EP0036004B1 - Coarse spinning-frame - Google Patents

Abstract

Coarse spinning-frame with suspended and pivotable blades (5), arranged at least on one row. The blades (5) are mounted on a frame (14) comprised of a longitudinal support (4) and of two arms (12, 13) arranged perpendicularly thereto. The frame (14) is pivotable about an axis (15) between an operating position and a removing position. A pivoting and loading system (18) is connected to the frame (14) so that the latter is blocked in its operating position. The present coarse spinning-frame has the particular advantage of providing, inter alia, a precise positioning of the pivoting blades (5) in their blocked operating position thereby providing a highly safe operation, particularly against accidents.

Description

The present invention relates to a pre-spinning machine with a machine frame and in this at least in one row of spindles and suspended above it, around a common, virtual longitudinal axis of the machine between an operating position and a pull-off position, into which the bobbins are pulled freely upwards out of the spindles can be pivoted wings.

Such a leader is z. B. in PCT-Anme avoidance No. WO 81/00264, which belongs to the state of the art within the meaning of Article 54 (3) EPC.

The pivotability of the wings of such a roving machine, which is also called a flyer, serves to decisively improve the usability of the machine, in particular the pulling and plugging operation of the bobbins. Because the wings can be pivoted away above the spindles, it is then possible to remove the finished bobbins placed on the spindles from the spindles in the vertical direction and also to place new empty sleeves on the spindles in the vertical direction. This simplifies the removal and attachment operation for the personnel if this operation is to be carried out by hand, or makes automation of this operation possible, as is described in detail in the PCT application mentioned.

• 1. die Positionierung aller Flügel einer Reihe senkrecht über den Spindeln präzis und sicher eingehalten wird ;
• 2. die Schwenkung aller Flügel einer Reihe absolut symmetrisch, d. h. unter Wahrung einer absoluten Parallelität aller Flügel der Reihe, geschieht ;
• 3. die Betriebslage der Flügel selbstverriegelnd ist, d. h. die Flügel der ganzen Reihe auch bei Stromunterbruch mit Sicherheit in dieser Lage bleiben sollen ;
• 4. Schwingungen der Flügel, vor allem während des Betriebs, d. h. wenn die Flügel in Betriebslage sind, vermieden werden ;
• 5. die tragenden und schwenkenden Elemente der Flügelreihe kräftemässig in der Betriebslage möglichst günstig gestaltet, bzw. diese genannten Elemente so gut wie möglich entlastet werden können. Dies bezieht sich vor allem auf die Längselemente (d. h. die Elemente in Längsrichtung) der Maschine.

The object of the present invention is to propose, in a roving machine of the type mentioned at the outset, a construction of the elements supporting and pivoting the wings of a row, in which:

• 1. the positioning of all wings in a row is maintained precisely and safely vertically above the spindles;
• 2. the pivoting of all the wings of a row is absolutely symmetrical, ie while maintaining an absolute parallelism of all the wings of the row;
• 3. the operating position of the wing is self-locking, ie the wing of the whole row should remain in this position with certainty even in the event of a power failure;
• 4. Vibration of the wings, especially during operation, ie when the wings are in the operating position, are avoided;
• 5. The load-bearing and pivoting elements of the row of wings are designed to be as cheap as possible in terms of force in the operating position, or these elements can be relieved as much as possible. This primarily relates to the longitudinal elements (ie the elements in the longitudinal direction) of the machine.

This object is achieved in a roving machine of the type mentioned above in that the wings of a row are mounted in a frame which consists of a longitudinal beam and at least two arms perpendicular to this, which are pivotally mounted at their free end in the machine frame about an axis of rotation , and which in the operating position are pressed by means of at least one pivot and loading system containing a spring against a first stop attached to the machine frame, and that the pivoting and loading system is kinematically connected to the frame and to the machine frame in such a way that it is in the operating position of the Frame by passing an unstable position, in which the pressing force has a maximum value, can be brought into a locking position, in which the pressing force is lower.

By passing an unstable position on the part of the frame supporting the wings of a row, the desired self-locking of the operating position of the wings is achieved. This ensures high operational and accident safety of the machine. The fact that the frame supporting the sash in its operating position is always pressed against a first stop attached to the machine frame by spring force, the exact positioning of all sashes in a row is ensured, the occurrence of vibrations in this position is avoided and the longitudinal elements are relieved. The storage of the wings of a row in a frame, as provided, also ensures the symmetrical positioning of all the wings of the row, while maintaining an absolute parallelism.

Further advantages of this invention are described in connection with the description of various preferred exemplary embodiments.

