Device for adjusting capsule thread brakes in twisting machines, in particular two-for-one twisters

A device for adjusting capsule thread brakes in twisting machines having inside the twisting spindle a capsule thread brake has a brake ring disposed on a brake ring support which may be moved against a spring force. On the brake ring support a ring piston is arranged, which is guided in a ring cylinder connected to a compressed air supply line. A first toothed segment with downwardly directed teeth is arranged on the periphery of the brake ring support, and a second toothed segment with upwardly directed teeth is located opposite the first toothed segment. A support stop engages the slots formed between the teeth of the toothed segments during displacement of the brake ring support. The tooth flanks of the two toothed segments are provided with inclined surfaces in such a way that an upward and downward movement of the brake ring support results in a rotation of the brake ring support by predetermined angle values and an adjustment of the capsule thread brake as a consequence of the support stop abutting against slot bottoms at different axial heights. Several capsule thread brakes may be adjusted simultaneously by a central control device with compressed air pulses supplied by a common compressed air supply line.

BACKGROUND OF THE INVENTION 
The invention relates to a device for adjusting capsule thread brakes in 
twisting machines, in particular two-for-one twisters with several 
twisting spindles, in which each of the capsule thread brakes, each 
arranged inside the hub of the bobbin carrier of the twisting spindles and 
provided with a brake cartridge supported between two brake rings 
positioned one above the other in the axial direction, may be adjusted in 
steps to different brake force values by axial displacement and rotation. 
The invention also relates to a device on a twisting machine, in 
particular a two-for-one twister, with at least one twisting spindle, 
which has a bobbin carrier and wherein a capsule thread brake with a 
cylindrical housing is arranged inside the hub of the bobbin carrier, 
through which the thread is passed in the axial direction and which on the 
thread outlet side has a first brake ring, on which a brake cartridge is 
supported, on the upper end of which a second brake ring sits. At least 
one of the brake rings is arranged on a cylindrical brake ring support 
movable in the axial direction within the housing. A pressure spring acts 
on the side of the brake ring support facing away from the brake ring and 
is supported on the housing with its respective other end. 
Such a capsule thread brake for twisting machines is described in German 
Patent 1 510 860, for example. The capsule thread brakes have a brake 
cartridge with an upper and a lower sleeve, which are joined onto one 
another so as to be freely movable and have a pressure spring enclosed 
between them. In the known capsule thread brake, the brake force is 
adjusted manually, whereby the brake ring support is raised in the axial 
direction against the bias of the pressure spring, rotated around its axis 
by a specific angle and then lowered by the action of the pressure spring 
into a new position, in which the support stop rests on one of the support 
shoulders arranged at different axial heights inside one of the axial 
slots. This brake force adjustment must be carried out manually on each 
individual twisting spindle in a twisting machine. 
Thread brakes are also known, which may be adjusted centrally at the same 
time. However, these brakes are, for example, in the form of disc brakes 
(see Swiss Patent 636 577) which are actuated by compressed air. 
A device for controlling thread brakes on a two-for-one twister is also 
known (see German Patent 1 510 853), in which a thread brake can be 
operated by means of an electromagnetic control device acting through the 
circulating thread balloon. In one embodiment of this known thread brake, 
an oval brake sleeve sits between two brake rings, one of which is mounted 
to move axially on an elastically expandable bellows which is filled with 
a fluid medium and connected via a pipe to a further bellows, which is 
filled with the same medium and on which a pressure is exerted by means of 
the electromagnetic control device. The pressure is transferred to the 
first bellows, thus applying a pressure to the axially movable brake body 
which results in an increase in the brake force. However, in this known 
device, which may also be actuated centrally, the brake force can only be 
adjusted within narrow limits. 
It is therefore an object of the present invention to provide in a twisting 
machine of the aforementioned kind central actuation of the capsule thread 
brake, which should be structurally simple and operationally reliable in 
association with a large manufacturing range. 
SUMMARY OF THE INVENTION 
The device for adjusting the braking power of capsule thread brakes of 
spindles of at least one twisting machine according to the present 
invention is primarily characterized by: 
a plurality of twisting spindles each having a bobbin carrier with a hub 
and a capsule thread brake with a step-wise adjustable braking power 
positioned in the hub, the capsule thread brake comprising: 
a) two brake rings arranged axially spaced from one another, wherein the 
braking power is adjusted by axially displacing and rotating one of the 
brake rings, 
b) a brake cartridge supported between the two brake rings, and 
c) a pressure cylinder coupled to one of the brake rings; 
a common compressed air supply line for supplying compressed air, the 
compressed air supply line having a control device; 
a connector connected to each spindle, wherein the compressed air supply 
line communicates via the connectors with the pressure cylinders, wherein 
the control device supplies compressed air pulses through the common 
compressed air supply line and the connectors to the pressure cylinders to 
affect simultaneously an axial displacement by a predetermined distance of 
one of the brake rings of all the capsule thread brakes. 
