US3797219A - Spindle bolster - Google Patents

Spindle bolster Download PDF

Info

Publication number
US3797219A
US3797219A US00230603A US3797219DA US3797219A US 3797219 A US3797219 A US 3797219A US 00230603 A US00230603 A US 00230603A US 3797219D A US3797219D A US 3797219DA US 3797219 A US3797219 A US 3797219A
Authority
US
United States
Prior art keywords
bearing
footstep bearing
spring
case
footstep
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
US00230603A
Other languages
English (en)
Inventor
J Kieronski
R Johnson
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.)
Whitin Machine Works Inc
Original Assignee
Whitin Machine Works Inc
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 Whitin Machine Works Inc filed Critical Whitin Machine Works Inc
Application granted granted Critical
Publication of US3797219A publication Critical patent/US3797219A/en
Assigned to CONGRESS FINANCIAL CORPORATION reassignment CONGRESS FINANCIAL CORPORATION SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). AGAINST PATENTS & TRADEMARKS Assignors: LESCATH CORPORATION
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/08—Elastic or yielding bearings or bearing supports, for exclusively rotary movement primarily for axial load, e.g. for vertically-arranged shafts
    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01H—SPINNING OR TWISTING
    • D01H7/00—Spinning or twisting arrangements
    • D01H7/02—Spinning or twisting arrangements for imparting permanent twist
    • D01H7/04—Spindles
    • D01H7/045—Spindles provided with flexible mounting elements for damping vibration or noise, or for avoiding or reducing out-of-balance forces due to rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2340/00—Apparatus for treating textiles
    • F16C2340/18—Apparatus for spinning or twisting

