US3186242A - Driving mechanism of circular knitting machines - Google Patents

Driving mechanism of circular knitting machines Download PDF

Info

Publication number
US3186242A
US3186242A US229455A US22945562A US3186242A US 3186242 A US3186242 A US 3186242A US 229455 A US229455 A US 229455A US 22945562 A US22945562 A US 22945562A US 3186242 A US3186242 A US 3186242A
Authority
US
United States
Prior art keywords
shaft
pinion
gear
clutch
oscillatory
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US229455A
Other languages
English (en)
Inventor
Frederick E Deans
Carlyle H Wainwright
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bentley Engineering Co Ltd
Original Assignee
Bentley Engineering Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bentley Engineering Co Ltd filed Critical Bentley Engineering Co Ltd
Application granted granted Critical
Publication of US3186242A publication Critical patent/US3186242A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • D—TEXTILES; PAPER
    • D04—BRAIDING; LACE-MAKING; KNITTING; TRIMMINGS; NON-WOVEN FABRICS
    • D04B—KNITTING
    • D04B15/00—Details of, or auxiliary devices incorporated in, weft knitting machines, restricted to machines of this kind
    • D04B15/94—Driving-gear not otherwise provided for
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18416—Rotary to alternating rotary
    • Y10T74/18488—Oscillating rack connections
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2107—Follower