• Figur 1 schematisch und perspektivisch eine Sektion der erfindungsgemässen Vorspinnmaschine, wobei einfachheitshalber nur diejenigen Elemente dargestellt wurden, welche für das Verständnis der Erfindung nötig sind ;
• Figur 2 eine Seitenansicht (in Richtung des Pfeiles R von Fig. 1) eines Teiles der Vorspinnmaschine der Fig. 1, mit einem Schwenk- und Belastungssystem ;
• Figur 3 ein Diagramm des Verlaufs der Andruckkraft P während der Schwenkbewegung des Rahmens ;
• Figur 4 eine weitere Variante des Schwenk-und Belastungssystems, in derselben Ansicht wie in Fig. 2 ;
• Figur 5 eine Variante der erfindungsgemässen Vorspinnmaschine mit zwei Reihen Flügeln, in einer Seitenansicht entsprechend derjenigen der Fig. 2.

The invention will now be explained in more detail with the aid of a few illustrated exemplary embodiments. Show it :

• Figure 1 shows schematically and in perspective a section of the roving machine according to the invention, for the sake of simplicity only those elements were shown which are necessary for understanding the invention;
• FIG. 2 shows a side view (in the direction of arrow R of FIG. 1) of a part of the pre-spinning machine of FIG. 1, with a swivel and loading system;
• Figure 3 is a diagram of the course of the pressing force P during the pivoting movement of the frame;
• FIG. 4 shows a further variant of the swivel and loading system, in the same view as in FIG. 2;
• 5 shows a variant of the roving machine according to the invention with two rows of wings, in a side view corresponding to that of FIG. 2nd

In Fig. 1, the spindle bank of a roving machine is indicated by 1. The spindle bench 1 carries along a row of spindles 2 arranged at regular intervals, which, in a manner known per se, with not shown be driven. The spindle bench 1 is guided in a manner known per se in the machine frame 3 by means of vertical guides (not shown) and is moved up and down along this with means not shown.

Above the spindle bench 1 are mounted in a longitudinal member 4 and driven by means not shown, wings 5, which, as is known from the above PCT application, around a common, virtual longitudinal axis of the machine between an operating position in which it is coaxial with the rotate corresponding spindles 2, and a withdrawal position in which the coils (only one coil 6 is shown) can be freely pulled upwards out of the spindles 2, are pivotable.

The axes 7 of the wings 5 are hollow, so that between the upper part of the longitudinal member 4 and the wings 5 through holes 8 for the known from a drafting system, of which only the delivery rollers 9 and 10 are indicated in FIG. 1 Fuse 11 are provided. The continuous rollers of the drafting system, such as. B. the lower roller 9 are stored in a conventional manner in the machine frame.

The longitudinal beam 4 is connected at both ends to an arm 12 or 13, which is perpendicular to it, with which it forms a rigid frame 14. At their free ends, the arms 12 and 13 are pivotally mounted in the machine frame 3 in an axis of rotation 15. 1, the machine frame 3 has a tab 16; but it is clear that the shape of the machine frame 3 can be chosen arbitrarily. The axes 15 of both arms 12 and 13 are coincident and form the virtual longitudinal axis of the machine known per se, about which the wings 5 of a row of wings can be pivoted from the operating position into the pull-off position.

Furthermore, each machine frame 3 has a stop 17 for the arm 12 or 13, with which the operating position of the frame 14 and thus the wing 5 is determined. In Fig. 1 the frame 14 is shown in the operating position, i. H. the arms 12 and 13 are pressed against the stop 17.

In this position, the spindles 2 and the wings 5 rotate about their axes, and the delivery rollers 9, 10 of the drafting system deliver fiber webs 11 to each spinning station. The winding of the fuse 11 onto each coil 6 by means of the interaction of the spindle 2 and the wing 5 is known per se and therefore need not be described in more detail here.

It should only be noted that all of the wings 5 of a row always run parallel to one another (that is, so that the planes containing the two legs 5a, 5b of each wing 5 are all parallel to one another), and that their parking position is chosen so that their Pivoting together with the frame 14 as described in PCT application No. WO 81/00264 happens.

The aforementioned pressing of the arms 12 and 13 against the corresponding stop 17 and the pivoting of the frame 14 from the operating position into the pull-off position are now realized by means of the pivoting and loading system according to the invention, for the explanation of which the help of FIGS. 2 and 3a to 3c is necessary.

FIG. 2, in which the roving machine of FIG. 1 is shown from the side in the direction of the arrow R, shows a first variant of the pivoting and loading system 18 for the frame 14.

