjustment;

Fig. 6 is an enlarged horizontal'sectional vies:

taken substantially on the line 6-6 of Fig. 5;

Fig. 'l' is a fragmentary end elevation of parts of. the control mechanism of Fig. 4;

Fig. 8 is a view similar to Fig. 4 but showing control mechanism used in performing a warp winding or combination winding cycle;

I Fig. 9 is an enlarged fragmentary front elevation'of details of the mechanism shown in Fig. 8; Fig. 10 is a sectional view taken substantially on the line lll|0 ofFig. 9; and

Fig. 11 is an enlarged fragmentary front elevabobbins 25 are led through eyelets 24 on the standard thread board l5, thence through the travelers I 3, and so to the spindles or bobbins 2| which are rotated at high speed by any suitable means. Conventional means is provided for reciprocating the ring rail 22 as the bobbins 2| are rotated, the entire mechanism being driven, in accordance with standard practice, from a main shaft 23'.

According to the present invention, a motor 21, mounted upon a suitable frame, carries on its spindle a resiliently expansible pulley 23, which pulley may comprise a coned disc 23 fixed to the motor spindle, a mating coned disc 33 splined thereon, and spring means, contained within a housing 3|, continuously urging the disc 33 toward the disc 23. A belt 32 provides a. driving connection between the expansible pulley 23 and a v pulley 33 rotatationally fixed on, but axially slidable with respect to, a shaft 34 which is Journalled in a. frame 35 mounted for oscillation upon a journal element 23. Said journal element is supported upon a standard I4 which, in turn, is mounted upon an adjustably positionable base I 2 whereby, through adjustment of said base, said element 23 may be brought into substantial coaxial relation with the main shaft 23' of the spinning frame with which the control assembly is associated. The shaft 34 carries, outboard with respect to the frame 35, a V pulley I1, which is connected by a belt l3, to drive a V pulley I9 conventionally fixed to the main shaft of the spinning frame. A fluid motor, indicated generally by the reference numeral 35, has a journalled supporting association with the free end of the frame 35 through trunnions 35' received in ears 35'.

The motor 25 comprises a cylinder 31 within which is reciprocably received a piston 33 having a stem or rod 39 projecting through one end of the cylinder 31 and pivotally supported, as at 43, upon a portion ll of the base l3. Obviously, as fluid is supplied to one end or the other of the cylinder 31, said cylinder will be moved bodily, in the general direction of its axis, in one direction or the other with relation to the piston 33. Because of the rocking connection between said cylinder and the free end of the frame 35, the frame 35 will be correspondingly oscillated about the element 25, carrying with it the shaft 34 and pulleys 33 and I1. Since the axis of oscillation of the frame 35 is substantially coincidental with the axis of the pulley I! on the machine main shaft, such movement of the pulley i1 does not affect the belt connection between the'pulleys l1 and I9. As the pulley 33 is moved away from the axis of the spindle of the motor 21, however, the belt 32 will be crowded more deeply between the discs 23 and 30, separating said discs against the tendency of said spring means in the housing 3|, and reducing the effective diameter of the pulley which drivesthe belt 32 to reduce the speed at which the shaft 34 will be driven. Concurrently, the pulley 33 will drift axially toward the right, as viewed in Fig. l, to maintain alignment of the belt 32. Correspondingly. as the shaft 34 is moved toward the axis of the spindle of the motor 21, the belt will be squeezed outwardly between the cones 29 and 33 by the action of the spring associated therewith, to increase the effective diameter of the pulley 23 and to increase the speed at which the shaft 34 will be driven; while the pulley 33 will move to the left on said shaft 34.

