DE2310323A1 - HIGH SPEED SPINDLE ARRANGEMENT FOR SPINNING MACHINES AND BEARINGS FOR SUCH SPINDLES - Google Patents

Description

Applicant: Whitin Machine Worcs, Inc.,

Charlotte, North Carolina 282ol / USA

High-speed spindle arrangement for spinning machines and storage for such spindles

The invention relates to a high-speed bearing arrangement for spinning machines and a bearing for spindles in spinning machines; In particular, the invention relates to a device in which the spindle shaft is resiliently supported, about stresses and strains as a result of vibrations and oscillations on the shaft and the associated structure reduce to a minimum.

Spindles in spinning and twisting machines are operated at very high speeds, namely with speeds of up to I5ooo rpm. If a larger amount of yarn is placed on the bobbin attached to the spindle, there is an imbalance as a result of the Mass of the yarn with respect to the spindle axis is generally unavoidable. Even a slight imbalance is a consequence the high speed is a possible source of great vibration and oscillation forces. In general, the

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the vibrations and oscillations caused loads and stresses on the spindle shaft and minimized on support bearings when the spindle shaft is in a rigid, rigid Bearing or neck bearing is resiliently supported.

In a known spindle holder and in the preferred embodiment of the invention, the spindle shaft is supported in its middle part, which is mounted in a fixed radial bearing, while its lower end on one resiliently built-in support bearing is supported. In such an arrangement, the radial bearing forms a support or Pivot point around which the spindle shaft is laterally influenced by centrifugal forces caused by an imbalance on the Can swing spindle. Such forces are absorbed by damping and centering devices on the lower support bearing and damped, which is moved laterally together with the lower end of the spindle shaft.

According to the invention, a holder for the support bearing in a spindle neck bearing or bearing is to be created, through which the vibration and oscillation caused by the lateral displacement of the protective bearing by a Centering spring is precisely controlled, through which the support bearing in a centered, centrally set or ideal position is resiliently biased. In addition to and in addition to the centering of the support bearing and the spindle shaft carries and supports the centering spring, the support bearing and the spindle shaft in the vertical direction. In addition, by means of the spring is a Prevents rotation of the support bearing.

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In the embodiment shown, the spindle neck bearing or the spindle bearing arrangement on a solid tube, at the upper end of which a radial bearing is attached. A spindle shaft is mounted in this radial bearing and extends down into the bearing tube to a support bearing. The shaft is supported both in the radial and in the axial direction in such a way that it can be rotated in the support bearing; a centering spring is with one of its ends in a lower end wall of the bearing tube and with its other end attached to the support bearing. This arrangement allows the spring to deflect the support bearing laterally from a centered position "with respect to the bearing tube counteract due to their spring action.

The spring is dimensioned so that it vertically supports the support bearing in a certain axial position in the bearing tube Direction supports and creates a torsional strength so that rotation of the support bearing with respect to the bearing tube is prevented. By means of an intermediate or spacer piece to limit the axial displacement of the support bearing from the intended axial position, the spring is against damage protected if, for example, a spindle shaft is dropped into the bearing tube at an accelerated rate. Furthermore, through the centering spring in the axial direction a compulsion or a Holding force exerted on the support bearing, whereby, when removing the spindle shaft is prevented from being pulled out.

According to the invention, a spindle neck bearing or a spindle bearing arrangement is thus created in which a spindle shaft resiliently by means of a support bearing in a bearing housing for a lateral displacement of its lower end is held in order to reduce vibration or vibration loads to a minimum. The support bearing is in one

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centered position resiliently preloaded by means of a spring anchored at the lower end of the bearing housing, which is also fixed in the axial direction and prevents the support bearing from rotating.

On the basis of preferred exemplary embodiments, the invention is described below with reference to FIG attached drawings explained in more detail. Show it:

FIG. i a longitudinal section through a spindle bearing arrangement according to the invention;

FIG. 2 is a partial sectional view showing details of a portion of the circuit shown in FIG. 1 shown Bearing arrangement are shown on a slightly larger scale and the mounting of the support bearing in detail is shown;

FIG. 3 one of FIG. Partial sectional view similar to Fig. 2, in the details of a further embodiment a bracket and spring mount for the support bearing are shown; and

FIG. k a FIG. 2 and 3, similar partial sectional view, in which a third embodiment of the spring centering device for the support bearing is shown.

