US2182745A

US2182745A - Reciprocating mechanism

Info

Publication number: US2182745A
Application number: US28117A
Authority: US
Inventors: Ferris Walter
Original assignee: Oilgear Co
Current assignee: Oilgear Co
Priority date: 1935-06-24
Filing date: 1935-06-24
Publication date: 1939-12-05
Anticipated expiration: 1956-12-05

Description

Deg. 5, 1939. w. FERRIS 2,182,745

- RECIPROCATING MECHANISM Filed June 24, 1935 l1 Sheets-Sheet l INVENT :IR'

VVAYUJI'ER F'EHHIS B ATTEIHNEY.

W. FERRIS RECIPROCATING MECHANISM Dec. 5, 1939. 2,182,745

11 Sheets-Sheet 2 Filed June 24, 1935 'V VA TER FEHRIS TTURNEY- INVENTEIR Dec. 5, 1939 w. FERRIS 2,182,745

v RECIPROCATING MECHANISM Filed June 24, 1935 ll'Sheets-Sheet 4 r INVENTDR' V VA LTER F EFi'RlS Dec. 5, 1939.

w. FERRIS REGIPROCATING MECHANISM Filed June 24, 1935 Sheets-Sheet 6 WALT ER FERRIS ATTORNEY.

Dec. 5, 1939. QF R 2,182,745

RECIPR OCATING MECHANISM Fil d June 24; 1935 11 Sheets-Sheei 7 INVENTEIF? WALTER FERHIS BY 9 V r TDVHNEY.

w. FERRls 7 2,182,745

BEGIPROCATING MECHANISM Filed June 24, 1935 11 Sheets-Sheet a INVENTEIR 3 WALTER -F-ERHIS AT TElRNEY- Dec. 5, 1939. w. FERRIS RECI PROCATING MECHANISM Filed June 24, 1935 11 Sheets-Sheet 9 INVENTDR' MLTER FEHR'IS BY ATTORNEY.

. 5, 1939. w. FERRIS RECIPROCATING MECHANISM 11 Sheets-Sheet 10 Filed June 24, 1935 NM ll mum l I I m E H R m m H M 9 T x M w M \& a w W w m\\ h. @v .I r

Dec. 5, 1939. w. FERRIS I 2, 82,745v

RECIPROCATING MECHANISM Fild June 24, 1935 11 Sheets-Sheet 11 INVENTIJR WALTER FEH'HIS BY ATTE IRNEY.

Patented Dec. 5, 1939 UNITED STATES RECIPROCATING MECHANISM Walter Ferris, Milwaukee, Wis., assignor to The Oilgear Company, Milwaukee, Wis., a corporatien of Wisconsin Application June 24, 1935, Serial No. 28,117

19 Claims.

This invention relates to reciprocating mechanisms and. is particularly adapted for recipro-- threads during the winding thereof upon or.

within suitable carriers. In one type of machine, the rayon threads are wound upon the inside of a hollow bucket or cup from which the thread is removed in a single annular mass or cake.

If the thread or yarn is to be unwound by withdrawing it radially from the winding, it is wound upon the carrier in a form known as warp-winding. In this form, the thread or yarn is wound in uniform layers with each turn 5 in each layer in contact with the adjacent turn in that layer.

In guiding the thread or yarn to make a warpwinding, the ring rail or traverse bar should travel at a uniform speed in both .directions and, unless the thread or yarn is being wound between fianges which extend at right angles to the axis of the winding, the stroke or traverse of the ring rail or traverse bar should be grad-.

wound in tight spirals in alternate layers and in open spirals in the intermediate layers to prevent the thread or yarn from sloughing off the end of the winding when drawn axially therefrom.

In guiding the thread or yarn to make a filling-winding, the ring rail must travel at one speed in one direction, in order to wind the thread or yarn in tight spirals, and at a much greater speed in the opposite direction to wind the thread or yarn in open spirals. Also, its range of reciprocation must be gradually moved 0; advanced in order to produce the overlapping layer characteristic of the filling winding,

Ring rails, traverse bars and the like have heretofore been reciprocated mechanically, by vmeans of cams, gears and suitable linkage but, due to the inertia of the moving parts, both the speed and the permissible weight of the rciprocating parts have heretofore been limited and in some instances the wear on the cams and other parts is 'so great that frequent renewal is required. Y

The present invention has as an object to 10 provide a reciprocating mechanism which may be operated at high speeds without injury to itself or to any part of the machine with whic it is associated.

Another object is to provide a reciprocating mechanism which is capable of reciprocating relatively heavy machine parts Without injury to itself or to the machine with which it is associated.

Another object is to provide a reciprocating 20 mechanism which is positive and precise in operation, and which is capable of reversing much more quickly than is possible with the mechani cal cams heretofore used.

Another object is to provide a reciprocating 26 mechanism which is susceptible of close adjustment and control.

Other objects and advantages will appear from the description hereinafter given of a reciprocating mechanism in which the invention is em-,

bodied.

According to the invention in its general aspect, the mechanism is provided with a reciprocating hydraulic motor, a valve for controlling the motor, and mechanism to operate the valve to obtain both the desired speed and length of stroke.

"According to the invention in another aspect, the reciprocating mechanism is provided with means for changing the length of its stroke.

According to the invention in another aspect, the reciprocating mechanism is provided with means for changing the range of its stroke.

The invention is exemplified by the reciprocating mechanism shown in part schematically and in part in detail in the accompanying drawings in which the views are as follows: I

Fig. 1 is a front elevation of a hydraulically operated reciprocating mechanism which is 50 adapted to reciprocate or traverse, the ring rail 'or traverse bar of a spinning machine.

Fig. 2 is a top plan view thereof and shows the parts in the positions occupied when the machine employed to reciprocate or traverse a ring rail or traverse bar during the production of a warp-winding.

1 Fig. 3 is in part an end view and in part a transverse vertical section taken on the line 3-4 5 of Fig. 1.

Fig. 4 is a transverse vertical section taken approximately on the irregular line 44 of Fig. 2.

Fig. 5 is in. part a transverse vertical'section and in part a sectional plan view taken on the irregular line 55 of Fig. 1.