- Pipes 42 and 43 lead from a control valve 44,

4 5 carried on the cylinder 31, to the opposite ends of said cylinder; and flexible conduits and 43 lead, respectively, from a source of fluid under pressure to the valve 44, and from said valve to a reservoir or to waste. A control lever 41 controls the flow of fluid to and from the opposite ends of the cylinder 31 through the pipes 42 and 43. As the lever 41 is moved in a clockwise direction, as viewed in Fig. 1. fluid under pressure will be supplied to the lower end of the cylinder 31 and will be exhausted from the upper end of said cylinder, thereby swinging the frame 35 in a counterclockwise direction to reduce the speed at which the shaft 34 is driven. When the lever 41 is in its position illustrated in Fig. l, fluid flow to and from the cylinder 31 will be arrested. When the lever 41 is moved in a counterclockwise direction from its position so illustrated, fluid will be supplied to the upper end of the cylinder and will be released from the lower end thereof, to move the frame 25 in a clockwise direction to increase the speed at which the shaft 34 is driven.

A control panel 43 (Fig. 4) is mounted adjacent the spinning frame 23, being carried either on said machine or on the supplemental base supporting the drive train; and preferably a closure cover 43 (Fig. 1) is normally associated therewith. A rod is operatively associated, by means'of a pair of collars 5| removably and adjustably mounted on its upper end, with a projection 52 from the ring rail 22; and at its lower end, said rod carries a block 53. The rod 53 reciprocably penetrates a second block 54 fixed to a slide 55 reciprocably mounted upon a guide 53 whose axis is parallel with that of the rod 53. Near its upper end, the rod 53 is guided in a block 51 fixed to the panel 43.

Fixed to the block 53 is a rigid strap 53 to the outer end of which is pivoted, as at 53, one end of a link 60. To the upper end of said link 30 is pivoted, as at 6|, one end of a second link 52 which carries at its opposite end, a roller 63. Pivoted to the link 62 upon the axis of the roller 53 is one end of a lever 64 pivoted, intermediate its ends at 35, upon a projecting portion of the slide 55. The other arm 53 of the lever 64 is urged in a clockwise direction by a coiled spring 51 anchored at 68 upon the slide 55.

The link 32 rigidly carries, at that end upon which is supported the roller 33. an arm 33 to which is fixed a slotted guideway 13. Slidably penetrating the slot of the guideway 10 is a screw 1| engaged in one end of a link 12 whose opposite end is pivoted, at 13, to one arm 14 of a bell crank lever 15 mounted at 13 upon a projecting arm 11 of the panel 43. A stop 12' is adjustably secured in the guideway 13 near the lower end thereof to limit downward movement of said screw 1| relative to said guideway; and upward movement of said screw is limited by the block 33'. The other arm '13 of .said lever 15 is pivotally associated, as at 13, with the lower end of an actuator rod 33. A coiled spring 31 has one end secured, at any one of a plurality of points in the length thereof, to the lever arm 13, its opposite end being suitably anchored to exert a clockwise force upon the lever 15. The upper end of the rod 33 is operatively connected to the lever 41, at any one of a plurality of points in the length of said lever; and a tumbuckle 32 is preferably interposed in the length of the rod 33 (see Fig. 1).

As is clearly illustrated in Fig. 6, the slide 55 comprises mating elements 33 and 34 snugly but slidably embracing the guide 53. The element 34 is provided with a neck 35 internally threaded for adjustable reception of a plug a abutting one end of a coiled spring 61 received in said neck,-the other end of said spring bearing against a friction shoe '5 which bears upon the guide with a frictional effect dependent upon the adjustment of the plug 56. Thus, the slide 55 is frictionally restrained against movement upon the guide 56.

of the rod 55, and a further region 52 which is curved on a radius such that, in one position of the plate 56, the region 52 is centered on the pivot point 13. In the illustrated embodiment of the invention, such cam means comprises two separate plates, one of which 65, provides the sure face 56 and is formed with a vertically elongated.

slot 54 penetrated by clam-p means 55, whereby the position of the plate 55, and so of the surface 56, may be adjusted; and the other of which, 56, provides the surfaces and 52 and is mounted upon the panel 48 through the medium .of two slots 51 and 96, elongated upon lines substantially perpendicular-to the rod 56 and penetrated by clamping means 59 and I", respectively. It will be understood. of course, that this cam means herein ililustrated is designed to correspond to tension conditions in a particular spinning frame;

and that the particular design of the cam means used with any specific machine will depend upon the tension variation conditions found to exist in that specific machine.

