CN1062919C

CN1062919C - Drawing apparatus of spining machine

Info

Publication number: CN1062919C
Application number: CN94117598A
Authority: CN
Inventors: 罗兰德·埃贝哈德特; 海茵茨·米勒
Original assignee: SKF Textilmaschinen Komponenten GmbH
Priority date: 1993-10-22
Filing date: 1994-10-20
Publication date: 2001-03-07
Anticipated expiration: 2014-10-20
Also published as: JPH07189050A; IT1268129B1; ITTO940825A0; DE4336028A1; JP2610588B2; CN1112968A; DE4336028C2; ITTO940825A1; CH691265A5

Abstract

In the top-roller carrier of a drawframe for spinning machines, the said top-roller carrier being provided with mechanical compression springs, an at least largely constant-pressure loading of the top rollers over the entire possible operating range of adjustment of the links (15) is ensured by a choice of the position of the action point (19) of the compression spring (12) accommodated in the individual slides (10) in relation to the pivot-bearing point (16) of the link (15) in the slide (10) and to the axis (17) of the top roller in the link (15). This can be assisted by additionally varying the position of the action point (19) of the compression spring (12) in dependence on the pivoting position of the link, additionally also to achieve a part relief of the top roller in a part-load position of the top-roller carrier.

Description

Drafting assembly of spinning frame

The present invention relates to a kind of drafting assembly of spinning frame.

This drafting system is known by DE3905285A1 for example.

The prerequisite of the complete operate as normal of drafting system is that top roller acts on a pressure load of predesignating on associated bottom roll, even also must remain unchanged through long operation.Exist various influences and satisfy the factor of this requirement, wherein at first being top roller with respect to the position of upper roller frame variation has taken place, and this is owing to sometimes requiring polishing roller skin to cause to eliminate the charging indentation.Consequently make the compression spring elongation that produces load, what link with it is to have reduced it to act on pressure on the top roller trailing arm.It is inaccurate that other some sources of trouble comprise that the Height Adjustment of upper roller frame gets, and the mismachining tolerance of drafting system part.This can cause needs time-consuming and superfine heart to adjust drafting system, especially requires to proofread and correct the Height Adjustment to upper roller frame.

Therefore, generally speaking the objective of the invention is to avoid as far as possible fully to adjust drafting system at its life period.The specific purposes that proposed are, can be big as far as possible and avoid adjusting the height and position of drafting system upper roller frame in this possible roller change in location scope of the life period of top roller at one.

This purpose realizes by the drafting system that the present invention utilizes this paper to begin described type, promptly the invention provides a kind of drafting assembly of spinning frame, be provided with a upper roller frame, it is contained in one pivotally and is fixed on machine fixedly on the bearing on the pole, and in upper roller frame, be equiped with slide, free end at slide is equipped with a trailing arm that is used for a top roller at least, trailing arm can rotate perpendicular to the upper roller frame fore-and-aft plane, trailing arm is subjected at least one pressure that is contained in the compression spring in the slide, it is characterized by: the site of action of at least one compression spring on trailing arm, be chosen as with respect to the pivot point and the axle of top roller in trailing arm of trailing arm at slide, at least along the limited working clearance (x) of compression spring that loads, the constant that keeps basically at the pressure load of top roller effect.

Proved already, by the selection pressure spring on the trailing arm with respect to the site of action of trailing arm at pivot point on the slide and the top roller axis in trailing arm, just can in drafting system, pass through the common working clearance of compression spring of loading, the load variations of top roller is remained within the small range, even this scope also is to allow to exist by the allowance error of regulation so far when producing the high-quality yarn.Here, the elastic constant of selected loading spring plays an important role.Act on the variation of the pressure load of top roller, also can avoid fully by taking accurately to adjust the such addition thereto of compression spring, at this moment, the site of action of compression spring on trailing arm is designed to, the overcompensation that shortening is scheduled to spring that the short arm of force of pyknosis is caused, can the pressure load that act on top roller be compensated to a constant value by continuously changing the spring contact point in bigger working range.

