PatentDe  


Dokumentenidentifikation EP0281168 12.12.1991
EP-Veröffentlichungsnummer 0281168
Titel Einstellvorrichtung für die Radiallage der Platinen an einer Rundstrickmaschine.
Anmelder Savio S.p.A., Pordenone, IT
Erfinder Bini, Franco, I-50143 Florence, IT
Vertreter derzeit kein Vertreter bestellt
DE-Aktenzeichen 3865985
Vertragsstaaten DE, FR, GB
Sprache des Dokument En
EP-Anmeldetag 28.01.1988
EP-Aktenzeichen 882001464
EP-Offenlegungsdatum 07.09.1988
EP date of grant 06.11.1991
Veröffentlichungstag im Patentblatt 12.12.1991
IPC-Hauptklasse D04B 15/24
IPC-Nebenklasse D04B 15/34   

Beschreibung[en]

The present invention relates to a control device for adjusting the radial position of the sinkers in a circular knitting machine, and, in particular, for adjusting their radial position in those machines which are equipped with devices for varying the density of the formed fabric, by means of an axial shift of the sinkers ring.

It is known that in circular knitting machines, the stitch loops are formed by the vertical reciprocating movement of the needles running inside slots provided along the generatrices of the revolving needle cylinder, and of radially movable sinkers which are arranged on a ring revolving with the needle cylinder and located at the end of the cylinder, in such a position that the feed yarn comes into engagement with a needle, with a sinker, with the subsequent needle, and so on. It is also known that, in order to obtain a good operation and a good-quality product, the sinkers must be given a certain radial mobility, in order to always keep properly tensioned the loops, in order to enable the needle latches to open, and the formed stitch loops to be discharged, with the needles being prevented from penetrating, during the production of the subsequent course, the loops formed in the preceding course. Should such an event occur, a faulty knitted fabric would be produced.

The need is known as well, during the production of a tubular knitted fabric destined, e.g., to form a hosiery article, for the length of the stitch loops formed at each course, viz., the density of the fabric, to be changed, in order to obtain lengths of tubular knitted fabric showing different extensibility.

This is generally achieved by axially shifting the sinker ring, driven by means of lifting cams. An equivalent contrivance to it is, on the contrary, the axial shift, to the opposite direction, of the stitch forming cams acting on the needle butts. This, because such a contrivance is equivalent to the shifting, relatively to the sinker knocking-over plane (the A or B level in Figures 1A and 1B), of the whole path of the needles.

In order to give the yarn loops a proper tension, the radial mobility of the sinkers is realized, in the most widely used machines, according to Figures 1A and 1B, by placing said sinkers on lower, annulus-shaped revolving support 1, provided with radial slots 2, inside which the sinkers 3 are guided during their reciprocating movement in the radial direction.

In the upper portion of each sinker 3, two vertical butts 4 and 5 are provided, which alternatively get engagement with two concentrical cam rings 6 and 7 having a substantially circular contour in a plane perpendicular to the axis of the needle cylinder and with their center being positioned on the axis of the cylinder. The cam rings 6 and 7 are supported by an upper, annulus-shaped stationary support 8.

The contour of rings 6 and 7 is shown in Figure 2.

The inner can ring 6 is radially stationary and rigid with, the support 8, by being fastened to it by means of stud bolts 9; the outer cam ring 7 is subdivided into a plurality of segments ― in exemplifying Figure 2, four segments ― and is fastened to the support 8 by means of pins 10 inserted inside hollows 11, having a larger size, so forming a slack link which allows the cam ring 7 to radially move through a certain stroke into discrete positions. A circumferential spring 12 applies a containment force to the portions of the outer cam ring 7, weakly pushing it inwards. However, the inwards force radially applied by the spring 12 should never exceed the tensile strength of the yarn 14, and when the needle 13 pulls the yarn 14 outwards, and applies an outwards-directed tensile force to the recess 15 of the sinker 3, the same spring should yield and allow the sinker to retract.

The recess 15, viz., the sinker, is pushed inwards by the spring 12 through an as long distance as allowed by the yarn 14; the yarn 14 is hence always under tension, and the loop is never slack.

  • Figure 1A corresponds to long loops, with the sinkers high at level A.
  • Figure 1B corresponds, on the contrary, to short loops, with the sinkers low at level B.

One can observe that, with long loops, the "abundance" of yarn enables the sinkers 3 to move inwards by a longer stroke. The A and B levels are normally denominated as the "sinker knocking-over levels".