A stop plate llll, having a forwardly projecting finger I52 disposed in the path of movement of the lever 12, is adjustably secured to the panel 45 by means of a vertically extending slot III in said plate and one or more clamping elements I04 penetrating said slot and engaging the panel 46.

'Adjustably fixed to the rod 55 to move therewith is a block 165 which, under certain circumstances, engages the block 54 to shift the slide 55 downwardly in response to downward movement of said rod, as will appear more fully hereinafter.

In the operation. of a spinning frame 25 to produce a filling type of wind or build upon the bobbins 2|, the ring rail is caused to reciprocate through a path of constant length but of varying position. That is, the ring rail starts at the bottom of its stroke and moves upwardly through a a predetermined distance and then returns to its original position. Customarily, on each fourth cycle, the upward movement of the ring rail is slightly elongated, whereafter its downward movement is of the previous extent, so that the bottom end of the path of the ring rail is 10 At the beginning of the cycle of the machine. when the ring rail 22 is at its lowermost position, the parts of the control of this invention will occupy positions substantially below those illustrated, the bottom end of the slide 55 being slightly above the position of the bolts I56, and the rod 56 being positioned to locate its attached block 55 closely adjacent the bottom end of said slide. In that. position of the parts. the link I2 will be in contact with the projection I02 of the stop plate Ill and the screw II will be near the top of the guideway 16, depending upon the adjustment of said stop plate. The roller 62 will be pressed against the lower end of the cam surface 66 under the influence of the springs 61. and II. The position of the bell crank lever I5 will, thus, be dependent upon the current position of adjustment of the stop plate Ill, since the position of the finger I62 relative to the adjusted position of the slide 55 will determine the-location of the screw 1| in the guideway 10. Dependent upon that relation, the screw ll may be above or below the axis of the roller 63, or it may be coincident with said axis. The lever 41 will be in its neutral position, with the auxiliary frame 55 near the counterclockwise end of its stroke as viewed in Figs. 1 and 2, so that the speed ratio between the spindle of the motor 21 and the shaft 24 will be near its maximum and the spinning frame will be operated at or near its minimum speed.

Now, as the ring rail starts upwardly, the first reaction of the control will be to lift the block 52 and its attached strap 58 without affecting the position of the slide 55. Since the link 64 is connected to that end of the link 62 which carries the roller 63, and since the link 64 cannot move upwardly except upon corresponding move-- ment of the slide 55, it will be clear that the above-described movement of the rod 56 will cause clockwise swinging movement of the link 62, as viewed in Fig. 4, about the axis of the pivotal connection between the links 62 and 64. Since the guideway 15 is fixed with respect to the link 62,

the guideway 10 will likewise be swung in a clockwise direction about the pivotal axis between the links 62 and 64. If the screw II is currently coincident with that axis, thelever 15 will not be affected by such upward movement of the rod 50. If the screw ll is currently above that pivotal axis, the lever 15 will be moved in a clockwise direction by such swinging movement of the guideway 10; or if the screw H is currently below that axis, such upward movement of the. rod 50 will result in counterclockwise movement of the lever-15.

Clockwise movement of the lever 15, of course.

lifts the rod" to move (the lever 41 in a counter-- clockwise direction, as viewed in Fig. l, to admit fluid to the upper end of the cylinder 31 and release fiuid from the lower end thereof, which, of

course, results in clockwise movement of the cated above the lower end of the path through whichthe ring rail moved upon its three previous reciprocations. Preferably, the block I" will be so positioned on the rod 56, relative to the block I frame 25 about-itsjournal element 26, and an increase in the speed of the shaft 54; while counterclockwise movement of the lever 15 operates oppositely to decrease the speed of the shaft 34, and so of the spinning frame. It will be seen that movement of the cylinder 31 in response to either type of adjustmentof the lever 41 carries with it the valve housing and has the effect ,of returning the lever 41 to a neutral position.