The present invention has important advantage, and is for example outer and when top roller is changed with respect to the position of upper roller frame when requiring to polish roller, the Height Adjustment mechanism that no longer needs to calibrate upper roller frame.The present invention can realize by simpler structure, and not need to change the structural design of slide.In addition, the assembling of drafting system does not bother yet.Another significant advantage of the present invention is, has adopted the measure that achieves the above object, can be when adjusting the upper roller frame sub-load, and that realizes drafting system exports the partial relief that top roller is known at least.Can additionally establish a contact site at least at position of slide and/or near its pivot point on the trailing arm by the present invention, when keeping top roller to have unclamping upper roller frame under the situation of sub-load, compression spring can be pressed on this position.Therefore, adopt the less spring arm of force, just correspondingly reduced the load of top roller, and/or pass through the contact point of additional springs on slide, a part of spring force is passed to slide.

The relative position of above-mentioned change spring contact point, trailing arm gyroaxis and top roller axle, can structurally reach by different modes to a normal value with the whole top roller load of accurate adjustment.For example, can design a plurality of compression springs contact site on trailing arm, they have the different distances that plays arm of force effect with the pivot point of trailing arm, and compression spring can one by one or according to the long-armed rotary position with respect to slide act on these contacts site.The site of action of compression spring on trailing arm also can be made of the contact track of a bending, between it and the trailing arm pivot point as the coverage of the arm of force, continuously change contact track or each projection (they can be located on the trailing arm or also and can be located on the spring base) along its length and preferably can be made by a kind of harder material, this material is harder than trailing arm (the especially plastics trailing arm) material of remainder.

By means of the accompanying drawing that comprises working curve, describe the embodiment that realizes drafting system slide of the present invention therein in detail below.

Wherein:

The top roller trailing arm that Fig. 1 and 2 is hinged on the slide is in different rotary positions

The time, be provided with the diagrammatic side view of the slide of loading spring, loading spring

Act on the top roller trailing arm;

The sketch map of Fig. 3 and 4 two kinds of signals is relative in order to explanation compression spring site of action

Different in the pivot point of trailing arm with the top roller axis in trailing arm

Effect during arrangement

Fig. 5 adopts the present invention can getable different top roller loading characteristic curve;

Fig. 6 schematically illustrates along contact zone under the compression spring of axle of spring direction, and each

Between spring action position and the trailing arm pivot point as effective distance of the arm of force

From;

The corresponding slide side view of Fig. 7 and Fig. 1 and 2 with different structure.

Fig. 1 and 2 represents to remove slide 10 diagrammatic side view of sidewall first break draft device upper roller frame (not shown).Slide 10 has one to go up contact-making surface 11, and slide abuts against on the upper roller frame of representing with chain-dotted line by it.A helical compression spring 12 has been adorned by known way in the inside of slide 10.Spring 12 is pressed between spring base 14 and the trailing arm 15, and spring base can swingingly be bearing on the slide 10 around axle 13, and trailing arm is at the following free end of slide 10, and the axle 16 that it can wind perpendicular to the upper roller frame longitudinal extension is supporting pivotally.But trailing arm 15 be designed in the load map not expression two top rollers spools 17.

Trailing arm 15 carries out particular design with the contact zone 18 that helical compression spring 12 polishes end, makes helical compression spring that a unique definite site of action 19 be arranged on trailing arm 15.Among the represented in the drawings embodiment, in fact this is a wire site of action 19a as seen from Figure 6.Only by selecting site of action 19 with respect to trailing arm pivot point 16 and the position that is contained in the top roller axle 17 in the trailing arm 15, just can obtain acting on a characteristic curve that concerns between the length variations of the gyration of load on the top roller and trailing arm 15 or compression spring 12, very little at load in the possible working clearance scope of compression spring 12 for the situation bias of constant.Two schematic diagrames 3 and 4 have been represented this point, and wherein the relative position of the rotating shaft 16 of the axle 17 of the site of action 19 of compression spring on trailing arm 15 and top roller and trailing arm is selected differently.In the embodiment shown in fig. 3, the distance between the axle 17 of site of action 19 and top roller is greater than the respective distance in embodiment illustrated in fig. 4.Only because this structural difference, in the embodiment shown in fig. 3, by changing the degree of compensation that the arm of force brings the variation of spring force, greater than the situation among the embodiment that presses Fig. 4.For the pressure that definite value is arranged is lax, also require to have higher elastic constant C here ₁When the trailing arm 15 of not expression in Fig. 3 and 4 rotates an angle of revolution α equally, Fig. 3 and 4 different geometrical size make between the length variations ds of the compression spring 12 that produces therefrom and compression spring longitudinal axis 22 and the trailing arm gyroaxis 16 the change dh as the coverage of the arm of force that different values is arranged.Ds among Fig. 3 ₁Less than the ds among Fig. 4 ₂In contrast, the dh among Fig. 3 ₁Greater than the dh among Fig. 4 ₂For the pressure that often is worth relaxes, under the situation of physical dimension embodiment illustrated in fig. 4, its elastic constant C2 must be less than the C among the embodiment shown in Figure 3 ₁