According to Figure 2, both the contours of the innermost cam ring 6 are active: the inner contour 6i engages the butts 4, and pushes inwards the sinkers 3 when the corresponding needles are lowered under them, and the outer contour 6e engages the butts 5 and pushes outwards the sinkers 3 when the corresponding needles start sinking after yarn catching.

Through the portions along which the inner cam ring 6 does not act, the radial position of the sinkers 3 in then determined by the outermost cam ring 7.

The cam ring 7 operates ― as regards the sinkers ― by means of its inner contour only, which gets engaged with the butts 5 and pushes the sinkers 3 inwards, keeping the yarn loops always under tension.

This known technical solution does not show serious drawbacks when the machine runs at not very high speeds.

In high-productivity machines, which operate at speeds higher than 1,000 revolutions per minute, the effects of the centrifugal forces applied to the sinkers, and applied by these latter to the cam ring 7, are such that such a technical solution cannot be any longer adopted without serious drawbacks.

In fact, it should be reminded that a circular knitting machine must be capable of considerably varying its revolution speed during the production of an article, e.g., when a change in needle selection is carried out.

If then, when high-speed operation is expected, a stronger spring 12 is adopted, which is also capable of counteracting the effect of the centrifugal forces developed at high speeds, when the machine operates at slow speeds, the centrifugal forces applied to the spring are small, and the force of the spring can hence exceed the tensile strength of the yarn 14, and, consequently, tear it.

Thus, in order to be able to control the radial position of the sinkers in high-speed circular knitting machines, it is necessary to resort to a control system which determines a radial approach and a radial pushing away of the outer cam ring 7 as a function of the length of the formed loops.

In the prior art, some technical solutions to meet this requirement have been proposed.

In GB-A-2091301, the approach and pushing away of the cam ring which controls the radial position of the sinkers is controlled by levers which move on vertical planes passing through the axis of the cylinder, and are directly driven by the lifting of the needle cylinder.

In DE-A-3246653, the contour segments constituting the outer cam ring 7 are articulated and hinged to the support 8, and they are made radially approachable and movable away with a pivoting movement by means of telescopic components.

In DE-A-2020524, the length of the stitch loops is controlled by subdividing the sinkers into two half-sinkers, arranged side-by-side and capable of relative radial movement, which makes it possible to change the overall configuration of the sinkers.

The radial movement of the two half-sinkers is controlled by acting on the butts located at their ends, one upwards, and the other downwards, which are engaged inside two cam/countercam ring are assemblies, analogous to those as hereinabove described, positioned on different planes perpendicular to the axis of the cylinder.

The cam ring and coutercam ring are moved by radially moving sliders, inwards urged by radial springs, and driven by means of further periferally positioned approaching and pushing-away cams.

Such radial springs cause the position of the sinkers to be influenced by the revolution speed of the machine.

But such technical solutions result complex, and do not secure the accuracy and gradualness of the radial movement.

The control device according to the present invention makes it possible to adjust the radial position of the outer cam ring 7 as a function of the level of the sinkers 3 with gradualness and accuracy.

It will first be disclosed with reference to the practical embodiment of Figure 3, wherein the elements 6, 7, 8, 9, 10, correspond to the same elements as of Figure 2.

According to the invention, the outer cam ring 7, and, more precisely, its component segments, have, along their outer contour or periphery, a plurality of shaped portions in form of peripheral protrusions 16, preferably having a curved outline.

Externally around the cam ring 7, a substantially circular countercam ring 17 is concentrically located, whose inner contour is provided with shaped inner portions in form of recesses 18 with gradual radial approach and pushing-away profile i.e. with zones which are closer to the center and further zones spaced relatively further away from the center in a complementary formation to the protrusions 16. The countercam ring 17 is supported and held in position by the annular-shaped support 8.

In the Figures, the protrusions 16 are provided on the outer circular cam ring 7 and the recesses 18 are provided on the circular countercam ring 17. It is evident that such an arrangement can be inverted, with the recesses 18 being provided on the cam ring 7, and the protrusions 16 being provided on the circular countercam ring 17, without changing the spirit and the scope of the invention, the two arrangements being perfectly equivalent.

It results evident that, when the machine is operating, and the needle cylinder is revolving, and with it also the sinker bearing group revolves, the cam ring 7 ― or, better, its component segments ― by the effect of the centrifugal force acting on the sinkers 3 adhere to the counter cam ring 17, so that the protrusions 16 of the cam ring 7 are in contact with the recesses 18 of the countercam ring 17 and vice versa.