' As the rod 56 returns to its lowermost position, of course the guideway 10 is returned to its starting position, and concurrently the lever I5 is returned to its starting position, whereby the rocation of the rod II lifts the block it to anew.

high position, which may be only a fraction of an; inch above its previous high position. As said block attains its new position, itstrikes the block II to lift the slide II slightly, thereby elevating the position of the link It and the position of the roller 63. Since the roller it is carried on ,8 I It. Under those circumstances, of course, the

meanspeedofthemachinewillnotvaryesthei roller ll rides the surface 02, since movement of the roller along said surface will not shift the lever II. In practice, with the particular machine and strands selected for this disclosure,

' however, the plate is tilted somewhat in a the link 62 and is pressed against the cam surface 80 by forces applied by spring II through lever it and by spring II through lever Ii, link I2, and guideway I0, such elevation of its position will cause it to move toward the right as viewed in Fig. 4, pivoting about the pin 55, and moving the link I slightly in a clockwise direction about its pivot point 59. The guideway I0 moves with the roller 63 to shift the lover I! in a clockwise direction, thereby increasing the speed of the shaft 34 corresponding with the top of the path of the block It. As the rod II again descends, the slide It will remain stationary in its new high position, so that the speed of the shaft 2| corresponding to the lowermost position of the block it will also be slightly higher than the previously corresponding value.

Operation of the machine continues in this same fashion, the slide ll being elevated slightly each time the position of the path of reciprocation of the rod BI is changed, and the roller 63 continually following the cam surface OII until finally the roller moves of! the cam surface 80 and onto the cam surface ll.

Depending upon the position of the adjustable stop I2, the parts will ultimately reach a condition in which the link I2 is always held above the stop finger I02.

It will be seen that this peculiar movement will cause the control elements to move continuously through a path of substantially constant length but of varying position. As the position of the path of reciprocation of the parts advances upwardly, the mean speed of the spinning frame will progressively increase, while still varying, during each reciprocating cycle, to compensate for variations in the factors determining tension in the strands being handled. The speed variation within each reciprocating cycle will be determined by the position or positions assumed by the screw II in the guideway III during the cycle.

It will, of course, be obvious that the shape or contour of the cam surface with which cooperates the roller 63 determines the mean speed of the controlled machine during any specific reciproeating cycle of the rod 5|. It will further be obvious that the optimum cam contour for any given machine, operating with a given type of strands, may be formed upon a single cam element which may be non-adiustably mounted upon the panel 48. with the particular machine illustrated, and with the type of strands selected for this disclosure, the mean speed of the machine should increase relatively rapidly during the early parts of the build, during which the roller It is riding on the surface 8!, should then increase more gradually for a further period, during which the roller 63 is riding on the-surface SI, and should then continue to increase. at a predetermined rate through the remainder of the machine cycle. As has been stated, the surface 52 is machined on a curvature of such radius that, when the plate It is in one position, the surface 92 will be centered upon the pivot point clockwise direction, whereby the concentricity of the surface 12 with the point It is disturbed. The degree of tilting of the plate of course,

will determine the rate at which the mean speed of the machine will increase as the roller rides the surface 92. It will be obvious that. if the plate It is tilted in a counterclockwise direction as viewed in Fig. 4', the mean speed of the ma-, chine will be caused to be reduced as the roller 63 traverses the cam surface 82. We presently believe that adiustability of the plate 2', which produces such flexibility of the mean speed of the machine during the final phases of the machine cycle, will be desirable in order to compensate for diiferences'in the operation of individual machines and for differences in the strands being handled by the machine.

The wind or build will have been completed when the ring rail reaches a position in which the upper end of its stroke carries the roller ll substantially to the upper end of the cam surface 92 and at that point, the machine will be stopped and the bobbins 2I will be doifed and replaced by a new set of empty bobbins. Now, by conven-' tional manipulation of the controls of the spinning frame, the ring rail will be returned to its bottom, or starting. p sition; and as it moves downwardly, its extension 82 will carry with it the rod Ill. The block II! engages the block it to carry the slide 55 back to its lowermost, or starting position; and the above described cycle will be repeated.