Fig. 6 is a partial front view with certain parts omitted and other parts broken away to expose other parts which control the functioning of the mechanism during the production of a warp- 15 winding, the several parts being shown in the positions occupied when the traverse bar is at the bottom of its traverse and about to start a warp-winding having fiat ends.

Fig. '7 is a view showing a part of the mechago nism illustrated in Fig. 6 but with the parts thereof in the positions occupied at the completion of a warp-winding having fiat ends.

Fig. 8 is a view similar to Fig. 7 but showing the parts in the positions occupied. just after 25 starting a warp-winding which will have a tapered shoulder at each end thereof.

Fig. 9 is a view similar to Fig. 8 but showing the parts in the positions occupied at the completion of a winding having tapered shoulders 80 at the ends thereof.

Fig. 10 is a view showing a part of the mechanism illustrated in Fig. 6 but with the parts thereof in the positions occupied at thebeginning of a warp-winding which will have one flat parts in the positions occupied when the mocha-- nism is employed to reciprocate a ring rail or traverse bar during the production of a fillingwinding.

Fig. 15 is a partial front view with certain parts omitted and other parts broken away to expose other parts which control the functioning of the mechanism during the production of a filling-winding, the several parts being shown in the positions occupied when the ring rail is at the bottom of its lowermost traverse, that is, in position to start the first layer of a filling winding.

Figure 16 is a view showing a part of the mechanism illustrated in Fig. 15 but with the parts ,thereof in the positions occupied at the completion of the first layer of a filling-winding.

Fig. 17 is a view similar to Fig. 16 but with the parts in the positions occupied at the beginning of the last layer of a filling-winding.

Fig. 18 is a view similar to Fig. 16 but with the parts in the positions occupied at the completion of the last layer of a filling-winding.

Fig. 19 is a diagram illustrating how the stroke of the reciprocating mechanism may be shortened at both ends thereof as is necessary during the production of a winding having both ends tapered.

Fig. 20 is a diagram illustrating how the stroke of the reciprocating mechanism may be shortened at one end only as is necessary during the production of a winding having one tapered end.

Fig. 21 is a diagram illustrating how the range of reciprocation may be advanced as is necessary during the production of a fillingwinding.

The reciprocating mechanism is provided with a basal which supports the other parts of the mechanism and has formed therein a reservoir 2 to contain a supply of motive liquid, such as oil.

The base is shown provided with two bearing brackets 3 and l which support a relatively long rockshaft 5 having a plurality of levers 6 fixed thereon. Each lever S is provided at its outer end with a link I the lower end of which may be connected to the ring rail or traverse bar of a textile machine (notshown).

The shaft 5, levers 6 and links I are ordinarily parts of a textile machine; and the shaft 5 is ordinarily supported independently of the reciprocating mechanism but, for the purpose of illustration, the shaft 5 is shown supported at least in part by the base I.

When the shaft 5 is rocked or rotated in opposite directions through a limited angular distance, the links 1 will be raised and loweredand thereby reciprocate or traverse the ring rail or traverse bar to which they may be connected.

The shaft 5 is rocked by a hydraulic motor 8 (Figs. 4 and 12) which has its cylinder arranged upon the base I intermediate the front and rear sides thereof and provided with a vertical bore 9 in which a piston l ciprocate therein.

The piston I II has secured thereto or formed integral therewith a piston rod II and a tail rod I2 which are equal in diameter so that the upper and lower ends of the piston have equal pressure areas. 'The piston rod ll extends upward through the end of the motor cylinder and is connected at its upper end to a crosshead I3 intermediate the ends thereof. The tail rod I2 extends through the lower end of the motor cylinder into the reservoir 2.

The crosshead I3 is arranged between and has is closely fitted to reits ends pivoted to the depending arms of a yoke H which has the lower end of each of its arms connected by a pin I to the outer end of a lever I 8 fixed upon the rockshaft 5. The crosshead l3 and the head or crossrail of the yoke I4 form a rigid truss which holds the several parts in correct alinement during operation of the motor 8. i I

When the motor 8 is .operated, it .will reciprocate the crosshead l3 and the yoke H which will oscillate the levers l6 and thereby rock the shaft 5 and cause the levers i and links I to reciprocate or traverse the ring, rail or traverse bar to which the links are connected.

Liquid for operating the motor 8 is supplied thereto by a pump I! which is shown fastened to a front plate I! secured to or formed integral with the base I and extending vertically upward from the front side. thereof.

The pump is driven by a sprocket wheel I! which is fixed upon the shaft 20 of the pump and connected by a chain 2| to a sprocket wheel 22 fixed to the shaft of an electric motor 23 c'arried by the base I.

The electric motor 23 drives the pump IT at a constant speed and, in order that variations in the load upon the pump due to opening and closing of the cylinder ports as later described may not cause sudden fluctuations in the speed thereof, a flywheel 24 may be fixed upon the pump shaft 20.

The pump 'l'l draws liquid from the reservoir 2 through a suction pipe 25 and discharges liquid into a supply pipe 2 at a rate somewhat in excess of the rate required to operate the motor 8 at the desired speed, the liquid delivered by the pump. in excess of motor requirements being discharged into the reservoir 2 through a relief valve 21 which enables the pump to keep the pressure of the liquid in supply pipe 2'5 constant.

Delivery of liquid from the pump H to the motor 8 is controlled by a follow-up valve 38 fitted in a bore 3| formed in a block 32 which is shown as being integral with the cylinder or casing of the motor 8.

The ends of the bore 3| are open at all times to the reservoir 2 to permit liquid discharged from the motor 8 to return to the reservoir 2. As shown, the upper end of the bore 3| is open to a discharge port 33 which is connected to the reservoir by a pipe 34, andthe lower end of the bore 3| communicates with the reservoir through an opening. 35 formed in the bottom of a socket 35 which is carried by the base in alinement with the bore 3 I.

The supply pipe 25 is connected to the block 32 in communication with an annular groove or port 31 which is formed in the wall of the bore 3| between two annular grooves or'ports 38 and 39 also formed therein. Two

fluid channels

48 and 4| formed in the block 32 connect the ports 38 and 39, respectively, to two

annular grooves

42 and 43 formed in the wall of' the bore 9 at the uper and lower ends thereof.

