GEARBOX WITH AN ADJUSTING DEVICE FOR A COMBING MACHINE

Description

[0001] The present invention relates to a gear for a pilgrim step movement of detaching rollers of a combing machine, comprising a housing, a detaching roller cam disc and a detaching roller auxiliary shaft.

[0002] In a combing machine with multiple combing stations, each nipper unit, which has a lower nipper plate and a rotatably mounted upper nipper, receives a fiber sliver from a lap roll and is presented to a circular comb located below the nipper unit for combing. During a combing cycle, the nipper unit moves from an open rear position to a closed front position. During this back-and-forth movement of the nipper unit, the upper nipper opens and closes. When the nipper unit is closed, the lower nipper plate forms a clamping point with the upper nipper, thereby presenting a dangling fiber tuft to a combing segment of the circular comb.After combing with the circular comb, the nipper unit opens, with the upper nipper lifting from the lower nipper plate. The combed-out fiber tuft is fed via a feed cylinder rotatably mounted in the nipper unit to a downstream pair of detaching rollers for soldering the combed-out fiber slivers. The combed-out fiber slivers formed at the individual combing stations are then transferred side by side on a conveyor table to a downstream drafting system, where they are drafted and subsequently combined into a single comber sliver. The fiber sliver produced in the drafting system is then deposited into a can via a hopper wheel.

[0003] The soldering process at the stripping rollers depends on the position of the gripper unit and the position of the stripping rollers. During the soldering process, the stripping roller, as described in GB 04425 A, moves first toward the gripper unit and then in the opposite direction to solder a fiber end that has already been combed out and clamped by the stripping rollers to a fiber end combed out by the circular comb. The distance that is not laid down and soldered in a roof-tile-like manner is called the soldering distance and can be defined by the movement of the stripping rollers.

[0004] The soldering of fiber packages to form the desired fiber sliver requires, in particular, that the fiber packages, laid on top of one another like roof tiles, achieve a uniform result. In practice, this uniformity of the fiber sliver is determined by capacitive measurement on the sliver, which measures the layering of the individual fiber packages. A disadvantage for the yarn quality is the shifting of the fiber tips by adjusting a control disc on a conventional combing machine. However, this has the consequence that, although deep irregularities (CV value) in the sliver are measured, the resulting yarn quality is not recommended for further processing.

[0005] Another requirement for the nonwoven fabric is the mass distribution within the nonwoven fabric and its cutability. When soldering the fiber packages, care should be taken to ensure that there are minimal mass fluctuations in the nonwoven fabric, as this would significantly affect the uniformity.

[0006] The object of the present invention is therefore to provide a gear for a pilgrim step movement of detaching rollers of a combing machine, which makes it possible to optimize the uniformity of the fiber sliver with regard to the soldering process in such a way that the yarn quality is maintained for a wide selection of fiber masses presented.

[0007] The problem is solved by a drive device for detaching rollers of a combing machine having the features of independent patent claim 1.

[0008] A gear mechanism for a pilgrim step movement of detaching rollers of a combing machine is proposed, comprising a housing, a detaching roller cam disc and a detaching roller auxiliary shaft.

[0009] According to the invention, an adjustment device is provided for adjusting the detachment roller cam disk relative to the detachment roller auxiliary shaft. The adjustment device comprises a sleeve that is non-rotatably mounted on the detachment roller auxiliary shaft and detachably connected to the detachment roller auxiliary shaft. The sleeve is connected to the detachment roller cam disk via a drag coupling. This adjustment device enables a very simple and cost-effective technical solution for phase-shifting the detachment roller movement. In this way, the soldering process and the mass distribution in the fiber fleece can be optimally adjusted to different fiber lengths.

[0010] Preferably, the adjustment device is located outside the housing. This allows for easy access to the tear-off roller auxiliary shaft from the outside.

[0011] Further preferably, for the drag drive, an end of the sleeve facing the tear-off roller cam disc is designed as an annular shoulder, in which a number of receptacles are introduced radially outwardly, which interact with pins inserted in the tear-off roller cam disc.

[0012] Furthermore, it is preferred that the sleeve is connected to the tear-off roller cam disc via screw connections.

[0013] Preferably, the tear-off roller cam disc is coupled to the tear-off roller auxiliary shaft via a spring element, wherein a clamping effect is created when the sleeve is fastened to the tear-off roller auxiliary shaft in that a mandrel protruding from the sleeve displaces the spring element inserted in the tear-off roller cam disc into a transverse position such that the cam disc presses against the tear-off roller auxiliary shaft via the spring element.

[0014] Further preferably, the sleeve is connected to the tear-off roller auxiliary shaft via screw connections.

[0015] Particularly preferably, an end of the sleeve facing away from the tear-off roller cam disc has blind hole-like holes for mounting the sleeve on the tear-off roller auxiliary shaft via screw connections.