In Figs. 8 to 11, I have illustrated a modified form of control mechanism to be used in connection with a spinning frame being operated to produce a. warp build. In that type of operation. the first reciprocating stroke of the ring rail moves from the bottom of the bobbin substan-' tially to the top of the bobbin and returns to 'a' level 9, fraction of an inch short of its original starting position. On its next reciprocation, the ring rail stops a fraction of an inch short of the upper end of its first reciprocation, and so on; each subsequent stroke of the ring rail being slightly shorter than the preceding stroke, but being symmetrical with respectto the midpoint of its original stroke. Thus, the ring rail may be said to travel in a, path of constant position but continually varying length.

' In that form' of the invention illustrated in Figs. 8 to 11, a panel I20 takes the place of the panel 48 of the previously described form, the rod 50 being guided in blocks I" and It! fixed to said panel. Block I2I is fixed to, and travels with, the rod 50; and a second block I22 is likewise fixed to said rod at a lower point. Clamping screws I23 and I24 operatively engage the respective blocks I2I and I22 to secure to said blocks a, cam plate I25, said screws passing through laterally elongated slots I 21 and I2! in said plate I25 to provide for adjustment of said plate relative to the rod 50. The cam plate is formed with a rectilinear cam surface I26 which retreats from the axis of the rod III as'its extends upwardly. A lever I29 is pivotally mounted, near one end, as at I30, upon a block I3I extending laterally from one edge of the panel I20. A bell crank lever I02 is pivotally mounted. as at I00, at a point intermediate the ends of the lever I20, one arm I04 oi said bell crank lever being pivotally connected at I25 to the lower end of the rod 00 which, as is illustrated in Pig. 1, is operatively connected to shift the valve-controlling lever 41. A spring I00 has one end connected to the lever arm I04 and has its other end anchored upon an abutment I01 adjustably supported on the adjacent edge of the panel I20, said spring continuously urging counterclockwise movement of the lever I02 as seen in Fig.8. The other arm I00 of the lever I02 carries a roller I00 which rides the cam edge I of the plate I undertheiniluence of the spring I00.

The free end of the lever I20 pivotally engages the lower end of a strap I40 which terminates in a slotted uide I. In the illustrated embodiment of the invention, the guide I is welded to the upper end of the strap I40; but it will be obvious that said guide could be an integral portion of said strap.

Brake means, indicated generally by thereference numeral I42, is associated with the guide I. Such brake means comprises a pin I40 fixed to the panel I20 and projecting forwardly there from with a spacer I44 mounted thereon and providing an abutment for a friction washer I45 bearing against the rear surface of the guide I.

A second friction washer I45, mounted on the pin I40. bears against the front surface of said guide under the influence of a spring I41 confined between said washer I45 and a washer I which is adjustably positioned upon' the pin I43 and is backed by an adjusting nut I40 threaded on the end of the pin I43. It will be obvious that, by manipulation of the nut I49, the degree of force with which the spring I41 grips the guide I between the washers I45 and I45 may be adjusted to a nlcety. It will also be seen that the spring I35 tends always to lift the strap I40 and its associated parts.

Clutch means, indicated generally by the reference numeral I50, is likewise associated with the guide I below the point of association there with of the brake means I42. Said clutch means comprises a pin I5I penetrating the slot of the guide I and having a head I52 bearing against the rear iace. of a link I53. A friction washer I54 is sleeved on the pin I5I and is pressed against the forward face of the guide I under the influence of a coiled spring I55 confined between said washer and a washer I55 sleeved on the pin I51 and backed by an adjusting nut I51 threaded on. the outer end of the pin I5I. It will be obvious that the degree of frictional engagement between i0 elongated slot I12 in the panel I20 and-Is clamped in adjusted position therein by means of a spacer sleeve I10 and a nut I14.