The ports 38 and 39 are controlled, respectively, by two heads-or pistons 44 and 45 which are formed upon the valve 38 and closely fitted in the bore 3| to reciprocate therein. The pistons 44 and 45 are spaced apart exactly the same distance that the ports 38 and 39 are spaced apart and each is the same width as the port which is controls.

When the valve 38 in the position shown in Fig. 4, the pistons 44 and 45 block the ports 38 and 39 and prevent any liquid from being delivered to or discharged from the bore 9 so that the piston I8 is stationary.

When the valve 38 is lowered, liquid delivered by the pump |1 into the port 31 may flow through the bore 3|, the port 39 and the passage 4| to the lower end of the bore 9 and raise the piston l8 which will discharge.liq'uid .from the upper part of bore 9 through the pasage 48, the port 38, the bore 3| the port 33 and the pipe-34 to the reservoir 2,

When the valve 38 is raisediinotive liquid may flow from the port 31 through thef bore 3|, the port 38 and the passage 48 to the upper end of the bore- 9 and move the piston |8 downward, thereby causing liquid to be exhausted from the lower end of the bore 9 through the pasage 4|, the port 39, the bore 3| and the opening 35 into the reservoir 2.

Since the pump |1 delivers liquid at a con-" In practice, the valve 38 is moved only 'a very short distance (for instance, about 3 2' of an inch) in each direction from its central position so that the liquid must flow to and from the bore 9 through restricted openings which limit the flow to the rate necessary to produce the desired motor speed. If that distance is increased or decreased, the speed of the motor will be increased or decreased accordingly.

The maximum stroke of the motor 8 is deflnitely limited by the heads which close the ends of the bore 9, and the distance between the end heads is such that a machine part reciprocated by the piston |8 can not overrun far enough to damage the machine before the piston stalls against the end head of the motor cylinder.

The motor 8 is ordinarily reversed before the piston |8 reaches the end of the bore 9 but, in order to cushion the blow should the motor not be reversed in time to prevent the piston from striking the end of the motor cylinder, the piston I8 is provided upon its upper end with a dashpot plunger 48 and upon its lower end with a dashpot plunger 41 to cooperate, respectively, with

dashpots

48 and 49 formed in the heads of the motor cylinder.

The valve 38 is urged upward by a helical compression spring 58 (Fig. 4) which has its lower end supported in the socket 35 and its upper end provided with'a washer 5| to engage the lower end of valve 38. The spring 58 urges the valve 38 upward against a plunger 52 which is fitted for reciprocation in the bore of a cylinder 53 formed on the cap of the block 32 with its bore in alinement with the bore 3|.

The plunger 52 carries at its upper end a pin 54 having rollers 55 arranged upon the ends thereof in engagement with the bearing faces of a segmental bearing block 55 (Figs. 4, and 13) which is fastened in a ring 51 formed in a'lever 58 intermediate the ends thereof. That part of the ring 51 which extends below the lever 58 is bifurcated to straddle the cylinder 53.

The-ring 51 has a slot 59 formed in the upper part thereof to permit the passage therethrough of a bolt 58 which is threaded into the bearing block 55 and clamps it against the upper inner peripheral surface of the ring 51, the head of the bolt 58 bearing against a washer. 5| which bears upon the ring 51 upon both sides of the slot 59.

As shown, the bearing faces of the bearing block 55 are arranged" at right angles to the axis of the plunger 52 when the motor is at midstroke but, by loosening the bolt 58, the bearing block 55 may be moved around the inner periphcry of the ring 51 in one direction or the other and then the bearing faces will be inclined to the axis of the plunger 52.

The lever 58 is urged upward by the action of the spring 58 but its left end is either retained in a stationary position or moved at a relatively slow speed during the production of various types of windings as will be presently explained, and its right end has a roller 52 (Figs. 1 and 2) arranged thereon in engagement with the underface of a lug 53 which is carried by a floating lever 54 and prevents the right end of the lever 58 frommoving upward except when the lug 53 is moved upward. I

The lever 54 (Figs. 1 and 2) has its left end connected to the crosshead |3 by a pair of links tically upward from the base I and secured to or formed integral with the base I and the front plate l8.

The function of thefloating lever 84 is to actuate valve 38 both in response to movements trans- 5 mitted to the right end of the lever 84 by rotation of the cam 81 and. in response to movements transmitted to the left end of the lever 84 from the piston l8 through the crosshead l3 and the links 85. The movement caused by rotation of lo the cam 61 acts to open the valve 38 and admits -motive fluid to the bore 3| at one side or the other of the piston l8. The motive fluid moves the piston ID in one direction or the other, and in each instance the piston movement transmitted to the lever 84 through the links 85 tends to close the valve 38 as fast as it is opened by To tation of the cam 81 Thus at any given instant the valve 38 can open only just enough to permit motive fluid to pass therethrough at the rate required to drive the motor 8 at the speed determined by the contour and rotary speed of the cam 81.

The cam 81 rotates continually at .a uniform speed when the mechanism is in operation. As it. rotates, it will move the right end of the lever 84 downward during one part of a revolution and permit it to be moved upward by the spring 58 during another part of a revolution, the pin 88 and the slot 89 causing the right end of the lever 84 to be reciprocated in a vertical plane.

When the cam 81 first starts to move the right end of the lever 84 downward, the left end of the lever 64 is held stationary by its connection to the crosshead I3 and the left end of the lever 58 is held stationary by its connection to strokechanging mechanism to be presently described. Consequently downward movement of the right end of the lever 84 will cause the lug 83 to depress the right end of lever 58 which, acting through the block 58,'the rollers 55, the pin 54 and the plunger 52, will depress the valve 38 and thereby open the port 39 to the pressure port 31 and open the port 38 to the exhaust port- 33.