Definitions

  • ABSTRACT A spindle bolster assembly of the type wherein a spindle blade is resiliently mounted in a bolster case for lateral movement of its lower end with a footstep bearing to minimize vibrational stresses.
  • the footstep bearing is resiliently biased to a centered position by a SPINDLE BOLSTER Inventors: John P. Kieronskl, Charlotte, NC;
  • the invention relates to improvements in textile spindle assemblies and in particular to apparatus of the type in which the spindle blade is resiliently mounted to minimize vibrational stresses in the blade and associated structure,
  • Textile spindles in spinning and doubling frames are operated at extremely high speeds, in the order of up to 15,000 r.p.m.
  • an unbalance of the mass of the yarn with respect to the axis of the spindle is generally unavoidable. Even a slight unbalance is a potential source of high vibrational force owing to the high rotational speed. It is generally recognized that vibrational stresses in the spindle blade and support bearings may be minimized if the spindle blade is resiliently mounted in a rigid bolster.
  • the spindle blade is mounted with its midportion journaled in a fixed radial bearing while its lower end is supported in a resiliently mounted footstep bearing.
  • the radial bearing provides a fulcrum or pivot point about which the spindle blade may oscillate laterally under the influence of centrifugal forces developed by an unbalance in the spindle. Such forces are resisted and damped by damping and centering means operating on the lower footstep bearing which is laterally displaced with the lower end of the spindle blade.
  • the invention relates to improvements in mounting of the footstep bearing in a spindle bolster wherein vibration induced lateral displacement of the footstep bearing is precisely controlled by centering spring means resiliently biasing the footstep bearing to a centered or ideal position. Besides its principal function of centering the footstep bearing and spindle blade, the
  • centering spring means vertically supports the footstep bearing and spindle blade. Additionally, the spring means functions to prevent rotation of the footstep bearing.
  • the spindle bolster includes a rigid tube in the upper end of which a radial bearing is fixed.
  • a spindle blade is journaled in this radial bearing and extends downwardly into the bolster tube to a footstep bearing.
  • the blade is both radially and axially supported for rotation in the footstep bearing.
  • a centering spring is anchored at one of its ends in a lower end wall of the bolster tube and at its other end in the footstep bearing. This arrangement permits the spring to resiliently resist lateral deflection of the footstep bearing from a centered position relative to the bolster tube.
  • FIG. 1 is a longitudinal section view of a spindle bolster assembly embodying the principles of the inventron.
  • FIG. 2 is a fragmentary sectional view illustrating details of a portion of the bolster assembly illustrated in FIG. 1 on a somewhat enlarged scale showing details of the mounting of the footstep bearing.
  • FIG. 3 is a fragmentary sectional view, similar to FIG. 2, illustrating details of another embodiment of a mounting and spring arrangement for the footstep bearing.
  • FIG. 4 is a fragmentary sectional view, similar to FIGS. 2 and 3, showing another embodiment of the spring centering means for the footstep bearing.
  • a spindle bolster assembly 10 which includes a cylindrical tubular bolster case 11. External threads 12 adjacent an upper end 13 of the case 11 along with a compatibly threaded nut (not shown) provide means for rigidly mounting the bolster tube 1 1 on a rail of a conventional spinning or doubling frame. In a known manner, the bolster assembly 10 is clamped on the rail by gripping the latter between an internally threaded flange 14 and the threaded nut. An upstanding projection 16 integral with the flange 14 supports a doffer latch 17 pivotal on a pin 18.
  • a conventional spindle blade 21 having a cylindrical portion 22 and a tapered end portion 23 is journaled in the bolster case 11 by means of an upper radial bearing 26 and a lower footstep bearing 27.
  • the upper radial bearing 26. is of the roller bearing type and is retained in a counterbore 29 in the upper end 13 of the bolster case by a press fit.
  • the outer surface of the cylindrical portion 22 of the spindle blade 21 thus forms an inner race for the rollers, designated 30, of the radial bearing 26.
  • the radial bearing may be constructed to be retained on the blade 21 for removal therewith from the bolster base 11. In this case, the fit between the bearing and the counterbore 29 is free enough to permit ready removal of the bearing with the blade 21.
  • the cylindrical portion 22 of the blade extends axially through a first cylindrical bore 31 in the case 11.
  • a damping spring 36 Positioned in this'cylindrical bore 34 is a damping spring 36 of well known construction which comprises a plurality of precisely formed helical coils having capillary like spaces 37 (FIGS. 2-4) therebetween.
  • a coil forming the outer diameter of the spring 36 engages the wall of the associated bore 34 while a coil forming the inner diameter of the spring engages an outer cylindrical surface 38 of the footstep bearing 27.
  • the coils of the damping spring 36 are capable of moving laterally or eccentrically of the bolster axis to accommodate lateral movement of the footstep bearing 27.
  • a tapered bore 41 having an included angle slightl greater than that of the tapered portion 23 of the spindle blade 21 is provided in the upper end of the footstep bearing 27 for reception therein of the blade.
  • a lower end of the tapered bore 41 there is provided a generally conical seat or bearing area 43 on which a compatibly shaped conical blade end 44 is vertically and laterally supported.
  • a radial hold 46 and an axial groove 47 on the exterior of the footstep bearing 27 provide passage for lubricating oil to the bearing seat 43.
  • a cylindrical counterbore 51 in the lower end 33 of the bolster case 11 terminates at a radial shoulder 52 adjacent the bore 34.
  • a cylindrical plug or end wall 53 is positioned in the counterbore 51 against the shoulder 52 and held in position by spin rolling an edge 54 of the case 11 against the plug.
  • a conventional elastomeric O-ring seal 56 on the plug 53 prevents leakage of oil from the interior of the case 11.
  • the footstep bearing 27 is centered with respect to a longitudinal axis defined by the bolster case 11 by means of a substantially straight resilient spring or pin 71.
  • the pin 71 is round and is centered on the axis of the bolster case 11 by mounting one of its ends 72 in a blind axial hole 73 drilled in the plug 53.
  • the pin 71 ideally, is mounted in a cylindrical tubular bushing 75.
  • the pin 71 is preferably made of a high strength material such as music wire and is knurled at each of its ends 72 and 74 to maximize the grip of surrounding material when such ends are press fitted into the plug 53 and bushing 75.
  • the footstep bearing is formed of relatively hard material such as a heat treated tool steel to provide satisfactory wear resistance against frictional contact with the spindle blade 21. It has been found that the hardness of the footstep bearing 27 may be enough to destroy the knurled edges of the pin 71 when the pin is pressed into a suitable hole in the footstep bearing. Use of a relatively softer material in the bushing 75 avoids this problem.
  • the bushing is subjected to a heavy compressive load in a blind axial bore 76 sufficient to cause the bushing 75 to be plastically deformed. Upon removal of the deforming load the residual compressive stress in the bushing will be at a maximum to insure that the pin end 74 will be permanently retained therein.
  • Spacer means in the form of a tubular cylindrical bushing 78 is dimensioned with an axial length slightly less than the axial spacing between the plug 53 and footstep bearing 27.
  • the rigid spacer 78 is provided to protect the centering spring 71 from excessive column loads which would cause it to buckle plastically such as when the spindle blade is dropped into the footstep bearing with usual force.
