EP0636718A1 - Broche textile - Google Patents

Broche textile Download PDF

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Publication number
EP0636718A1
EP0636718A1 EP94109596A EP94109596A EP0636718A1 EP 0636718 A1 EP0636718 A1 EP 0636718A1 EP 94109596 A EP94109596 A EP 94109596A EP 94109596 A EP94109596 A EP 94109596A EP 0636718 A1 EP0636718 A1 EP 0636718A1
Authority
EP
European Patent Office
Prior art keywords
spindle
bearing
textile
joint
shaft
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.)
Withdrawn
Application number
EP94109596A
Other languages
German (de)
English (en)
Inventor
Thomas Pesek
Helmut Speiser
Kurt Janser
Hans-Peter Förstner
Klaus Gunter Dürr
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.)
Loepfe AG Gebrueder
Original Assignee
Loepfe AG Gebrueder
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 Loepfe AG Gebrueder filed Critical Loepfe AG Gebrueder
Publication of EP0636718A1 publication Critical patent/EP0636718A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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

Definitions

  • the invention relates to a textile spindle according to the preamble of claim 1.
  • Such a textile spindle is already known from EP-A1-0 209 799, which allows an unbalance compensation by approximation of the actual main mass inertia axis to the axis of rotation of the spindle bearing over two degrees of freedom of the spindle shaft.
  • the spindle shaft the shaft of which is rotatably supported in a spindle bearing housing via a neck bearing and a foot bearing, is able to execute a wobbling movement around the neck bearing against the action of a damping device arranged inside the spindle bearing housing.
  • the spindle bearing housing is in turn connected at a distance from the spindle bench via a mounting sleeve to the one end of axially parallel bending spring bars distributed over its circumference, the opposite ends of which are anchored to the spindle bench via a further mounting sleeve.
  • the whorl is arranged on the spindle shaft in the area of the neck bearing.
  • the spindle shaft with the upper part carrying the yarn spool can tip over the neck bearing to the extent of its ability to tumble against the action of the damping device.
  • the mutually parallel bending spring rods of the same length form, together with the mounting sleeves, a spatially formed, parallelogram-like connection, the imaginary pairs of joints of which each lie in one of two axially spaced radial planes, that run parallel to the spindle bench.
  • the spindle bearing housing can thus only be moved practically in the sense of a parallel displacement in the radial direction, counter to the spring tension of the spiral spring bars.
  • the belt tensile force acts as a result of the whorl arrangement in the area of the neck bearing, an inclined position of the spindle shaft or its upper part carrying the spool is thus avoided; the spindle bearing housing executes the radial movements at right angles to the spindle bank.
  • the spindle bearing housing In order to compensate for unbalance when rotating the spindle, the spindle bearing housing, in the position displaced parallel from the neutral position, carries out a translatory torsional vibration movement together with the associated mounting sleeve.
  • the spindle bearing housing alone represents a relatively large mass. In the supercritical speed range, the inertia hinders the dynamic mobility in the radial direction of the spindle shaft. This is accompanied by an increase in the undesirable bearing reaction forces between the spindle shaft and the neck bearing and the foot bearing. This leads to premature wear of the bearings mentioned.
  • the object of the invention is to provide a textile spindle in which, while reducing the reaction forces in the bearings and by reducing the stress on the bending-elastic elements involved, the design and material and production costs can be reduced and the range of application can thus be expanded.
  • the solution is based on the knowledge that the bearing reaction forces can be most effectively achieved by reducing the mass involved in the vibrations.
  • the flexurally elastic configuration of the shaft of the spindle shaft between the neck bearing and the foot bearing has an effect, which allows a spring-elastic shaft bearing element and therefore its resonating mass to be avoided.
  • the arrangement according to the invention of the tilting joint at a distance from the neck bearing which enables the radial deflection of the spindle shaft in the neck bearing area, only a reduced part of the total mass resonates and is therefore effective for the inertia of interest here.
  • the whorl is arranged on the spindle shaft below the neck bearing.
  • the deformation of the two resilient elements, i.e. of the shaft part of the spindle shaft and of the tilt joint lead to opposite, practically compensating deflections in relation to the upper part of the spindle shaft.