As soon as the ports 38 and 39 are opened slightly, liquid will flow at a limited rate into the bore 8 and start the piston l8 on its up stroke. Upward movement of the piston [8 causes the 'crosshead l3 and the links 85 to raise the left end of the lever 84 and thereby tend to permit 50 the spring 58 to close the valve 38 but, since the cam 81 is rotating continuously, it moves the right end of the lever 84 steadily downward so that the lever 84 rocks upon the roller 82 and holds the valve 38 substantially stationary in its slightly open position.-

The piston I8 moves upward at a speed exactly proportional to the speed at which the right end of the lever 84 is moved downward by the cam 81. If it should move faster momentarily, the pivot point on the lug 83 would be raised and the spring 58 would raise the valve 38, thereby reducing the delivery of liquid to the bore 9 and decelerating the piston l8. If it should move slower momentarily, the lug 83 would depress 65 the right end of the lever 58 and thereby depress the valve 38 to increase the delivery of liquid to the bore 8 and accelerate the piston I8. Contions shown in Fig. 6 and the cam 81 is rotating.

When the cam 81 has opened the valve 38, the 1 piston III will move upward and raise the crosshead l3 which will raise any ring rail or traverse bar carried by the links 1 and will also raise the left end of the lever 84 as the cam 81 depresses the right end thereof.

The piston I 8 will continue to move upward and the cam 81 will continue to move the right end of the lever 84 downward until the highpoint on the cam 81 is on the pin 88 at which time the 1.

- several parts are in. the positions shown in Fig. 7

and downward movement of the pin 88 ceases.

Since the cam 81 is rotating continuously, the valve 38 and the right end of the lever 84 will move steadily upward after the high point on the 1' cam passes the pin 88. At the beginning of the upward movement of the right end of the lever 84, the piston I8 is still-raising the left end thereof. Therefore, the lever 84 is moved bodily upward until the valve 38 blocks the ports 38 and 3 38 to stop the motor 8.

Continued upward movement of the right end 'of the lever 84 permits the valve 38 to rise until the ports 38 and 38 are opened wide enough to cause the piston I8 to move downward at the desired speed. The piston l8 then moves the left end of the lever 84 downward at a'speed exactly proportional to the speed at which the cam 81 permits the right end of the lever 84 to rise so that the lever 84 simply rocks upon the roller 82 and its point of contact therewith remains stationary but in a higher plane than when the piston l8 was moving upward. h a The piston l8 moves downward and thereby moves the links 1 and the ring rail or traverse bar connected thereto downward at a speed determined by thecontour and rotative speed of the cam 81, and as previously explained it cannot vary from that speed. While the cam 81 is shown as having a contour which will cause the motor 8 to operate at the same speed in both directions, its contour may be changed to cause the motor 8 to operate at one speed in one direction and at another speed in the opposite direction as will be explained hereinafter.

The piston l8 will continue to move downward and the cam 81 will continue to permit the right end of the lever 84 to move upward until the low point on the cam 81 is on the pin 88 at which time the several parts are again in the positions shown in Fig. 6 and upward movement of the pin 88 ceases. After the'low point on the cam 81 passes the pin 88, the cam will force the right end of the lever 84 steadily downward. At the beginning of the downward movement of the right end of the lever 84, the piston I8 is still lowering the left end thereof. Therefore, the lever 84 is moved bodily downward until the valve 38 blocks the ports 38 and 39 and stops the motor. 50

Continued downward movement of the right end of the lever 84 depresses the valve 30 until the ports 38 and 38 are opened wide enough to cause the piston l8 to move upward at the desired speed as previously explained. a

The cam 81 may be rotated at a constant speed from any suitable power source. As shown, it is fixed upon a cam shaft .15 (Figs. 2 and 5) and driven through a change speed drive from the electric motor 23 which drives the pump I1. In

order that the cam 81 may be readily removed and replaced by a cam having a different contour, it is keyed upon the tapered rear end'of the shaft 15 and retained thereon by a locknut 18.

The cam shaft 15 is journaled in suitable bearings carried by a bearing bracket 11 which is supported by the front plate l8 upon the rear closely fitted ina circular opening 19 formed in the front plate I8.

The axis of the hub 18 coincides with the axis of the shaft 15 in order that the bracket 11 may be turned upon the hub 18 about the axis of the shaft 15 to adjust it upon the plate I8 and then clamped in adjusted position by means of two bolts 89 which are threaded into the front wall of the bracket and extend through slots formed in the front plate I8.

The cam shaft 15 has a gear 8| fixed thereon intermediate the ends thereof and in mesh with a pinion 82 fixed upon a shaft 83 which is journaled in suitable bearings arranged in an eccentric cylindrical bushing 84 at one side of the axis thereof.

The bushing 84 is clamped by means of a bolt 85 in a split sleeve 86 which is shown as being formed integral with a bearing 81 having an tance.

annular hub 88 formed upon its front end and closely fitted in a circular recess 89 formed in the bracket 11.

The bearing block 81 is fastened to the bracket 11 by two or more bolts 90 which extend through the flange of the bearing block 81 and are threaded into the bearing bracket 11. The flange of the bearing block 81 may be provided with a slot for each bolt 90 and the bearing bracket 11 may be provided with one or more threaded holes for each bolt 90, the slot and the threaded holes being arranged at the same distance from the axis of the hub 88. Then the bearing block 81 may be rotated upon its hub 88 through a limited angular distance by simply looseningthe bolts 90, and it may be rotated through a greater angular distance by withdrawing the bolts 98 from the threaded holes and inserting. them into other threaded holes.

The bearing block 81 has a shaft 9| arranged therein with its axis coincident with the axis of the hub 88. The shaft 9| has its inner end journaled in a bearing carried by the bearing block 81, and its outer end journaled in a bearing arranged in a tubular projection 92 which is formed upon the front of the bearing bracket 11 concentric with the recess 89 in which the hub 88 of the bearing block 81 is journaled.

The projection 92 extends through an opening 93 which is formed in the front plate I8 and is large enough to permit the bracket 11 to turn upon its hub 18 through a givenangular dis- The shaft 9| has its rear end provided with a gear 94, which meshes with a gear fixed-upon the rear end of the shaft 83, and its front end provided with a sprocket wheel 96 which is connected to a sprocket wheel 91 by a chain 98. The sprocket wheel 91 may be keyed direct to the pump shaft 28 but, in order to avoid the necessity of providing the pump 1 with a special shaft,

it is shown fixed upon a stub shaft 99 which is fastened to the hub of the sprocket wheel I9.