Preferably, each capsule thread brake has a cylindrical housing through 
which cylindrical housing the thread is guided in the axial direction, 
wherein a first brake ring is positioned at a lower end of the cylindrical 
housing and wherein the brake cartridge is supported on the first brake 
ring and a second brake ring is positioned at the upper end of the brake 
cartridge. The device further comprises: 
a cylindrical brake ring support for supporting one of the brake rings, the 
brake ring support arranged so as to be axially slidable within the 
cylindrical housing; 
a pressure spring for supporting the brake ring support at the housing, 
said pressure spring resting with one end on a side of the brake ring 
support opposite the brake ring and with the other end on said housing; 
a cylindrical guide element that is axially slidable and rotatable within 
the housing together with the brake ring support; 
the guide element having a first toothed segment with first teeth 
distributed directly adjacent to one another in the circumferential 
direction of the guide element, the first teeth defining therebetween 
first axial slots with a first slot bottom functioning as support 
shoulders, wherein the first slot bottoms are positioned at different 
axial heights of the guide element, wherein a leading flank of the first 
axial slots in the circumferential direction extends downwardly at an 
acute angle of less than 90.degree. to the circumferential direction and 
wherein a rearward flank of the first axial slots in the circumferential 
direction extends substantially axially; 
the guide element having a second toothed segment with second teeth 
distributed directly adjacent to one another in the circumferential 
direction of the guide element, the second toothed segment positioned 
opposite the first toothed segment, wherein the second teeth define 
therebetween second axial slots with a second slot bottom, the second 
axial slots opening toward the first axial slots, wherein a leading flank 
of the second axial slots in the circumferential direction extends 
upwardly at an acute angle of less than 90.degree. to the circumferential 
direction and wherein a rearward flank of the second axial slots in the 
circumferential direction extends substantially axially; 
the second toothed segment being staggered in the circumferential direction 
relative to the first toothed segment such that the leading flanks of the 
first axial slots are positioned opposite the slot bottoms of the second 
axial slots and the leading flanks of the second axial slots are 
positioned opposite the slot bottoms of the first axial slots; 
a radially inwardly projecting support stop for engaging the first axial 
slots of the first toothed segment such that as a function of an angular 
position of the guide element in a circumferential direction the support 
stop is inserted into the axial slots and brought into contact with the 
slot bottoms; 
the pressure cylinder positioned within the housing; 
a piston connected radially outwardly to the guide element so as to be 
coaxial thereto, the piston guided within the pressure cylinder; 
the pressure cylinder communicating with the compressed air supply line via 
a first end of the pressure cylinder remote from the piston; 
a pressure line connected to the first end of the pressure cylinder and 
guided through the housing to a connection opening external to the bobbin 
carrier; and 
the connector having a first movable connecting device connected to the 
compressed air supply line for connecting the connector to the connection 
opening positioned opposite to the first connecting device of the 
connector. 
Advantageously, the acute angle of the leading flank of the first teeth is 
equal to the acute angle of the leading flank of the second teeth. 
Expediently, the axial heights of the slot bottoms of the first teeth 
decrease in one direction about the circumference and a height of the 
second teeth increases in the same direction about the circumference. 
Preferably, the first toothed segment is staggered relative to the second 
toothed segment by a distance that equals substantially 0.4 to 0.6 the 
spacing between the teeth. 
Advantageously, the guide element is arranged coaxially to the brake ring 
support and is fixedly connected thereto. The brake ring support supports 
the second brake ring and is rotatable. The support stop is fixedly 
connected to an inner wall of the housing. The piston is a ring piston 
extending toward the brake cartridge. The pressure cylinder is a ring 
cylinder, wherein the pressure line is guided through the bottom of the 
bobbin carrier radially outwardly. The bobbin carrier has a protective 
pot, with the connection opening positioned in the protective pot. 
In a preferred embodiment of the present invention, the connector comprises 
a guide cylinder connected to the compressed air supply line, a slide 
piston guided within the guide cylinder, and a piston spring biasing the 
slide piston into an end position within the guide cylinder remote from 
the bobbin carrier. The slide piston is movable radially relative to the 
bobbin carrier from the end position against the force of the piston 
spring toward the bobbin carrier. The first connecting device is connected 
to the slide piston and is in the form of a plunger extendable from and 
retractable into the guide cylinder. The plunger has a free end with a 
ball valve comprising a valve spring for biasing the ball valve into a 
closed position. The connection opening has a receiving element for the 
plunger. The receiving element has a conical opening element fixedly 
connected thereto that upon introduction of the plunger into the 
connection opening opens the ball valve. 
Preferably, the connection opening further comprises a gasket. 
Advantageously, the bobbin carrier further comprises a balloon limiter and 
the balloon limiter has a bore opposite the connector that is penetrated 
by the plunger when the plunger is displaced radially toward the bobbin 
carrier. 
In another embodiment of the present invention, the bobbin carrier further 
comprises a compressed air supply unit for a threading device. The 
connector comprises a first guide cylinder connected to the compressed air 
supply line, a first slide piston guided within the first guide cylinder, 
and a first piston spring biasing the first slide piston into an end 
position within the first guide cylinder remote from the bobbin carrier. 
The connector further comprises a second guide cylinder connected to a 
further compressed air supply line, a second slide piston guided within 
the second guide cylinder, and a second piston spring biasing the second 
slide piston into an end position within the second guide cylinder remote 
from the bobbin carrier. The second guide cylinder is positioned adjacent 
to the first guide cylinder so as to be coaxial to the first guide 
cylinder. The first slide piston is movable radially relative to the 
bobbin carrier from the end position against the force of the first piston 
spring toward the bobbin carrier. The second slide piston is movable 
radially relative to the bobbin carrier from the end position against the 
force of the second piston spring toward the bobbin carrier. A first 
connecting device is connected to the first slide piston and is in the 
form of a first plunger extending from the first guide cylinder, wherein 
the first plunger has an axially extending compressed air channel. The 
connector further comprises a second movable connecting device that is 
connected to the second slide piston and is in the form of a second 
plunger extending from the first guide cylinder, wherein the first plunger 
extends coaxially into the second plunger and has a length such that, when 
the first slide piston is displaced from the end position toward the 
bobbin carrier, the first plunger projects past a free end of the second 
plunger. The connection opening receives the second plunger. The bobbin 
carrier has a receiving element for the first plunger positioned radially 
inwardly relative to the connection opening, wherein the connection 
opening is connected to a compressed air feed line connected to the 
threading device and wherein the receiving element is connected to the 
pressure line connected to the pressure cylinder. 
Preferably, the receiving element has a sealing device for sealing the 
interior of the receiving element relative to the interior of the 
connection opening. The sealing device comprises a valve element and a 
spring for biasing the valve element into a closed position. The valve 
element is displaced into an open position by the first plunger when the 
first plunger is displaced by the first slide piston toward the bobbin 
carrier and is inserted into the receiving element. 
The first plunger has a free end with a ball valve comprising a valve 
spring for biasing the ball valve into a closed position for closing off 
the compressed air channel. The valve element has an opening element for 
opening the ball valve when the first plunger is introduced into the 
receiving element. 
The bobbin carrier further comprises a balloon limiter and the balloon 
limiter has a bore opposite the connector penetrated by the first and the 
second plungers when the first and the second plungers are displaced 
radially toward the bobbin carrier. 