  • the deflection resulting from the tilting of the bearing sleeve causes the spindle shaft to be inclined approximately in a direction corresponding to the belt force, during which the deflection of the shaft part of the spindle shaft results in the deflection of the upper part thereof in the opposite direction.
  • the upper part of the spindle shaft assumes an almost vertical position with respect to the spindle bank.
  • the tilting joint is distanced from the neck bearing approximately by the length of the shaft part of the spindle shaft, so that the extent of the elastic deformation in the tilting joint can be kept small for a given radial movement of the neck bearing from the neutral position.
  • the neutral position of a bearing axis is denoted by 1, which also corresponds to the neutral position of the spindle shaft 2 represented by its axis.
  • the axis 1 is cut by the imaginary articulation axis 3 of a flexurally flexible tilting joint that leads in a horizontal plane.
  • the tilting joint which is actually rigidly connected to the spindle bank, is shown at 9 at one end as being held stationary, while at its other end the lower end of a bearing sleeve 4 is connected.
  • a (elastically shown) flexurally elastic shaft part 2a 'of the spindle shaft 2 is rotatably mounted in a neck bearing 5 and a foot bearing 6 shown coincident with the articulation axis 3.
  • the tensile force F (corresponding to the direction of the arrow) of a drive belt indicated as attacking at 8 acts on a whorl 4 seated on the spindle shaft 2.
  • the bearing sleeve 4 under the action of the tensile force F , has assumed a position pivoted by an angle 1 with respect to the bearing axis 1.
  • the location of the attack 8 of the tensile force F on the whorl at a distance h below the neck bearing 5 has caused a bending moment F * h on the shaft part 2a.
  • the textile spindle shown physically in FIG. 2 comprises a tubular spindle housing 10 which is provided with an external thread 12 for rigid attachment in a bore in the spindle bench (not shown).
  • a thin-walled intermediate tube 20 forming the bearing sleeve.
  • a cup-shaped head piece 42 rigidly attached in the lower end 22 of the intermediate tube 20 in the lower end 22 of the intermediate tube 20 in the lower end 22 of the intermediate tube 20 in the lower end 22 of the intermediate tube 20 is a press fit 24 a cup-shaped head piece 42 rigidly attached.
  • the head piece 42 forms part of a single-axis tilt joint, generally designated 40, which comprises a web 44 and a foot piece 46.
  • the rocker joint 40 takes with its web 44 a position coaxial to the longitudinal axis 16 of the housing a.
  • the foot 46 is pressed into the lower end 18 of the spindle housing 10.
  • the tilting joint 40 is made in one piece and consists of steel, which is made flexible in the area of the web 44 by reducing the cross-section.
  • a bearing bush 62 receiving a neck bearing 60 is pressed into the upper end 26 of the intermediate tube 20.
  • the neck bearing 60 rotatably receives a spindle shaft 50, which will be described in more detail below and which carries a belt-driven whorl 30 and a yarn spool (not shown) on an upper part (not shown).
  • the whorl 30, which is connected to the spindle shaft 50 in a rotationally rigid manner, is arranged below the neck bearing 60, i.e. with respect to the latter axially offset in the direction of the tilt joint 40.
  • the shaft part 52 of the spindle shaft 50 which extends in the interior of the intermediate tube 20 below the neck bearing 60 is designed to be flexurally elastic by appropriate tapering.
  • a foot bearing 64 designed as a sliding bearing which is arranged in the cup-shaped head piece 42, receives an end piece 54 of the shaft part 52, the spherically shaped end face 56 of which rests on a sliding plate 66 acting as an axial bearing.
  • a pin 68 inserted into the head piece 42 supports the sliding plate 66 and therefore the entire spindle shaft 50 in the intermediate tube 20.
  • the neck bearing 60 is a known radial roller bearing equipped with a circular clearance between the shaft and bearing rollers.
  • the foot bearing 64 has sufficient bearing play to allow misalignments between the shaft part axis - resulting from the deflection - and the bearing axis. The latter coincides with the housing axis 16 if the intermediate tube does not fail the vertical position shown is deflected.
  • the flexurally elastic shaft part 52 is surrounded by a damping device 70 provided in the intermediate tube 20 approximately in the region of the greatest deflection.
  • the damping device 70 has a guide bush 72 designed as a slide bearing, a thin-walled spring sleeve 74 and a damping element 76 designed as a spiral spring.
  • the guide bush 72 which receives the part 52 of the spindle shaft 50, is pressed into the spring sleeve 74 and transmits to it the forces exerted on the former.
  • the spring sleeve 74 is arranged in the damping element 76 and secured by end widenings 78.