. When the electric motor 23 is energized, the

pump I! will be driven through the sprocket relative to the speed of the pump H, the

gears

82, 94 and 95 and the

sprocket wheels

96 and 91 are arranged upon the ends of their respective shafts. By replacing the

sprocket wheels

96 and 91 with other sprocket wheels having differ'ent ratios, the speed of the cam 61 may be varied through a wide range. After the

sprockets

96 and 91 have been changed and whenever the chain 98 should become slack, the tension of the chain 98 may be adjusted by loosening the bolts 80, turning the bearing bracket 11 upon its hub 18 until the correct tension is obtained and then tightening the bolts 80. Since the bearing bracket '11 is turned upon the axis of the shaft 15, the cam 61 remains in its permanent position, and since the

shafts

15, 83 and 9| are carried by the bracket 11, the relative positions thereof are not changed.

While the speed of the cam 61 may bevaried through a wide range by changing the

sprocket wheels

96 and 91, the difference of one tooth more or less on either sprocket wheel will make a material change in the speed of the cam 61. In order' to obtain finer graduations in speed change, the

gears

82, 94 and 95 may be replaced by gears having a different ratio.

If it is desired to replace the gear 82 with a larger or smaller gear,.the bolts 90 may be loosened or removed, the bearing block 81 turned its hub 88 until the replaced gear meshes properly with the gear 8| and then the bolts 90 tightened,

or replaced. Since the block 81 turns upon the axis of the shaft 9| and since the shaft 83 is:

. permit the gears to mesh properly, the bolt 85 may be loosened and the bushing 84 turned until the axis of the shaft 83 is spaced the correct distance from the axis of the shaft 9|.

From the foregoing it will be apparent that, by changing one or more of the gear and/or sprocket wheel ratios, the cam 61 may be rotated at almost any speed within a wide range.

The cam on the cam shaft 15 may have one or more high points formed thereon and the pitch of the cam surfaces or tracks on opposite sides of each high point may be the same or different. If the cam is provided with but one high point, as shown, the motor 8 will make one complete reciprocation each time the cam shaft 15 makes a complete revolution. If the cam is provided with more than one high point, the motor 8 will make as many complete reciprocatlons per revolution of the cam shaft 15 as there 'are high points on the cam.

the high point on the cam have the same pitch,

the motor 8 will operate at the same speed in both directions as is necessary during the production of warp-winding. If the cam surface or track on one side of the high point has a different pitch than the cam surface or track on the other side thereof, the'motor 8 will operate at one speed in one direction and at another speed in the op. posite direction as is necessary during the production of a filling-winding.

In-Figs.-1 to 11, the shaft 15 is shown provided with the cam 61 which has but one high point and similar cam tracks on opposite sides of the high point so that the motor 8 operates at the same speed in both directions and makes one complete reciprocation per revolution of the cam shaft 15. In Figs. 15 to 18, the cam shaft 15 is shown provided with a cam 61 which has four identical lobes formed thereon and so shaped that the cam surface or track I00 on one side of the high point on each lobe has a. diiferent pitch than the cam surface or track IOI on the other side thereof.

During rotation of the cam '61, the cam track I00 will ride over the pin 06 and slowly depress the right end of the lever 64, thereby opening the valve 30 wide enough to cause .the motor 8 to raise the crosshead I3 at a predetermined rate which is ordinarily the speed required to permit the spinning machine to wind the thread in tight spirals on a bobbin or other carrier.

When the high point on the lobe of the cam passes the pin 56, the right end of the lever 64 will rise and the pin 66 will travel along the cam track IOI. Since the cam track- IOI has a steeper pitch than the cam track I00, the right end of the lever 84 will rise at a rate greater than the rate at which-it was depressed by the cam track I 00, thereby opening the valve 30 more rapidly and consequently to a greater extent than it was opened during the upstroke of the piston I0 and causing the motor 8 to lower the crosshead I3 at a rate which is greater than the rate at which it was raised and which is ordinarily the rate required to permit the spinning machine to wind the thread in open spirals ona bobbin or other carrier.

The movement of the crosshead I3 upward at one speed and downward at another speed causes the ring rail or traverse bar connected to the links I to be moved upward at one speed and downward at another speed, the upward and downward speeds being such that a thread guided by the ring rail or traverse bar will be wound in tight spirals or contiguous turns during the upstroke and in open spirals during the down stroke. By providing a cam on which the cam tracks I00 and I 0| are reversed, the upward and downward speeds of the ring rail or traverse bar will be reversed. I

The mechanism thus far described will reciprocate a ring rail or traverse bar at the same speed in both directions, as is necessary during the production of a warp-winding, or at different speeds in opposite directions as is necessary during the production of a filling-winding. The distance through which the ring rail or traverse bar is reciprocated may be changed by changing the contour of the cam on the shaft 15 but, after the mechanism is adjusted, the range of reciprocation and the distance through which the ring rail or traverse bar is reciprocated or traversed will not vary regardless of the number of recipro-' In order to produce a winding in which each layerof thread overlaps and extends beyond the preceding layer, such as in a filling-winding, or a winding having both ends tapered, or a winding having one flat end and one tapered end, it is necessary to change the range of reciprocation, or to change the length of stroke, or to simultaneously change both the range of reciprocation and the length of stroke, and it is the function of the lever 58 to modify the motions transmitted from the cam 01 or 61 to the valve 30 to thereby produce those results.

The length of piston stroke is changed by moving the lever 58 bodily to the right or left at right angles to the axis of the valve 30 to thereby move the roller 62 toward or from the pin 66. That is, to shorten or lengthen the distance between the point atwhich the lever 58 contacts the lug 63 on lever 64 and the point at which the

cam

61 or 61 contacts the pin 66 on lever 64 to thereby vary the speed at which the cam first moves and later "move the roller 02 along apath substantially parallel to the axis of the valve 30 to thereby progressively move in one direction or the other the points at which the piston I0 is reversed.

