Title of Invention

A METHOD OF MANUFACTURING A SLIVER IN A TEXTILE MACHINE AND A DEVICE FOR THE SAME

Abstract Method for Pressing a Feeler Member Against a Fibre Assembly in a Sliver Guide and Device for the Production of this Pressing-Against Action The invention relates to the pressing of a feeler member against a fibre assembly in a sliver guide, such as is used for measuring the thickness of fibre assemblies on a textile machine. The object of the invention is to guarantee a linearity of the measuring signal for the entire measuring range of a sliver guide with feeler member, which sliver guide is arranged on a textile machine for measuring the thickness of a sliver, and to reduce the effort for its resetting during a batch change. According to the invention, the object is achieved in that the contact force of the movable feeler member (28\ 40f, 86) is maintained at a substantially constant value over the entire measuring range of a sliver guide with feeler member by means of actuating member (30, 45, 60, 70, 90, 99). (Figure 5)
Full Text


The invention relates to the pressing of a feeler member against a fibre assembly in a sliver guide, such as is used for measuring the thickness of fibre assemblies on a textile machine. Such a textile machine may be a carding machine, a draw frame, a fly frame or a spinning machine. The pressing-against action of the feeler member is important for the formation of a correct measuring signal for the thickness of the fibre assembly. The measuring signal for the thickness is important for the control of other processes on the textile machine.
In order to determine the thickness of a fibre assembly, the fibre assembly is guided over a sliver guide which is fixedly installed. Such a sliver guide may be a feeler roll with its axis of rotation fixed, a bar, a sliver-guiding channel or a sliver funnel. The sliver assembly has contact with the sliver guide and is guided thereby. A feeler member is pressed onto the fibre assembly guided in the sliver guide. The pressing-against action is effected by a spring which is tensioned and is connected to the feeler member. The feeler member is movably mounted, i.e. moves at a distance from the sliver guide in dependence on the thickness of the conveyed fibre assembly. The feeler member may perform a pivoting movement or lifting movement in the process.
The feeler member is arranged with a signal converter which detects the movement of the feeler member and converts it into an electrical measuring signal. The feeler member may, for example, be a movable feeler roll. The movable feeler roll is pressed onto the fixed feeler roll. The movable feeler roll may be arranged here in a pivoting arm or lifting carriage. A spring acts on the pivoting arm or lifting carriage and enables the pressing-against action.
A feeler member is also understood to mean a feeler element which, schematically, may have the shape of a finger. This feeler element projects in the conveying direction onto the sliver

guide. The part of the feeler element touching the fibre assembly is constructed as a sliding surface. The feeler element is movable vertically and at right angles in relation to the running direction of the fibre assembly. Since the feeler element is constructed as a lever arm, it is pressed by means of a spring in the direction of a stationary sliding surface of a sliver-guiding channel or of a sliver funnel. The sliver-guiding channel or sliver funnel corresponds to a sliver guide. Through the movement of the feeler element, the thickness of the fibre assembly is determined. A connected signal converter converts the quantity of movement into an equivalent electrical signal.
The term fibre assembly is understood to mean a fibrous web, a sliver doubled from a plurality of slivers, or a drafted sliver.
The deficiencies which exist in respect of the pressing of a feeler member against a fibre assembly in a sliver guide are explained below with the aid of a pair of feeler rolls. These deficiencies in respect of the pressing-against action of a pair of feeler rolls can be applied generally to the pressing-against action of a feeler member.
The construction, use and mode of operation of such a pair of feeler rolls is described in detail in the operating instructions for Draw frame RSB 851 (4135), SB 851 (4131) of RIETER Spinning Systems, of August 1990. In section 4.5.1. the setting of the feeler-roll loading for a feeler roll arranged upstream of the entrance to a drafting arrangement is described. The fixed feeler roll is rotatably mounted and has a groove radially at the periphery. The sliver to be measured is guided in this groove. The movable feeler roll has its axis of rotation mounted in a pivoting arm, the pivoting arm being pivotable about its axis of rotation. The pivoting arm pivots in accordance with an arc of a circle. The movable feeler roll has a ring arranged circumferentially at the periphery. Since the movable feeler roll is arranged in a pivoting arm, via a spring acting on the pivoting arm the movable feeler roll is pressed onto the fixed feeler roll. The ring of the movable feeler roll presses into the groove of the fixed feeler roll and, as a result of the spring loading, presses the sliver to be measured. The pair of feeler rolls is driven by force-transmitting means of a drive. Both feeler rolls rotate synchronously with one another.