The adjustement of the radial position of the cam ring 7 is determined by making the countercam ring 17 ― i.e. its segments ― rotate through a discrete angle around the centre C, which lays on the axis of the needle cylinder, according to arrows R. With such a rotation into discrete angular positions, the protrusions 16 engage a portion of the recesses 18, which is more or less near to the centre C, and through such a contact the component segments of the cam ring 7 are respectively moved inwards or retracted.

In Figures 3A and 3B there is respectively shown the A position ― long loops ― which corresponds to a longer inwards advancement of the sinkers, and the B position ― short loops ― corresponding to a longer outwards retraction of the sinkers.

The rotation R from a position of minimum radial inwards advancement, to a position of maximum radial inwards advancement of the cam ring 7, and, consequently, of the sinkers, is enslaved by known means ― e.g., by means of a kinematic transmission containing conical gearings ― to the respectively minimum and maximum axial level of the sinker knocking-over plane, i.e., the recess 15.

Such kinematic transmission is shown, for exemplifying purposes, in Figures 4 and 5A and 5B.

Figure 4 is a diagram showing the circular knitting machine and the kinematic transmission in an elevational view. Figure 5A shows a top plan view of the transmission and the contercam ring 17, and Figure 5B shows a side view of the upper part of the kinematic transmission.

The lifting of the splined needle cylinder of the machine, and, with it, of the circular support 1 which supports and guides the sinkers 3, is achieved by means of a cylinder-holder plate 19 which is pivotally mounted around a pivot 20, according to a kinematic arrangement known in the art.

The lifting of the circular support 1 causes the stitch loops formed in cooperation by the needler 13 and the sinkers 3 to be made longer. Simultaneously to the lifting and the sinking of the needle cylinder caused by the pivoting movement of the plat 19, its movement in the axial direction is transmitted to a vertical rod 21, which moves as shown by arrow A&min;.

The rod 21 is rigid with an arm 22, which translates coherently, remaining parallel to itself, relatively to a stationary frame 23, according to the movement allowed by a through pin 24 which moves rigid with the arm 22 inside a through slot 25 provided in the support 23.

The vertical motion of the arm 22 is transmitted, by means of an adjustable push-rod 26, to an arm 27, which is constrained with a pivot pin 28 to move according to a pivotal motion B&min; about a horizontal axis; a conical gear wheel 29 rotates with the pin 28, and makes a second conical gear 30 rotate according to revolving motion C&min; about a vertical axis.

A pivot pin 31 is rigid, with its lower end, with the conical gear wheel 30 and, with its upper end, with an arm 32 which, by means of a fork-shaped end 33, engages with a vertical stud 34 rigid with the countercam ring 17, and causes the above mentioned rotation R. A through bore 35 provided at the other end of the arm 32, and a clamp 36 make it possible to lock the arm 32 on the revolving pivot pin 31.

The contact of the arm 22 with the push-rod 26 is always secured by a spring 37.

The device according to the invention makes it possible to gradually and accurately position all the component segments of the cam ring 7 by means of the rotation of one single actuator element, and does not resort to a plurality of complex components, whose action must be coordinated and controlled.