Four characteristic curves have been represented in the curve map shown in Figure 5 altogether, wherein three top roller load characteristic line 25a, 25b and 25c, can different relative positions be arranged and adopt different elastic constants to obtain by the site of action of selection pressure spring on trailing arm, main interested be the situation of change of possible working clearance " x " of these curves helical compression spring when drafting system work in regional.Article 4, load characteristic line 25d represents, by obtain the pressure curve of a normal value after accurate the adjustment along whole working clearance x.

The ordinate of curve map is represented intensity of load F/N.Along working clearance x, drawing has hatched region representation to think the fluctuation range that allows so far.Select the relative position of spring action position and trailing arm rotating shaft and top roller axle, and select certain elastic constant, can accomplish to make all characteristic curves, comprise the characteristic curve 25b of the characteristic curve 25a that produces after the overcompensation, normal compensation back generation, characteristic curve 25c and the characteristic curve 25d that undercompensation produces by deriving by characteristic curve 25a after accurately adjusting, all within error range, change along working clearance x, and can accomplish the characteristic curve maximum M in error range is selected in the diverse location of working clearance x.

The site of action 19 that compression spring 12 is different, by the curve modeling of trailing arm 15 contact zones 18 (Fig. 1,2) or there design one by one projection 20,21 (Fig. 7) obtain.They are designed to change in position shown in Figure 2 from it when the rotary position of trailing arm 5 as Fig. 1, and thereby cause that top roller axle 17 moves one apart from a from its position of representing with chain-dotted line among Fig. 1, therefore and when shortening 12 1 amounts of helical compression spring ds, the site of action 19 of compression spring 12 on trailing arm 15 is changed, different with Fig. 2, obtained size relationship as shown in Figure 1.By position shown in Figure 1, change to L1 apart from projection from amount L2 between roller shaft 17 and the parallel with it rotating shaft 16.What have the decision meaning is because the site of action 19 of spring 12 on trailing arm 15 changes, to make effective arm of force of compression spring be reduced to h1 from length h2.Since the spring contraction in length amount ds, its elastic force is increased.But because the arm of force shortens to an amount h1, the moment that acts on the trailing arm 15 is in fact constant, or remains and draw horizontal properties line 25d drawn among Fig. 5.

Fig. 7 represent the different slide of structure 10 ', it has a common eccentric wheel 23, in order to change compression spring 12 ' at the home position of upper spring seat 14 ' locate.Mention as top, slide 10 ' the side 18 contact with spring of trailing arm 15 ' go up ' be cast with protruding 20 and 21, here be by trailing arm 15 ' plastic body in insert metallic pin and constitute, they cause different spring action positions, compression spring 12 ' according to trailing arm 15 ' position of rotation one by one act on the projection.With the very near contact projection 21 of trailing arm rotating shaft 16 ' distance, constituted compression spring 12 ' very short arm of force, compression spring 12 ' be just to its pressurization when the part loading position of upper roller frame, to obtain the well-known local off-load of top roller, this local off-load feeds back in the draw zone in order to the line that prevents to twist as drafting system port of export top roller is desired.The load characteristic line of Fig. 5 has been represented this sub-load district " T ".Site of action 19b is corresponding with contact projection 21 in Fig. 6.Fig. 7 has also represented an additional projection 24 that is located on the slide shell, compression spring 12 when sub-load ' end additionally be pressed against above it, thereby with the part of remaining spring force import into slide 10 '.