Advantageously, the brake ring support supports the first brake ring. The 
pressure spring biases the brake ring support in an upward direction. The 
guide element is positioned coaxially and radially outwardly relative to 
the brake ring support and is supported on the brake ring support and 
comprises a compression spring for biasing the guide element in a downward 
direction against the force of the pressure spring. The compression spring 
has a greater spring force than the pressure spring. The support stop is 
fixedly connected to an inner wall of the housing. The piston is a ring 
piston extending away from the brake cartridge. The pressure cylinder is a 
ring cylinder, wherein the pressure line is axially guided through a 
bottom of the bobbin carrier. The bobbin carrier has a spindle rotor and a 
supply channel extending axially through the spindle rotor, the supply 
channel having at an outer end thereof the connection opening. 
In another embodiment of the present invention, each capsule thread brake 
has a cylindrical housing through which housing the thread is guided in 
the axial direction. A first brake ring is positioned at a lower end of 
the housing, wherein the brake cartridge is supported on the first brake 
ring and a second brake ring is positioned at the upper end of the brake 
cartridge. The device further comprises: 
a cylindrical brake ring support for supporting the first brake ring, the 
brake ring support arranged so as to be axially slidable within the 
housing; 
a pressure spring for supporting the brake ring support at the housing, the 
pressure spring resting with one end on a side of the brake ring support 
opposite the brake ring and with the other end on the housing for biasing 
the brake ring support in an upward direction; 
a cylindrical guide element axially slidable and rotatable within the 
housing together with the brake ring support and coaxially fixedly 
connected to the brake ring support; 
the guide element having a first toothed segment with first teeth 
distributed directly adjacent to one another in the circumferential 
direction of the guide element, the first teeth defining therebetween 
first axial slots with a first slot bottom, the first axial slots opening 
toward the brake cartridge, wherein the first slot bottoms are positioned 
at different axial heights of the guide element, wherein a leading flank 
of the first axial slots in the circumferential direction extends upwardly 
at an acute angle of less than 90.degree. to the circumferential direction 
and wherein a rearward flank of the first axial slots in the 
circumferential direction extends substantially axially; 
the guide element having a second toothed segment with second teeth 
distributed directly adjacent to one another in the circumferential 
direction of the guide element, the second toothed segment positioned 
opposite the first toothed segment, wherein the second teeth define 
therebetween second axial slots with a second slot bottom, the second 
axial slots opening toward the first axial slots, wherein a leading flank 
of the second axial slots in the circumferential direction extends 
downwardly at an acute angle of less than 90.degree. to the 
circumferential direction and wherein a rearward flank of the second axial 
slots in the circumferential direction extends substantially axially; 
the second toothed segment being staggered in the circumferential direction 
relative to the first toothed segment such that the leading flanks of the 
first axial slots are positioned opposite the slot bottoms of the second 
axial slots and the leading flanks of the second axial slots are 
positioned opposite the slot bottoms of the first axial slots; 
a radially inwardly projecting support stop for engaging the axial slots of 
the first toothed segment such that as a function of an angular position 
of the guide element in a circumferential direction the support stop is 
inserted into the axial slots and brought into contact with the slot 
bottoms of the first axial slots; 
a guide member positioned radially outwardly and coaxially to the guide 
element and axially slidable; 
the support stop fixedly connected to an inner wall of the guide member; 
the guide member comprising a compression spring biasing the guide member 
in an upward direction; 
the compression spring having a greater spring force than the pressure 
spring; 
the pressure cylinder positioned within the guide member; 
a piston connected radially outwardly to the guide element so as to be 
coaxial thereto, the piston guided within the pressure cylinder; 
the pressure cylinder communicating with the compressed air supply line via 
a first end of the pressure cylinder; 
the connector having a first movable connecting device connected to the 
compressed air supply line for connecting the connector to the connection 
opening positioned opposite to the first connecting device of the 
connector; 
the bobbin carrier comprising a spindle rotor having a thread guide tube 
with an outwardly extending section and having an inlet channel extending 
axially through the spindle rotor and having at an outer end thereof the 
connection opening; 
the pressure cylinder communicating via a through opening with the thread 
guide tube; and 
the bobbin carrier further having an injector connected to the inlet 
channel and opening into the outwardly extending section. 
Advantageously, the guide member at an upper end thereof is in the form of 
an annular piston guided within an annular cylinder. The bobbin carrier 
further comprises a threading device with an injecting member and a 
compressed air inlet. The annular cylinder has a connecting line 
communicating with the compressed air inlet of the threading device. 
According to the present invention, for a centrally controlled adjustment 
of all capsule thread brakes of a twisting machine or several twisting 
machines at the same time, a control device is provided, from which 
compressed air pulses are emitted and passed to the pressure cylinders, 
coupled to the brake rings, via a common compressed air supply line and 
connectors arranged on each twisting spindle. The compressed air pulses 
cause an axial displacement by a predetermined length of the brake rings 
of all the capsule thread brakes. A twisting machine with an inventive 
device for adjusting a capsule thread brake is characterized by a 
cylindrical guide element, which may be axially moved and rotated together 
with the brake ring support and which has several support shoulders on its 
periphery in the form of axial slots opening towards the brake cartridge. 
The axial slots have slot bases positioned at different axial heights. 
Into the axial slots, depending in each case on the angle position in the 
circumferential direction of the guide element, a support stop, arranged 
opposite the guide element and projecting radially inwardly, may be 
inserted upon axial displacement of the guide element and may abut against 
the slot base (support shoulder). A piston disposed in the pressure 
cylinder arranged in the housing is arranged radially outside the brake 
ring and coaxially thereto on the guide element, and the pressure cylinder 
is connected at its end opposite to the ring piston to a pressure line 
subjectable to pressure and directed outward to a connection opening 
outside the bobbin carrier. Located opposite the connection opening is a 
movable connecting device of a connector connected to the compressed air 
supply line source. The axial slots are provided in the form of 
intermediate spaces on a first toothed segment with first teeth directly 
adjoining one another in the peripheral (circumferential) direction. The 
tooth flank leading in the circumferential direction (direction of 
rotation of the guide element) is provided in the form of a downwardly 
inclined surface extending at a predetermined acute angle of &lt;90.degree. 
to the peripheral (circumferential) direction, whereas the respective 
rearward tooth flank extends essentially in the axial direction. A second 
toothed segment is located opposite the first toothed segment at a 
predetermined axial distance and has second teeth facing the first teeth 
of the first toothed segment, wherein the tooth flank leading in the 
circumferential direction is provided in the form of an upwardly inclined 
surface extending at a predetermined acute angle of &lt;90.degree. to the 
peripheral direction, whereas the respective rearward tooth flank extends 
essentially in the axial direction. The second toothed segment is offset 
in the peripheral (circumferential) direction in relation to the first 
toothed segment by a predetermined magnitude, which ensures that in each 
case an inclined surface of the first toothed segment is located opposite 
a slot base of the second toothed segment, and conversely, an inclined 
surface of the second toothed segment is located opposite a slot base of 
the first toothed segment. 