Anspruch[de]
  • 1. Einstellvorrichtung für die Radiallage der Platinen (3) an einer Rundstrickmaschine, die mit Mitteln zur Änderung der Maschenlänge versehen ist, welche durch zwei konzentrische Steuerkurvenringe (6, 7) gebildet ist, die im wesentlichen kreisförmige Kontur in einer Ebene senkrecht zur Achse des Nadelzylinders haben und deren Mitte auf der Achse des Nadelzylinders positioniert ist und die durch einen ringförmigen Träger (8) in Stellung gehalten werden, wobei der innere Steuerkurvenring (6) radial stationär und der äußere Steuerkurvenring (7) in eine Vielzahl von Segmenten unterteilt ist, die an den Nadelzylinder in radialer Richtung in diskrete Positionen heranbewegt oder vom Nadelzylinder wegbewegt werden können, indem sie an den ringförmigen Träger (8) über eine schlaffe Verbindung angeschlossen sind, dadurch gekennzeichnet daß die Segmente entlang ihrer Außenkontur oder ihres Umfanges geformte Abschnitte in Form von Vorsprüngen (16) oder Ausnehmungen aufweisen; daß der ringförmige Träger (8) weiters einen im wesentlichen kreisförmigen Gegensteuerkurvenring (17) abstützt, der konzentrisch um den äußeren Steuerkurvenring (7) herum angeordnet ist, wobei der Gegensteuerkurvenring (17) eine Innenkontur hat, die mit geformten inneren Abschnitten in Form von Ausnehmungen (18) oder Vorsprüngen mit Zonen versehen ist, welche näher zur Mitte liegen, und weiteren Zonen, die relativ weiter von der Mitte entfernt sind, in einer komplementären Formation zu den vorstehend erwähnten Vorsprüngen (16) bzw. Ausnehmungen, wobei die Vorsprünge (16) des äußeren Steuerkurvenringes (7) in Kontakt mit den Ausnehmungen (18) des Gegensteuerkurvenringes (17) sind und umgekehrt; und daß das Einwärtsbewegen des äußeren Steuerkurvenringes (7), d.h. seiner Segmente, durch diskrete Winkelstellungen des Gegensteuerkurvenringes (17) bestimmt wird.
  • 2. Einstellvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Vorsprünge (16) gekrümmte Außenform haben.
  • 3. Einstellvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Vorsprünge (16) mit den Ausnehmungen (18) des Gegensteuerkurvenringes (17) unter der Wirkung der Zentrifugalkraft in Eingriff stehen, die auf die Platinen (3) während der Drehung der Strickmaschine einwirkt.
  • 4. Einstellvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die diskreten Winkelstellungen des Gegensteuerkurvenringes (17) auf die Höhe der Abschlagebene der Platinen (3) beschränkt sind.
  • 5. Einstellvorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß die Winkelstellungen des Gegensteuerkurvenringes (17), die einer Position minimalen radialen Vorschubes bzw. einer Position maximalen radialen Vorschubes der Platinen (3) entsprechen, auf das unterste Niveau bzw. das oberste Niveau der Abschlagebene der Platinen (3) beschränkt sind.
  • 6. Einstellvorrichtung nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß eine Zylinderhalteplatte (19) über eine vertikal bewegbare Stange (21) mit einem Arm (27) in Wirkverbindung steht, der um eine horizontale Achse schwenkbar ist, wobei der Arm (27) über Kegelräder (29, 30) mit einem Arm (32) in Wirkverbindung steht, der um eine vertikale Achse schwenkbar ist und mit einem vertikalen Zapfen (34) in Eingriff steht, welcher mit dem Gegensteuerkurvenring (17) fest verbunden ist, wobei die Axialbewegung der vertikalen Stange (21) eine Winkelbewegung des Gegensteuerkurvenringes (17) verursacht.
Anspruch[en]
  • 1. Control device for adjusting the radial position of the sinkers(3) in a circular knitting machine provided with means for varying the length of the stitch loops, constituted by two concentrical cam rings (6, 7) having a substantially circular contour in a plane perpendicular to the axis of the needle cylinder and with their centre being positioned on the axis of the needle cylinder, kept in position by an annulus-shaped support (8), wherein the innermost cam ring (6) is radially stationary and the outermost cam ring (7) is subdivided into a plurality of segments which can approach to, and move away from, the needle cylinder into discrete positions in radial direction by being connected to the annulus-shaped support (8) by means of a slack link, characterized in that the said segments have along their outer contour or periphery shaped portions in form of protrusions (16) or recesses; in that the annulus-shaped support (8) further supports a substantially circular countercam ring (17) concentrically located around said outer cam ring (7), the countercam ring (17) being provided with an inner contour which is provided with shaped inner portions in form of recesses (18) or protrusions with zones which are closer to the centre and further zones spaced relatively further away from the centre in a complementary formation to the above said protrusions (16) or recesses, respectively, the protrusion (16) of the outer cam ring (7) being in contact with the recesses (18) of the countercam ring (17) and vice versa; and in that the moving inward of the outer cam ring (7) ― i.e., of its segments ― is determined by discrete angular positions of said countercam ring (17).
  • 2. Control device according to claim 1, characterized in that the protrusions (16) have a curved outline.