In FIG. 1 shows a spindle bearing arrangement Io, which has a cylindrical, tubular bearing housing 11. Through an external thread 12 at the upper end 13 of the Housing il is threaded together with a matching one provided (not shown) screw nut a

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Device created by means of which the bearing tube 11 can be firmly attached to a cross rail of a conventional spinning or twisting machine. As is known, the bearing arrangement Io is clamped to the cross rail in that the latter is clamped between the internally threaded flange Ik and the screw nut. A protruding extension 16 formed on the flange I ^ carries a doffer latch 17 which is rotatably mounted about a pin 18.

A conventional spindle shaft 21 with a cylindrical part 22 and a tapered part 23 is in the Bearing housing 11 is mounted above by means of a radial bearing 26 and below by means of a support bearing 27. As shown, the upper Rudiallager 26 is a roller bearing, which is in an aluminum counterbore 29 at: the upper end 13 of the bearing housing is secured by means of a press fit. The outer surface of the cylindrical toilet 22 of the spindle shaft 21 forms then an inner ring for the rollers 3o of the radial bearing. On the other hand, if desired, the radial bearing be designed in such a way that it is secured on the spindle shaft in such a way that it is withdrawn from the bearing housing 11 can be. In this case, the fit between the bearing and your countersink 29 is chosen so that the bearing j: it the: shaft 21 can be easily removed. The cylindrical portion 22 extends from the iliac ulcer 26 generally in the axial direction through a first cylindrical üoarung 31 in the Göhäusc 11.

uiil'üron end 33 of the housing 11 is a second cylindrical Axial bore 34 is provided. In this cylindrical

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Bore 34 is a compression spring 3b of known type used, which a number of precisely formed helical or spiral turns with capillary-like spaces 37 (FlG. 2 to 4) in between. A winding forming the outer diameter of the spring 36 lies on the wall of the corresponding bore 34, while a turn forming the inner diameter of the spring a cylindrical outer surface 3S of the support bearing 37 is applied. The turns of the damping spring 36 can laterally or be shifted eccentrically to the bearing axis, thereby causing a lateral displacement of the support bearing 37 adapt.

A conical bore 41 with einir. "Angle that is slightly Larger than that of the tapered part 23 of the spindle shaft 21 is at the lower end of the support bearing 27 designed to receive the shaft. At the lower end of the conically tapering bore 'ti there is an iu; generally conical seat or bearing surface 43 is provided on which a suitably shaped, conical shaft end 44 is supported in the vertical and lateral directions. One in the radial direction running bore 46 and a groove 47 running in the axial direction on the outside of the support bearing 27 ensure the passage of lubricating oil to the bearing surface

A cylindrical countersink 51 a; · '. lower linden 33 of the Luger housing-11 ends at a radially extending shoulder 52 at the bore 34. A cylindrical plug or plug 53 is inserted into the countersink 5-L so that it rests against the shoulder 52; it is held in this position by a protruding edge ^r jh of the housing II. A conventional, resilient O-ring seal 56 on plug 53 prevents leakage

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of the lubricating oil from inside the housing 11.

In the first in FIG. 1 and in particular in FIG. 2 illustrated embodiment according to the invention the support bearing 27 with respect to a longitudinal axis determined by the bearing housing 11 by means of an essentially straight spring or a pin 71 centered or set in the middle. The pin 71 is preferably round and in the axis of the bearing housing 11 centered in that one of its ends 72 is drilled into the end plug 53 in an axial direction Bore 73 is used. The other end 74 of the pin

71 is held in a cylindrical pipe socket 75. The pin 71 is preferably made of a high strength material such as steel wire and is at both ends

72 and 7k knurled so that it is maximally retained in the material surrounding it when the ends are inserted into the plug 53 and into the socket 75 with an interference fit.

Typically, the support bearing is made of a relatively hard material, such as hardened tool steel, in order to provide sufficient wear resistance against frictional contact with the spindle shaft 21. It has been found here that the hardness of the support bearing 27 can be so great that the knurled edges of the pin 71 are destroyed when the pin is pressed into a corresponding bore in the support bearing. If a somewhat softer material is used in the sleeve 75, this difficulty is eliminated. With the end Ik of the spring located in the bushing 75, before these parts are assembled in the bearing housing, the bushing 75 is preferably subjected to a strong compressive load in one

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Axial blind hole 76 exposed, whereby the bush 75 is sufficiently plastically deformed. l \ ^T oh iintfernen the Verfoinungsbelastung is the remaining Druckbean- spruchung maximum in the sleeve, thereby ensuring that the pin end ~ lh fixed and permanently held in the üuchse.