Fixed to the block I22 is a bumper plate I00, whose upper end is inclined upwardly and toward the rod 50. The position of the plate I05 is such that, as it is moved upwardly into registry with the roller I54, it will engage said roller to tend to straighten the toggle comprising the links I00 and I52.

In Figure 8, the parts are shown in the positions which they occupy when the ring rail 22 is at the bottom of its stroke, and which correspond with minimum machine speed. As the ring rail rises, the cam plate I25 moves upwardly therewith, and the roller I30, under the influence of the spring I35, follows the inclined cam surface I25, whereby the speed of the machine .will be gradually increased in the manner hereinabove described. Before the ring rail reaches the top of its stroke, the bumper plate I05 will engage the roller I54 to straighten the toggle, thereby moving the clutch means I upwardly. The tension of the spring I is so adjusted with respect to the tension of the spring I41 that the upward movement of the clutch means I50 will carry with it the guide I4I, the strap I40, and the left-hand end of the lever I29, the clutch being assisted, of course, by the tendency of the spring I55. Thus, the position of the pivot point I33 will be elevated, whereby the position of the cylinder 01 corresponding to any position of rotational adjustment of the lever I02 will be elevated.

As the ring rail descends, the bumper plate I55 leaves the roller I54 to permit the spring I55 to bend the toggle, returning the roller I64 into its illustrated position, where it is stopp d by engagement of the pin head I52 with the post head I1 I. The relative effectiveness of the brake means I42 and the clutch means I50, and the effect of the spring I35, are such that the guide I is retained, by the brake means, against retrograde J movement with the clutch means I50.

the clutch means I50 and the guide I may be nicely adjusted by manipulation of the nut I51.

The link I53 cooperates with a link I52 to provide a toggle mechanism for producing movement of the clutch means I50. One end of the link I02 is mounted upon a fixed pivot I5I, while its other end is pivotally connected, as at I53, with that end of the link I50 remote from the pin I5I. At its end adjacent the pin I5I, the link I53 carries a post I50 to which is secured one end of a coiled spring I55, the opposite end of which is anchored upon a post I50 fixed to the panel I20.

The spring I50 tends always to move the upper- Said pin I10 passes through a vertically peripheries of the bobbins.

Preferably the parts will be so proportioned that each actuation of the toggle by the bumper plate I05 will shift the lever I20 by precisely the amount necessary to compensate for the reduction of the weighted algebraic sum of the factors determining tension in the strands being wound:

but if absolute accuracy cannot be attained, the

parts are so related that each actuation oi'th'e toggle will move the guide I a little farther than necessary. The block I22 is so proportioned and arranged that its path is intersected by the roller I51 carried on the lever I29; and therefore, if the lever I29 is over-adjusted by any individual actuation of the toggle, it will be returned to ac curate position when the block I22 strikes said roller near the downward end of the return stroke of the rod 50.

It will be seen, thus, that the speed of operation of the spinning frame is progressively increased during each upward stroke of the ring rail, to compensate for the corresponding 'reduc-' tion in the lineal distance between the travelers I6 and the eyelets 24, and is progressively de-. creased during each descent of the ring rail to compensate for the increase in that lineal tance. However, the mean speed of the machine is continually increased to compensate for the progressive reduction in the lineal distance between the travelers I5 and the effective surfaces of the associated bobbins, and for the change in the angle at which the strands meet the effective escapes l1 build having been completed, the operator e machine and will return the mastartingposition, whereby the ring rail returned to its lowermost 'l'he i2. 'constant-speedpower,

. sionincludinganinputsbaftdrivenfroml'aid source,- an output shaft, and means-shiftable opvary-oppositeiy thespeed ratio beas itmoves downwardly, the block ill-will engage'thc roller'ill to return the'lever III, and 7 associated parts, against the tendencyof the spring m and the brake ill, to its starting potween said. shafts, a fluid-pressure motor including an'element'movalile oppositely and opera-- .tively connected to shift said shiftable means, a

control element for said motor adjustable op-,

posit'ely from a'neutral position about an axis while itis presentlybeiieved that, when -a frame of the type selected for illustrastood that,'under different conditions, a modified camcontour might be desirable. The cam conselected for cooperation with the roller its will'be designed to produce suchchanges in speedofthecontrolledmachineastomaintain maximummachine speeds consonant with ourmovable withsaid movable element to actuate said motor oppositely, whereby movement of laid movable element in response to adjustment of said control element in either direction tends to restore saidcontrol element to neutral podtion.