The sliver is conveyed through the pair of feeler rolls and passed on to the pair of drawing-in rollers of the drafting arrangement.
Also known are pairs of feeler rolls in which the movable feeler roll executes a lifting movement with respect to the fixed feeler roll. Here, too, the movable feeler roll is pressed on. The following statements concerning a pair of feeler rolls are also applicable to this form of construction.
The distance between the axis of the fixed feeler roll and the axis of the movable feeler roll changes with the thickness of the sliver. As a result of the variation in thickness of the sliver, the corresponding pivoting movements of the movable feeler roll are converted into an electrical signal by a signal converter. This electrical signal is supplied to electronics which control the drafting of the sliver in the drafting arrangement.
The size of the contact force required for the movable feeler roll, which is realised by a tension spring, is dependent on the processed sliver material and the drawing-in speed. To set the desired contact force, shackles of different spacing on the spring are used, so that each shackle at a different position can be hung into the pivoting arm. The different shackles represent different contact pressures. This changeover requires effort in terms of mounting, and the drafting arrangement has to be stopped. It is also disadvantageous that the contact force is adjustable only in steps in accordance with the available shackles of the spring. The spring is an actuating member which is set only manually. It is not possible to set intermediate values.
With varying deflection of the movable feeler member, the tensile force of the spring also changes, so that a varying contact force on the sliver arises in the entire measuring range. A lack of linearity of the measuring signal over the measuring range of the feeler member is observed, i.e. there is no direct linearity between the thickness of the sliver and the deflection of the movable feeler member. This is a considerable deficiency. It leads to the formation of incorrect measuring signals and ultimately to incorrect drafting. This observation also applies to a sliver funnel as sliver guide with a feeler element as feeler member.

A sliver guide with feeler member may, however, also be employed downstream of a drafting arrangement. In this case, the stated deficiencies apply just the same. According to the operating instructions mentioned at the beginning, this concerns the drawing-off rollers (section 4.4.3, page 28 and section A4, page 86 ff). These drawing-off rollers are employed for measuring the thickness of the sliver downstream of the drafting arrangement. These drawing-off rollers work analogously to the pair of feeler rolls described. The drawing-off rollers deliver a measuring signal to a sliver monitor which checks that the sliver count is met.
The object of the invention is to guarantee a linearity of the measuring signal for the entire measuring range of a feeler member of a sliver guide, which feeler member is arranged on a textile machine for measuring the thickness of a sliver, and to reduce the effort for its resetting during a batch change.
The object is achieved in the case of a feeler member of a sliver guide of the generic type by the characterising features according to Claims 1 and 9.
In the pressing of a feeler member against the fibre assembly in a sliver guide, it is ensured that the contact force of the movable feeler member is maintained substantially constant over the entire measuring range of the feeler member by means of an actuating member.
The actuating member may be formed by a cylinder and piston, which is so designed that it acts as a pneumatically or hydraulically working volume accumulator. In the volume accumulator, a pressure is set which acts via the connection of piston to feeler member and which, with deduction of corresponding resistance forces on this connection path, corresponds to the desired contact force at the movable feeler member. The volume accumulator is so dimensioned in its volume that the movements transmitted from the feeler member to the piston lead merely to insignificant pressure changes in the volume accumulator. Owing to the fact that insignificant pressure changes occur, it is possible for the pressure in the volume accumulator and hence the contact force at the movable feeler member to be maintained at a substantially constant value in the entire measuring range.

The volume accumulator may advantageously be constructed as a cylinder and pressure compensation cylinder. The pressure compensation cylinder may also be designed as a defined length of a hose with extensible wall. The pressure compensation cylinder may have a connection to a pressure generator. The pressure which is set and maintained in the volume accumulator is transmitted to the feeler member at the piston by means of force-transmitting means (for example a rod). It should be borne in mind here that the force with which the piston is prestressed on one side is to be overcome. The pressure which is set and maintained in the volume accumulator is equivalent to the contact force of the movable feeler roll. In a further advantageous embodiment, the volume accumulator, i.e. cylinder and pressure compensation cylinder, may be connected to a pressure-reducing valve. The pressure-reducing valve enables the desired value of the pressure in the volume accumulator and hence, ultimately, the contact force of the movable feeler roll to be continuously adjustable. With the connection of a regulatable pressure generator to the inlet of the pressure-reducing valve, pressure is transmitted to the volume accumulator. When the preset desired value is exceeded, the pressure-reducing valve relieves the excess pressure automatically until the desired value is reached again. With the regulatable pressure generator, it is possible to control its own mode of working. When the desired value at the pressure-reducing valve is reached, the pressure generator can be shut off, so that the inlet pressure reached at the pressure-reducing valve is maintained. By continuously changing the desired value at the pressure-reducing valve, it is possible to make values of the contact force continuously variable and adjustable. This is particularly advantageous when, during a batch change, new values of the contact force have to be set owing to changed delivery speeds or changed sliver material. On interruption of the inlet pressure to the pressure-reducing valve or during relief of the volume accumulator via the pressure-reducing valve, the pressure of the volume accumulator can be reduced to such a degree that the piston is switched over due to the one-sided prestress of a compression spring from a pushing movement to a pulling movement. The tensile force obtained at the piston, due to the one-sided prestress of the compression spring, with respect to the movable feeler member guides the feeler member from a working position into an open position. This guiding of the feeler member into an open position makes it easier for the operator, particularly during a batch change, to insert a new fibre assembly between feeler member and sliver guide. After insertion of the fibre assembly between feeler member and sliver guide, there is an automatic changeover to contact force due to the