  • the outside diameter of the spacer 78 is substantially equal to that of the footstep bearing 27.
  • the resulting axial clearance between the spacer 78 and footstep bearing 27 normally permits the footstep bearing to shift laterally or radially with respect to the longitudinal axis of the bolster case 11 without frictional contact between the spacer and bearing.
  • the spindle i blade 21 is rotated relative to the bolster case 11 by a drive belt (not shown) engaging a whorl 81, shown in phantom, telescoped over the upper end 13 of the case 11.
  • the whorl 81 in a typical manner is fixed to the spindle blade 21 by means (not shown) above the radial bearing 26.
  • the interior of the bolster case 11 will be filled with a suitable lubricant or oil to a point approximately midway along the length of the cylindrical portion 22 of the blade 21. This oil serves both to lubricate the contacting surfaces of the blade 21 and footstep bearing 27, in particular, the bearing seat 43 and blade end 44, and to fill the spaces 37 between the coils of the spring 36.
  • the spindle blade 22 extends above the radial bearing 26 to a sheath (not shown) on which a tube may be positioned for winding yarn thereon.
  • the sheath is supported exclusively by the spindle blade 21 so that lateral forces on the sheath are resisted only by the radial bearing 26 and footstep bearing 27. Slight unbalance or eccentricity of the yarn package on the spindle creates a centrifugal force on the upper end of the spindle tending to rock or pivot the spindle blade 21 in the upper radial bearing 26.
  • the lower tapered end 23 of the blade is permitted to move laterally off the axis of the bolster case 11 in response to centrifugal forces acting on the members above the radial bearing 26.
  • lateral movement of the footstep bearing 27 is resisted and damped by viscous forces in the oil in the capillary spaces 37 between the coils of the spring 36 when such oil is displaced from the side of the spring towards which the footstep bearing 27 moves.
  • lateral movement of the footstep bearing 27 from its illustrated centered position is resisted by bending resistance of the resilient centering spring or pin 71 which continually biases the bearing to the centered position.
  • the centering pin is fixedly secured to both the plug 53 and footstep bearing 27 relative rotation between them is limited by the spring action of pin 71 in torsion. Also, because of the clearance between the footstep bearing 27 and spacer 78, the bearing has a certain amount of vertical resistance.
  • the centering spring 71 and damping spring 36 permit the footstep bearing 27 to controllably yield to dynamic vibrational forces on the spindle to thereby minimize stresses in various critical parts such as the radial bearing 26, spindle blade 21 and footstep bearing 27. Furthermore, lateral displacement of .the upper end or sheath portion of the spindle is limited to a reasonably small amplitude for maximum use of available winding space.
  • FIG. 3 there is shown a second embodiment of the invention in which the centering spring means is provided in a modified form.
  • the portion of the bolster assembly not illustrated in FIG. 3 is substantially the same as that described above with reference to FIGS. 1 and 2.
  • the bolster case and damping spring are given the previously used numeral designations l1 and 36, respectively.
  • a footstep bearing 86 includes a tapered bore section 87 and a conical bearing seat 88 substantially identical to the corresponding surfaces 41 and 43 of the first embodiment. At the opposite or lower end 89 of the footstep bearing 86 there is formed a conical recess 91 concentric with an axial hole 92.
  • Spring centering means in the form of a helical coil 96 resiliently biases the footstep bearing 86 to the illustrated centered condition in the bolster case 11.
  • the coil 96 is formed of round wire stock.
  • An axially extending tang 97 of the spring 96 is press fitted into the axial hole 92 of the footstep bearing 86.
  • An end wall or plug 98 is retained in the counterbore 51 of the bolster case 11, again, by spin rolling the edge 54 against the plug.
  • An elastomeric O-ring 99 seals the plug 98 in the bore 51 to prevent leakage from the case 11.
  • a conical recess 103 is formed in the end plug 98 concentrically with an axial hole 104 therein.
  • a tang 106 of the centering spring 96 is retained in this hole 104 with a press fit.
  • the conical recesses 91 and 103 in the bearing 86 and plug 98 facilitate assembly of the pin 71 to improve the permanency of the assembly of the spring 96, bearing 86 and plug 98.
  • a suitable bushing such as the bushing 75 illustrated in the first embodiment and a suitable bore in the bearing 86 may be provided to additionally improve the connection between the tank 97 and bearing.
  • a suitable number of coils 108 and wire diameter of the centering spring 96 a satisfactory stiffness or resilience may be provided to bias the footstep bearing to the illustrated centered position.
  • the coils 108 are wound close enough with respect to each other so that when they are subjected to an unusually high axial compressive load they abut one another to form a rigid spacer thereby limiting downward movement of the footstep bearng 86 and preventing plastic deformation of the spring 96. Under normal axial operating loads, the coils- 108 are stiff enough to remain out of contact with one another and thus avoid friction between themselves when they shift laterally with the footstep bearing 86.
  • FIG. 4 illustrates a third embodiment of the invention wherein a footstep bearing centering spring 111 is specially formed to provide desired deflection rate characteristics.
  • the centering spring 111 is formed of, preferably, round wire with a single bent portion or bend 112 at its midportion and coaxial ends 113 and 114.
  • the bent portion 112, as illustrated, lies in a plane of the drawing.
  • Each end 113 and 114 is press fitted into the associated parts 53 and 75. As discussed and illustrated in FIGS. 1 and 2, these ends 113 and 114 may be knurled to improve the permanency of the assembly of the parts.
  • the convoluted configuration of the spring 111 results in a spring or deflection rate somewhat less than that which results from a straight pin of the same diameter, such as that shownin F IGS. 1 and 2.
  • the tubular spacer 78 is dimensioned to limit axial movement of the footstep bearing 27 towards the end plug 53 to prevent plastic deformation of the spring
  • the centering springs 71, 76, and 111 being securely anchored to the associated end wall or plug 53 or 98, and footstep bearing 27 or 86, prevent rotation of the footstep bearing relative to the end wall.
  • centering springs 71, 96 and 111 prevent their associated footstep bearings from being pulled upwardly out of the damping spring 36 in such cases as when a suction is formed on a bearing surface 43 or 87 upon removal of the spindle blade .21.
  • a textile spindle assembly including a tubular cylindrical bolster case having an open upper end and an end wall closing its lower end, means on the exterior of the case for mounting it to a rail, a radial spindle bearing supported on the case adjacent said open upper end, a footstep bearing axially spaced from said radial bearing in the case, an elongated damping coil spring in said case having its lower end adjacent to said case end wall and its upper end below said radial bearing, an outer coil of said damping spring engaging the inner wall of the case, said footstep bearing being laterally supported in and in engagement with the inner coil of the damping spring, a lower end of said footstep bearing being axially spaced in said damping spring from, said end wall and an upper end of said footstep bearing terminating within said damping spring, a footstep bearing locating spring in said damping coil below said footstep bearing, said locating spring rigidly engaging the lower portion of said footstep bearing atone of its ends and rigidly engaging the case end wall at the other of its ends, the rigid engagement of