The mode that compression spring also can not represented from figure is established in form at an end at its trailing arm place and is the connector of spring base, and one of design and the cooperative inter_curve of trailing arm on it are to change the site of action of spring on trailing arm.

Claims

1. drafting assembly of spinning frame is provided with a upper roller frame, it is contained in one pivotally and is fixed on machine fixedly on the bearing on the pole, and in upper roller frame, be equiped with slide (10,10 '), free end at slide is equipped with a trailing arm (15 that is used for a top roller at least, 15 '), trailing arm can rotate perpendicular to the upper roller frame fore-and-aft plane, trailing arm is subjected at least one and is contained in slide (10,10 ') in compression spring (12,12 ') pressure, it is characterized by: at least one compression spring (12,12 ') is at trailing arm (15,15 ') on site of action (19), with respect to the pivot point (16 of trailing arm (15,15 ') in slide (10,10 '), 16 ') and top roller in trailing arm the axle (17) be chosen as, at least along the limited working clearance (x) of compression spring (12,12 ') that loads, remain constant basically at the pressure load of top roller effect.

2. according to the described drafting system of claim 1, it is characterized by: the axle (17) of the site of action (19) of compression spring (12) on trailing arm (15), top roller is with respect to the position of site of action (19) and trailing arm (15) pivot point (16), and the elastic constant (c) of compression spring (12) should be elected as, when site of action (19) is constant, the load of top roller depends on that along the possible working clearance (x) of compression spring (12) that loads stroke presents a maximum (M) in narrow error district.

3. according to claim 1 or 2 described drafting systems, it is characterized by: the site of action (19) of compression spring (12) on trailing arm (15) should be chosen as, make between spring action position (19) and trailing arm (15) pivot point (16) and/or and the axle (17) of top roller between as the distance (h) of the arm of force, along with the length of compression spring (12) changes (ds) and changes.

4. according to the described drafting system of claim 1, it is characterized by: between the site of action (19) of compression spring (12) and the pivot point (16) of trailing arm (15) as the distance (h) of the arm of force, increase and same increasing with spring length, and reducing and reduce with spring length.

5. according to the described drafting system of claim 1, it is characterized by: a plurality of contacts site (20 that on trailing arm (15 '), are provided with compression spring (12 '), 21), between the pivot point (16 ') of they and trailing arm (15 '), and thereby also with between the top roller axle (17) in trailing arm (15 ') different effective arm of forces (h) is arranged, compression spring (12 ') can one by one act on these contacts site according to the position of rotation (α) of trailing arm (15 ') with respect to slide (10 ').

6. according to the described drafting system of claim 1, it is characterized by: the site of action (19) of compression spring (12) on trailing arm (15) is made of the contact track of a bending, and the distance (h) as the arm of force between it and trailing arm (15) pivot point (16) continuously changes along its length.

7. according to the described drafting system of claim 5, it is characterized by: each contact site (19a-19c) of compression spring (12,12 ') is made of each projection (20,21) of trailing arm (15,15 ').

8. it is characterized by according to the described drafting system of claim 5: the contact track (18) of trailing arm (15,15 ') or projection (20,21) are made by a kind of harder material, and this material wants hard than the material of making trailing arm (15,15 ') remainder.

9. according to the described drafting system of claim 1, it is characterized by: compression spring (12) abuts against on the spring base (14) with its that end away from trailing arm at least, and spring base is contained in the slide (10) and can rotates perpendicular to the support fore-and-aft plane.

10. according to the described drafting system of claim 1, it is characterized by: compression spring (12 ') is with its that end away from trailing arm, and what abut against a rigidity can be along on the spring base that vertically moves (14 ') of slide (10 ').

11. according to the described drafting system of claim 1, it is characterized by: compression spring (12,12 ') is provided with a connector at trailing arm one end, one of design and the cooperative inter_curve of trailing arm (15) on it.

12. according to the described drafting system of claim 1, it is characterized by: go up at position of slide (10 ') and/or at trailing arm (15 ') it pivot point (16 ') near, at least additionally establish a contact site (24,21), when upper roller frame is unclamped in the part, under the situation that keeps the top roller sub-load, compression spring (12 ') is pressed on this contact site.