increase in pressure in the volume accumulator, so that the feeler member is also guided back from the open position into the working position.
If a mobile, external pressure generator were to be employed, the inlet to the pressure-reducing valve would have to be connected to a non-return valve.
According to a further advantageous embodiment, the actuating member is controllable. For this purpose, a pressure sensor which determines the current pressure and transmits this to a control means is arranged in the volume accumulator of the actuating member. A control valve is controlled in dependence on a desired value for the pressure, which is preset in the program of the control means. This control valve is connected to a pressure generator. In the event of an unwanted pressure increase in the actuating member, this is recognised via the sensor and reported to the control means. The control means actuates the control valve in the discharge direction and closes again when the desired value is reached. If there is a reduced pressure in the actuating member, the sensor reports this to the control means, in which case the control means switches the control valve to permit transmission with regard to the pressure generator and at the same time sets the pressure generator in operation. When the desired value of the pressure in the actuating member is reached, the control means closes the control valve, so that the pressure in the actuating member is maintained and the pressure generation is shut off.
With the program for such a control means, it is possible to select from a large number of desired values, the selection being able to be made in conjunction with a command input from an operator interface by the machine personnel. The control means thus automatically sets the desired pressure in the actuating member, as already described, in the interplay between actuating member, control valve and pressure generator. As already explained, this pressure corresponds to the desired contact force at the feeler member, with deduction of the one-sided prestressing force on the piston. With this control means, in an advantageous manner the feeler member can be automatically guided from a working position into an open position.
According to another embodiment, the actuating member is formed from an electric torque motor. As a rule, a gear unit is integrated in torque motors. The output of the gear unit is

connected to the feeler member directly or by means of force-transmitting means. The torque motor serves for the delivery of a constant torque at very low rotational speed or at standstill. This corresponds to a working characteristic. It is thus possible to generate a constant torque for the entire measuring range of the feeler member, which guarantees an approximately constant contact force of the feeler member. This actuating member is also controllable. By changing the phase control in the voltage supply to the torque motor, it is possible to set its rotational speed and thus its torque to a desired value. This corresponds to the procedure during a batch change. The direction of rotation may be changed as well. This is expedient when the movable feeler member has to be guided away from the sliver guide into an open position.
The invention and features thereof will be described below with reference to embodiments. In this connection:
Figure 1 shows locations of use of a pair of feeler rolls on a draw frame;
Figure 2 shows the state of the art for producing a contact force at the pair of feeler
rolls;
Figure 2a shows the state of the art for producing a contact force at the feeler
element of a sliver funnel;
Figure 3 shows an actuating member in the form of a volume accumulator
designed with a cylinder;
Figure 4 shows an actuating member in the form of a volume accumulator
designed with a cylinder and pressure compensation cylinder;
Figure 5 shows an actuating member in the form of a volume accumulator
according to Figure 4 with a pressure-reducing valve;

Figure 6 shows an actuating member in the form of a volume accumulator with a
pressure-reducing valve and non-return valve;
Figure 7 shows a controllable actuating member;
Figure 7a shows a control valve in the form of a 3-way valve; and
Figure 8 shows an actuating member in the form of a torque motor.
Figure 1 shows, in a schematic representation, a draw frame of the textile industry. The slivers 1 which are drawn off from cans are supplied to a sliver funnel 2 via a feed table 4. This sliver funnel 2 layers the slivers to form a sliver 5. The sliver 5 appearing at the mouth of the sliver funnel 2 runs through a pair of feeler rolls 3,3\ This pair of feeler rolls 3,3' measures the thickness of the sliver and, in conjunction with a signal converter, forms a measuring signal 6 for the sliver thickness. This measuring signal 6 is made available to a regulating device in order to control the drafting of the sliver 5 in the drafting arrangement 7. In addition, this measuring signal 6 can also be supplied to further signal-processing devices serving, for example, to improve the drafting control. The sliver 5 is passed on from the pair of feeler rolls 3,3' to the pair of drawing-in rollers 8,8' of a drafting arrangement 7. The drafting arrangement 7 possesses furthermore a pair of middle rollers 9,9' and a pair of delivery rollers 10,10'. The sliver 5 is conveyed from the pair of delivery rollers 10,10' to a depositing apparatus 11. This depositing apparatus 11 contains known working members, such as a fibrous-web funnel, sliver channel, sliver funnel and a pair of calender rollers 300, 300f. The sliver 5 runs through these working members, some of which are not shown, in the depositing apparatus 11 and is ultimately coiled in a can 13 by means of a revolving plate 12.
The pair of calender rollers 300, 300* has the task of measuring the thickness of the sliver at the exit from the drafting arrangement. The measuring function of the pair of calender rollers 300, 300f is analogous to that of the pair of feeler rolls 3,3\ The pair of calender rollers 300,300' delivers a measuring signal 600 which is delivered, for example, to a sliver monitor. The sliver monitor checks, for example, that the sliver count is met.