In other words, the point of contact between the roller 62 and the lug 63 is moved transverse to the axis of the valve 30 to change the length of stroke of the piston I 0 and is moved substantially parallel to the axis of the valve 30 to change the range of reciprocation of the piston I0. For this purpose the lever 58 is provided at its left end with a segmental gear I01 to engage a range changing pinion I08 and near its left end with an adjustable pin I09 to engage a stroke changing cam IIO.

When the mechanism is adjusted for the production of a warp-winding, the pin I09 is in engagement with the cam IIO as shown in Figs. 2 and 6 and the gear I01 is out of mesh with the pinion I08 as shown in Fig. 2. When the mechanism is adjusted for the production of a fillingwinding, the gear I01 is in mesh with the pinion I08 as shown in Figs. 14 and 15 and the pin I09 is out of engagement with the cam IIO as shown in Fig. 14.

The pinion I08 and the cam IIO are arranged upon a control shaft III which is journaled in suitable bearings carried by a bearing bracket I I2 (Figs. 1 to 3) fixed to the block 32 in which the valve 30 and the piston I0 are arranged. The shaft III has the cam IIO keyed thereon immediately in front of the bearing bracket I I2 and the pinion I08 splined thereon in front of the cam I I0 and restrained from axial movement by a suitable set screw which, when loosened, permits the pinion I08 to be moved along the shaft III into mesh with the segmental gear I01, as shown in Fig. 14, or out of mesh therewith as shown in Figs. 2 and 3.

' In order to prevent the left end of the lever 58 from being moved vertically by the motor 8 when the pinion l08 is out of mesh with the gear I01, the pin I09 is adapted to be extended pas the cam I I0 and into a slot I I3 formed in a disk I II which is fastened to the front face of the bearing II2. As shown, the disk I I4 is fastened to the bracket II2 by a bolt II5 which is rigidly secured to or formed integral with the disk H4. The bolt II5 is ordinarily arranged upon the axis of the disk I I4 so that, by loosening the nut, the disk may be rotated upon the axis of the bolt to change the angle of the slot II3 for reasons which will be presently explained. The pin I09 is clamped by a suitable set screw either in its operative position,,as shown in Fig. 2, or in its inoperative position as shown in Fig. 14.

The pinion I08 and the pin I09 should never be in their operative positions at the same time, that is, the pinion I 08 should be moved out of mesh with the gear I01 when the pin I09 is inserted into theslot II3 and the pin I09 should be withdrawn from the slot II3 when the pinion I08 is moved into mesh with the gear I01.

The lever 58'is urged toward the left, to hold the pin I09 in contact with the cam H0 or to hold the segmental gear I01 in mesh with the pinion I08 as the case may be, by a spring I I6 which has one of its ends connected to the lever 58 and its other end connected to a lug I I1 formed upon the bearing bracket I I2 .and extending upward there from.

The control shaft III has a gear II 8 journaled thereon at the rear of the bracket I I2 between acollar II9, which is fixed to the shaftI I I, and a friction disk I which is splined upon the shaft III and urged against the gear II8 by a helical compression spring I2I arranged around the shaft between the disk I20 and a collar I22 fixed upon the shaft III at the rear end thereof.

The collars 'I I9 and I22, the disk I20, the spring I2I together with the gear II8 form a friction or slipping clutch which causes the shaft III to be rotated when the gear H8 is rotated but which permits the control shaft II I to be rotated manually to reset the cam I I0 when the gear I I8 is stationary, a hand wheel I23 or other suitable means being fastened to-the front end of the shaft III for that purpose.

Power for driving the control shaft III is ordinarily supplied from an independent source, such as an electric motor and reduction gear unit (Figs. 1 to 3)'consisting of a constant speed motor I24 and a reduction gear I25 mounted upon a pad I26 which is shown as being formed integral with the base I.

The motor and reduction gear unit has not been illustrated nor described in detail for the reason that it is a well known commercial article. It is deemed sufiicient to state that the reduction gearing I25 has a very large ratio, for instance 900:1 and enables the motor I24 to drive at a slow speed, for instance 2 R. P. M., a pinion I21 which is fixed upon the output shaft of the reduction gearing I25.

The pinion I 2I meshes with'a gear I28 fixed upon the rear end of a horizontal shaft I29 which is journaled in suitable bearings arranged in a bearing bracket I30 which is fixed upon the pad I26 and extends vertically upward therefrom. I

The shaft I29 has a gear I3I fixed thereon and in mesh with a gear I32 fixed upon the front end of a horizontal shaft I33 which is'journaled in The shaft I36 is journaled in suitable bearings carried by an eccentric bushing I38 which is clamped in adjusted position in a split bearing I39 by means of .a clamping bolt I40. By loosening the bolt I40, the bushing I38 may be rotated in the bearing I39 to change the distance between the axes of the shafts I36 and I33.

The bearing I39 is provided upon its under side with a flange I4I which is fastened by means of bolts I42 to the front face of the bearing bracket I30 at the upper end thereof and provided with an annular shoulder I43 which is fitted in a circular recess I44 formed in the front face of the bracket I30 upon the axis of" the shaft I33.

The flange MI is provided with slots for the bolts I42 each of which extends through one of the slots and is threaded into one of a series of holes formed in the front face of the bracket I30 upon an arc struck from the axis of the shaft I33. By loosening or removing the bolts I42, the bearing I39 may be swung upon the shoulder I43 to change the distance between the axis of the shaft I36 and the axis of the shaft II I, the distance between the axes of the shafts I36 and I33 remaining unchanged for the reason that the bearing I39 turns upon the axis of the shaft I33.

When the motor I24 is energized, it will drive the control shaft I II through the reduction gearing I25, pinion I21, gear I28, shaft I29, gears I3I and I32, shaft I33, gears I34 and I35, shaft I36 and gears I31 and H8, thereby rotating the cam I I0 and the pinion I08 at a speed determined by the ratios of the several pairs of intermeshing gears which are ordinarily s0 proportioned that the control shaft III is driven at a very slow speed.

The gears I26, 'I3I, I32," I34, I and I31 and the pinion I2I are arranged upon the free ends of their shafts so that any pair of gears may be readily removed and replaced by gears of a different ratio, thereby permitting the mechanism to be adjusted to vary the speed of the control shaft II I througha wide range, for instance from 1/40 R. RM. to 1/120 R. P. M.