  • 3. Control device according to claim 1 or 2, characterized in that the protrusions (16) engage the recesses (18) of the countercam ring (17) under the effect of the centrifugal force acting on the sinkers (3) during rotation of the knitting machine.
  • 4. Control device according to claim 1, characterized in that the discrete angular positions of the countercam ring (17) are enslaved to the level of the knocking-over plane of the sinkers (3).
  • 5. Control device according to claim 4, characterized in that the annular positions of the countercam ring (17) corresponding respectively to a position of minimum radial advancement and a position of maximum radial advancement of the sinkers (3), are enslaved respectively to the lowermost level and the uppermost level of the knocking-over plane of the sinkers (3).
  • 6. Control device according to claim 4 or 5, characterized in that a cylinder-holder plate (19) is operatively connected by a vertically movable rod (21) to an arm (27) pivotable about a horizontal axis, which arm (27) is operatively connected by conical gearings (29, 30) to an arm (32) pivotable about a vertical axis and engaging a vertical stud (34) rigid with the countercam ring (17), whereby axial displacement of said vertical rod (21) causes angular displacement of said countercam ring (17).
Anspruch[fr]
  • 1. Dispositif de commande pour ajuster la position radiale des platines (3) dans une machine à tricoter circulaire munie de moyens pour faire varier la longueur des boucles de maille, constitués par deux anneaux de came concentriques (6, 7) ayant un contour substantiellement circulaire dans un plan perpendiculaire à l'axe du cylindre d'aiguille, avec leur centre positionné sur l'axe du cylindre d'aiguille, maintenu en position par un support en forme d'anneau (8), dans lequel l'anneau de came situé le plus à l'intérieur (6) est radialement stationnaire et l'anneau de came situé le plus à l'extérieur (7) est divisé en une pluralité de segments qui peuvent s'approcher du cylindre d'aiguille et s'éloigner de celui-ci dans des positions discrètes dans la direction radiale en étant connectés au support en forme d'anneau (8) au moyen d'une liaison lâche, caractérisé en ce que lesdits segments possèdent, le long de leur contour extérieur ou de leur périphérie extérieure, des parties ayant une forme donnée formant des saillies (16) ou des cavités; en ce que le support en forme d'anneau (8) comporte de plus un anneau de contre-came substantiellement circulaire (17) disposé de façon concentrique autour dudit anneau de came extérieur (7), l'anneau de contre-came (17) étant muni d'un contour intérieur qui est muni de parties intérieures ayant une forme donnée, sous la forme de cavité (18) ou de saillies avec des zones qui sont plus proches du centre et d'autres zones espacées relativement plus loin du centre dans une formation complémentaire auxdites saillies (16) ou cavités ci-dessus, respectivement, la saillie (16) de l'anneau de came extérieur (7) étant en contact avec les cavités (18) de l'anneau de contre-came (17) et vice versa; et en ce que le déplacement vers l'intérieur de l'anneau de came extérieur (7) ― à savoir de ses segments ― est déterminé par des positions angulaires discrètes dudit anneau de contre-came (17).
  • 2. Dispositif de commande selon la revendication 1, caractérisé en ce que les saillies (16) ont un contour en courbe.
  • 3. Dispositif de commande selon la revendication 1 ou 2, caractérisé en ce que les saillies (16) viennent en contact avec les cavités (18) de l'anneau de contre-came (17) sous l'effet de la force centrifuge agissant sur les platines (3) durant la rotation de la machine à tricoter.
  • 4. Dispositif de commande selon la revendication 1, caractérisé en ce que les positions angulaires discrètes de l'anneau de contre-came (17) sont asservies au niveau du plan d'abattage des platines (3).
  • 5. Dispositif de commande selon la revendication 4, caractérisé en ce que les positions angulaires de l'anneau de contre-came (17) correspondant respectivement à une position d'avance radiale minimale et à une position d'avance radiale maximale des platines (3) sont asservies respectivement au niveau le plus bas et au niveau le plus haut du plan d'abattage des platines (3).
  • 6. Dispositif de commande selon la revendication 4 ou 5, caractérisé en ce qu'une plaque de support de cylindre (19) est connectée de façon opérationnelle par une tige mobile verticalement (21) à un bras (27) pouvant pivoter autour d'un axe horizontal, lequel bras (27) est connecté de façon opérationnelle par des engrenages coniques (29, 30) à un bras (32) pouvant pivoter autour d'un axe vertical et s'engrenant avec un goujon vertical (34) qui forme un tout rigide avec l'anneau de contre-came (17), grâce à quoi le déplacement axial de ladite tige verticale (21) provoque le déplacement angulaire dudit anneau de contre-came (17).






IPC
A Täglicher Lebensbedarf
B Arbeitsverfahren; Transportieren
C Chemie; Hüttenwesen
D Textilien; Papier
E Bauwesen; Erdbohren; Bergbau
F Maschinenbau; Beleuchtung; Heizung; Waffen; Sprengen
G Physik
H Elektrotechnik

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