Figure 2 shows further details with regard to the pair of feeler rolls, as are known in the state of the art. The pair of feeler rolls has a feeler roll 28 which is mounted to be rotatable at the axis of rotation 14. The axis of rotation 14 is fixed. The fixed feeler roll corresponds to a sliver guide. The complementary component is the feeler roll 28'. The movable feeler roll 28' corresponds to a feeler member. The feeler roll 28! is mounted to be rotatable about the axis of rotation 15. The axis of rotation 15 is arranged in a pivoting arm 17. The pivoting arm performs the function of a movement device. The pivoting arm 17 is pivotable about the axis of rotation 16. This mechanical arrangement applies analogously to the pair of calender rollers 300,300'. An angle arm 18 which carries a metallic target 19 is arranged on the pivoting arm 17. Arranged opposite the target 19, in a fixed position, is a sensor 20 which works in a contactless manner. The sensor 20 has a signal line which leads to a control, which may, for example, be the regulation of the draw frame or another signal evaluation for improving the regulation. The sliver 5 is nipped between the pair of feeler rolls 3,3\ The feeler roll 3 has a groove N, in which the sliver is guided and the feeler roll 3! has a ring R which holds the sliver 5 in the groove N. This geometry is advantageous for the sliver guidance, but is not necessary for the functioning of the invention. Ring R and groove N may be dispensed with, for example, in the case of the pair of calender rollers 300,300'. Situated at the end of the pivoting arm 17 is a drill hole 23, in which a spring 22 engages. This spring 22 hangs by its spring end, constructed as a shackle 26, on a fixed hook 27. The spring 22 is thereby tensioned and presses the feeler roller 28? against the fixed feeler roll 28, i.e. the ring R presses the sliver into the groove N. Thick places or thin places in the sliver 29 lead to a pivoting movement of the pivoting arm 17 and thus to a pivoting movement of the feeler roll 28'. This is also applicable to the pair of calender rollers 300,300', the calender roller 300' being the movable one. This pivoting movement is transmitted through the target 19 opposite the fixed sensor 20 which works as a proximity sensor. The sensor 20 forms an electrical signal in accordance with the pivoting movement of the feeler roll 28', which signal is equivalent to the sliver thickness. In the case of this known device, there is the disadvantage that, in the event of relatively large disruptions of the sliver thickness, a relatively large deflection of the feeler roll 28' takes place. However, with a relatively large deflection of the feeler roll 28', the spring loading and thus the contact force changes in a different order of magnitude than compared with a relatively small deflection. This observation is also applicable to the pair of

calender rollers 300, 300'. Measuring signals which have been produced at varying contact pressures are therefore emitted via the signal line 21. This is an incorrect measurement.
In the case of a batch change, with a different material of the sliver or with a different delivery speed, a changed value of the contact pressure is also necessary. For this purpose, the spring 22 has further shackles 24, 25, so that during a batch change either shackle 24 or 25 is hung onto the fixed hook 27. This corresponds to a step-by-step, abrupt change. It is not possible to set intermediate values. A new, process-dependent contact force of the spring is thus manually produced. This requires a manual effort for resetting. The draw frame has to be stopped for this purpose. Moreover, the deficiency of there being no constancy of the contact force over the entire measuring range of the pair of feeler rolls remains after the batch change as well.
In the state of the art, it is known to measure the sliver thickness, for example, on a draw frame not only using pairs of feeler rolls. It is also known to measure the sliver thickness using a sliver funnel and a feeler element. In this context, the sliver funnel 2 could contain a feeler element, and the pair of feeler rolls 3, 31 as measuring member could be dispensed with. Further details are illustrated in Figure 2a.
Figure 2a shows details with regard to a sliver funnel with feeler element, as are known in the state of the art. In the same way as the pair of feeler rolls, the sliver funnel with feeler element is a specific embodiment of a sliver guide with feeler member.
The sliver funnel 80 is arranged, for example, upstream of a drafting arrangement of a draw frame. A plurality of slivers 87 are layered by the sliver funnel 80 and compressed to form a sliver 88. In a cutout of a funnel wall there is arranged a feeler element 86. The feeler element 86 is pivotably mounted at a pivot 81. The lever of the feeler element 86, which lever lies outside the funnel 80, is connected to a spring 82 which tensions the feeler element 86. The spring 82 presses the sliding surface of the feeler element 86, which surface lies inside the funnel 80, against the incoming sliver in the direction of the stationary wall of the sliver funnel. The feeler element 86 may furthermore be connected to a plunger core 84 which projects into an electrical measuring element 83. The electrical measuring element 83 may, for example, be a plunger coil.

