EP0620301B1 - Device for adjusting capsule yarn brakes on twisting machines, in particular two-for-one twisting machines - Google Patents

Description

The invention relates to a device for adjusting capsule thread brakes on twisting machines, in particular double-wire twisting machines with several twisting spindles, in which each capsule thread brakes, which are arranged within the hub of the coil carrier of the twisting spindles and have a brake cartridge supported between two brake rings lying one above the other in the axial direction, by axial displacement the force of a compression spring and wiring of a brake ring can be adjusted in stages to different braking force values. The invention further relates to a device on a twisting machine, in particular a double-wire twisting machine, with at least one twisting spindle which has a bobbin and in which a capsule thread brake with a cylindrical housing is arranged within the hub of the bobbin. through which the thread is passed in the axial direction, and the thread outlet part has a first brake ring on which a brake cartridge is supported, on the upper end of which a second brake ring is seated, at least one of the brake rings being attached to a cylindrical brake ring carrier which is movable in an axial direction in a housing is arranged, on the side facing away from the brake ring, a compression spring acts, which is supported with its other end on the housing.

Such a capsule thread brake for a twisting spindle is described for example in DE-PS 1 510 860. Capsule thread brakes have a brake cartridge with an upper and a lower sleeve, which can be freely moved together and between which a compression spring is enclosed. In the known capsule thread brake, the braking force is set by hand, by lifting the brake ring carrier in the axial direction against the action of the compression spring, rotating it about a certain angular amount about its axis and then lowering it under the action of the compression spring into a new position in which the support stop on one of the support shoulders arranged at different axial heights within one of the axial slots. This braking force setting must be carried out manually on each individual twisting spindle of a twisting machine.

Thread brakes are also known which can be simultaneously adjusted in a centrally controlled manner in parallel operation. However, these brakes are designed, for example, as disc brakes (see CH-PS 636 577), which are controlled with compressed air.

A device on a double-wire twisting spindle for controlling thread brakes or the like is also known (see DE-PS 1 510 853), in which a thread brake can be actuated via an electromagnetic control device which is effective through the rotating thread balloon. In one embodiment of this known thread brake, an oval-shaped brake sleeve sits between two brake rings, one of which is axially movably mounted on an elastically expandable bellows which is filled with a fluid medium and is connected via a line to a further bellows which is made of the same medium is filled and to which a pressure is exerted by means of the electromagnetic control device, which is transmitted to the first bellows and thus exerts a pressure on the axially movable brake body, which leads to an increase in the braking force. In this known device, which can also be controlled centrally, an adjustment of the braking force is only possible within narrow limits.

The invention is based on the object, in a twisting machine in which the twisting spindle or the twisting spindles are each provided with a capsule thread brake which has the above-mentioned features, to enable central control of the capsule thread brake which is structurally simple and functionally reliable and which is large Adjustment range entails.

This object is achieved according to the invention according to the features of the characterizing part of patent claim 1. A twisting machine with a device according to the invention for controlling a capsule thread brake is described in claim 2. Advantageous developments of the invention are the subject of dependent claims 3 to 15.

The basic idea of the invention is to develop the capsule thread brake according to DE-PS 1 510 860 in such a way that the brake ring carrier or the guide part connected to it is automatically axially displaceable and automatically performs a rotation by a predetermined angular amount during the displacement process, which cycles it in Positions moved in which, after the brake ring carrier has been pushed back, the support stop rests on a support shoulder which is arranged at a different axial height, as a result of which the braking force is adjusted.

As explained in more detail below with the aid of exemplary embodiments, the two opposing toothed segments on the brake ring carrier or guide part can be designed such that a sufficient number of brake settings is achieved over the desired braking force range and due to the special design of the opposing inclined surfaces when being pushed back and forth of the brake ring carrier by means of compressed air and spring force, a safe and automatic rotation of the brake ring carrier by the desired angular amounts is achieved.

Of course, it is also possible to design the device in a kinematic reversal of the conditions so that the support shoulders are arranged on the inside of the housing, while a radially outwardly projecting support stop is arranged on the circumference of the guide part and can be inserted into the axial slots.

The supply of the compressed air pulses required for lifting the brake ring carrier takes place via a compressed air line which is guided through the hub of the coil carrier and the coil carrier base and can, for example, be guided radially outwards to the wall of the protective pot jacket to a connection opening in the outer jacket of the protective pot, which is a radial Movable connector connected to a compressed air source is opposite a connector unit. A "compressed air pulse" in the sense of the invention is understood to mean a brief increase in the pressure in the compressed air line with subsequent relaxation or a brief decrease in pressure with a subsequent rise in the sense of a "negative pressure pulse". The connection units of all the twisting spindles of a twisting machine are connected to a common compressed air line, into which a control device for generating compressed air pulses is switched on.

The invention opens up the advantageous possibility of combining the control of the thread brake by means of compressed air with the known control of a threading device by means of compressed air, as described for example in DE-PS 2 461 796 and US-PS 3 975 893. In this way, both the threading and the adjustment of the capsule thread brake can be carried out centrally via one connection unit or two connection units per twisting spindle. This leads to a significant reduction in set-up times for multi-position machines.

Overall, a considerable amount of time is saved when operating the twisting machines.

Exemplary embodiments of a twisting machine according to the invention are explained in more detail below with reference to the accompanying drawings.