The basic concept of the invention is to further develop the capsule thread 
brake according to German Patent 1 510 860 in such a way that the brake 
ring support, or the guide element connected thereto, is automatically 
axially movable and during the axial movement automatically completes a 
rotation about a predetermined angle value to move it at intervals into 
positions, in which, after the brake ring support has returned axially, 
the support stop sits on a support shoulder (slot base) arranged at a 
different axial height, thus effecting the adjustment of the brake force. 
As will be explained in further detail below by means of examples, the two 
opposing toothed segments on the brake ring support or guide element may 
be structured in such a way that a sufficient number of brake adjustments 
is achievable over the desired brake force range, and a reliable and 
automatic rotation of the brake ring support at the desired angle values 
is achieved on the basis of the special configuration of the opposing 
inclined surfaces, while the brake ring support is pushed back and forth 
by means of compressed air and spring force. 
It is, of course, also possible to design the system by kinematic reversal 
of the conditions in such a way that the support shoulders are arranged on 
the inside of the housing, whereas a support stop is arranged on the 
periphery of the guide element so as to project radially outwardly and be 
insertable into the axial slots. 
The compressed air pulses required for raising the brake ring support are 
supplied via a pressure line, which is passed through the hub of the 
bobbin carrier and the bobbin carrier base and may, for example, be 
directed radially outwardly onto the wall of the protective pot to a 
connection opening in the outer shell of the protective pot The connection 
opening is located opposite a radially (relative to the bobbin carrier) 
movable connecting device of a connector connected to the compressed air 
source (compressed air supply line). The term "compressed air pulse" here 
should be understood to mean in the scope of the invention a short 
increase in pressure in the compressed air supply line followed by a 
release of pressure, or a short drop in pressure followed by a further 
increase in the sense of an "underpressure pulse". The connectors of all 
twisting spindles of a twisting machine are connected to a common 
compressed air supply line, in which a control device is provided to 
generate compressed air pulses. 
The invention provides the advantageous possibility of combining the 
actuation of the thread brake by means of compressed air with the 
actuation known per se of a threading device by means of compressed air, 
as is described in German Patent 2 461 796 or U.S. Pat. No. 3,975,893, for 
example. In this way, the threading process and the adjustment of the 
capsule thread brake may both be carried out centrally via one connector 
or two connectors for each twisting spindle. This leads to a substantial 
reduction in set-up times in the case of multipoint machines. 
Overall, quite a considerable amount of time is gained with the device of 
the present invention in the operation of twisting machines.

DESCRIPTION OF PREFERRED EMBODIMENTS 
FIG. 1 shows only those parts of a two-for-one twisting spindle S1 
necessary for the following explanation of the capsule thread brake and 
its actuation, namely the bobbin carrier with its base 1.1 and protective 
pot 1 and the hub of the bobbin carrier with the hollow spindle shaft 
mounted therein, on which a supply bobbin SP is positioned, from which two 
threads F1 and F2 are withdrawn and fed through the thread feed tube 3 
into the hollow spindle shaft 2 and passed through the capsule thread 
brake in a manner not evident from FIG. 1. The twisted thread F emerging 
radially from the thread storage disc 4 of the spindle rotor 5 is directed 
within the thread balloon between the shell of the protective pot 1 and a 
balloon limiter 6 upwards to a thread guide eyelet (not shown). The 
spindle rotor 5 is driven in rotational motion with a whorl. 
The capsule thread brake, which will be explained in more detail below, 
inside the hub, respectively, hollow spindle shaft 2 of the bobbin carrier 
is actuated centrally by compressed air. For this purpose, a connector 7 
is disposed outside the twisting spindle in the area of the lower edge of 
the protective pot 1. The connector is connected to a compressed air 
source via a compressed air supply line and has a slide piston 23, which 
may be moved radially toward the protective pot 1 of the bobbin carrier 
and may be attached through a bore 6.1 in the balloon limiter 6 to a 
connection opening 28 on the bobbin carrier base 1.1. A pressure line 16 
is connected to the connection opening 28, and compressed air pulses can 
be passed therethrough. 
The compressed air is supplied to the adjustment mechanism--to be explained 
below--in the same way as in the threading device known from German Patent 
2 461 796 and U.S. Pat. No. 3,975,893. 
As can be seen from FIG. 2, the compressed air is supplied via a compressed 
air supply line 48, which is guided along a spindle bearing plate 51 with 
twisting spindles S1 to S5 and to which the connectors 7 are connected via 
branch lines 21. The compressed air supply line 48 is connected to a 
compressed air source (not shown) via a supply line 49. The compressed air 
pulses, which lead to the adjustment (explained below) of all capsule 
thread brakes in the twisting spindles connected to the compressed air 
supply line 48 with the connectors 7, may be generated in said line 48 
with the indicated control device 50. 
The structure and operation of the adjustment mechanism for the capsule 
thread brakes will be explained in more detail below with the aid of FIGS. 
3, 4, and 4a to 4c. 
The capsule thread brake shown in FIG. 3 is inserted into the hub of the 
bobbin carrier as an extension to the hollow spindle shaft 2. It has a 
housing 8, which is sealed at the top by a screw-on housing cover 9 
through which the thread feed tube 3 exits upwardly. The capsule thread 
brake arranged in the housing 8 has a first brake ring 10, which is 
arranged on the thread outlet side and is firmly connected to the housing 
8 and on which a brake cartridge 11 is supported that is comprised of two 
sleeve portions 11 and 11.1 movable toward one another against a spring 
force in a known manner. A second brake ring 12, which is secured to a 
brake ring support 12.1 arranged on the lower end of a cylindrical guide 
element 13, sits on the upper end 11.1 of the brake cartridge 11. The 
guide element 13 may be moved in the axial direction and rotated with the 
upper brake ring support 12.1 inside the housing 8. Upward movement acts 
against the pressure from a pressure spring 17, which sits on a shoulder 
of the guide element 13 and is supported at its upper end on the underside 
of the cover 9. 