Owing to the varying sliver thickness, the feeler element 86 is moved. The movement of the feeler element 86 leads to a movement of the plunger core 84, so that the electrical measuring element 83 produces an electrical measuring signal 85. In the case of a relatively large deflection of the feeler element 86, the contact force due to the spring 82 reaches different values than in the case of a relatively small deflection. The deficiency exists of there being no constancy of the contact force over the entire measuring range of the feeler element 86. This is analogous to the fault as already described in the case of the pair of feeler rolls 28,28Figure 3 shows an embodiment of the invention. The actuating member 30 may be designed as an hydraulically or pneumatically working volume accumulator. The volume accumulator comprises a cylinder 32, 34 and piston 33. Arranged in the cylinder 34 is a compression spring 35 with known spring characteristics. The force action of the spring 35 is so directed that the piston 35 can be moved in the direction of the cylinder 32. The piston 33 is connected to rod 36. The other end of the rod 36 is connected to a pivoting arm 41. The pivoting arm 41 carries a pivot 43, at which the rod 36 is movably mounted. At its end, the rod 36 carries a target 39. A proximity sensor 44 is arranged in a contactless manner opposite the target. The pivoting arm 41 carries a movable feeler roll 40\ The pivoting arm 41 is pivotable about the axis of rotation 42.
The volume accumulator is connected by means of connection 37 to a controllable pressure generator 38 via the connection line thereof. The volume accumulator is to be so dimensioned in its extent that all the pressure changes produced via the feeler roll 40' - piston 33 connection in the cylinder 32 are so damped that the pressure in the cylinder 32 can be maintained at a substantially constant value.
In order to establish the readiness for operation of the pair of feeler rolls 40, 40', the desired contact force of the movable feeler roll 40' must be set. In this regard, it should be noted that the spring force of the spring 35 is to be overcome. For this purpose, compressed gas, for example, is blown in at the connection 37 by means of pressure generator 38. The connection 37 can therefore be directly connected to a central compressed-gas generator of a draw frame. The pressure generator 38 is regulatable, so that when the appropriate gas pressure is reached in the cylinder 32 the pressure generation is discontinued. The pressure existing in the cylinder 32 has

reached that value which is ultimately equivalent to the required contact force of the movable feeler roll 40'. The cylinder 32, designed as a volume accumulator, makes it possible for movements of the piston 33 to lead to an insignificant change in the pressure in the cylinder 32, so that the contact force of the movable feeler roll 40* can be maintained substantially constant over its entire measuring range.
Figure 4 shows an actuating member 45 in an embodiment which is slightly modified compared with Figure 3. The actuating member 45 has a cylinder 47, 49 with a piston 48. As in Figure 3, the piston 48 is connected by a rod 51 to a movable feeler roll (not shown hereafter). The movement of the feeler roll is transmitted to the piston 48 via rod 51. Arranged in the cylinder 49 is a compression spring 50 which exerts a force on the piston 48. A pressure sensor 5 connected to an indicating device can be arranged in the cylinder 47.
The cylinder 47 is connected to a pressure compensation cylinder 46. The pressure compensation cylinder 46 is connected to a regulatable pressure generator 52 via the connection line thereof.
The actuating member 45 works on the principle of the volume accumulator. The cylinder 47 is so dimensioned that it can accommodate all the movements of the piston 48. The pressure compensation cylinder 46 constitutes an additional volume. The pressure compensation cylinder 46 is so dimensioned that the pressure changes caused by the piston 48 become so small and insignificant that the pressure prevailing in the cylinder 47 remains substantially constant. This pressure is sensed by the sensor S and displayed by means of indicating device A. The pressure compensation cylinder 46 may, for example, by a defined length of a connection tube. The pressure compensation cylinder 46 may, however, also be a defined length of an extensible hose. The extensible hose has the advantage that it can be kept shorter in its length since its walls are extensible. By means of regulatable pressure generator 52, the actuating member 45 can be filled, for example, with compressed gas. The indicating device A shows the machine personnel the current gas pressure in the actuating member 45. The pressure in the actuating member which is required to set a necessary contact force at the movable feeler roll can be determined on the basis of calculations or measurements. Once this equivalent pressure in the actuating