• Figur 1 in schematischer Darstellung in teilweise geschnittener Seitenansicht eine Doppeldraht-Zwirnspindel mit einer zentral ansteuerbaren Kapselfadenbremse;
• Figur 2 in perspektivischer Darstellung einen Teil einer Spindelbank für eine Zwirnmaschine mit fünf Zwirnspindeln, deren Kapselfadenbremsen zentral ansteuerbar sind;
• Figur 3 in einem Teilschnitt die Spindelhohlachse einer Zwirnspindel nach Figur 1 mit einer ansteuerbaren Kapselfadenbremse und einer Einrichtung zum automatischen Einfädeln;
• Figur 4 in einer vergrößerten, abgewickelten Teildarstellung den Bremsringträger nach Figur 3; Figuren 4a bis 4c in perspektivischer Teildarstellung den Bremsringträger nach Figur 3 in unterschiedlichen Stellungen;
• Figur 5 in einer geschnittenen, gegenüber Figur 1 vergrößerten Darstellung, einen Teil des Schutztopfes der Zwirnspindel nach Figur 1 mit der Anschlußöffnung und der Anschlußeinheit für die Druckluft;
• Figur 6 in einer Darstellung analog Figur 5 eine Variante für die Ausbildung der Anschlußöffnung und der Anschlußeinheit zur Zuführung der Druckluft.
• Figur 7 in einer Darstellung analog Figur 1 eine Doppeldraht-Zwirnspindel mit einer durch eine Einrichtung nach Figur 9 oder 10 zentral ansteuerbaren Kapselfadenbremse.
• Figur 8 in einer Darstellung analog Figur 2 einen Teil einer Spindelbank für eine Zwirnmaschine mit fünf Zwirnspindeln, deren Kapselfadenbremsen mittels einer Einrichtung nach Figur 9 oder 10 zentral ansteuerbar sind;
• Figur 9 in einem Teilschnitt ähnlich Figur 3, die Spindelhohlachse einer Zwirnspindel nach Figur 7 mit einer ansteuerbaren Kapselfadenbremse und einer Einrichtung zum automatischen Einfädeln;
• Figur 10 in einer Darstellung ähnlich Figur 3, in einem Teilschnitt die Spindelhohlachse einer Zwirnspindel nach Figur 7 mit einer weiteren Ausführungsform einer ansteuerbaren Kapselfadenbremse und einer Einrichtung zum automatischen Einfädeln.

The drawings show:

• Figure 1 is a schematic representation in a partially sectioned side view of a double-wire twisting spindle with a centrally controllable capsule thread brake;
• FIG. 2 shows a perspective view of part of a spindle bench for a twisting machine with five twisting spindles, the capsule thread brakes of which can be controlled centrally;
• 3 shows a partial section of the hollow spindle axis of a twisting spindle according to FIG. 1 with a controllable capsule thread brake and a device for automatic threading;
• FIG. 4 shows the brake ring carrier according to FIG. 3 in an enlarged, developed partial representation; Figures 4a to 4c in perspective partial representation of the brake ring carrier according to Figure 3 in different positions;
• FIG. 5 shows a section of the protective pot of the twisting spindle according to FIG. 1 with the connection opening and the connection unit for the compressed air in a sectional illustration, enlarged compared to FIG. 1;
• Figure 6 in a representation analogous to Figure 5 shows a variant for the formation of the connection opening and the connection unit for supplying the compressed air.
• FIG. 7 in a representation analogous to FIG. 1, a double-wire twisting spindle with a capsule thread brake which can be controlled centrally by a device according to FIG. 9 or 10.
• FIG. 8 in a representation analogous to FIG. 2, part of a spindle bench for a twisting machine with five twisting spindles, the capsule thread brakes of which can be controlled centrally by means of a device according to FIG. 9 or 10;
• Figure 9 in a partial section similar to Figure 3, the hollow spindle axis of a twisting spindle according to Figure 7 with a controllable capsule thread brake and a device for automatic threading;
• 10 in a representation similar to FIG. 3, in a partial section the hollow spindle axis of a twisting spindle according to FIG. 7 with a further embodiment of a controllable capsule thread brake and a device for automatic threading.

In FIG. 1, only the parts necessary for the following explanation of the capsule thread brake and its actuation are shown of a double-wire twisting spindle S1, namely the bobbin with bobbin bottom 1.1 and protective pot 1 and the hub of the bobbin with spindle hollow shaft 2 mounted therein, on which a supply spool SP is arranged, from which two threads F1 and F2 are drawn off and inserted through the thread inlet tube 3 into the spindle hollow axis 2 and passed through the capsule thread brake in a manner not shown in FIG. 1.
The thread F radially emerging on the thread storage disk 4 of the spindle rotor 5 becomes upward in the thread balloon between the jacket of the protective pot 1 and a balloon limiter 6 to a thread guide eyelet, not shown guided. The spindle rotor 5 is rotated via a whorl.

The capsule thread brake, explained in more detail below, within the hub 2 of the bobbin is controlled centrally by means of compressed air. For this purpose, a connection unit 7 is arranged outside the twisting spindle in the region of the lower edge of the protective pot 1, which is connected to a compressed air source and has a plunger 23 which can be extended radially in the direction of the protective pot of the bobbin 1 and which passes through an opening 6.1 in the balloon limiter 6 can be attached to a connection opening 28 on the coil carrier base 1.1, to which a compressed air line 16 connects, via which compressed air pulses can be supplied.

The supply of compressed air to the adjusting mechanism of the capsule thread brake, which is explained further below, thus takes place in the same way as in the threading device known from DE-PS 2 461 796 and US-PS 3 975 893.

As can be seen from FIG. 2, the compressed air is supplied via a compressed air line 48 which is guided along a spindle bank 51 with twisting spindles S1 to S5 and to which the connection units 7 are connected via branch lines 21. The compressed air line 48 is connected via a feed line 49 to a compressed air source, not shown. Via an indicated control device 50, the compressed air pulses can be generated in line 48 lead in the manner explained below to the adjustment of all capsule thread brakes in the twisting spindles which are connected to the line 48 via the connection units 7.

The design and mode of operation of the adjustment mechanism for the capsule brakes are explained in more detail below with reference to FIGS. 3, 4 and 4a to 4c.