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • Support Of The Bearing (AREA)
US00230603A 1972-03-01 1972-03-01 Spindle bolster Expired - Lifetime US3797219A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US23060372A 1972-03-01 1972-03-01

Publications (1)

Publication Number Publication Date
US3797219A true US3797219A (en) 1974-03-19

Family

ID=22865851

Family Applications (1)

Application Number Title Priority Date Filing Date
US00230603A Expired - Lifetime US3797219A (en) 1972-03-01 1972-03-01 Spindle bolster

Country Status (6)

Country Link
US (1) US3797219A (enrdf_load_stackoverflow)
JP (1) JPS5617450B2 (enrdf_load_stackoverflow)
CH (1) CH558893A (enrdf_load_stackoverflow)
DE (1) DE2310323A1 (enrdf_load_stackoverflow)
GB (1) GB1349634A (enrdf_load_stackoverflow)
IT (1) IT977932B (enrdf_load_stackoverflow)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3945187A (en) * 1973-07-16 1976-03-23 Spindel-,Motoren- Und Maschinenfabrik A.G. Textile spindle
US4452540A (en) * 1981-05-05 1984-06-05 Rivoir Karl Heinz Bearing assembly for the movable member of a measuring instrument
US5528892A (en) * 1993-07-28 1996-06-25 Gebruder Loepfe Ag Flexible textile spindle assembly
US6612625B1 (en) * 2000-09-11 2003-09-02 Genesis Technical Marketing, Inc. Case locking system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2664620A1 (fr) * 1990-07-12 1992-01-17 Schlumberger Cie N Dispositif de montage des broches de continus a filer sur le banc porte-broches.