member 45 is reached, the pressure generator 52 is shut off. The desired pressure is preserved in the actuating member 45.
Figure 5 shows a further, modified embodiment. The actuating member 60 comprises a cylinder 55, 57 with a piston 56. As in the preceding figures, the piston 56 is connected by means of rod 59 to a movable feeler member (not shown). The connection to a feeler element of a sliver funnel, for example, would also be possible. Arranged in the cylinder 57 is a compression spring 58 which exerts a force on the piston 56. The cylinder 55 is connected to a pressure compensation cylinder 54. The pressure compensation cylinder 54 is connected to a pressure-reducing valve 53. Cylinder space 55 and pressure compensation cylinder 54 work on the principle of the volume accumulator. This volume accumulator is ultimately connected to a pressure-reducing valve. The inlet of the pressure-reducing valve 53 is connected to a regulatable pressure generator 61 via the connection line thereof. A desired value for the gas pressure in the volume accumulator can be set at the pressure-reducing valve 53. The pressure generator 61 generates the gas pressure. If the gas pressure in the actuating member 60 gets too high, the pressure-reducing valve 53 automatically reduces the gas pressure to the set desired value. For the functioning of the pressure-reducing valve 53 it is important that a necessary inlet pressure is constantly made available by the pressure generator 61.
Figure 6 shows a possible embodiment for an actuating member 70, in which a pressure generator 72, either a stationary pressure generator or a mobile pressure generator, may be used. The actuating member 70 likewise works on the principle of the volume accumulator, with a cylinder 65, 66 with a piston 67 and a pressure compensation cylinder 64 being provided. The piston 67 is connected by means of rod 69 to a movable feeler member (not shown). Situated in the cylinder 66 is a compression spring 68 which exerts a force on the piston 67. The pressure compensation cylinder 64 is connected to a pressure-reducing valve 63. Furthermore, the inlet of the pressure-reducing valve 63 is connected to a non-return valve 62. The non-return valve 62 with its connection 71 forms the connection to the actuating member 70.
It is possible, for example, for a mobile pressure generator 72 to be connected to the connection 71. The pressure generator 72 may, for example, be a compressed-gas generator. Compressed

gas would be conveyed through the non-return valve 62 and the pressure-reducing valve 63 into the pressure compensation cylinder 64 and the cylinder 65. In the process, the piston 67 would be moved against the spring 68. At the same time, the piston 67 presses the movable feeler member by means of rod 69. The pressure generator 72 is taken away from the connection 71 when the desired pressure is reached in the pressure compensation cylinder 64 and cylinder 65. This can be determined on the indicating instrument of the pressure generator 72 or by installation of a sensor in the cylinder 65 and connection thereof to an indicating device. The pressure set in the volume accumulator corresponds to the set desired value at the pressure-reducing valve 63. This pressure on the piston 67 is equivalent to the contact force measurable at the movable feeler member. This contact force at the movable feeler member must remain substantially constant over the entire measuring range of the feeler member. This requirement is met by the fact that, in the actuating member 70, cylinder 65 and compensation cylinder 64 work on the principle of the volume accumulator. The non-return valve 62 makes it possible for the pressure at the inlet of the pressure-reducing valve 63 to remain constant after interruption of the connection to the pressure generator 72. In contrast to Figure 5, the pressure generator may be interrupted or removed.
Figure 7 shows in a further embodiment an actuating member 90 which is controllable. The actuating member 90 contains a cylinder 75, 76 with piston 77 and a pressure compensation cylinder 74. As already shown, piston 77 is connected by means of rod 79 to a feeler member. The piston 77 is again prestressed by a spring 78 arranged in the cylinder 76. Cylinder 75 is connected to pressure compensation cylinder 74. Situated in the cylinder 75 is a sensor 73 which has a connection to a control means 93. The pressure compensation cylinder 74 is connected to a control valve 91. The control valve 91 is connected to a pressure generator 92 by connection line. The pressure generator 92 is, for example, a compressed-gas generator and delivers compressed gas into the actuating member 90, The sensor 73 communicates the current pressure in the actuating member 90 to the control means 93. Once a desired value which has been programmed into the control means 93 is reached, the control means 93 switches the control valve 91. The desired value for the pressure which has been programmed into the control means 93 corresponds to that value which is likewise equivalent to the contact force to be set at the movable feeler member. On closure of the control valve 91, the desired value of the pressure in