If all of the gears rotated upon fixed centers, the number of speed changes would be limited and the speed of the control shaft I I I would be varied by distinct steps. However, by providing the shaft I36 with the above described mounting which permits the distances between its axis and the axes of the shafts I II and I33 to be varied, one or all of the gears I34, I35 and I3'I may be replaced by gears which vary but little from the replaced gears, thereby-permitting the mechanism to be so adjusted that the motor I24 will drive the control shaft III at substantially any speed within a wide range of speeds.

When the control shaft I II is stationary and the pin I09 is inserted into the slot H3 or the segmental gear I01 is in mesh with the pinion I08, the left end of the lever 58 will be held stationary and the stroke of the motor 8 will remain unchanged both as to range and length, as previous- 1y explained, and a ring rail or traverse bar connected to the links I will be reciprocated or traversed between fixed limits.

As previously explained, the lever 64 pivots upon the roller 62 as long as the cam 61 is moving the right end of the lever 64 downward or permitting .the valve spring to move it upward.

Therefore, the roller '62 corresponds to the fulcrurn-of a lever, the pin 66 corresponds to the point of application of power to thelever, and the link 65 corresponds o the load to be moved by the lever. 1

If the fulcrum of a. lever is moved relative to the point of application of power, the load will be moved through a proportionally shorter or greater distance asgraphically illustrated in Figs. 19 and 20 in which the

levers

58 and 64 are represented by single lines. moves but slightly from its central or neutral position, the rollers supported thereby are represented as being stationary.

Rotation of the cam 61 causes the pin 66 to be moved from its upper position at 66U to its lower position at 66L and, when the lever 58 is in the position shown in full lines, the lever 64 will pivot upon the roller 62 and the left end thereof will position at U. The distance between U and L represents the stroke of the motor 8 which will Since the valve 30 move from the lower position at L to its upper in which the lever 58 is shifted.

Rotation of the cam II causes the lever 58 to be shifted to the right to lengthen the stroke of the motor or to the left to shorten the stroke of the motor depending upon the position and direction of rotation of the cam IIO. As shown,

the shaft III is adapted to rotate the cam IIO in the direction of the arrow on Fig. 10, thereby permitting the spring II6 to gradually move the lever 58 toward the left, the pin I09 moving along the slot H3 in the disk II4. However, by simply reversing the cam on the shaft or by simply rotat- 2 ing it in the opposite direction, the lever 58 will" be gradually shifted to the right.

When the lever 58 has been shifted to the left, as indicated in dotted lines in Fig. 19, the roller 62 will be nearer the rollers 55 so that, when the right end of the lever 64 is moved through the same distance as formerly, the left end will move through a shorter distance or from L' to U' as indicated in dotted lines in Fig. 19. Consequently, the motor 8 will not have to move the left end of the lever 64 as far toshift the valve 30 as it did before the lever 58 was shifted toward the left. The stroke of the motor 8 is therefore shortened at each end thereof. j

As the shaft III is rotated at a very low speed, the cam IIO thereon will permit the spring II6 to move the lever 58 toward the left only at a very slow speed, thereby slowly reducing the stroke of the piston I0 at each end thereof as is necessary during the production of a, winding having both of its ends, tapered.

If it is desired to produce a winding having only one of its ends tapered, it is necessary to shorten the stroke of the piston III at only one end thereof. This may be accomplished by turning the reaction block 56 and the disk II4 until the slot H3 and the bearing surfaces on the block 56 are parallel to the axis of the lever 64 when it is at that end of the strokewhich is not to be shortened.

Assuming that the upper end only of "the winding is to be tapered so that the stroke of the motor 8 should be shortened atits upper end only, the slot I I3 and the bearingsurf aces on the reaction block 56 are arranged parallel to the line L66U as shown in Fig. 20.

When the lever 58 is in its initial position as indicated in full lines and the pin 66 is moved from 66U to 66L, the lever .64 will pivot upon the roller 62 and its left end will move from L to U which represents the initial stroke of the motor 8.

Rotation of the cam IIO willpermit the spring 'I I 6 to move the lever 58,toward the left. Engagement of the pin I09 with the slot I I3 and engagev axis of the rollers 55 and in a lower plane. Then,

when the right end of the lever 64 is moved from 66U to 66L, the lever 64 will pivot upon the roller 62- in its new position and the left end of the lever 64 will move a shorter distance upward to U as indicated in dotted lines in Fig. 20, the distance L-U representing the stroke of the motor 8 after it has been shortened.

Since the roller 62 is moved along the line L-66U, the motor 8 must move the left end of the lever 64 downward to the same point each time to shift the valve 30 and, since the roller 62 is moved nearer the vertical axis of the rollers 55, the motor 8 during each succeeding reciprocation need not raise the left end of the lever 64 as far to shift the valve 30 as it did during the preceding reciprocation.

The stroke of the motor 8 is thus shortened a winding having its upper end tapered and its lower end fiat. If it is desired to shorten the stroke at the bottom end only, it is simply necessary to'tilt the slot H3 and the reaction block 56 in the opposite direction. J

In producing a winding in which each succeeding layer of thread is offset from or extends beyond the preceding layer, such as a filling-winding, it is necessary to progressively advance the range of reciprocation or stroke of the motor piston I0 in order to progressively advance the traverse of the ring rail or traverse bar connected to the links I. That is, the limit of piston movement in both directions must be progressively advanced. in one direction while the stroke remains the same length.

If it is desired to change the range of reciprocation, the pin I09 is disengaged from the slot H3 and the cam IIO, the pinion I08 is moved into mesh with the gear I01 and the electric motor I24 is energized to thereby cause rotation of the pinion I08 which will move the gear I01 and the at the top end only as is necessary to produce left end of the lever 58 upward or downward depending upon the direction of rotation.