Outside the second brake ring 12 and coaxially thereto a ring piston 14 is 
arranged on the guide element 13, which extends downward and is slidable 
in a ring cylinder (pressure cylinder) 15 disposed in the wall of the 
housing 8. The ring cylinder 15 is connected at its end opposite the ring 
piston 14 to the pressure line 16, which extends radially through the base 
1.1 of the bobbin carrier to the connection opening 28 in the manner 
already described and as shown in FIG. 1. 
As may also be seen from FIG. 3, the twisting spindle according to FIG. 1 
is additionally provided with a threading device 51 of known design in the 
form of an injector, to which compressed air P2 may be supplied via a 
compressed air feed line 47. The brake ring support 10.1 for the lower 
brake ring 10 of the capsule thread brake is provided as a compressed air 
piston, which may be moved downward against the force of a helical spring 
10.2. In the threading process a vacuum is generated by the action of the 
injector 52 underneath the brake ring support 10 such that the brake ring 
support 10.1 is moved downward and the lower brake ring 10 thus releases 
the brake cartridge 11. The brake cartridge 11 is held by a support ring 
8.1 connected to the housing 8 in such a position that the thread fed 
through the thread feed tube 3 is sucked in past the brake cartridge 11 by 
the action of the vacuum ("under pressure") and is guided through a thread 
guide tube 4.1 into the thread storage disc 4. Such a device is known and 
described in DE-PS 3 243 157, for example. 
A first upper toothed segment 18 and a second lower toothed segment 19 
extend in the peripheral direction about the guide element 13. The 
downwardly extending teeth of the upper toothed segment 18 form with their 
intermediate spaces slots opening downwardly in the axial direction, 
whereby their slot bases form support shoulders arranged at different 
axial heights. On the support shoulders a radially inwardly protruding 
support stop 20 in the form of a positioning pin may abut depending in 
each case on the position of the rotatable guide element 13. The structure 
and arrangement of the upper toothed segment 18 and the lower toothed 
segment 19 may be seen in closer detail in FIGS. 4, 4a, 4b and 4c. The 
downwardly oriented teeth of the upper toothed segment 18 directly adjoin 
one another in the circumferential direction and each have a leading flank 
18.2 extending from the slot base 18.1 in the circumferential direction UR 
in the form of a downwardly inclined surface relative to the 
circumferential direction UR that forms an angle of about 45.degree. to 
the circumferential direction UR. The rearward flank 18.3 behind the slot 
base 18.1, on the other hand, extends at a small angle to the axial 
direction. Similarly, the lower toothed segment 19 has leading flanks 19.2 
extending from the slot bases 19.1 in the circumferential direction UR in 
the form of upwardly inclined surfaces relative to the circumferential 
direction UR and forming an angle of about 45.degree. to the 
circumferential direction UR. The rearward flanks 19.3 behind the slot 
bases 19.1 extends essentially in the axial direction. As may be seen in 
FIGS. 4, 4a to 4c, the lower toothed segment 19 is offset in the 
circumferential direction UR relative to the upper toothed segment 18 by 
about half the tooth spacing, which offset corresponds approximately to 
the diameter X of the support stop 20. Accordingly, the inclined leading 
flanks 18.2 of the upper toothed segment 18 lie opposite the slot bases 
19.1 of the lower toothed segment 19, while the inclined leading flanks 
19.2 of the lower toothed segment 19 lie opposite the slot bases 18.1 of 
the upper toothed segment 18. 
Consequently, the raising and lowering of the guide element 13 causes it to 
rotate section by section (tooth by tooth) in the circumferential 
direction UR. The individual steps may be seen in FIGS. 4 and 4a to 4c. In 
FIG. 4a, the support stop 20 is located in the slot base 18.1 of the upper 
toothed segment 18 indicated at reference numeral I, with the guide 
element 13 in the lower position. When, as shown in FIG. 4b, the guide 
element 13 is raised in the direction of arrow H, the support stop 20, 
which is firmly connected to the housing 8, moves along the inclined 
surface (leading flank) 19.2 of the lower toothed segment 19 with the 
result that, in addition to the axial displacement in direction H, a 
movement component in the circumferential direction UR occurs, which 
directs the support stop 20 into the slot base 19.1 of the lower toothed 
segment 19, as shown in FIG. 4b. The upward movement of the guide element 
13 in direction H is caused by feeding compressed air into the ring 
cylinder (pressure cylinder) 15 through the pressure line 16. On release 
of the compressed air from the ring cylinder 15, the direction of movement 
of the guide element 13 is reversed and a downward movement results in the 
direction of arrow T shown in FIG. 4c. Due to this downward movement, the 
support stop 20 is directed onto the inclined surface of the leading flank 
18.2 of the toothed segment 18, which, in turn, results in a movement 
component in the circumferential direction UR so that, upon completion of 
the axial downward movement T, the support stop 20 now sits in the slot 
base 18.1 indicated with reference numeral II in FIGS. 4a to 4c. 
Accordingly, the guide element 13 together with the brake ring support 
12.1 has been rotated in the circumferential direction UR by exactly one 
tooth spacing or slot base spacing. Since the slot base 18.1 indicated at 
II lies higher in the axial direction than the slot base 18.1 indicated at 
I, the brake ring 12 is also positioned in a correspondingly higher 
position. This results in a different adjustment of the brake force 
between the brake cartridge 11 of the capsule thread brake and the two 
brake rings 10 and 12. As may be seen from FIG. 4c, the slot base 18.1 of 
the upper toothed segment 18 indicated at III is similarly located at a 
higher level in the axial direction so that, by applying a further 
compressed air pulse, adjustment of the guide element 13 occurs in the 
aforementioned manner. 