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US279674A (en) * 1883-06-19 Joseph e
US410974A (en) * 1889-09-10 Support for spinning-spindles
US549727A (en) * 1895-11-12 Henry d
GB190501075A (en) * 1905-01-19 1905-06-29 James Charles Potter Improvements in and relating to Spinning Spindles.
US2650465A (en) * 1950-06-23 1953-09-01 Tmm Research Ltd Mounting for spindles
US2680659A (en) * 1952-02-08 1954-06-08 Skf Ind Inc Spinning spindle
US3065593A (en) * 1959-12-10 1962-11-27 Tmm Research Ltd Spindles for textile spinning and like machines
US3100375A (en) * 1961-09-23 1963-08-13 Bourgeas Pierre Spindle-holder
GB952177A (en) * 1959-05-06 1964-03-11 Skf Kugellagerfabriken Gmbh Improvements in or relating to spindle mountings for textile spinning and doubling frames
US3298757A (en) * 1963-10-25 1967-01-17 Skf Kugellagerfabriken Gmbh Spindle bearing arrangement for a textile machine

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US279674A (en) * 1883-06-19 Joseph e
US410974A (en) * 1889-09-10 Support for spinning-spindles
US549727A (en) * 1895-11-12 Henry d
GB190501075A (en) * 1905-01-19 1905-06-29 James Charles Potter Improvements in and relating to Spinning Spindles.
US2650465A (en) * 1950-06-23 1953-09-01 Tmm Research Ltd Mounting for spindles
US2680659A (en) * 1952-02-08 1954-06-08 Skf Ind Inc Spinning spindle
GB952177A (en) * 1959-05-06 1964-03-11 Skf Kugellagerfabriken Gmbh Improvements in or relating to spindle mountings for textile spinning and doubling frames
US3065593A (en) * 1959-12-10 1962-11-27 Tmm Research Ltd Spindles for textile spinning and like machines
US3100375A (en) * 1961-09-23 1963-08-13 Bourgeas Pierre Spindle-holder
US3298757A (en) * 1963-10-25 1967-01-17 Skf Kugellagerfabriken Gmbh Spindle bearing arrangement for a textile machine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3945187A (en) * 1973-07-16 1976-03-23 Spindel-,Motoren- Und Maschinenfabrik A.G. Textile spindle
US4452540A (en) * 1981-05-05 1984-06-05 Rivoir Karl Heinz Bearing assembly for the movable member of a measuring instrument
US5528892A (en) * 1993-07-28 1996-06-25 Gebruder Loepfe Ag Flexible textile spindle assembly
US6612625B1 (en) * 2000-09-11 2003-09-02 Genesis Technical Marketing, Inc. Case locking system

Also Published As

Publication number Publication date
IT977932B (it) 1974-09-20
JPS5617450B2 (enrdf_load_stackoverflow) 1981-04-22
JPS4898131A (enrdf_load_stackoverflow) 1973-12-13
DE2310323A1 (de) 1973-09-13
CH558893A (de) 1975-02-14
GB1349634A (en) 1974-04-10

Similar Documents

Publication Publication Date Title
JPH0151682B2 (enrdf_load_stackoverflow)
US3797219A (en) Spindle bolster
US2771635A (en) Apparatus for stretching filaments
US2479168A (en) Textile spindle
US2699033A (en) Textile spindle
DE2411236B2 (de) Abstützung von an zwei Stellen wälzgelagerten Spinn- und Zwirnspindeln, insbesondere Offen-End-Spinn-Rotoren
US2698772A (en) Twister mounting
US2625336A (en) Textile spindle
US4674272A (en) Device for radially movably mounting a spinning or twisting spindle
CN1075991A (zh) 钢领旋转装置
US2576124A (en) Double twist spindle
US3510181A (en) Spindle bearing for a spinning or twisting machine
JPS585291B2 (ja) セイボウ ナラビニ ネンシスピンドル
US3782660A (en) Textile spindle
US2486730A (en) Textile spinning and twisting spindle
US5182901A (en) Spinning or twisting spindle arrangement
US3306543A (en) Yarn carrier mounting device
US3546871A (en) Damped support for double twist spindle
US2909027A (en) Textile spindle
US892480A (en) Spinning and twisting spindle.
US2798775A (en) Textile spindle
US2095901A (en) Spinning or twisting spindle
US4809491A (en) Plastic traveler for spinning rings, twisting rings and the like
US3491529A (en) Textile spinning spindle assembly
US467649A (en) Spindle-bearing for spinning-machines

Legal Events

Date Code Title Description
AS Assignment

Owner name: CONGRESS FINANCIAL CORPORATION

Free format text: SECURITY INTEREST;ASSIGNOR:LESCATH CORPORATION;REEL/FRAME:004087/0502

Effective date: 19830103