a lever operatively connected to said'control element, a cam,-a camfollowenmcans ,operatively connecting said'cam follower to shift said lever,

"and vibratory means driven from said output shaft and acting to produce relative movement rent tension conditions throughout-the cycle of themachine;andtothatenditmaybenecesbetween said cam and cam follower.

8. a device of th'e'classdescribed, a reciprocater, means for driving said recipro'cator'- g, through a path of constant length but varying sary under special conditions-to have-a surface.

like the surface lit oppcsitelyinclined, or curved, or irregular, dependingupon tension factors determined for a particular We claim as our invention: 1. For use with a spinning frame or including a main shaft and an element driven from said main shaft through a vibratory path,

means for controlling the speed at which said main shaft isdriven by a constant speed power source, comprising stepless variable-speed trans-- Q2. The speed-controlling means of claim 1 in.

svhich said power means is a iluid-pressur 8. ,The speed-controlling means ,whichysaid last-named means comprises a cam, a cam follower, means connecting said cam follower with said member, and means operatively said element to produce relative movement between said cam and said cam follower in response to movement of said element through said vibratory path.

' 4. For use with a'spinning frame including a inain shaft, a plurality of bobbins. and a ring rail driven from said shaft, said ring rail carrying a traveler for each of said bobbins, means ofclaimlinmovement or said ,sliderelative to said guide, means moving with said reciprocator to limit position; 'a-guide paralleling said D ub a slide mounted on said guide, friction means resisting movement thereof relative to said slide and op- ,e'rable to shift the position of-said slide to correspond with changing positions of the path of said reciprocator, a linkage including a portion carried by said recipro'catorand a portion carried-by said slide and elements connecting said portions, whereby relative movement between said regdprocator and said slide produces changes in the relative positions of said connecting elements, a guideway carried by one of said connecting elements, pivot means slidably engaged in said guideway, lever means, a link connecting said pivot means with said lever means, and

ineans connecting said lever means to actuate a control for said driving means in response to Y movements of said link.

for controlling the speed of operation .of. said I shaft, and so of said bobbins, to maintain subltantially constant tension in strands being wound on said bobbins, while said shaft is driven from a substantially constant-speed power source, comprising a variable-speed power transmission mechanism operatively connected to r t power from such source to such shaft and including an element shiftable oppositely to.

vary oppositely the output speed of said transmksion, a fluid-pressure motor connected to shift lid element, a control element for said motor shiftable oppositely from a neutral position to cause opposite actuation of said motor, and control mechanism operatively connected between said ring rail and said control element and operable to vary the eifect on said control element of a given degree of movement of said ring rail.

5.. In combinatio a ource oi'suhstsstisllr' 7. The device of claim 6 including'cam means located adjacent the' path of said slide, a cam follower fixed with respect to said guideway, and spring means railiently urslns said'cam follower intocooperative engagement with said cam 8. The device of claim 6-in which said linkage portion carried by said slide is a lever pivotaiiy mounted on said slide and pivoted, at a point remote from its connection with said slide, to that. one of said elements carrying said guideway, and including cam means located adjacent the path of said slide, a cam follower substantially coaxial with the pivotal connection be- .tween said lever and said element, and spring means acting on said lever to urge said cam foilower resiliently into cooperative engagement with said cam means.