Definitions

  • the knitting motion is required to be performed sometimes as a continuous rotary motion and at other times as a reciprocatory or oscillatory motion with alternating swings in opposite directions, as for example in knitting heel and toe pouches. It is usual in forming heel and toe pouches of hose for relative oscillation to be caused to take place between the needle cylinder and the cam box in such manner that knitting will take place on one group of needles usually extending around approximately one half of the needle circle, while the remaining needles hold their loops.
  • Such reciprocatory knitting is necessarily slow compared with continuous rotary knitting and imposes a substantial limitation on the' rate of overall output of a machine.
  • the change from rotary movement to oscillating movement is normally effected by means of a clutch interposed in the drive of-the cylinder or cam box enabling the drive to be taken alternatively from a shaft which is driven continuously in the same direction or from a rack and pinion drive usually provided by an oscillating gear or quadrant engaging a driven pinion.
  • the oscillating gear is caused to move to and fro continuously during the operation of the machine and the usual manner of driving it is by a crank and connecting rod.
  • This manner of driving a quadrant does not permit attainment of thehighest possible efiiciency because it is inherent in a crank motion that the movement transmitted through, the connecting rod only attains maximum speed for a very short proportion of the cycle, the remaining portions of the quadrant movement being occupied by periods of acceleration and deceleration.
  • a circular knitting machine, driving meansfor performing reciprocatory knitting comprising an oscillatory gear, two complementary cams for oscillating said gear, and cam 3,136,242 Patented June 1, 1965 followers co-operating respectively with said cams and coupled to the oscillatory gear at positions which are in balanced arrangement in relation to the central plane of the oscillatory gear.
  • the two complementary cams have their cam tracks so formed as to provide the required short periods of acceleration and deceleration with a lengthened period of maximum speed movement between them and to operate the oscillating gear in its opposite directions of movement respectively.
  • the cams are edge cams.
  • FIGURE 1 is a perspective View from the rear, showing part of the'driving mechanism of a circular knitting machine,with certain parts broken away;
  • FIGURE 2 is a back view of part of the frame of the machine showing in detail an oscillatory quadrant and its mating pinion and the quadrant cams carried on the main cam shaft of the machine;
  • FIGURE 3 is a cross sectional view showing the quadrant and quadrant cams and cam followers taken on the line III-III of FIGURE 2;
  • FIGURE 4 is a view showing in detail the means for adjusting one of the followers to remove play
  • FIGURE 5 is a view showing a means for timing the quadrant cams with respect to the cam shaft gear in order to obtain alignment of the clutch dogs;
  • FIGURE 5 is a side elevation view of the parts shown in FIGURE 5;
  • FIGURE 7 shows graphically the rate of travel of a cam driven quadrant as in comparison with the rate of travel of a crank driven quadrant.
  • FIGURE 1 shows the driving gearing for use on a circular knitting machine having a rotary needle cylinder or two rotary co-axial needle cylinders.
  • the needle cylinder, or each needle cylinder is gear driven from a vertical shaft which in turnis driven by a bevel gear 8 carried on a horizontal shaft 9 which is mounted in bearings in the walls of a frame 4 (FIG. 2).
  • pinions 1t Freely mounted on the shaft are two pinions 1t) and 11 each of which has clutch dogs respectively shown at 12 and 13 formed on one face, with such dogs projecting towards one another; Between the two pinions is mounted a clutch body 7 having dogs 14 and 15 formed on oppositely directed end faces.
  • the clutch body is mounted on splines formed locally on the shaft so that it can be slid along the shaft to engage either of the clutch dogs of the pinions thus coupling the shaft to one or the other of the pinions 10, 11.
  • FIGURES l and 2 show the clutch body 7 in engagement with the pinion 11 which is meshed with pinion 16 (FIG. 1) fixed to a lay shaft 17.
  • Lay shaft 17 (shown broken in FIG. 1) is driven .by any one of three speed change gears 18, 19 or'Zil which mate respectively with three gears 21, 22. and 23 mounted on a pulley shaft 24.
  • the quadrant 29 is of open construction allowing it to straddle a cam shaft 31. It is firmly secured to the shaft 30, the ends of which are located in bearings in the walls of a frame 4. This construction, by spacing the two bearings far apart, ensures a minimum of play in the quadrant.
  • cams 32 and 33 are fixed together and secured to revolve with the shaft 31.
  • spindles carrying respectively cam followers 34- and 35 which follow the peripheries of cams 3?. and 33 respectively.
  • cam followers 34 will be moved in a counter clockwise direction by the slope 32a of the cam 32 thus driving the quadrant 29 in a counterclockwise direction about the axis of the shaft 30.
  • a counterclockwise movement of the quadrant will continue until the peak of the cam 32 is past the followers 34 and then the cam 33 will take over the drive, the slope 33a moving the follower 35 and the quadrant in a clockwise direction.
  • Cam follower 35 is adjustable as shown in detail in FIGURE 4 so that any discrepancies in manufacture of the various components which could result in play between the cams and followers can be counteracted.
  • the spindle of follower 35 is provided with fiats which locate in a slotted hole in the quadrant and a screw 44 is positioned to bear onto the spindle to adjust its position in the slot. Screw 44 is adjusted until the follower 35 is contacting cam 33 while the follower 34 is also in contact with cam 32. The nut 45 on the spindle is then tightened to lock the spindle to the quadrant (FIG. 3).
  • the cam shaft 31 has a spline formed locally, upon which a gear 3? is mounted and this gear is driven through an intermediate gear by a gear which is fixed to the lay shaft 17. As explained earlier the lay shaft 17 is driven through the three speed change gears and is revolving constantly whether the cylinders are rotating or oscillating.
  • the cams 32 and 33 are located with respect to one another by means of a stud or pin 36 the said cams being locked together between the shoulder of the stud and the nut 3'7, with a spacer 38 between them.
  • the shaft 31 is shouldered and the cam assembly is pushed up to this shoulder.
  • the end of shaft 31 is splined to be driven by the gear 39 which is mounted adjacent to the cam assembly.
  • Gear 39 has a block 40 fixed to it in a position where it straddles the stud 36 protruding from the cams.
  • the block carries two screws 41 and 42 which contact the stud 36 on opposite sides and by adjusting these screws the cams may be rotated to a limited extent with respect to the gear.
  • FIG- URE 2 also shows a cam 44 used for other purposes, which may be plined to the shaft and locked between the inner race and the nut washer 43.
  • the illustrated construction provides aquadrant and quadrant drive mechanism which is compact, with the forces contained in the plane of motion, the cams and followers being located within the side walls of the quadrant body.
  • the improved efiiciency obtained from this form of construction with suitably designed cams can readily be seen in comparison with that of a quadrant driven by a crank through a connecting rod, by reference to FIG. 7.
  • the horizontal scale indicates of turning movement of the cam or crank and the vertical scale shows the rates of travel of quadrants driven by the two methods.
  • Line B denotes the rate of travel by the crank method and line A by the cam method, with the crank and cam shafts revolving at the same speed
  • a driving mechanism for performing reciprocatory knitting on circular knitting machines comprising an oscillatory gear of hollow form, a shaft on which said oscillatory gear is mounted, a rotatable cam shaft disposed through the hollow form of said oscillatory gear, two complementary cams for oscillating the oscillatory gear in opposite directions mounted thereon within the hollow form, two cam followers cooperative with their respective cams coupled to said oscillatory gear, mounting means supporting the shafts of said oscillatory gear and cams, a first pinion in mesh with said oscillatory gear having a clutch dog on one face, a supported shaft passing through said pinion and clutch dog, a bevel gear attached to one end of said shaft, 21 second pinion attached to the other end of said shaft and having a clutch dog on one face, a clutch body disposed between said clutch dogs on said shaft and movable to engage one of said clutch dogs, speed change gears, a supported lay shaft on which said speed change gears are mounted, a third pinion mounted on said lay shaft in mesh with said second pinion, drive means connected to said speed change
  • a driving mechanism according to claim 1 wherein said cam followers are at balanced positions in relation to the central plane of said oscillatory gear, and further wherein the two complementary cams have their cam track-s formed to provide short periods of acceleration and deceleration with a longer period of maximum speed movement between said short periods, and are mounted to operate the oscillatory gear in its opposite directions of movement respectively.
  • a driving mechanism according to claim 1 wherein the mounting means for said cam fol-lowers provides facility for accurate adjustment of the cams about the shaft for timing engagement of the clutch body with the clutch dogs on the two pinions.
  • said mounting means includes a block formed with an elongated aperture, a stud engaging in the aperture in said block, adjusting screws for fixing the stud in adjusted position in the elongated aperture, and means connecting the block and stud one to the driving wheel and the other to the cams.
  • Driving mechanism further comprising mounting means for one of the followers wherein it is adjustable on the oscillatory gear in a direction transversely of a line joining the follower to the pivotal axis of the oscillatory gear.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Knitting Machines (AREA)
US229455A 1961-10-11 1962-10-09 Driving mechanism of circular knitting machines Expired - Lifetime US3186242A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB36496/61A GB1040021A (en) 1961-10-11 1961-10-11 Improvements in or relating to driving mechanism of circular knitting machines