[0016] Furthermore, it is preferred that an annular receptacle is formed on the end of the sleeve facing away from the tear-off roller cam disc, on which an adjusting disc is detachably arranged to conceal the screw connections in the assembled state and the adjusting disc has a pointer on the circumference for indicating a position of the tear-off roller cam disc relative to the tear-off roller auxiliary shaft by means of a scale attached to the housing.

[0017] Particularly preferably, a sensor is provided on the housing to monitor the presence of the adjustment disc on the tube. Since the sensor is connected to a control unit of the combing machine, the control unit can indicate to the user via a display on the combing machine whether the adjustment has been made and whether the adjustment disc is attached to the tube.

[0018] Most preferably, the rotation of the tear-off roller cam disc via the sleeve is provided in steps of 9° or 18° relative to the tear-off roller auxiliary shaft.

[0019] The invention further relates to a combing machine with a gear.

[0020] Further advantages of the invention can be seen from an embodiment described and shown below.

[0021] They show: Fig. 1 shows a cross-section through a combing machine; Fig. 2 shows a combination of three gear modules with a common drive motor; Fig. 3 shows a schematic representation of a tear-off roller cam device; Fig. 4 shows a graphic representation of a tear-off roller movement; Fig. 5 shows a schematic representation of a tong cam device; Fig. 6 shows a graphic representation of a tong movement; Fig. 7 shows a graphic representation of the tear-off roller movement according to Fig. 4 and the pincer movement according to Fig. 6 and phase-shifted tear-off roller movements; Fig. 8 a schematic illustration of the ends of a fiber web on the tear-off rollers depending on the phase-shifted tear-off roller movement; Fig. 9 a separating device according to the invention for phase-shifting the tear-off roller movement; Fig. 10 an adjustment device for manually rotating a tear-off roller cam disk relative to a tear-off roller auxiliary shaft by means of a sleeve; Fig. 11 an enlarged view of the adjustment device according to Fig. 10 ; Fig. 12 an enlarged view of an alternative embodiment of an adjustment device.

[0022] Fig. 1 shows a schematic cross-section of a combing station 2 of a combing machine 4. In practice, eight such combing stations 2 are arranged next to one another. Each combing station 2 consists of a nipper unit 10 (referred to as nipper for short), which executes a back and forth movement of the nipper 10 via front rockers 12 and rear rockers 14. The front rockers 12 (only one shown) are rotatably mounted on a circular comb shaft 16 and on a front nipper axis 18 of the nipper 10. The rear rocker 14, which is rotatably mounted on a rear nipper axis 20 of the nipper 10, is connected in a rotationally fixed manner to a driven nipper shaft 22. A batt 26 is fed to a feed cylinder 24, which is rotatably mounted within the nipper 10. The cotton 26 is unwound from a cotton reel (not shown), which rests on winding rollers (also not shown) for the unwinding process.

[0023] In the Fig. 1 In the position shown, the tongs 10 are open, i.e. an upper tong 11 is pivotally mounted relative to a lower tong 13 via an upper tong shaft 27 and is thus lifted from the lower tong 13 and the tongs 10 are in a front position in which the fiber tuft 28 protruding from the tongs 10 is placed on a fiber end 30 of an already formed fiber web 32 and soldered to it. The fiber web 32 is held by a pair of tear-off rollers 34 which execute a rotary movement marked by the arrows for the soldering and tearing process and thus move the fiber web 32 or its fiber end 30 in the transport direction T.

[0024] In a rear end position (not shown) of the pliers 10, the pliers are closed, and the fiber tuft 28 protruding from the pliers 10 is combed out by a combing segment 36 or by a combing set of a rotatably mounted circular comb 38. The combing segment 36 is in an upper position during the combing process. The combing segment 36 is typically provided with set teeth that engage the fiber tuft 28 during the combing process.

[0025] The circular comb 38, which is rotatably mounted in the machine frame via the circular comb shaft 16, is located within a substantially completely enclosed suction shaft 40, which opens into a channel 42. As shown schematically, the channel 42 is connected to a vacuum source 44, by means of which the separated material is fed to a collection point (not shown).

[0026] The separated material consists of short fibers, husk parts, and other impurities, which are combed out of the fiber tuft 28 by the combing segment 36 during the combing process. A portion of the combed-out material is transferred directly to the channel 42 by the applied negative pressure via the negative pressure source 44 and the resulting air flow. The remaining portion, in particular the combed-out fibers, remains in the combing segment 36 or settles between the clothing teeth and is drawn downwards by the rotary movement of the circular comb 38 into the Fig. 1 shown position. In this case, the combing segment 36 enters the effective range of a brush 48, which is also rotatably mounted in the suction shaft 40 via a brush shaft 46 and is equipped with bristles 50 distributed around its circumference.