At any point on the frame 14, e.g. B. at a point of the arm 12, the piston rod 20 of a spring-loaded cylinder-piston system 21 is articulated by means of an axis 19. A preloaded compression spring 23 is contained in the interior of the cylinder 22 and continuously exerts a compressive force on the piston 24. The cylinder 22 is connected at its end opposite the piston rod 20 to the crank 25 of a crankshaft 26 rotatably mounted in the machine frame 3 by means of an axis 27. 2, the operating position of the frame 14 is shown in solid lines, while its retracted pull-off position is shown in broken lines, in which the coils 6 can be pulled off vertically via the spindles 2. F also denotes the curve which describes the center of the axis 19 when the frame 14 is pivoted about the axis of rotation 15. It is an arc with a center in the axis of rotation 15.

• a) Die Verbindungslinie m zwischen den Zentren der Achsen 19 und 27 bildet mit der Verbindungslinie n zwischen den Zentren der Kurbelwelle 26 und der Achse 27 einen spitzen Winkel β.
• b) Der Kolben 24 ist im Zylinder 22 frei bewegbar, d. h. steht nicht am Anschlag 28 des Zylinders 22 an ; dies bedeutet, dass in dieser Lage die volle Federkraft der Feder 23 sich über die Kolbenstange 20 auf den Arm 12 und somit auf den Rahmen 14 überträgt : der Rahmen 14 wird also gegen den Anschlag 17 ständig angedrückt.

The arrangement of the axes of rotation 15 and 27 fixed in the machine frame 3 in space as well as the dimensions of the different lever arms (distance between the axis 15 and the axis 19 in the arm 12, between the axis 19 and the axis 27 in the cylinder-piston system and the length of the crank 25) and the position of the first stop 17 are selected so that the following two conditions are met in the operating position of the frame 14:

• a) The connecting line m between the centers of the axes 19 and 27 forms an acute angle β with the connecting line n between the centers of the crankshaft 26 and the axis 27.
• b) The piston 24 is freely movable in the cylinder 22, ie is not in contact with the stop 28 of the cylinder 22; this means that in this position the full spring force of the spring 23 is transmitted via the piston rod 20 to the arm 12 and thus to the frame 14: the frame 14 is therefore constantly pressed against the stop 17.

Because the line of action m of the spring force forms an acute angle β with the connecting line n, a reaction in the clockwise direction is exerted on the crank 25 of the crankshaft 26 by the reaction of the pressing force. This moment can be recorded in that the shaft 26 is blocked against further rotation in the clockwise direction in this position. According to a preferred solution of the fiction According to the roving machine, however, there is a second stop 29 attached to the machine frame 3, against which the crank 25 is pressed, thus preventing further rotation thereof in the clockwise direction.

This solution has the advantage that the torque exerted on the crank 25 in a clockwise direction is not transmitted to the crankshaft 26, but is carried by the machine frame 3 via the stop 29. This allows a welcome relief of the crankshaft 26 in the operating position of the frame 14, which is of particular importance if, as is often the case in practice, the machine has a large number of spindles 2.

In such cases, the machine is divided into individual sections by a few spindles, which are separated by the walls of the machine frame 3: the forces are thus transmitted to the various intermediate walls of the machine frame 3, while the long, continuous crankshaft 26 does not subject to any torsional stress during the time the swing phase is subjected to a much longer operating phase.

It should be noted that the expression “cylinder-piston system” should not be understood here in a pneumatic sense. The cylinder 22 merely forms a straight guide for the piston 24, on which the pressure force of the spring 23 acts. The choice of a closed cylinder 22 as a guide offers only constructive advantages, since the guides, or the piston 24 and the spring 23 in particular, can be shielded well from the external influences (such as flight deposits, etc.); however, other mechanisms with the same function of the cylinder-piston system, such as. B. open guides, thought and realized within the scope of this invention.

In Fig. 2, the pull-off position of the frame 14 and the corresponding position of the pivoting and loading system 18 are shown with dashed lines: by rotating the crankshaft 26 counterclockwise, the axis 27 of the crank 25 is moved along the arcuate path o, with which the cylinder Piston system 21 moves the axis 19 along the line f clockwise and causes the frame 14 to pivot. During this movement of the swiveling and loading system 18, it is clear that the piston 24 in the cylinder 22 is first displaced from the right to the left by the spring 23 up to the stop 28 in the cylinder 22.