For the,purpose of illustration, the lever 58 is shown as being prevented from moving toward the left under. the influence of the spring 6 by the teeth of the pinion I08 meshing full depth with the teeth on the segmental gear I01 which has its teeth arranged upon a pitch line so shaped that, when the pinion I08 moves the gear I01 upward or downward and thereby causes the lever 58 to pivot upon the rollers 55, the roller 62 will be moved vertically in a substantially straight line. However, the pinion I08 may be provided with a roller and the gear I01 provided with a cam which is urged by the spring I I6 against that roller and has its contact face so shaped that upward or downward movement of the gear I01 will cause 4 62, as graphically illustrated in Fig. 21, the left end of the lever 64 will move from L to U when the roller 62 is in its initial position and the pin 66 is moved from 66U to 66L as indicated in full lines. r

When the left end of the lever 68 is swung down ward in the correct arc, the roller 62 will be moved vertically upward. Then when the pin 66 is reciprocated between 66U and 66L, the lever 64 will pivot upon the roller 62 in its new position and the left end of thhe lever 64 will reciprocate through the same distance but in a higher range or between L and U as indicated in dotted lines in Fig. 21. If the left end of the lever 58 were swung upward, the roller 62 would be'lowered and'the left end of the lever 64 would reciprocate in a lower range.

When the electric motor I24 is energized, the

control shaft III will be rotated at a very slow 2o upward but the stroke remains unchanged for speed, as previously explained. As shown, the shaft III is adapted to be rotated in the direction of the arrow on Fig. and to cause the pinion I08 to move the segmental gear I01 and the left end of the lever 58 downward to move the roller 62 slowly upward.

Since the piston of the motor 8 moves upward when the valve 30 is in its lower position and downward when the valve 30 is in its upper posi tion, and since the point of contact between the roller 62' and the lever 64 is gradually moved upward, the motor 8 during each succeeding rethe reason that the distance between the pin 66 and the roller 62 remains substantially the same and the 'right end of the lever 64 is caused to, reciprocate through a fixed distance by the cam on the shaft 15.

Since the stroke of the motor 8 remains the same length while the range of reciprocation is progressively advanced upward, it is apparent that a ring rail or traverse bar connected tothe links I will be reciprocated through a fixed distance during each reciprocation of the motor 8 and that, during each succeeding reciprocation,

the ring rail or traverse bar will not be lowered quite as far as during the preceding reciprocation and will be raised slightly farther than during the preceding reciprocation, thereby raising the range of reciprocation at the rate determined by the rate at which the control shaft I II is rotated.

Orsnarrori Assuming that the electric motor 23 is operating so that the cam .61 is rotating and the pump I! is delivering liquid at a rate in excess of the rate required to operate the motor 8 at the desired speed, that the electric motor I24 is idle so that the left end of the lever 58 is held stationary, and that the several parts in the positions shown in Figs. 1 to 6, the mechanism will operate as follows: a Asthe cam 61 rotates, it depressesthe right end of the lever 64 and thereby depresses the valve 30 to permit liquid from the pump -II to enter the lower end of the bore 9 and raise the piston Ill-which carries the c rosshead I3, the links I and 65 and the left end of the lever 64 upward with it.

Upward movement of the left end of the lever 5 64 tends to permit the spring 58 to shift the valve 38 but the cam 61 is rotating continually and moving the right end of the lever 64 downward so that the valve 38' is held in its depressed position until the high point on the cam 61 passes the pin 65 and thereby permits the spring 58 to shift the valve 30 upward at which time the right end of the lever 64 is still moving upward so that the valve 30 is shifted very rapidly."

- The valve 38 in its upper position permits liquid from the pump I I to enter the upper end of the bore 9 and lower the piston In which carries the crosshead I3, the links I and 65 and the left end of the lever 64 downward with it.

Downward movement of the left end of .the lever V '64 tends .to depress the valve 30 but the cam 61 -'continues'" to permit the right end of the lever 84 to rise until the low point on the cam passes the pin 68 and then the cam depresses the right end of the lever 64 and thereby shifts the valve 38 to its lower position to start the piston I 0 on another upward stroke.

The'motor 8 will continue to operate in this manner as long as the cam 61 is rotated and thepump I1 is operated. The stroke and speed of the motor 8, and consequently the stroke or Figs. 6 and 7 For the purpose'of illustration, let it be assumed that the links I are connected to the traverse .bar of a rayon spinning machine, that the bar is provided with a plurality of spinnerets through which rayon threads are fed from the machine, that each spinneret extends into a cup or winding form, and that, each cup is attached to and rapidly, rotated-by a spindle. A fragment of spinneret is shown at I50,'the cup is indicated by the reference numeral I5I, the spindle by the reference numeral I52 and the spindle hear-- :ing by the reference numeral I53.

Fig. 6 shows the several parts of the recipro eating mechanism in the positions occupied at the end of a down stroke and a winding just being started. Fig. 7 shows the parts in the positions occupied at the end of an up stroke and a winding just being completed.

When the reciprocating mechanism is operated as above described andthe spinning machine is in operation, the spinneret I58 will be reciprocatedvertically in the cup I5I. Near the end length of traverse and the rate of reciprocation of the down stroke of the spinneret, the thread or threads I54 being fed therethrough will come into contact with the bottom of the rapidly rotating cup I5I and be thrown outward by centrifugal force against the side wall of the cup I5I, as

shown in Fig. 6, and the rapidly revolving wall of the cup I5I will cause the thread to be wound thereon as it is fed through the'spinneret. If

several threads are fed through the spinneret simultaneously, the winding thereof in the above described manner will cause them to be twisted into a single thread.

v As the spinneret, moves upward, the thread I54 will be wound in a uniform layer of tight spirals on the wall of the cup I 5.I' and, when the spinneret next moves-downward, a' similar layer of thread will be wound upon the first layer. As the spinneret continues to reciprocate, the thread will be wound in succeeding layers until a. .wind-v ing I55 of the desiredthickness is produced, as

shown in Fig. '7. l

Since the spinneret I50 is reciprocated through a fixed distance, each layer of thread will .be the same length and the winding I54 will have fiat ends.

Figs. 10 and 11 If it is desired to produce a winding having one flat end and one tapered end, the slot I I3 and the bearing surfaces of the reaction block 56 are inclined downward toward theleft'at the correct angle, as previously explained and as shown graphically in ig. 20, and the electric motor I24