The capsule thread brake shown in FIG. 3 is inserted into the hub of the bobbin 1 as an extension to the hollow spindle axis 2. It has a housing 8, which is closed on its upper side with a screw cap 9, through which the thread inlet tube 3 is led upwards. The capsule thread brake arranged in the housing 8 has a first brake ring 10 arranged on the thread outlet side and firmly connected to the housing 8, on which a brake cartridge is supported, which in a known manner consists of two sleeve parts 11 and 11.1 which can be displaced against each other against spring force. On the upper end of the upper sleeve part 11.1 of the brake cartridge sits a second brake ring 12, which is fastened to a brake ring carrier 12.1, which is arranged at the lower end of a cylindrical guide part 13. The guide part 13 with the upper brake ring carrier 12.1 is displaceable and rotatable in the axial direction within the housing 8. A shift upwards is counteracted by the force of a compression spring 17, which rests on a shoulder of the guide part 13 and is supported with its upper end on the underside of the cover 9.

On the guide part 13, an annular piston 14 is arranged outside the second brake ring 12 and coaxially thereto, which extends downward and is displaceably guided in an annular cylinder 15 arranged in the wall of the housing 8. The ring cylinder 15 is connected at its end opposite the ring piston 14 to the compressed air line 16, which is guided radially through the bottom 1.1 of the coil carrier 1 to the connection opening 28 in the manner already described and as shown in FIG. 1.

As can also be seen in FIG. 3, the twisting spindle according to FIG. 1 is additionally provided with a threading device 52 of a known type, which is designed as an injector, to which compressed air P2 can be fed via a compressed air line 47. The brake ring carrier 10.1 for the lower brake ring 10 of the capsule thread brake is designed as a compressed air piston which can be moved downward against the force of a helical spring 10.2. During the threading process, under the action of the injector 52, a negative pressure is generated below the brake ring carrier 10.1, as a result of which the brake ring carrier 10.1 is moved downward and thus the lower brake ring 10 releases the brake cartridge 11, which is supported by a support ring 8.1 connected to the housing 8 in such a position it is noted that the thread fed through the thread inlet tube 3 is sucked past the brake cartridge 11 under the effect of the negative pressure and is guided through a thread guide tube 4.1 into the thread storage disk 4. Such a device is known and described for example in DE-PS 3 243 157.

A first upper toothed segment 18 and a second lower one are circumferential on the guide part 13 in the circumferential direction Tooth segment 19 arranged. The downward-facing teeth of the upper toothed segment 18, with their gaps, form slots that open downwards in the axial direction, the slot bottoms of which represent support shoulders, which are each arranged at different axial heights and to which each radially follows depending on the setting of the rotatable guide part 13 inside projecting support stop 20, which is designed as a positioning pin, can be brought into contact. The more precise design and arrangement of the upper toothed segment 18 and the lower toothed segment 19 can be seen in FIGS. 4, 4a, 4b and 4c. The downward-facing teeth of the upper toothed segment 18 directly adjoin one another in the circumferential direction and each have a flank 18.2 leading the slot bottom 18.1 in the circumferential direction UR, which is designed as an inclined surface that slopes away from the circumferential direction UR and is at an angle with the circumferential direction UR 45 ° includes. The flank 18.3 trailing the slot bottom 18.1, however, runs at a small angle to the axial direction. In an analogous manner, in the lower toothed segment 19, the flank 19.2 leading the slot bottom 19.1 in the circumferential direction UR is designed as an inclined surface rising to the circumferential direction UR, which likewise encloses an angle of approximately 45 ° with the circumferential direction, while the flank 19.3 trailing the slot bottom 19.1 essentially runs in the axial direction. Furthermore, as can be seen from FIGS. 4, 4a to 4c, the lower tooth segment 19 is offset from the upper tooth segment 18 in the circumferential direction UR by the amount of approximately half a tooth spacing, which is approximately the diameter X corresponds to the support stop 20, so that in each case an inclined surface 18.2 of the upper toothed segment 18 is opposite a slot bottom 19.1 of the lower toothed segment 19, while conversely the inclined surface 19.2 of the lower toothed segment 19 is opposite one of the slot bottoms 18.1 of the upper toothed segment 18.

The result of this design is that when the guide part 13 is raised and lowered, a section-wise rotation thereof in the circumferential direction UR is initiated. The processes can be read from FIGS. 4 and 4a to 4c. In FIG. 4a, the support stop 20 is located in the lowered guide part 13 in the slotted bottom 18.1 of the upper toothed segment 18, as is shown in FIG. 4b. If the guide part 13 is raised in the direction of arrow H, the support stop 20 firmly connected to the housing 8 arrives at the Inclined surface 19.2 of the lower tooth segment 19, which has the consequence that, in addition to the axial displacement in the direction H, a movement component occurs in the circumferential direction UR, which leads the support stop 20 into the slot bottom 19.1 of the lower tooth segment 19, as shown in FIG. 4b. The upward movement of the guide part 13 in the direction H takes place by introducing compressed air via the compressed air line 16 into the cylinder 15. When the compressed air is released from the cylinder 15, the direction of movement of the guide part 13 reverses under the action of the compression spring 17 and a downward movement takes place in the direction of arrow T in FIG. 4c. With this downward movement the support stop 20 led to the inclined surface 18.2 of the toothed segment 18, which in turn leads to a movement component in the circumferential direction UR, so that when the axially performed downward movement T is completed, the support stop 20 now sits in the slot bottom 18.1 designated by II in FIGS. 4a to 4c, and thus that Guide part 13 and with it the brake ring carrier 12.1 was rotated by exactly one tooth spacing or slot bottom spacing in the circumferential direction UR. Since the slot bottom 18.1 is higher in the axial direction at point II than the slot bottom 18.1 at point I, the brake ring 12 is also in a correspondingly higher position, which leads to a different setting of the braking force between the brake cartridge 11 of the capsule thread brake and the two Brake rings 10 and 12 leads. As can be seen from FIG. 4c, the slot bottom 18.1 of the upper ring gear 18, designated III, is arranged in the axial direction a further distance higher, so that when a further pressure pulse is applied, the guide part 13 is adjusted again in the manner already described .