[0027] In Fig. 2 is a combination 51 of a first gear 52 for generating a pilgrim step movement for the tear-off rollers 34 (see Fig. 1 ), a second gear 54 for the non-uniform driving of the circular comb 38 (see Fig. 1 ) and a third gear 56 for the back and forth movement of the pliers 10 (see Fig. 1 ). The three gears 52, 54, 56 are provided in a modular design, with the combination 51 of the three gear modules 52, 54, 56 being enclosed by a housing 60.

[0028] The first transmission module 52 has a first drive train 62 with a first drive shaft 64, which transmits a continuous rotary motion to a ring gear 74 via a differential gear 66. The transmission module 52 also has a second drive train 68 with a tear-off roller auxiliary shaft 70, on which a tear-off roller cam device 72 is arranged to generate a forward and backward movement.

[0029] The differential gear 66 is designed as a planetary gear, with the first drive train 62 driving a sun gear 78 via a ring gear 74 in conjunction with planetary gears 76 to transmit the continuous rotational movement of the differential gear 66 to the tear-off rollers 34. Independently of this, the forward and backward movement is achieved by the tear-off roller cam device 72, which has two tear-off roller cam discs 80 arranged in a rotationally fixed manner on the tear-off roller auxiliary shaft 70, which interact with two tear-off roller cam rollers 82.The two tear-off roller cam rollers 82 are connected to a planetary carrier 86 of the differential gear 66 via a tear-off roller rocker arm 84, so that the forward and backward movement of the tear-off roller cam discs 80 is superimposed via the planetary carrier 86 with the continuous rotational movement of the ring gear 74 in order to transmit a pilgrim step movement to the tear-off rollers 34.

[0030] The second gear module 54 has a circular comb auxiliary shaft 92 which is connected to the circular comb shaft 16 via a non-circular gear stage 94 consisting of two intermeshing non-circular gears 96a, 96b, wherein the non-circular gear stage 94 converts a continuous rotary movement of the circular comb auxiliary shaft 92 into a non-uniform rotary movement for the circular comb shaft 16.

[0031] It should be noted here that the diameter of the circular comb shaft according to the state of the art is between 30 mm and 35 mm. Increasing the combing machine speed causes the multiples of the natural frequency to overlap with the combing machine speed, thus inducing undesirable resonance of the circular comb shafts. To prevent this, it is proposed to minimize the natural frequency by stiffening the circular comb shafts. Therefore, ideally, a circular comb shaft diameter of 35 mm to 45 mm, preferably 40 mm, is recommended.

[0032] The third gear module 56 is designed for the reciprocating movement of the pliers 10 with a pliers cam device 98, wherein in the embodiment according to Fig. 2 The tong cam device 98 has two tong cams 102 (only one shown) arranged on a tong auxiliary shaft 100 in a rotationally fixed manner, which interact with two tong cam rollers 104 (only one shown). The two tong cam rollers 104 are connected to the driven tong shaft 22 (see Fig. 1 ) so that the movement profile, in particular the back and forth movement of the pliers cam discs 102 on the pliers 10 (see Fig. 1 ) is transferred.

[0033] In the embodiment according to Fig. 2 The combination 51 of gear modules 52, 54, 56 is controlled by a common motor 128. A tear-off roller drive gear 130 is mounted on the tear-off roller auxiliary shaft 70 of the second drive train 68, a circular comb drive gear 132 is mounted on the circular comb auxiliary shaft 92, and a tongs drive gear 134 is mounted on the tongs auxiliary shaft 100. All drive gears 130, 132, 134 are the same size and mesh with one another. By designing the drive gears 130, 132, 134 with the same dimensions, the same speed is transmitted to all gear modules via the common motor 128. An intermediate gear 136, which engages with the tear-off roller drive gear 130, is non-rotatably mounted on an auxiliary motor shaft 138, and the auxiliary motor shaft 138 is guided outward through the housing 60, where a motor intermediate gear 140 is non-rotatably mounted.The motor intermediate gear 140 is drive-connected to a motor gear 144 via a toothed belt 142, wherein the motor gear 144 is non-rotatably mounted on a motor shaft 146 of the common motor 128.

[0034] Alternatively, a toothed belt drive can be used instead of the drive gears 130, 132, 134.