the actuating member 90 is preserved. With the control valve closed, the pressure generator vi reaches an upper limiting value of the pressure, at which it shuts itself off.
The embodiment according to Figure 7 has the advantage that, for example during a batch change, the setting to another contact force can be carried out by the control means 93. If the control means 93 receives the instruction, by manual input or by command from a control program, to change over to another desired value of the pressure in the actuating member 90, the control means 93 can accomplish this with the aid of the control valve 91.
If, for example, a higher pressure were to be set in the actuating member 90, which corresponds to a higher contact force of the movable feeler member, the control valve 91 would be switched by means of control means 93 to the direction permitting transmission between pressure generator 92 and actuating member 90. At the same time, the pressure generator 92 would be set in operation by the control means via the connection line. The pressure generator 92 is able to increase the pressure in the actuating member 90 to the desired value. When the sensor 73 delivers the current pressure values in the actuating member 90 to the control means 93, the control means recognises when the new, desired value is reached. Once the new desired value is reached, the control valve 91 is shut. The new desired value of the pressure in the actuating member 90 is maintained on closure of the control valve 91. The pressure generator 92 switches off automatically, as already described.
If, on the other hand, a lower desired value of the pressure in the actuating member 90 is required, i.e. a correspondingly lower contact force, the control valve can be switched by means of program of the control means 93 to a discharge position, i.e. compressed gas is able to escape outwards into the atmosphere from the actuating member 90 via the control valve 91. When the sensor 73 senses the corresponding lower value of the pressure, the control means 93 closes the control valve 91 and maintains the lower desired value of the pressure. The control valve 91 may be designed, for example, as a 3-way valve 100.

Figure 7a shows a possible embodiment of a 3-way valve 100. Three valve states can be set. The valve state A relates to the establishment of a connection V between connection line to the pressure generator 92 and conduit to the actuating member 90, so that compressed gas can be delivered from the pressure generator 92 into the actuating member 90. The valve state B relates to the interruption U of the said connection, so that no compressed gas is able to escape from the actuating member 90. The valve state C relates to the establishment of a connection V from the actuating member 90, i.e. from the pressure compensation cylinder 74, to a discharge tube AR. The mouth of the discharge tube AR leads into the surrounding atmosphere, so that compressed gas is able to escape from the pressure compensation cylinder 74 along with cylinder space 75 into the atmosphere. In this case, the pressure in the actuating member 90 is reduced. The corresponding valve state A, B or C at the control valve 91, which is designed as a 3-way valve 100, is controlled by the control means 93.
Figure 8 shows a further embodiment of the invention. The actuating member 99 is formed by an electrical torque motor 94 which is integrated with gear unit 95. The gear unit 95 is connected by means of force-transmitting means 96 to a feeler member. The torque motor 94 is connected by means of transmission line 98 to a controllable voltage source 97. The torque motor serves for the delivery of a torque at very low rotational speed or at standstill. It is thus possible, for a fixed measuring range of the feeler member, to generate a constant torque which, via the force-transmitting means 96, guarantees an approximately constant contact force of the feeler member.
By changing the phase control of the voltage source 97, it is possible to set the rotational speed of the torque motor 94 and thus its torque to a desired value. The direction of rotation can be changed as well. This is expedient when the movable feeler member is to be guided away from the fixed sliver guide into an open position.




Claims
1. A method of manufacturing a thread in an open-end spinning machine, comprising the step of pressing a feeler member against a fibre assembly in a sliver guide which is arranged on a textile machine for measuring the thickness of a moving fibre assembly, the feeler member being movably mounted with its axis and an actuating member in connection with the movable feeler member exerting a contact force on the movable feeler member, wherein the contact force of the movable feeler member (28',40', 86) on a fibre assembly in a sliver guide is maintained at a substantially constant value over the entire measuring range of the movable feeler member (28', 40', 86) by means of actuating member (30,45,60,70,90,99).
2. Method according to Claim 1, wherein the actuating member (30, 45, 60, 70, 90) works as a pneumatic or hydraulic volume accumulator.
3. Method according to Claim 1, wherein the actuating member (99) works as a torque motor.
4. Method according to Claim 1, wherein the actuating member (90,99) is controllable.
5. Method according to Claim 4, wherein the actuating member (90) is controlled in dependence on its pressure change with respect to a set desired value by a control means (93) with control valve (91).
6. Method according to one or more of Claims 1 to 5, in which the contact force is set to a new value during a batch change, wherein the contact force is changed and set to a new, process-dependent value by means of actuating member (30,45,60,70,90,99).