The path of the support stop 20 between the teeth of the two tooth segments can be read from FIG. From the slot bottom 18.1, the support stop 20 runs during the upward movement in the direction H into the position 20a, in which it meets the inclined surface 19.2, on which it slides into the position 20b. From there it arrives during the downward movement of the guide part 13 in the direction T, into the position designated 20c, in which it moves onto the the next leading flank 18.2 'of the upper toothed segment 18 arrives, on which it is guided into position 20d in the next slot bottom 18.1'. The angles of the inclined surfaces 18.2 and 19.2 are selected so that a sliding of the support stop 20, which leads to a rotation of the guide part 13 in the circumferential direction UR, is possible without the risk of self-locking.

The toothed segments 18 and 19 are distributed over the entire circumference of the guide part 13, and the position of the slot bottoms and the arrangement of the inclined surfaces and the height of the teeth are dimensioned such that the above-described process of guiding the support stop 20 over the entire circumference and thus the guidance of the guide part 13 from a raised position into more lowered positions and back into the raised starting position is ensured over the entire circumference.

The supply of the compressed air pulses actuating the piston-cylinder unit 14-15 is explained below with reference to FIGS. 5 and 6.

FIG. 5 shows the connection unit 7 already indicated in FIG. 1 and arranged in the region of the lower edge of the protective pot 1 outside the balloon limiter 6, which is designed as a piston-cylinder unit with the cylinder 7, which is connected via the line 21 to the collecting line 48 shown in FIG and in which a piston 22 is guided, on which a plunger 23 is seated as a connecting piece, which plunger leads out of the cylinder 7 through an opening 7.1 on the side facing the balloon limiter 6 is. The movement of the piston 22 when the cylinder 7 is pressurized with compressed air 21 takes place against the action of a compression spring 24. An axial passage channel 25 is passed through the piston 22 and the tappet 23, the outer end of which is closed by a ball valve 27, which is closed under the Effect of another compression spring 26 is. The balloon limiter 6 has an opening 6.1 in the area opposite the tappet 23 and a connection opening 28 is arranged on the protective pot 1 in the corresponding area, to which the compressed air line 16 connects. A conical opening element 30 is arranged in the connection opening 28. Furthermore, the connection opening 28 for sealing the retracted plunger 23 is closed with a sealing collar 29. When the cylinder 7 is pressurized with compressed air, the piston 22 moves to the right in FIG. 5 and the tappet 23 extends, with no compressed air escaping from the front end of the tappet 23 because of the closed ball valve 27. Only when the plunger 23 is inserted into the connection opening 28 and sealed there and the conical opening element 30 penetrates into the tip of the plunger 23 and the ball valve 27 opens against the force of the spring 26, does the compressed air P1 flow out of the line 21 through the axial passage channel 25 into the compressed air line 16.

This configuration of the connection unit has the advantage that, in an arrangement according to FIG. 2, one central line and several to be acted upon After the central line 48 has been pressurized with compressed air, the connecting units first of all extend the pistons 22 evenly and only after the tappets 23 have been docked does an air loss occur due to outflow into the compressed air line 16.

FIG. 6 shows another embodiment of a connection unit which represents a combination of a connection unit for controlling the capsule thread brake and a connection unit for controlling the threading device shown in FIG. 3.

The connection unit has two compressed air cylinders 7 'and 7''arranged one behind the other, in each of which pistons 32 and 42 are guided, to which plungers 33 and 43 arranged one inside the other are fastened. The cylinder 7 'is connected to a first compressed air supply line 31, while the cylinder 7''is connected to a second compressed air supply line 41. The movement of the cylinders 32 and 42 takes place against the force of compression springs 34 and 44. An axial passage 45 is passed through the piston 42 and the plunger 43, which is also penetrated by the plunger 33, which in turn together with the piston 32 has axial passage channel 35. At the front end of the axial passage channel 35 in the inner plunger 33 there is a ball valve 37, which acts under the action of a compression spring 36 and closes the outlet opening of the plunger 33. Across from The plungers 33 and 43, which are movable in the radial direction onto the protective pot 1 ', have a passage opening 6.1' arranged in the balloon limiter 6 ', and the protective pot 1' has a connection opening 46 to which the plunger 43 can be attached. The connection opening 46 is connected to a first compressed air line 47 which leads to the threading device 52. A further connection element 38 is arranged inside the connection opening 46, to which the tappet 33 docks when it is extended. This connection element is connected to the compressed air line 16 ', which leads to the cylinder 15 for actuating the capsule brake. In the connection element 38, behind a sealing sleeve 39, there is a valve 40, which closes the passage opening of the sealing sleeve and is under spring force, on the outside of which an opening element 40.1 is arranged.

The operation of the connection unit shown in Figure 6 is as follows.

When the line 41 is pressurized with compressed air P2, the piston 42 extends radially to the protective pot 1 'and the plunger 43 comes into contact with the connection opening 46. Compressed air enters the line 47 through the axial channel 45 to actuate the threading device 52. If the line 31 is pressurized with compressed air P1, the piston 32 extends and the plunger 33 comes into contact with the connecting element 38, the valve 40 being opened and by means of of the opening element 40.1, the ball valve 37 is also pressed into the open position. The compressed air flowing out of the line 31 now passes through the axial channel 35 into the line 16 ' for actuating the capsule thread brake.