3a to 3d show the pivoting and locking process based on a simplified representation of the lever mechanism described. In Fig. 3a, the frame 14, or the arm 12, is shown in its pull-off position: the crank 25 has assumed the position shown here, which is referred to here as the initial position of the pivoting process and by the angle a = 0 (a = angle between the position of the crank 25 at the beginning of the pivoting process and its respective position) is characterized. The frame is not pushed against the stop 17, so that the pressing force P is zero in this position. The spring 23, on the other hand, presses the piston 24 (FIG. 2) of the loading system 18 against the stop 28, with a force that corresponds to the pretension of the spring 23.

3b, the crank 25 has now been rotated clockwise by the angle a = 38 °: in this position, the arm 12 just comes into contact with the stop 17, so that the pressing force P _b is still = 0. Every small rotation of the crank 25 in a clockwise direction, however, compresses the compression spring 23, ie the piston 24 (FIG. 2) rises from the stop 28 of the cylinder 22 and the full preload of the spring 23 is on the axis 19 of the arm 12 transfer. The pressing force P _" now acts against the stop 17, which is equal to the preload of the spring times the lever length ratio. In other words, at the angle a == 38 °, the pressing force against the stop 17 increases abruptly from 0 to the value P _v : from from now on, each further rotation of the crank 25 in a clockwise direction will cause the pressing force P to increase, corresponding to the spring characteristic of the compression spring 23. The course of the pressing force P as a function of the angle a is shown in FIG.

3c shows the position of the swivel and loading system 18, in which the axes 19, 27 and the crankshaft 26 come to lie on a straight line, in which case a = 51 °. In this position, the compression spring 23 is pressed the most, ie the pressing force P is reached, at a = 51 °, the maximum value P _max . This position is therefore an unstable position of the system, since from now on the pressing force P can only decrease with a further rotation of the crank 25 in the clockwise direction as well as in the counterclockwise direction.

In Fig. 3d, the operating position of the frame 14, or the arm 12 and the pivoting and loading system 18 is shown. The crank 25 has been rotated clockwise relative to FIG. 3c up to the angle a = 58 °: the pressing force P has therefore dropped from the value P _max to the value P _B. The system has become stable again because the spring force of the spring 23 is now clearly trying to turn the crank 25 clockwise. The position in FIG. 3d is therefore a locking position of the pivoting and loading system 18, since the frame 14 can only be returned from this operating position by passing an unstable position (FIG. 3c) into the pull-off position of FIG. 3a using an external force .

4 shows a variant of the pivoting and loading system 18 which offers advantages in terms of power engineering. The same elements as in the arrangement of FIGS. 1 and 2 are denoted by the same reference numerals. The difference between this arrangement and that of the previous figures is that here the crank 25 is part of a toothed segment 30. The position of axes 19, 27 and 31 corresponds exactly to that of the variant described above, so that this device works in exactly the same way. The toothed segment 30, which is rotatably mounted about an axis 31 which is fixed in the machine frame (not shown), is rotated in both directions of rotation by means of a toothed pinion 33 which is seated on a longitudinal shaft 32, which is also rotatably mounted in a fixed point of the (not shown) machine frame driven. Due to the reduction between the pinion 33 and the toothed segment 30, it can thus be achieved that the longitudinal shaft 32, which preferably extends along the entire machine side, has to transmit a smaller torque for the swiveling process (or in particular for overcoming the unstable position), so that it is lighter in weight can be. Furthermore, this reduction in strength allows the toothed pinion 33 to select relatively soft, but low-noise and low-maintenance materials, such as. B. plastics, and especially if, as shown in Fig. 4, the toothed segment 30 is secured in the operating position against further rotation in the clockwise direction by means of a stop 34 (the function of which corresponds to that of the stop 29 of Fig. 2) . In this case, the stop 34 carries the torque exerted by the load system 18 on the toothed segment 30 during the long-term operating position, so that the pinion 33 and the longitudinal shaft 32 are relieved and are only used for the pivoting operation.

FIG. 4 further shows that a plate spring assembly 35 can advantageously be used as the spring in the cylinder-piston system 21. This type of spring, which is known per se, is very well suited for use in the context of this invention because of its stiff characteristic, since naturally relatively small deflections can be expected here.

5 shows a variant of the roving machine according to the invention, in which, as is often the case in practice, two parallel rows of wings are provided, each of which is mounted in a pivotable frame.