  • the former distributes the forces absorbed over the length of the damping element 76, which is supported on the inside 28 of the intermediate tube 20. In the axial direction, the damping element 76 is held between a thin-walled spacer sleeve 80 standing on the head piece 42 and the bearing sleeve 62.
  • At least the cup-shaped head piece 42 contains an oil bath for bearing lubrication, but this can also completely or partially fill the intermediate pipe 20, so that the damping device 70 is also located therein. Accordingly, a sealing ring 49 cooperating with the intermediate tube 20 is provided in a circumferential groove 48 provided in the head piece 42 in order to prevent oil from flowing out.
  • the intermediate tube 20 in the spindle housing 10 can deflect by the radial play indicated at 19, or tip out of the housing axis 16, specifically by the lower end thereof adjoining tilt joint 40.
  • the stresses occurring in the web 44 are small due to the axial distance from the neck bearing 60.
  • the tilt joint Since the radial deflection of the intermediate tube or bearing sleeve 20 can take place with its parts by tipping over the tilt joint, only a fraction of the mass involved is also oscillating; the lower end of the bearing sleeve, which itself is low in mass, remains practically stationary in this regard. Due to the distance to the neck bearing and the corresponding leverage, the tilt joint is subject to low stresses. Thus, there are no high requirements to be met with regard to material and processing, in particular surface quality, and the tilting joint can be produced inexpensively. Due to the flexible design of the shaft part of the shaft itself, the deflection of the upper part of the spindle shaft around the neck bearing is realized in a simple and low-mass manner.
  • FIG. 3 corresponds completely to that according to FIG. 1 with regard to the design and mounting of the spindle shaft 50, the same parts bearing the same reference numerals. However, this differs mainly in that a tilt joint 140 is provided as part of an intermediate tube 120. An independent, cup-shaped bearing element 132 is pressed into a lower end part 122 of the intermediate tube 120, which is distanced from the neck bearing and thus from the spindle bank and which replaces the head piece 42 according to FIG. 1 with regard to its function as a bearing holder.
  • the tilting joint 140 comprises, in addition to the part 122, a tubular section 144 which is designed as a bellows and is thus designed to be flexible, and a tubular foot part 146 this foot part 146 in turn is rigidly fixed, in that it has a larger diameter than the part 122 and is pressed into the lower end 18.
  • the exemplary embodiment according to FIG. 3 has no differences from that according to FIG. 2.
  • the tilt joint 140 is designed as a spring-elastic element.
  • the spring-elastic element is again integrated into the intermediate tube 220.
  • a cup-shaped bearing element 232 which corresponds functionally to that according to FIG. 3, protrudes from below into the spindle housing 210 and is rigidly fastened in the lower end 216 thereof.
  • a foot part 246 of the tilting joint 240 is pressed onto a collar 234 of the bearing element 232 which is tapered in diameter and which comprises a tubular section 244 designed as a bellows.
  • the part of the intermediate pipe 220 surrounding the damping device 70 directly adjoins the pipe section 244.
  • the resilient, resilient part of the tilting joints 140 and 240 is formed by a section of a tube designed as a bellows, specifically the intermediate tube 120 and 220, respectively, this flexibility can be used as an alternative by means of other measures which sufficiently reduce the rigidity of the corresponding pipe section, while maintaining the structure of the textile spindle described in each case.
  • the tilt joint as part of another component, i.e. Integrated into the intermediate tube or into the bearing housing, this can also be designed as an independent component, corresponding to the tilt joint 40 of FIG. 1.
  • the tilt joint provided according to the invention in the spindle housing instead of an arrangement between the spindle housing and the intermediate tube, as shown in FIG. 2 or an integration into the intermediate tube according to FIGS. 3 and 4, and that directly above the bearing element, the same as in Fig. 4 is pressed into the lower end of the spindle housing.
  • the rigid holding element is formed by the main part of the spindle housing adjoining above the tilt joint.
  • the tilt joint can be provided in the part of the intermediate tube 120 or 220 adjoining the bearing part 132 or 232, without impairing the principle of action of two mutually independent, spring-elastic degrees of freedom of the spindle shaft.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
EP94109596A 1993-07-28 1994-06-22 Broche textile Withdrawn EP0636718A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH229393 1993-07-28
CH2293/93 1993-07-28