Thus, both the threading device and the capsule thread brake can be actuated independently of one another with a connection unit.

In the following, two further embodiments of devices for adjusting capsule thread brakes on twisting machines are described with reference to FIGS. 7-10, which, like the device described above, are combined with a threading device.

A difference to the embodiment of the device described above is that the compressed air for actuating the capsule thread brake is not supplied radially but axially to the individual twisting spindle, while the compressed air for actuating the threading device is supplied radially to the twisting spindle in a known and already described manner.

Figures 7 and 8 serve similarly to Figures 1 and 2 to explain the basic structure of the twisting spindle and the arrangement of the twisting spindles on a spindle bench.

FIG. 7 shows a double-wire twisting spindle S6 with a bobbin holder which has a protective pot 61 and a bobbin holder base 61.1. The spindle hollow shaft 62 is mounted in the hub of the bobbin, on which a supply spool SP is arranged, from which the threads F1 and F2 are drawn off and inserted through the thread inlet tube 63 into the spindle hollow axis 62 and through the capsule thread brake are passed through. The thread F emerges from the thread storage disk 64 of the spindle rotor 65 and, as already described, is guided upwards between the jacket of the protective pot 61 and a balloon limiter 66 to the thread guide eyelet (not shown). Outside the twisting spindle, two connection units for supplying compressed air are arranged, namely a connection unit 67.1, which is connected to a pressure source D1, for supplying compressed air P1 for controlling the capsule thread brake and a connection unit 67.2, which is connected to a compressed air source D2, for supplying Compressed air D2 to control a threading device. This connection unit 67.2 is not described in more detail below and can be designed in a manner known per se, for example in a manner as shown in FIG. 5 and described with reference to this figure.

As can be seen from FIG. 8, the compressed air supply for controlling the capsule thread brake takes place via a compressed air line 85 which is guided along a spindle bank 83 with twisting spindles S6 to S10 and to which the connection units 67.1 are connected via branch lines 84. As already described, the compressed air line 85 is connected via a feed line 87 to the compressed air source, not shown. Via the control device 86, the compressed air pulses can be generated in the line 85, which lead to the adjustment of all capsule thread brakes in the twisting spindles which are connected to the line 85 via the connection units 67.1.

The compressed air line, to the branch lines of which the connection units 67.2 are connected, are not shown in FIG. 8.

FIG. 9 shows a section of the bobbin carrier and the hollow spindle axis as well as the spindle rotor of a twisting spindle. The spindle hollow axis 62 has a housing 68, which is closed on its upper side with a screw cap 69, on which the thread inlet pipe 63 attaches. The capsule thread brake is arranged within the screw cap, with an upper brake ring 72 arranged on the thread inlet side and firmly connected to the housing, an axially movable lower brake ring 70 and the brake cartridge arranged between the two brake rings, which consists of the sleeve parts 71 and 71.1. The housing 68 is supported on the bottom 61.1 of the coil carrier. The lower brake ring 70 is arranged on an essentially tubular brake ring carrier 70.1, which is supported on its underside via a first compression spring 70.2 on the housing 68, such that it can be axially displaced in the housing against the action of this compression spring. A substantially hollow cylindrical guide part 73 is arranged coaxially outside of this lower brake ring carrier 70.1 and is supported on an appropriate output shoulder of the lower brake ring 70.1 via an inner shoulder 73.1. With its upper side, the guide part 73 is supported on the cover 69 of the housing 68 by a second compression spring 77. The two compression springs 70.2 and 77 are designed so that the second compression spring 77 has a stronger spring force than the first compression spring 70.2. The lower section of the guide part 73 is designed as an annular piston 74 which extends downward from the brake cartridge 71 and is guided in an annular cylinder 75 arranged in the housing 68 is. A compressed air line 76 leads to the ring cylinder 75, which is led into the bottom 61.1 of the coil carrier and is connected via a passage 76.1 to an outward supply channel 65.1 running axially through the spindle rotor 65. The spindle rotor 65 with the thread storage disk 64 is rotatably mounted in the bobbin support base 61.1 via bearings 65.2 and has a whorl 89 for driving at its lower end. The spindle rotor 65 is mounted in the spindle bank 83 via further bearings 82.1 and brackets 82. The supply channel 65.1 opens at the lower end of the spindle rotor 65 into a connection opening 65.3, to which a connection unit 67.1 for supplying compressed air pulses P1 is connected.

An upper toothed segment 78 and a lower toothed segment 79 are arranged circumferentially around the circumference of the guide part 73. The upper toothed segment 78 corresponds to the upper toothed segment 18 described with reference to FIG. 3 and the lower toothed segment 79 corresponds to the described lower toothed segment 19. A radially inwardly projecting support stop 80 arranged in the housing 68 and designed as a positioning pin engages between the toothed segments 78 and 79. The more precise configuration and arrangement of the two tooth segments 78 and 79 with respect to one another can be seen in FIGS. 4 and 4a to 4c, as already described. The mode of operation described there also corresponds exactly to the mode of operation of the tooth segments 78 and 79, and is therefore not described again in detail below.

The arrangement of the toothed segments 78 and 79 on the guide part 73 has the result that when the guide part is raised and lowered 73 a sectionwise rotation of the same is initiated in the circumferential direction. The upward and downward movement of the guide part 73 is brought about by supplying compressed air pulses into the cylinder 75 for moving the annular piston 74. The different heights of the guide part 73 that can be achieved hereby in the described manner in relation to the upper brake ring 72 fixed to the housing are transferred to the lower brake ring carrier 70.1, since the latter always bears against the inner shoulder 73.1 of the guide part 73 under the force of the first compression spring 70.2. The selection of the spring strength of the two compression springs 70.2 and 77 ensures that only the lower brake ring carrier 70.1 is raised by the first compression spring 70.2 until it rests on the guide part 73, but this cannot be raised against the force of the second compression spring 77. In this way, the brake ring carrier 70.1 and with it the lower brake ring 70 adjust themselves to the different altitudes given by the position of the guide part 73, which leads to the different settings of the braking force between the brake cartridge 71 of the capsule thread brake and the two brake rings 70 and 72.