An intermediate or spacer in the form of a cylindrical, tubular sleeve 78 is dimensioned so that their length in the axial direction is somewhat smaller than the axial distance between the closure part 53 and the support bearing 27. The solid, stable spacer 73 is closed; Protection of the centering spring 71 against excessive kicking loads provided that would cause kinking or bending, for example when the spindle shaft on the support bearing is dropped with unusual force. Preferably, the outer diameter of spacer 78 is substantially equal to that of the support bearing 27. The resulting axial play between the spacer 78 and the support bearing 27 normally allows the support bearing in a lateral or radial direction with respect to the longitudinal axis of the bearing housing 11 can be moved or changed in its position without causing frictional contact between the spacer and the bearing koiauit. Even if an excessive axial load is exerted on the support bearing 27, which can happen, for example, when a spindle is pushed down into the bearing housing, the pin 71 bends or curves laterally Direction only until the underside of the support bearing 27 touches the upper surface of the spacer 7S, so that thereby which are exerted on the centering spring 71 in the axial direction Loads are limited.

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In the usual mode of operation, the spindle shaft 21 is rotated relative to the bearing housing 11 by means of a drive belt, not shown, which is attached to a one shown in FIG. 1 engages whorl 81 shown by dash-dotted lines, which is pushed over the upper end 13 of the housing 11. The whorl 81 is usually attached to the spindle shaft 21 via the radial bearing 26 by means not shown. Normally, the interior of the bearing housing 11 is filled with a suitable lubricant or oil up to a point approximately in the middle of the cylindrical part 22 of the spindle shaft 21. The oil serves both to lubricate the contacting surfaces of the spindle shaft 21 and the support bearing 27, in particular the bearing surface 43 and the shaft end hhy, and to fill up the spaces between the turns of the spring 36.

The spindle shaft 22 extends over the Itadiallager out into a case (not shown) or a protective cover on which a tube or tube for wrapping with yarn can be attached or used. The sheath or the protective cover is exclusively from the spindle shaft borne, so that forces acting laterally on the protective cover are only absorbed by the radial bearing 26 and the support bearing 27 will. A slight imbalance or eccentricity of the yarn wound on the spindle creates a centrifugal force at the upper end of the spindle, causing the spindle shaft 21 to rock in the upper radial bearing 26 or to begins to sway.

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Through the upper bearing 26, which acts as a support or pivot point for the spindle shaft 21, the lower, conical end 23 of the shaft can be shifted laterally out of the axis of the bearing housing 11 according to the centrifugal forces acting on the parts above the radial bearing 26. As is known, the lateral displacement of the support bearing 27 is sustained and dampened by viscosity forces in the oil in the capillary-like spaces 37 between the windings of the spring 36 when the oil is displaced from the side of the spring when the support bearing 27 moves towards it. In addition, the lateral displacement of the support bearing 27 from the centered position shown is absorbed by the bending resistance of the resilient centering spring or the pin 71, which constantly biases the bearing in the centered position.

Since the centering pin is fastened both to the end part 53 and to the support bearing 27, relative rotation between them is limited by the torsion spring of the pin 71. Because of the play between the support bearing 27 and the spacer 78, the bearing also has a certain strength in the vertical direction. The combination of the centering spring 71 and the damping spring 36 the support bearing 27 can be controlled to yield the dynamic vibration and vibrational forces to the spindle to thereby control the stress and strain in various critical parts, such as dera radial bearing 26, the spindle shaft 21 and your support bearing 27, reduce to a minimum. Furthermore, the lateral displacement or offset of the upper end or the shell part of the spindle has been limited to a fairly small amplitude, so that the available winding space can be used to the maximum.

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In FIG. 3 is a second embodiment of the invention shown, with the centering spring a modified one Has shape. Of course, the part of FIG. 3 bearing arrangement not shown ici essential the same as based on FIG. 1 and 2 described. In this embodiment, the bearing housing 11 and the Damping spring 36 with the reference symbols previously used designated. A support bearing 86 has a tapered bore portion 87 and a conical bearing surface 88, which are essentially the same as the corresponding surfaces 41 and 43 in the first embodiment are trained. On the opposite or lower side 89 of the support bearing 86 is one to one axial bore 92 concentric, conical recess 91 formed. A centering device in the form a coil spring 96 tensions the support bearing 86 in the centered state shown in the bearing housing 11 before. The helical spring 96 is preferably made of round wire manufactured. A part of the spring 96 extending in the axial direction is press fit into the axial bore 92 of the Support bearing 86 fitted.