Publications (1)

Publication Number Publication Date
EP0636718A1 true EP0636718A1 (fr) 1995-02-01

Family

ID=4230390

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94109596A Withdrawn EP0636718A1 (fr) 1993-07-28 1994-06-22 Broche textile

Country Status (3)

Country Link
US (1) US5528892A (fr)
EP (1) EP0636718A1 (fr)
JP (1) JP2759870B2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19536874A1 (de) * 1995-10-03 1997-04-10 Novibra Gmbh Spindel für Spinn- oder Zwirnmaschinen
DE19612121A1 (de) * 1996-03-27 1997-10-02 Stahlecker Fritz Spindel für Spinn- oder Zwirnmaschinen
DE19726216B4 (de) * 1997-06-20 2007-11-22 Novibra Gmbh Spindel für Spinn- oder Zwirnmaschinen
US6273611B1 (en) * 1998-12-03 2001-08-14 Fritz Stahlecker Bearing for spindles in spinning or twisting machines
DE102009031886A1 (de) * 2009-07-06 2011-01-20 Rotorcraft Ag Spindellagerung für eine Ringspinnmaschine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA515112A (fr) * 1950-05-01 1955-07-26 Universal Winding Company Broche de filature
FR1204630A (fr) * 1957-04-27 1960-01-27 Support de broches à rotation rapide, notamment de broches à filer ou à retordre
FR1293897A (fr) * 1960-08-08 1962-05-18 Rieter Ag Maschf Broche pour métiers à filer et à retordre
DE3843651A1 (de) * 1988-01-29 1989-08-03 Rieter Ag Maschf Spinn- oder zwirnspindel
DE3942403A1 (de) * 1989-12-21 1991-06-27 Stahlecker Fritz Spinn- oder zwirnspindel
DE4121979A1 (de) * 1990-08-08 1992-02-13 Stahlecker Fritz Spinn- oder zwirnspindel

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1150447A (fr) * 1956-05-04 1958-01-13 Alsacienne Constr Meca Broche de métier à filer ou à retordre
BE558023A (fr) * 1956-06-15
CH379985A (de) * 1960-04-29 1964-07-15 Rieter Ag Maschf Spinn- und Zwirnspindel
US3708888A (en) * 1971-01-14 1973-01-09 Royal Oak Charcoal Co Apparatus for activating comminuted material
US3797219A (en) * 1972-03-01 1974-03-19 Whitin Machine Works Spindle bolster
DE2228246C3 (de) * 1972-06-09 1981-02-12 Zinser Textilmaschinen Gmbh, 7333 Ebersbach Spinn- oder Zwirnmaschine
CH539697A (de) * 1972-07-10 1973-07-31 Uster Spindel Motoren Maschf Textilspindel
DE2348908C2 (de) * 1973-09-28 1982-07-22 Spindel, Motoren & Maschinenfabrik AG, Uster, Zürich Spinn- oder Zwirnspindel mit einem durch einen Wirtel antreibbaren Spindelschaft
DE2749389C3 (de) * 1977-11-04 1980-11-06 Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt Lagerung für den Schaft einer Spinn- und Zwirnspindel
DD236762A1 (de) * 1985-04-29 1986-06-18 Spindel Und Spinnfluegelfabrik Justierbare spindel fuer spinn- oder zwirnmaschinen
CH667112A5 (de) * 1985-07-24 1988-09-15 Uster Spindel Motoren Maschf Einrichtung zum radial beweglichen befestigen eines spindellagergehaeuses einer spinn- oder zwirnspindel an einer spindelbank.
US5201170A (en) * 1989-12-23 1993-04-13 Fritz Stahlecker Spinning or twisting spindle having a spindle shaft
US5359842A (en) * 1989-11-17 1994-11-01 Fritz Stahlecker Spinning or twisting shaft bearing assembly with vibration isolation connection arrangement
DE4036353C2 (de) * 1989-12-23 2000-11-02 Stahlecker Fritz Spinn- oder Zwirnspindel
DE4004046A1 (de) * 1990-02-10 1991-08-14 Stahlecker Fritz Lagerung fuer eine spinn- oder zwirnspindel
US5119620A (en) * 1990-05-17 1992-06-09 Wilhelm Stahlecker Gmbh Holding arrangement for a spindle of ring spinning or ring twisting machines
CH683430A5 (de) * 1991-07-10 1994-03-15 Rieter Ag Maschf Spinn- oder Zwirnspindel.

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA515112A (fr) * 1950-05-01 1955-07-26 Universal Winding Company Broche de filature
FR1204630A (fr) * 1957-04-27 1960-01-27 Support de broches à rotation rapide, notamment de broches à filer ou à retordre
FR1293897A (fr) * 1960-08-08 1962-05-18 Rieter Ag Maschf Broche pour métiers à filer et à retordre
DE3843651A1 (de) * 1988-01-29 1989-08-03 Rieter Ag Maschf Spinn- oder zwirnspindel
DE3942403A1 (de) * 1989-12-21 1991-06-27 Stahlecker Fritz Spinn- oder zwirnspindel
DE4121979A1 (de) * 1990-08-08 1992-02-13 Stahlecker Fritz Spinn- oder zwirnspindel

Also Published As

Publication number Publication date
JPH0754223A (ja) 1995-02-28
US5528892A (en) 1996-06-25
JP2759870B2 (ja) 1998-05-28

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