The threading device of the twisting spindle according to FIG. 9 has, in a known manner, an injector 88, to which compressed air P2 can be supplied via a compressed air duct 81 which is guided radially through the bobbin base 61.1. As a result, a negative pressure is generated on the injector 88, which exerts a force on the underside of the lower brake ring carrier 70.1 designed as a piston surface, as a result of which the brake ring carrier 70.1 is moved downward against the force of the first compression spring 70.2, with the result that the lower brake ring 70 the brake cartridge 71 releases from one in the lid 69 of the housing 68 arranged support ring 69.1 is held in such a position that the thread fed through the thread inlet tube 63 is sucked past the brake cartridge 71 under the effect of the negative pressure and is guided through the thread guide tube 64.1 into the thread storage disk 64. Since the guide part 73 is held in the rest position by the support stop 80, the brake ring carrier 70.1 lifts downward from the guide part 73 during the threading process and, after the threading process, rests on the underside of the inner shoulder 73.1 under the action of the compression spring 70.2.

Also in the case of the spindle hollow axis of a twisting spindle shown in FIG. 10, the capsule thread brake is actuated by compressed air fed axially through the spindle rotor, while the compressed air is fed radially to the twisting spindle to actuate the threading device. The illustration according to FIGS. 7 and 8 therefore essentially applies to the arrangement of the twisting spindles and the feed line.

In the twisting spindle according to FIG. 10, the spindle hollow axis 92 has a housing 98 which is closed on its upper side with a screw part 99 from which the thread inlet tube 93 is led upwards. The capsule thread brake is arranged in the screw part 99, with the brake cartridge made up of parts 101 and 101.1, which is supported on an upper brake ring 102 which is fixedly connected to the screw part 99 and on a lower brake ring 100 which can be displaced in the axial direction. The lower brake ring 100 is arranged on a brake ring carrier 100.1, which is arranged on the top of a guide part 103 and in one piece connected to it. The guide part 103 is axially displaceable and rotatable and is supported on its underside designed as a piston 104 via a first compression spring 100.2 in the housing 98. An upper tooth segment 109 and a lower tooth segment 108 are in turn arranged circumferentially on the lateral surface of the guide part 103. Between the two toothed segments there is a radially inwardly guided support stop 97.1, which is fastened to an additional, hollow cylindrical, axially displaceable additional guide part 97 arranged coaxially outside the guide part 103. The additional guide part 97 is supported on its underside via a second compression spring 107 in the housing 98. The two compression springs 100.2 and 107 are designed such that the second compression spring 107 has a stronger spring force than the first compression spring 100.2.

The piston 104 arranged on the guide part 103 is guided in a cylinder 105 arranged in the additional guide part 97. This cylinder 105 is connected via a passage 106 to the interior of the thread guide tube 94.1 arranged in the spindle rotor 95. An injector 110 opens into the radially outward-pointing section of the thread guide tube 94.1 and is connected to a feed channel 95.1 which is led axially outward through the spindle rotor 95. This supply channel 95.1 opens into a connection opening (not shown), to which a connection unit similar to the connection unit 67.1 shown in FIG. 9 is connected for supplying the compressed air.

In the idle state of the guide part 103, the support stop 97.1 rests in the lower toothed segment 108 on one of the slot shoulders which represents the support shoulders. With an axial downward movement of the guide part 103, the processes take place again, as are described in the first-mentioned embodiment with reference to FIGS. 4 and 4a-4c. The lower tooth segment 108 in FIG. 10 corresponds to the upper tooth segment 18 in FIG. 4, while the upper tooth segment 109 in FIG. 10 corresponds to the lower tooth segment 19 in FIG.

The displacement of the guide part 103 takes place in that a compressed air pulse P1 is fed through the feed channel 95.1, which, as a result of the action of the injector 110, leads to a “vacuum pulse” in the thread guide tube 94.1, which acts on the piston 104 through the passage 106 and on the piston 104 downwards emotional. After the external pressure has been reset, the piston 104 and with it the guide part 103 then move up again under the action of the first compression spring 100.2. As a result of the rotation of the guide part 103 that has occurred in the manner already described with reference to the other exemplary embodiments, after such a rotation the guide part 103 and with it the lower brake ring 100 are at a different altitude with respect to the upper brake ring 102, which leads to a different setting of the braking force on the brake cartridge. The different design of the two compression springs 100.2 and 107 ensures that the additional guide part 97 does not move downwards together with the guide part 103 when the negative pressure is present.

The spindle rotor 95 with the thread storage disk 94 is accommodated elastically via bearings 95.2 and a bearing bush 95.3 in the housing 98 and is rotatably supported. The threading device for the twisting spindle shown in FIG. 10 has, in a known manner, an injector 90 which is guided into the upper part of the thread guide tube 94.1 and which is connected to a compressed air line 96 which passes through the housing 98 and in the radial direction through the spindle carrier base 91.1 is led outside to a connection opening, not shown, through which the compressed air pulses P2 are supplied. Furthermore, the additional guide part 97 is formed on its upper side as an annular piston 97.2, which is arranged within an annular cylinder 97.3. The ring cylinder 97.3 is connected to the compressed air line 96 via a spur line 96.1. The compressed air supplied via the compressed air line 96, on the one hand, generates the negative pressure sucking in the thread at the injector 90 and, at the same time, the additional guide part 103 is moved downward against the force of the second compression spring 107 by the annular piston 97.2. The action of the support stop 97.1 takes the guide part 103 and with it the lower brake ring carrier 100.1 with the brake ring 100 downwards. This has the consequence that the brake cartridge 101, 101.1 is released from the lower brake ring 100 during the threading process and is held by the support ring 99.1 arranged in the screw part 99, so that the thread fed in is sucked past the brake cartridge under the effect of the negative pressure and into the thread guide tube 94.1 can be introduced.