An end wall or termination 98 is in the counterbore 51 of the bearing housing 11 is also held again against the end part 98 by pressure rolling of the edge 54. An elastic O-ring 99 seals the shut-off part 9S in the countersunk bore 51, whereby a leakage of Lubricant or oil from the housing 11 is prevented. A conical recess Io3 is in the end part designed concentrically to an axial bore Io4. An approach Io6 on the centering spring 96 is press fit in the axial bore io4 held. Through the conical or conical recesses 91 and Io3 in the support bearing

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and the end part 98 is the insertion of the corresponding Spring lugs 97 and Io6 in the respective holes 92 and Io4 facilitated. Approaches 97 and Io6 can, like is already executed above with reference to the spring pin 71, be knurled, the connection between the spring 96, the Bearing 86 and the end part 98 is improved.

Although not shown, a suitable bushing, such as the bushing 75 shown in the first embodiment, and a corresponding bore can be provided in the support bearing 86, whereby the connection between the spring extension 97 and the bearing is further improved. By choosing a corresponding number of turns Io8 and the wire diameter in the centering spring 96, sufficient rigidity, elasticity or tensioning force can be created to preload the support bearing in the centered position shown. Furthermore, the windings Io8 are wound tightly enough that, if they are subjected to an unusually high axial compressive load, they abut one another and thereby form a solid spacer, whereby a downward displacement of the support bearing 86 is limited and permanent deformation of the spring 96 is prevented . Under normal loads in the axial direction, the windings io8 are stiff enough and do not come into contact with one another, so that friction between them is avoided even if they are laterally displaced together with the support bearing 86 .

In FIG. k is a third embodiment of the invention is presented, in which a centering spring 111 for the support bearing is specially designed to create the required properties be with respect to the suspension or bending. In this embodiment too, parts with the same structure as in the embodiments described above are provided with the same reference numerals.

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In this embodiment, the centering spring is 111 preferably made of round wire and having a single curved portion or bend 112 in its middle section and liiit running coaxially Ends 113 and 114 provided. The curved part 112 lies, as shown, in the plane of the drawing. Each End 113 and 114 is press fit into the corresponding one Parts 53 and 75 used. As already stated and in FIG. 1 and 2, these ends 113 and 114 can be knurled to thereby establish the connection and to improve the hold of the assembled parts. The curved design of the spring 111 results in a spring or Deflection value that is slightly smaller than that found for a straight pin of the same diameter results, as shown in FIGS. 1 and 2 is shown. The tubular spacer is similar to the first version 78 dimensioned so that the axial displacement of the support bearing 27 is limited to the end part 53, in order to thereby prevent constant deformation of the spring 111.

Prevent in all of the embodiments shown the centering springs 71, 96 and 111, which are fixed in the corresponding end wall or the end part 53 or 98 and are anchored in the support bearing 27 or 86, a rotation of the support bearing with respect to the end wall. Farther is prevented by the centering springs 71, 96 and 111, that the respective piece bearings are pulled up out of the damping spring 36, for example in cases where there is suction on a bearing surface 43 or 87 at Removal of the spindle shaft 21 arises. Though only preferred embodiments according to the invention in detail As described and illustrated, the invention may of course take various other forms and forms Have embodiments that are under the subject of Invention fall.

Claims

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Claims (1)