The path of the support stop 20 between the first and second teeth of the 
two toothed segments is illustrated in FIG. 4. From the slot base 18.1 the 
support stop 20 is displaced upon upward movement of the element 13 in the 
direction H into the position 20a, in which it meets the inclined leading 
flank 19.2. It slides along the leading flank 19.2 into position 20b. From 
there, on downward movement of the guide piece 13 in direction T, it 
reaches the position 20c. From here it passes along the leading flank 
18.2' of the upper toothed segment 18 into the position 20d in the next 
slot base 18.1'. The angles of the inclined leading flanks 18.2 or 19.2 
are selected in such a way as to allow the support stop 20 to slide in the 
circumferential direction UR without the risk of automatic locking. 
The toothed segments 18 and 19 extend over the entire periphery of the 
guide element 13. The position of the slot bases, the arrangement of the 
inclined surfaces of the leading flanks, and the height of the teeth are 
such that the above-described movement of the support stop 20 together 
with the movement of the guide element 13 from a raised position into a 
substantially lowered position and back again into the initial raised 
position is assured over the entire periphery. 
The supply of compressed air pulses operating the piston cylinder unit 
14-15 is explained below in conjunction with FIGS. 5 and 6. 
FIG. 5 shows the connector 7, already indicated in FIG. 1, which is 
arranged outside the balloon limiter 6 in the area of the lower edge of 
the protective pot 1. The connector is in the form of a piston-cylinder 
unit, wherein the guide cylinder 7 is connected via line 21 to the 
compressed air supply line 48 shown in FIG. 2 and the slide piston 22 
guided in the cylinder has a plunger 23 connected thereto as a connecting 
device. The plunger 23 projects from the guide cylinder 7 through an 
opening 7.1 on the side facing the balloon limiter 6. When the cylinder 
guide 7 is supplied with compressed air (line 21), the slide piston 22 is 
moved against the action of a piston spring 24. An axial duct 25, which is 
sealed at its outer end by means of a ball valve 27 biased by a valve 
spring 26 extends through the slide piston 22 and the plunger 23. The 
balloon limiter 6 is provided with a bore 6.1 in the area opposite the 
plunger 23, and in the corresponding area on the protective pot 1 a 
connection opening 28 is provided, to which the pressure line 16 is 
connected. A conical opening element 30 is provided in the connection 
opening 28. For sealing the plunger 23 when entering the connection 
opening 28, the connection opening 28 is provided with a gasket 29. When 
the guide cylinder 7 is supplied with compressed air (line 21), the slide 
piston 22 in FIG. 5 moves to the right and the plunger 23 moves outward. 
No compressed air is discharged from the front end of the plunger 23 in 
this case because the ball valve 27 is closed. When the plunger 23 is 
moved into the connection opening 28 and sealed by the gasket 29, and the 
conical opening element 30 penetrates the tip of the plunger 23, the ball 
valve 27 opens against the force of the valve spring 26, so that 
compressed air P1 can flow through the axial duct 25 and out of the line 
21 into the pressure line 16. 
This connector design has the advantage that, in an arrangement according 
to FIG. 2 with a central compressed air supply line and several connectors 
to be subjected to pressure, after the central compressed air supply line 
48 has been supplied with compressed air, all pistons 22 initially move 
outward uniformly and only after the plungers 23 are in position an air 
loss occurs as a result of flow into the pressure line 16. 
FIG. 6 shows another embodiment of a connector, which is a combination of a 
connector for actuation of the capsule thread brake and a connector for 
actuation of the threading device shown in FIG. 3. 
The connector has two guide cylinders 7' and 7" arranged coaxially one 
behind the other, in which slide pistons 32 and 42, respectively, are 
guided. Plungers 33 and 43, respectively, are connected to the slide 
pistons 32, 42 and arranged coaxially such that plunger 33 is positioned 
inside the other. The guide cylinder 7' is connected to a first supply 
line 31, and the cylinder 7" is connected to a second supply line 41. The 
slide pistons 32 and 42 are moved against the pressure from piston springs 
34 or 44. An axial duct 45 extends through the slide piston 42 and the 
plunger 43. The plunger 33 extends through the duct 45. The slide piston 
32 and the plunger 33 are in provided with an axial duct 35. At the front 
end of the axial duct 35 within the inner plunger 33, a ball valve 37 is 
arranged, which is biased by a valve spring 36 to seal the outlet of the 
plunger 33. A bore 6.1' is provided in the balloon limiter 6' opposite the 
plungers 33 and 43, which are movable in the radial direction toward the 
protective pot 1'. The protective pot 1' is provided with a connection 
opening 46, to which the plunger 43 may be attached. The connection 
opening 46 is connected to a first pressure line 47 leading to the 
threading device 52. A connection element 38, at which the plunger 33 
stops when moved outwardly, is provided inside the connection opening 46. 
This connection element is connected to the pressure line 16', which leads 
to the ring cylinder (pressure cylinder) 15 for operating the capsule 
thread brake. A valve 40 biased by a value spring and having an opening 
element 40.1 arranged externally is positioned behind a gasket 39 in the 
connection element 38 to seal the passage in the gasket. 
The operation of the connector shown in FIG. 6 is as follows. 
When the supply line 41 is subjected to pressure (compressed air P2), the 
slide piston 42 moves out radially to the protective pot 1' until the 
plunger 43 abuts at the connection opening 46. Compressed air passes 
through the axial duct 45 into the line 47 for operation of the threading 
device 52. When the supply line 31 is supplied with compressed air P1, the 
slide piston 32 moves out and the plunger 33 abuts at the connection 
element 38, in which case the valve 40 opens and the ball valve 37 is 
forced into the open position by the opening element 40.1. The compressed 
air flowing out of the line 31 now passes through the axial duct 35 into 
the pressure line 16' for operation of the capsule thread brake. 
In this way, the threading device and the capsule thread brake may be 
operated independently of one another by using one connector. 
Two further embodiments of devices for adjusting the capsule thread brakes 
in twisting machines, which like the arrangement described above are also 
combined with a threading device, are described below in conjunction with 
FIGS. 7 to 10. 
A difference to the embodiment described above is that the compressed air 
for actuation of the capsule thread brake is not supplied radially but 
axially to the individual twisting spindles, whereas the compressed air 
for actuation of the threading device is supplied radially in the manner 
already described. 