Claims (15)

1. Device for adjusting capsule yarn brakes (10, 11, 12; 70, 71, 72; 100, 101, 102) on twisting machines, particularly two-for-one twisting machines having several twisting spindles, in the case of which each of the capsule yarn brakes, respectively located inside the hub of the bobbin carrier of the twisting spindles and having a brake cartridge supported between two brake rings (10, 12; 70, 72; 100, 102) which lie one above the other in axial direction, can be adjusted in stages to different brake power values by axial displacement against the power of a pressure spring (17, 77, 107) and by twisting of a brake ring (12, 70, 100), characterized in that, for the simultaneous, centrally controlled adjustment of all capsule yarn brakes (10, 11, 12; 70, 71, 72; 100, 101, 102) of the twisting machine or of several twisting machines, a control device (50, 86) is provided from which, by way of a shared compressed-air pipe (48, 85) to which compressed-air cylinders (15, 75, 105) coupled in each case with one of the brake rings (12, 70, 100) are connected via connection units (7, 67.1) provided on each twisting spindle, compressed-air pulses (P1) are emitted and supplied to the compressed-air cylinder, these giving rise to an axial displacement by a predetermined linear value in respect of the brake rings (10, 70, 100) of all the capsule yarn brakes, whereby on each capsule yarn brake a cylindrical guide component (13, 73, 103) is provided which, together with the brake ring (12, 70, 100), can be axially displaced and twisted and which, on its circumference, has several supporting shoulders in the form of axial slots opening towards the brake cartridge (11, 71, 101) with the bottoms of the slots lying at different heights into which in each case, depending on the angular position of the guide component in direction of circumference, a supporting stop (20, 80, 97.1) located opposite the guide component and projecting radially inwards can be introduced during axial displacement of the guide component and brought to rest on the bottom of the slot, and the axial slots are formed as spaces in a first toothed segment (18, 78, 108) with teeth directly following on from one another in direction of circumference (UR), whereby in each case the tooth flank (18.2) lying in a first direction of circumference (UR) is formed as a sloping surface falling away at a predetermined acute angle of less than 90° in relation to the direction of circumference (UR) whilst the tooth flank (18.3) respectively lying in the other direction of circumference runs substantially in axial direction and a second toothed segment (19, 79, 109) lies opposite the first toothed segment (18, 78, 108) at a predetermined axial distance with teeth facing the teeth of the first toothed segment, whereby the tooth flank respectively lying in the first direction of circumference (UR) is formed as a sloping surface (19.2) rising in relation to the direction of circumference (UR) at a predetermined acute angle of less than 90°, whilst the tooth flank (19.3) respectively lying in the other direction of circumference runs substantially in axial direction and the second toothed segment (19, 79, 109) is offset in relation to the first toothed segment by such a predetermined value in direction of circumference (UR) that in each case a sloping surface (18.2) of the first toothed segment (18, 78, 108) lies opposite the bottom of a slot (19.1) of the second toothed segment (19, 79, 09) and conversely a sloping surface (19.2) of the second toothed segment (19, 79, 109) lies opposite the bottom of a slot (18.1) of the first toothed segment (18).
2. Device according to Claim 1 on a twisting machine, particularly a two-for-one twisting machine having at least one twisting spindle, which has a bobbin carrier and in the case oF which inside the hub of the bobbin carrier a capsule yarn brake (10, 11, 12; 70, 71, 72; 100, 101, 102) is located with a cylindrical housing through which the yarn is guided in axial direction and which, on the side where the yarn emerges, has a first brake ring (10, 70, 100), on which a brake cartridge is supported, on the upper end of which a second brake ring (12, 72, 100) is seated, whereby at least one of the brake rings is located on a cylindrical brake-ring carrier (10.1; 70.1; 103) which can be moved in axial direction in the housing and on whose side facing away from the brake ring a pressure spring (17, 77, 107) acts in axial direction, this pressure spring being supported at its other end on the housing, characterized in that the guide component (13, 73, 103) together with the brake-ring carrier (12.1, 70.1, 100.1) can be axially displaced and twisted and on the guide component (13, 73, 103), radially outside the brake ring (12, 70, 100) and coaxially with this, a piston (14, 74, 104) is located which is guided in a cylinder (15, 75, 105) located in the housing (8, 68, 98) and the cylinder at its end lying opposite the ring piston is connected to a compressed-air pipe (16, 76, 106) which can be pressurized and which is guided outwards to a connection opening (28, 38, 65, 3) outside the bobbin carrier (1, 1', 61, 91) opposite which opening there is a movable connecting-piece (23, 33) of a connection unit (7, 7', 67, 1) connected to a compressed-air source.
3. Device according to Claim 1 or 2, characterized in that the angle of the sloping surfaces (18.2) of the first toothed segment (18, 78, 108) has the same value as the angle of the sloping surfaces (19.2) of the second toothed segment (19, 79, 109).
4. Device according to one of Claims 1 to 3, characterized in that the heights of the bottoms of the slots (18.1) of the first toothed segment (18, 78, 108) decrease in one direction of circumference (UR), whilst the heights of the teeth of the second toothed segment (19, 79, 109) decrease in the same direction of circumference and to the same degree.
5. Device according to one of Claims 1 to 4, characterized in that the offsetting of the second toothed segment (19, 79, 109) in relation to the first toothed segment (18, 78, 108) amounts to approximately 0.4 to 0.6 the distance between teeth in direction of circumference.
6. Device according to one of Claims 2 to 5, characterized in that the guide component (13) is located coaxially with the rotatable upper brake-ring carrier (12.1) and is firmly connected with this and the supporting stop (20) is fixed to the inside of the housing (8) and the piston (14) located on the guide component (13) is a ring piston (14) which extends towards the brake cartridge (11) and is guided in a ring cylinder (15) located in the wall of the housing and the compressed-air pipe (16) leading to the ring cylinder (15) is guided radially outwards through the base (1.1) of the bobbin carrier (1) to a connection opening (28, 38) in the outer casing of the bobbin carrier (1, 1'), opposite which there is a radially movable connecting-piece (23, 33) of a connection unit (7, 7').