7. Method according to Claim 6, wherein the change in the contact force by means of actuating member (30,45, 60, 70,90,99) is effected continuously.
8. Method according to one or more of Claims 1 to 7, in which the sliver guide with feeler member is stopped, wherein the contact force of the movable feeler member (281, 40', 86) is replaceable by a tensile force using the actuating member (30, 45, 60, 70, 90, 99), so that the movable feeler member (28', 40', 86) can be guided away from the fixed sliver guide (28,40, 80) into an open position.
9. Device for the production of a pressing-against action according to one or more of Claims 1 to 8, in which an actuating member is connected to a movable feeler member, wherein the movable feeler member (28', 40', 86) is connected to an actuating member (30, 45, 60, 70, 90,99) which produces a substantially constant contact force of the movable feeler member (28*, 40', 86) for the entire measuring range of the feeler member.
10. Device according to Claim 9, wherein the actuating member (30) has a cylinder (32, 34) with a piston (33), which cylinder is constructed as a volume accumulator.
11. Device according to Claim 10, wherein the cylinder (32) has a connection (37) to a pressure generator (38).
12. Device according to Claim 10, wherein the actuating member (45) has a cylinder (47, 49) with a piston (48), which cylinder is constructed as a volume accumulator, and a pressure compensation cylinder (46) in connection therewith.
13. Device according to Claim 12, wherein the pressure compensation cylinder (46) has a connection line to a pressure generator (52).
14. Device according to Claim 12, wherein a compression spring (50) is arranged in the cylinder (49).

15. Device according to Claim 10, wherein the actuating member (60, 70) has a cylinder (55, 57; 65, 66) with a piston (56, 67), which cylinder is constructed as a volume accumulator, and a pressure compensation cylinder (54, 64), the pressure compensation cylinder (54, 64) being connected to a pressure-reducing valve (53,63).
16. Device according to Claim 15, wherein the piston (56, 67) is connected to a feeler member (28\ 40', 86) by means of a rod (59,69).
17. Device according to Claim 15, wherein a compression spring (58, 68) arranged in the cylinder (57,66) acts on the piston (56,67).
18. Device according to Claim 15, wherein the desired value of the pressure is set at the pressure-reducing valve (53,63).
19. Device according to Claim 15, wherein the inlet of the pressure-reducing valve (53) is connected to a pressure generator (61).
20. Device according to Claim 15, wherein the inlet of the pressure-reducing valve (63) is connected to a non-return valve (62).
21. Device according to one or more of Claims 9 to 20, wherein the actuating member (30, 45,90) is connected to a control means (93).
22. Device according to Claim 21, wherein there is arranged in the actuating member (30, 45, 90) a pressure sensor (73) which is connected to the control means (93), and the actuating member (30,45,90) is in connection with a control valve (91), and the control means (93) has a connection to the control valve (91).
23. Device according to Claim 9, wherein the actuating member (99) has a torque motor.

24. Device according to Claim 21, wherein the torque motor (94) has a gear unit (95) which
is connected to a feeler member (28', 40\ 86) directly or by means of force-transmitting means
(96).
25. A method of manufacturing a thread in an open-end spinning machine substantially as
hereinbefore described with reference to the accompanying drawings.
26. A device for the production of a pressing action substantially as hereinbefore described
with reference to the accompanying drawings.


Documents:

14-mas-1996 abstract 19-07-2004.pdf

14-mas-1996 claims 19-07-2004.pdf

14-MAS-1996 CORRESPONDENCE OTHERS 19-10-2009.pdf

14-mas-1996 correspondence others.pdf

14-mas-1996 correspondence po.pdf

14-mas-1996 description (complete) 19-07-2004.pdf

14-mas-1996 form-1 19-07-2004.pdf

14-mas-1996 form-19 01-12-2003.pdf

14-mas-1996 form-4 19-07-2004.pdf

14-mas-1996 form-6 04-03-2005.pdf

14-mas-1996 petitions.pdf

14-mas-1996 power of attorney 19-07-2004.pdf

14-mas-1996- abstract.pdf

14-mas-1996- claims.pdf

14-mas-1996- correspondence others.pdf

14-mas-1996- description complete.pdf

14-mas-1996- drawings.pdf

14-mas-1996- form 1.pdf

14-mas-1996- form 26.pdf

14-mas-1996- form 3.pdf

14-mas-1996- form 4.pdf

14-mas-1996abstract.jpg

abs-14-mas-1996.jpg


Patent Number 248279
Indian Patent Application Number 14/MAS/1996
PG Journal Number 27/2011
Publication Date 08-Jul-2011
Grant Date 01-Jul-2011
Date of Filing 03-Jan-1996
Name of Patentee RIETER INGOLSTADT SPINNEREIMASCHINENBAU AKTIENGESELLSCHAFT
Applicant Address FRIEDRICH-EBERT-STRASSE 84, 85046 INGOLDSTADT, GERMANY
Inventors:
# Inventor's Name Inventor's Address
1 STROBEL, MICHAEL-MARIA AM WEINBERG 2, 85072 EICHSTATT
2 MUNNEKEHOFF, GERD DAMMSTRASSE 34, 42857 REMSCHEID
PCT International Classification Number G01B7/06 ; D01G 23/06 ; D01H 13/22
PCT International Application Number N/A
PCT International Filing date
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 19500189.3 1995-01-05 Germany