FIGS. 7 and 8, similar to FIGS. 1 and 2, serve to explain the basic 
structure of the twisting spindles and the arrangement of the twisting 
spindles on a spindle bearing plate. 
FIG. 7 shows a two-for-one twisting spindle S6 with a bobbin carrier 
provided with a protective pot 61 and a bobbin carrier base 61.1. In the 
hub of the bobbin carrier, a hollow spindle shaft 62 is mounted, on which 
a supply bobbin SP is positioned, from which the threads F1 and F2 are 
withdrawn and fed through the thread feed tube 63 into the hollow spindle 
shaft 62 and guided through the capsule thread brake. The thread F emerges 
at the thread storage disc 64 of the spindle rotor and, as already 
described, is guided between the shell of the protective pot 61 and a 
balloon limiter 66 upwards to the thread guide eyelet (not shown). Two 
connectors for the supply of compressed air are provided outside the 
twisting spindle, i.e. a connector 67.1, which is connected to a pressure 
source D1 to supply compressed air P1 to actuate the capsule thread brake, 
and a connector 67.2, which is connected to a compressed air source DE to 
supply compressed air P2 to actuate the threading device. The latter 
connector 67.2 is not described in further detail below and may have a 
structure known per se, e.g., as shown in FIG. 5 and described in 
conjunction with this Figure. 
As may be seen from FIG. 8, the compressed air for actuation of the capsule 
thread brake is supplied via a compressed air supply line 85 running along 
a spindle bearing plate 83 with twisting spindles S6 to S10 and with 
connectors 67.1 connected to it via branch lines 84. As already described, 
the compressed air supply line 85 is connected via a supply line 87 to the 
compressed air source (not shown). Compressed air pulses may be generated 
in the compressed air supply line 85 by the control device 86 resulting in 
adjustment of all capsule thread brakes in the twisting spindles connected 
to the compressed air supply line 85 via connectors 67.1. 
The compressed air supply line with its branch lines connected to the 
connectors 67.2 is not shown in FIG. 8. 
FIG. 9 shows the bobbin carrier and the hollow spindle shaft as well as the 
spindle rotor of a twisting spindle in section. The hollow spindle shaft 
62 has a housing 68 sealed at its top by a screw-on housing cover 69, to 
which the thread feed tube 63 is connected. The capsule thread brake is 
disposed inside the screw-on cover 63 with the upper brake ring 72 
arranged on the thread feed side and firmly connected to the housing 68. 
The axially movable, lower brake ring 70 and the brake cartridge 
comprising the sleeve parts 71 and 71.1 are arranged between the two brake 
rings 70, 72. The housing 68 is supported on the base 61.1 of the bobbin 
carrier. The lower brake ring 70 is disposed on an essentially tubular 
brake ring support 70.1, which is supported at its underside on the 
housing 68 with a pressure spring 70.2 in such a way that it may slide 
axially in the housing 68 against the bias of this pressure spring 70.2. 
Coaxially above this lower brake ring support 70.1, a guide element 73, 
essentially in the form of a hollow cylinder, is provided. It is supported 
via an inside shoulder 73.1 on a corresponding outward shoulder of the 
lower brake ring support 70.1. The guide element 73 is supported on its 
upper side with a compression spring 77 on the cover 69 of the housing 68. 
The design of the two springs 70.2 and 77 is such that the compression 
spring 77 has a stronger spring force than the first pressure spring 70.2. 
The lower section of the guide element 73 is in the form of a ring piston 
74, which extends downward and away from the brake cartridge 71 and which 
is guided in a ring cylinder (pressure cylinder) 75 disposed in the 
housing 68. A pressure line 76 extends from the ring cylinder 75 and into 
the base 61.1 of the bobbin carrier and is connected via a passage 76.1 to 
a supply line 65.1 extending outward and axially through the spindle rotor 
65. The spindle rotor 65 with the thread storage disc 64 is rotatably 
mounted in the bobbin carrier base 61.1 via bearings 65.2, and has a whorl 
89 as drive means on its lower end. The spindle rotor 65 is mounted in the 
spindle bearing plate 83 via further bearings 82.1 and mountings 82. At 
the lower end of the spindle rotor 65 the supply line 65.1 feeds into a 
connection opening 65.3, to which a connector 67.1 is connected for the 
supply of compressed air pulses P1. 
An upper toothed segment 78 and a lower toothed segment 79 extend about the 
periphery of the guide element 73. The upper toothed segment 78 
corresponds to the upper toothed segment 18 described in conjunction with 
FIG. 3 and the lower toothed segment 79 to the described lower toothed 
segment 19. A radially inwardly protruding support stop 80 provided in the 
housing 68 as a positioning pin engages between the toothed segments 78 
and 79. The structure and arrangement of the two toothed segments 78 and 
79 is shown in closer detail in FIGS. 4 and 4a to 4c, already discussed. 
The operation of the toothed segments 78 and 79 corresponds exactly to the 
operation already described in conjunction with these Figures and 
therefore will not be explained again here. 
The arrangement of the toothed segments 78 and 79 on the guide element 
results in that the raising and lowering of the guide element 73 causes it 
to rotate section by section (tooth by tooth) in the circumferential 
direction. The upward and downward movement of the guide element 73 is 
caused by supplying compressed air pulses to the ring cylinder (pressure 
cylinder) 75 to move the ring piston 74. The positioning of the guide 
element 73 at different heights in relation to the upper brake ring 72 
fixed in the housing, which may be achieved in the described way, also 
applies to the lower brake ring support 70.1, since this constantly abuts 
the inside shoulder 73.1 of the guide element 73 due to bias of the 
pressure spring 70.2. The selection of the spring force of the two springs 
70.2 and 77 assures that the pressure spring 70.2 only raises the lower 
brake ring support 70.1 until it abuts against the guide element 73, while 
the latter cannot be raised against the bias of the compression spring 77. 