7. Device according to Claim 6, characterized in that the connection unit has a cylinder (7) which is connected to the compressed-air source and in which a piston (22) is guided so as to move radially in relation to the bobbin carrier (1) against spring power, whereby on the piston (22), as connecting-piece, a plunger (23) which can move out from the cylinder (7) is located which has an axial air-outlet channel (25) which is provided at its outlet end with a ball valve (27) which closes under spring power and, in the connection opening (28) on a receiving element for the plunger, a conical opening element (30) is fixed which opens the ball valve when the plunger (23) enters the connection opening (28).
8. Device according to Claim 7, characterized in that a sealing ring (29) is located in the connection opening (28).
9. Device according to Claim 6, characterized in that the connection unit is combined with a compressed-air supplying device for a threading device and has a first cylinder (7') which is connected to a first compressed-air source and in which a first piston (32) is guided so as to be movable radially in relation to the bobbin carrier (1') against spring power (34), whereby a first plunger (33) which can be guided out from the first cylinder (7') is located on the first piston as connecting-piece, this plunger (33) having a first axial air outlet channel (35) and, coaxially in front of the first cylinder (7'), a second cylinder (7") connected to a second compressed-air source is located in which a second piston (42) is guided so as to move radially in relation to the bobbin carrier (1') against spring power (44) and a second plunger (43) which can be guided out from the second cylinder (7") is located on the second piston (42) as connecting-piece and the first plunger (33) is guided coaxially through the second plunger (43) and its length is such that, when the first piston (32) is extended, it projects from the outer end of the second plunger (43) by a predetermined amount and on the bobbin carrier (1') behind a connection opening (46) for the second plunger (43) a receiving element (38) is located For the first plunger, the connection opening (46) being connected to a first compressed-air pipe (47) leading to the threading device, whilst the receiving element For the First plunger (33) is connected to a second compressed-air pipe (16') leading to the ring cylinder (15).
10. Device according to Claim 9, characterized in that a sealing device (39) for sealing off the interior space of the receiving element from the interior space of the connection opening (46) is located on the receiving element (38) for the second plunger (33), this sealing device (39) having a sealing element (40) which closes under spring power and can be moved into an open position by the entry of the first plunger (33).
11. Device according to Claim 10, characterized in that the outlet end of the first plunger (33) is provided with a ball valve (37) which closes under spring power and the sealing element (40) of the receiving element (38) for the second plunger (33) bears an opening element (40.1) which opens the ball valve (37) on entry of the second plunger (33).
12. Device according to one of Claims 6 to 11, for twisting spindles with balloon limiters, characterized in that, in the region of the connection units (7, 7' - 7"), the balloon limiter (6, 6') has an opening (6.1, 6.1') which can be entered by the plunger (23) or plungers (33, 43).
13. Device according to one of Claims 2 to 5, characterized in that the guide component (73) is located coaxially outside the lower brake-ring carrier (70.1), which is subject to the dynamic effect operating upwards of a first pressure spring (70.2) and is axially displaceable, and it rests on this lower brake-ring carrier (70.1) under the dynamic effect operating downwards of a second pressure spring (77) with stronger spring power compared with the first pressure spring (70.2), and the supporting stop (80) is fixed to the inside of the housing (68) and the piston located on the guide component (73) is a ring piston (74) which extends in direction away from the brake cartridge (71) and is guided in a ring cylinder (75) located in the housing (68) and the compressed-air pipe (75) leading to the ring cylinder runs into the base (61.1) of the bobbin carrier (61) and is connected to a supply channel (65.1) which is guided axially outwards through the spindle rotor (65) and runs into a connection opening (65.3) to which a connection unit (67.1) is connected For the supply of compressed air.
14. Device according to one of Claims 2 to 5, characterized in that the guide component (103) is located coaxially with the rotatable lower brake-ring carrier (100.1), which is subject to the dynamic effect operating upwards of a first pressure spring (100.2), and is Firmly connected with this, and the supporting stop (97.1) is fixed to an additional coaxial guide component (97) - which can be axially displaced outside the guide component (103) - so as to project radially inwards, whereby the additional guide component (97) is subject to the dynamic effect operating upwards of a second pressure spring (107) having stronger spring power compared with the first pressure spring (100.2) and the piston (104) located on the guide component (103) is guided in a cylinder (105) which is located in the additional guide component (94) and which is connected by way of a passage (106) with the yarn-guiding tube (94.1) which is located in the spindle rotor (95) and into whose outward-pointing section an injector (110) flows which is connected to a supply channel (95.1) guided axially outwards through the spindle rotor (95) and running into a connection opening to which a connection unit is attached for the supply of compressed air.
15. Device according to Claim 14, characterized in that the additional guide component (97) is formed at its upper side as ring piston (97.2) guided in a ring cylinder (97.3) and the ring cylinder (97.3) is connected by way of a stub pipe (96.1) to the compressed-air pipe (96) leading to the injector of a threading device (90).

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