9. In a device of the class described, a recti- -linear guide. a slide mounted on said guide,

13 with respect to said reciprocator, a second link having one end pivoted to said first-named link at a point remote from the pivotal mounting of said first-named link, a lever pivotally mounted on said slide and pivotally connected, at a point remote from its mounting, with said second link at a point remote from the pivotal connection between said first and second links, cam means located adjacent the path of said slide, a cam follower substantially coaxial with the pivotal connection between said lever and said second link, spring means acting on said lever to urge said .cam follower resiliently into cooperative engagement with said cammeans, a guideway rigidly associated with said second link, pivot means slidably mounted in said guideway, lever means, a further link connecting said pivot means with said lever means, and means connecting said lever means to actuate a control in response to movements of said link.

10. The device of claim 9 in which said pivot means is reciprocable in said guideway in a direction generally transverse to the direction of length of said second link.

11. The device of claim 9 in which said guideway has a portion coincident with the axis of pivotal connection between said first-named lever and said second link.

12. The device of claim 9 in which said guideway intersects, and extends in opposite direct ons beyond, the axis of pivotal connection between said first-named lever and said second 13. In a device of the class described, a reciprocator, means for driving said reciprocator through a path 01' varying length but constant position, cam means mounted to move with said reciprocator, a first lever mounted on a pivot, a second lever pivotally mounted on said first lever at a point remote from said pivot, a cam follower supported on said second lever, spring means resiliently urging said cam follower into cooperative engagement with said cam means, said second lever being connected to actuate a control for said driving means, brake means associated with said first lever to hold the same in any selected position of adjustment, and actuating means for shifting said lever incrementally in one direction against the holding eflect of said. brake means, comprising a friction clutch opera-- tively associated with said lever and toggle mechanism for reciprocating said clutch, said toggle mechanism including a link mounted on a fixed pivot adjacent the path of said reciprocator, a second link having one end operatively attached to said clutch, the other ends of said links being pivotally connected together, means resiliently resisting straightening of said toggle mechanism, and means moving with said reciprocator and enmeable with said toggle mechanism to straighten the same against such resistance.

14. In a device of the class described, a reciprocator, means for driving said reciprocator through a vibratory path of varying length and comtant position, cam means moving with said reciprocator, a first lever mounted to swing about a pivot, a second lever pivotally mounted on said first leverat a point remote from said pivot, a cam follower supported on said second lever, means resiliently urging said cam follower toward cooperative engagement with said cam means; means connecting said second lever to actuate a control for said driving means, and means actuated by said reciprocator for moving said first said first lever, means actuated bysaid reciprocator upon each reciprocation thereof to shift said clutch means relative to said brake means tomove said first lever through a predetermined arc in onedirection, and means for returning said clutch means, after each such movement thereof, without correspondingly moving said first lever.

16. In a device of the class described, a reciprocator, means for driving said reciprocator through a vibratory path of varying length and constant position, cam means moving with said reciprocator, a first lever mounted to swing about a pivot, an element connected to said lever, a second lever pivotally mounted on said first lever at a point remote from said pivot, a cam follower supported on said second lever, means resiliently urging said cam follower toward cooperative engagement with said cam means, means connecting said second lever to actuate a control for said driving means, stationary friction brake means eng ing said element and resisting movement thereof in response to the tendency of said resilient means, clutch means fnictionally engaging said element, means moving with said reciprocator and operative to move said clutch means bodily relative to said brake means, and thereafter to release said clutch means, during each cycle of reciprocation of said reciprocator, and means operative,-upon such release of said clutch means, to return the same to its initial position.

17. The device of claim 16 in which said element is provided with an elongated slot and in which said brake'means comprises a stationarily mounted pin projecting through said slot, a spring sleeved on said pin, a friction member sleeved on said pin and bearing on said element, and a nut threaded on said pin and adjustable axially thereof, said spring being confined between said nut and said friction member, and in which said clutch means comprises a pin projecting through said slot, and having a head cooperating with one face of said elementto limit movement of said pin axially in one direction relative to said element, a friction member sleeved on said pin and cooperating with the opposite face of said element, a nut threaded on said pin and adjustable axially thereof, and a spring sleeved on said pin and confined between said nut and said friction member.

GEORGE M. HEIJER. PAUL B. REEVES.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Date

Images