In this way, the brake ring support 70.1 together with the lower brake 
ring 70 adjusts to the different height positions determined by the 
position of the guide element 73, which results in different adjustments 
of the brake 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 is 
conventionally provided with an injector 88, which may be supplied with 
compressed air P2 via a compressed air supply line 81 guided through the 
bobbin carrier base 61.1. In this way, a vacuum is generated at the 
injector 88 which applies a force on the underside of the lower brake ring 
support 70.1 in the form of a piston surface. This force causes the brake 
ring support 70.1 to move downward against the bias of the pressure spring 
70.2 with the result that the lower brake ring 70 releases the brake 
cartridge 71, which is firmly held by a support ring 69.1 disposed in the 
housing cover 69 of the housing 68 in such a position that the thread fed 
through the thread feed tube 63 is sucked in past the brake cartridge 71 
due to the vacuum ("underpressure"), and is guided through the thread 
guide tube 64.1 into the thread storage disc 64. Since in the resting 
position the guide element 73 is firmly held by the support stop 80, the 
brake ring support 70.1 is lifted downward from the guide element 73 
during the threading process, and abuts against the underside of the 
inside shoulder 73.1 once again after threading due to the bias from the 
pressure spring 70.2. 
In the case of the hollow spindle shaft of a twisting spindle shown in FIG. 
10, the capsule thread brake is also actuated by compressed air supplied 
axially through the spindle rotor, whilst the compressed air for actuation 
of the threading device is supplied radially to the twisting spindle. 
Hence, the arrangement shown in FIGS. 7 and 8 also essentially applies for 
the arrangement of the twisting spindles and the compressed air supply 
line. 
In the twisting spindle according to FIG. 10, the hollow spindle shaft 92 
has a housing 98 connected at its top to a screw-on housing cover 99. The 
thread feed tube 93 extends upwardly from the cover. A capsule thread 
brake comprising parts 101 and 101.1 is disposed in the screw-on housing 
cover 99 and supported on an upper brake ring 102 firmly connected to the 
screw-on housing cover 99 and on a lower brake ring 100 movable in the 
axial direction. The lower brake ring 100 is arranged on a brake ring 
support 100.1 disposed on the top of a guide element 103 and integrally 
connected thereto. The guide element 103 may be moved axially and rotated 
and is supported at its underside in the form of piston 104 in the housing 
98 by a pressure spring 100.2. 
An upper toothed segment 109 and a lower toothed segment 108 are arranged 
on the mantle surface of the guide element 103, each extending in the 
circumferential direction. Between the two toothed segments a radially 
inwardly directed support stop 97.1 is positioned which is secured to an 
additional axially movable guide member 97 essentially in the form of a 
hollow cylinder arranged coaxially outside the guide element 103. The 
additional guide member 97 is supported on its underside in the housing 98 
with a compression spring 107. The design of the two springs 100.2 and 107 
is such that the compression spring 107 has a stronger spring force than 
the first pressure spring 100.2. 
The piston 104 provided at the guide element 103 is positioned in a 
pressure cylinder 105 arranged in the additional guide member 97. This 
pressure cylinder 105 is connected to the inner area of the thread guide 
tube 94.1, arranged in the spindle rotor 95, via a passage 106. An 
injector 110 connected to a supply line 95.1 extending axially outwardly 
through the spindle rotor 95 opens into the section of the thread guide 
tube 94.1 pointing radially outward. The supply line 95.1 opens into the 
connection opening in a manner which is not shown. A connector similar to 
the connector 67.1 shown in FIG. 9 is connected to the connection opening 
for the supply of compressed air. 
In the rest position of the guide element 103, the support stop 97.1 abuts 
at one of the slot bases constituting the support shoulders in the lower 
toothed segment 108. When the guide element 103 moves axially downward, 
the processes are the same as those described in conjunction with the 
first mentioned embodiment in FIGS. 4 and 4a-4c. In this case, the lower 
toothed segment 108 in FIG. 10 corresponds to the upper toothed segment 18 
in FIG. 4, whilst the upper toothed segment 109 in FIG. 10 corresponds to 
the lower toothed segment 19 in FIG. 4. 
The guide element 103 is moved by supplying a compressed air pulse P1 
through the supply line 95.1, which as a result of the action of the 
injector 110 leads to a vacuum pulse ("under pressure pulse") in the 
thread guide tube 94.1, which passes through the passage 106 and acts on 
the piston 104, moving the piston 104 downward. After the external 
pressure has been reestablished, the piston 104 together with the guide 
element 103 moves upward again due to the bias of the first pressure 
spring 100.2. In the manner already described in association with the 
other embodiments, the guide element 103 together with the lower brake 
ring 100 are positioned at a different level in relation to the upper 
brake ring 102 as a consequence of the rotation of the guide element 103, 
thus resulting in a different adjustment of the brake force at the brake 
cartridge. The different design of the two pressure springs 100.2 and 107 
assures that the additional guide element 97 does not move upward with the 
guide element 103 when there is a vacuum. 
The spindle rotor 95 with the thread storage disc 94 is flexibly received 
and rotatably mounted in the housing via bearings 95.2 and a bearing bush 
95.3. The threading device for the twisting spindle shown in FIG. 10 is 
provided in a known manner with an injector 90, which is inserted into the 
upper portion of the thread guide tube 94.1 and is connected to a 
compressed air inlet 96, which is guided through the housing 98 and in the 
radial direction through the bobbin support base 91.1 outward to a 
connection opening (not shown) via which the compressed air pulses P2 are 
supplied. The guide member 97 is also in the form of a ring piston 97.2 on 
its upper side, which is arranged inside a ring cylinder 97.3. The ring 
cylinder 97.3 is connected to the compressed air inlet 96 via a branch 
line 96.1. The compressed air supplied through the compressed air inlet 96 
generates a vacuum for sucking in the threads at the injector 90. At the 
same time the additional guide member 97 is moved downward by the ring 
piston 97.2 against the bias of the compression spring 107. In this case, 
the guide element 103 together with the lower brake ring support 100.1 are 
moved downward together with the brake ring 100 by the action of the 
support stop 97.1. Thus, during threading the brake cartridge 101, 101.1 
is released from the lower brake ring 100 and is held by the support ring 
99.1 arranged in the screw-on cover 99 so that the supplied thread is 
sucked in past the brake cartridge 101, 101.1 as a result of the vacuum 
and can be fed into the thread guide tube 94.1. 
The present invention is, of course, in no way restricted to the specific 
disclosure of the specification and drawings, but also encompasses any 
modifications within the scope of the appended claims.