Publications (1)

Publication Number Publication Date
US3186242A true US3186242A (en) 1965-06-01

Family

ID=10388697

Family Applications (1)

Application Number Title Priority Date Filing Date
US229455A Expired - Lifetime US3186242A (en) 1961-10-11 1962-10-09 Driving mechanism of circular knitting machines

Country Status (3)

Country Link
US (1) US3186242A (de)
DE (1) DE1291845B (de)
GB (1) GB1040021A (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3841626A (en) * 1973-03-01 1974-10-15 Miller Printing Machinery Co Sheet feeding apparatus
US5666853A (en) * 1995-09-11 1997-09-16 Doboy Packaging Machinery, Inc. Dual configuration epicycle drive

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3844140A (en) * 1973-02-08 1974-10-29 F Lonati Device for increasing the average angular velocity of the cylinders of circular hosiery
IT1206414B (it) * 1977-12-16 1989-04-21 Chietti Giovanni Macchina circolare da calze e simili con mezzi di comando del programma semplificati

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US651828A (en) * 1899-11-06 1900-06-19 Alexander W Copland Mechanical movement.
US1118411A (en) * 1913-05-28 1914-11-24 Josef Granz Mechanism for the transmission of movements.
US1254617A (en) * 1916-05-09 1918-01-22 J F Westbrook Power-transmitting device.
US2103825A (en) * 1936-12-21 1937-12-28 Crompton & Knowles Loom Works Needle motion for axminster looms

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1288594A (en) * 1918-03-05 1918-12-24 Standard Machine Co Circular-kniting machine.
DE884542C (de) * 1951-04-10 1953-07-27 Werner Dr-Ing Wenzel Verstellbar gelagerte Haupt- und Nebenrolle des Schwinghebels bei Wirkmaschinen

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US651828A (en) * 1899-11-06 1900-06-19 Alexander W Copland Mechanical movement.
US1118411A (en) * 1913-05-28 1914-11-24 Josef Granz Mechanism for the transmission of movements.
US1254617A (en) * 1916-05-09 1918-01-22 J F Westbrook Power-transmitting device.
US2103825A (en) * 1936-12-21 1937-12-28 Crompton & Knowles Loom Works Needle motion for axminster looms

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3841626A (en) * 1973-03-01 1974-10-15 Miller Printing Machinery Co Sheet feeding apparatus
US5666853A (en) * 1995-09-11 1997-09-16 Doboy Packaging Machinery, Inc. Dual configuration epicycle drive

Also Published As

Publication number Publication date
GB1040021A (en) 1966-08-24
DE1291845B (de) 1969-04-03

Similar Documents

Publication Publication Date Title
US2662417A (en) Speed change gearing
US3516267A (en) Mechanism for transforming a unidirectional rotary motion into an oscillating motion
US3186242A (en) Driving mechanism of circular knitting machines
US2449852A (en) Gear drive for printing and other machines
US2748616A (en) Drive mechanism for textile combing machines
US2520688A (en) Ink roller vibrating means
US2106434A (en) Knitting machinery
US3785212A (en) Motion altering apparatus
US2130979A (en) Pattern wheel drive for warp knitting machines
US2482722A (en) Mechanism for producing intermittent rotary motion
US2844014A (en) Drive transmission in circular hosiery and knitting machines with compensation of the wear in the gear teeth
US2482811A (en) Motion for warp knitting machines
US2366462A (en) Cloth take-up
GB976016A (en) Improvements relating to epicyclic gearing
CN208758819U (zh) 一种激光蚀刻机的传送机构
US2582164A (en) Sheetsxsheet i
US2934977A (en) Indexing mechanism
US1271207A (en) Variable reversible shaft-drive.
US2445223A (en) Intermittent cam
US2477105A (en) Index mechanism
US2301642A (en) Mechanical movement
GB1212475A (en) A cam-controlled variable amplitude rotary oscillation mechanism
US2514350A (en) Pianta
US1530920A (en) Means for transmitting varying rotary motion
US1463408A (en) Speed-changing mechanism