In Fig. 5, which shows a schematic representation of the two-row roving machine, seen in the direction of arrow R of Fig. 1, 36 denotes the machine frame in which the two arms 37 and 38 are rotatably mounted in the corresponding pivot axes 39 and 40 are. The arms 37 and 38 each form a frame 43 and 44 with a longitudinal beam 41 and 42 and with an arm not visible, in the longitudinal beam 41 and 42 the wings (not shown) are mounted in rows and driven. According to the invention, both frames 43 and 44 are now connected to one another with a connecting piece 45 such that they always remain parallel to one another, which, for. B. can be achieved, as shown in FIG. 5, that the length of the connecting piece 45 is selected equal to the distance between the pivot axes 39 and 40, in the sense of a parallel guide.

In the context of this invention, however, all connection methods are conceivable in which the frames 43 and 44 are always kept parallel. In such a roving machine, the invention provides that, for both sets of blades, respectively, for both frames 43 and ^44: there is provided a common pivoting and loading system 46 which, for. B. may look exactly the same as that of the variant in FIG. 1 and therefore need no longer be described.

The advantage of this solution lies in the simplicity of the swivel and locking device.

Further advantages can be achieved in the roving machine mentioned here if, as also shown in FIG. 5, the pivoting and loading system 46 with the frame 43 of a row of wings, for. B. is connected via the axis 47, while the frame 44 of the other row of wings is pressed against the first stop 48. This solution offers the advantage that the flow of forces generated by the spring (not shown) of the pivoting and loading system 46 extends over all articulation points between the first stop 48 and the crankshaft 49, or the stop 50, if one is provided , whereby the entire system of the two frames 43 and 44 in the operating position (which is shown in Fig. 5 with solid lines) is kept under constant pressure. This prevents any swinging of the individual parts of the double frame structure.

In FIG. 5, the stripping position of the frames 43 and 44 is also shown in dashed lines.

Furthermore, FIG. 4 shows how, according to a further preferred embodiment variant of the invention, the first stop 17 determines the operating position of the wings and is designed to be adjustable: a very simple way to achieve the desired adjustability consists in the stop 17 to be designed as a screw 52 which can be screwed into a fixed support 51. The screw 52 is fixed in its position by a lock nut 53.

Claims (9)

1. Roving frame with a machine frame and spindles arranged therein in at least one row and flyers suspended thereabove and about a common, imaging longitudinal axis of the machine between an operating position and an removal position in which the packages can be freely removed upwardly from the spindles, characterised in that the flyers (5) are supported in a row in a framework (14 ; 43, 44) comprising a,longitudinal carrier (4 ; 41, 42) and at least two arms (12, 13 ; 37, 38) which are arranged normal thereto, are supported at their free ends in the machine frame (3 ; 36) for pivoting about an axis (15 ; 39, 40) and in the operating position are pressed by means of at least one pivoting and loading system (18 ; 46) including a spring (23 ; 35) against a first abutment (17 ; 48) mounted on the machine frame (3 ; 36), and in that the pivoting and loading system (18 ; 46) is kinematically connected to the framework (14 ; 43, 44) and to the machine frame (3 ; 36) in such manner that, in the operating position of the framework (14 ; 43, 44), the system can be moved, by passing an unstable position in which the contact force has a maximum value, into a latching position in which the contact force is less.

2. Roving frame according to claim 1, characterised in that the pivoting and loading system (18 ; 46) comprises a spring-loaded piston and cylinder system (21) which is pivotally connected on one side with a fixed point (19) on the framework (14 ; 43, 44) and on the other side with the crank (25) of a crankshaft (26 ; 31, 49) rotatably supported in the machine frame (3 ; 36).

3. Roving frame according to claim 2, characterised in that the crank (25) is formed by a part of a toothed segment (30).

4. Roving frame according to claim 2, characterised in that, in the operating position of the frame work (14), the crank (25) engages a second abutment (29) mounted on the machine frame (3).

5. Roving frame according to claims 3 and 4, characterised in that, in the operating position of the framework (14), the toothed segment (30) engages the second abutment mounted on the machine frame (3).

6. Roving frame according to claim 2, characterised in that the piston and cylinder system (21) is biased by an assembly of plate springs (35).

7. Roving frame according to claim 1, characterised in that the first abutment (17) determines the operating position of the flyer (5) and is made adjustable.

8. Roving frame according to claim 1, characterised in that two parallel rows of flyers are provided, supported in respective pivotable frameworks (43, 44), and in that the two frame works (43, 44) are so coupled by a connector piece (45) that they always remain parallel to one another, and in that a common pivoting and loading system (46) is provided for both parallel pivotable frameworks (43, 44).

9. Roving frame according to claim 8, characterised in that the pivoting and loading system (46) is connected to the framework (43) of one flyer row, while the framework (44) of the other flyer row is pressed against the first abutment (48).

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