Claims 1. High-speed spindle arrangement for spinning machines, characterized by a rohrförraiges Bearing housing (ll) with an open upper end (13) and a closed lower end (33), a device for fastening the bearing housing (ll) to a rail, one at the upper end (13) of the housing (ll) housed radial bearing (26), a support bearing (27., 86) in the housing (11) a spindle shaft (21), the extends through the radial bearing (26) into the support bearing (27), (86), this support bearing the The spindle shaft (21) is supported laterally and against axial loads, a resilient device (71, 96, 111), which is attached under the support bearing (27, 86) at the lower end (33) of the housing (Ii) and on the support bearing and the it is supported in the housing (11) in the vertical direction, thereby resiliently centering the support bearing in a Position in the housing (II) to keep or any lateral displacement of the support bearing with respect to its centered Location. 2. Spindle arrangement according to claim 1, characterized ge k e η η, that the resilient device (71, 96, 111) has devices (78j 73, 75; 92, Io4; 75, 113) which absorb the axial forces acting on the support bearing (27, 86) in both directions. 3. Spindle arrangement according to claim 1, characterized in that by means of the resilient device (71, 96, ill) rotation of the support bearing (27, 86) is prevented. k, spindle arrangement according to claim 1, characterized by a device for axially fixing the support bearing (27, 86) in the housing, whereby a lateral displacement - 15 3 0 9 8 3 7 / 0-886 of the support bearing is limited. 5. Bearing arrangement for a spindle arrangement according to one of claims ibis ² *, characterized by a tubular, cylindrical bearing housing (11) with an open upper end (13) and a closed lower end (33) »a device for holding the housing (Ii) on a rail, a cylindrical bore (3i) formed at the upper end of the housing iait a radial bearing (26), a support bearing (27, 86) in the housing (11) through which a spindle shaft (21) in radial and axial Direction is supported, a damping device (36) for accommodating a lateral displacement of the support bearing (27, 86) in the housing (Ii), a fixed, the lower part (33) of the housing closing wall (53), and a spring (71 , 96, Hl), which is fastened with one end (72, io6) in the end wall (53) and with its other end (74, 97, ± lk) on the support bearing (27, 86) to resiliently move the bearing in a centered position in the housing (ii) and to keep it vertical support r direction. 6. Bearing arrangement according to claim 5, characterized in that the spring (71, 96, Hl) is symmetrical is arranged with respect to a vertical axis of the support bearing (27, 86). 7. Bearing arrangement according to claim 6, characterized in that the end wall (53) has a device (73, io4) for holding the spring (7i, 96, iii) symmetrically with respect to an axis defined by the housing (11). 8. Bearing arrangement according to claim 7, characterized in that the support bearing (27, 86) has an axially extending bore (76, 92) which with respect to the - 16 309837/0886 is centered by the support bearing (27, 86) determined axis, and that the spring (71, 96, 111) has a ⁿ in this bore (76, 92) extending part (74, 97, 114). 9. Bearing arrangement according to claim 8, characterized in that the Ilalterungseinriclitung one in the end wall (55) has a bore (75, Io4) running in the axial direction, and that the spring (71, 96, 111) a part extending into this bore (75, Io4) (72, Io6, 113). 10. Bearing arrangement according to claim 9, characterized in that the spring (71) has a round wire, which is straight along its entire length and with respect to the axis of the housing (11) and the axis of the support bearing (27) is aligned. 11. Bearing arrangement according to claim 7, characterized in that the spring (ill) is a bent wire has, which on one side (114) in a bore (76) in the support bearing (27) and at its other end (115) in the Bore (73) is anchored in the end wall (55). 12. Bearing arrangement according to claim 11, characterized in that the bent wire is one in a radial Has flat part (112). 13. Bearing arrangement according to claim 7, characterized in that the spring (96) has a number of helical ones Has turns (lo8) which are centered in the radial direction with respect to the axis of the bearing housing (11). IV. Bearing arrangement according to Claim 7, characterized in that a spacer (7S) for delimiting a displacement of the support bearing (27) in the axial direction - 17 309837/0686 is provided on the end wall (53) to thereby overstress the spring (71, 111) to prevent if an unusually large axial load on the support bearing (27) in the direction of the end wall (53) is exercised. 15. Bearing arrangement according to claim 1Ί, characterized in that the spacer (78) is a hollow having a cylindrical tube, and that the spring (71, Hl) runs in the axial direction in the interior of the tube. 16. Bearing arrangement according to one of claims 5 to 15, characterized in that the other spring end (7 ² I, 97, 114) is held by means of a press fit in the support bearing (27, 86). 17. Bearing arrangement according to claim 16, characterized in that the part (74, 97, 114) of the spring has a mechanically deformable area in order to improve the hold of the interference fit. 18. Bearing arrangement according to claim 17, characterized in that a bushing (75) in the support bearing (27) is provided, the hardness of which is less than that of the support liner, and that the spring end (74, H ^) by a press fit is inserted into the socket (75). 19. Bearing arrangement according to claim 18, characterized in that the bush (75) around the spring end and is deformable in a bore (76) of the support bearing (27) to create the press fit. 309837/0886