[0035] On a shaft (e.g. 70, 92, 100) with a constant combing machine speed, at least one sensor in the form of a speed sensor (incremental with reference or absolute) can be mounted outside the housing 60. According to Fig. 3 is purely schematically the tear-off roller cam disk device 72 as already described in connection with Fig. 2 discussed. Two tear-off roller cam discs 80a, 80b are mounted in a rotationally fixed manner on the tear-off roller auxiliary shaft 70. The tear-off roller rocker arm 84, shown purely schematically, has two tear-off roller cam rollers 82a, 82b spaced apart from each other at an angle α, with the first tear-off roller cam disc 80a interacting with the first tear-off roller cam roller 82a, and the second tear-off roller cam disc 80b interacting with the second tear-off roller cam roller 80b. The second tear-off roller cam roller 82b prevents the first tear-off roller cam roller 82a from lifting off the first tear-off roller cam disc 80a. The detachment roller cam rollers 82a, 82b have a diameter of 90 mm, and the detachment roller cam discs 80a, 80b each have a disc width of 15 mm to 30 mm, preferably 20 mm. The detachment roller cam discs 80 can be mounted either by roller bearings or plain bearings.When using rolling bearings, their diameters range from 90 mm to 120 mm. When using plain bearings, their diameters are preferably in the range from 60 mm to 90 mm. Plain bearings are preferred, especially when space is limited.

[0036] The tear-off roller cam discs 80a, 80b each have a specific outer circumference on which the respective tear-off roller cam roller 82a, 82b rests. Through the mechanical connection of the respective cam roller 82a, 82b with the tear-off roller auxiliary shaft 70, a forward and backward movement 87 of the tear-off roller cam disc 80 is transmitted to the tear-off rollers 34, as described in connection with Fig. 2 detailed and in Fig. 4 shown purely schematically.

[0037] In Fig. 4 On the abscissa axis (horizontal X-axis) a single revolution, i.e. from 0° to 360°, of the tear-off roller cam disc 80 is shown and on the ordinate axis (vertical Y-axis) a cam disc deflection angle of 0° to 35° for the tear-off roller cam disc 80 is shown. The solid line is the forward and backward movement profile 87 as in connection with Fig. 2 and Fig. 3 explained. From 0° to approximately 60°, a negative movement pattern is provided; between approximately 60° and 110°, there is no change in the movement pattern; from approximately 110° to approximately 290°, a positive movement pattern is established; and from 290° to 360°, a negative movement pattern is provided again. This tear-off roller movement pattern corresponds to the forward and backward movement 87 for the tear-off rollers, which is controlled by the tear-off roller cam disk device 72 according to Fig. 3 is caused.

[0038] According to Fig. 5 The gripper cam device 98 is shown purely schematically. Two gripper cams 102a, 102b are mounted on the gripper auxiliary shaft 100 in a rotationally fixed manner.

[0039] The purely schematically illustrated tongs rocker arm 106 has two tongs cam rollers 104a, 104b spaced apart at an angle β, with the first tongs cam disc 102a interacting with the first tongs cam roller 104a and the second tongs cam disc 102b interacting with the second tongs cam roller 104b. The second tongs cam roller 104b prevents the first tongs cam roller 104a from lifting off the first tongs cam disc 102a. The tongs cam rollers 104a, 104b each have a disc width of 15 mm to 30 mm, preferably 20 mm. The cam plates 102 can be mounted either on roller bearings or plain bearings. When using roller bearings, their diameters are in the range of 90 mm to 120 mm. When using plain bearings, their diameters are preferably in the range of 60 mm to 90 mm.The use of plain bearings is preferred, particularly when space is limited.

[0040] The gripper cam discs 102a, 102b each have a specific outer circumference on which the gripper cam rollers 104a, 104b rest. Through the mechanical connection of the gripper cam rollers 104a, 104b with the gripper shaft 22, a gripper movement profile 134 of the gripper cam discs 102 is transmitted to the driven gripper shaft 22, as described in connection with Fig. 2 detailed and in Fig. 6 shown purely schematically.

[0041] In Fig. 6 On the abscissa axis (horizontal X-axis) a single revolution, i.e. from 0° to 360°, of the gripper cam disk 102 is shown and on the ordinate axis (vertical Y-axis) a cam disk deflection angle of 0° to 35° for the gripper cam disk 102 is shown. At about 150°, as in Fig. 1 As described, the pliers 10 are in the forward position, and the upper pliers 11 are seated on the lower pliers 13 and are closed. At 0° and 360°, the pliers 10 are in the rear position with a pliers deflection angle of approximately 31°.

[0042] In Fig. 7 are the forward and backward movement 87 according to Fig. 4 and the pincer movement 134 according to Fig. 6 By a phase shift of the forward and backward movement 87 starting from the state according to Fig. 4 , as in Fig. 7 with a double arrow, the optimal time can be determined when the tear-off rollers 34 move the fiber fleece 32 back towards the pliers 10 (pilgrim step) in order to start the soldering process with the combed-out fiber beard 28, as shown in Fig. 1 This has the advantage that there are fewer mass fluctuations and less cutting for the formed fiber fleece 32 between the individual fiber packages, and fewer folded fiber tips occur during the soldering process.

[0043] In Fig. 8 the pliers 10 are enlarged and the tear-off roller pair 34 is connected downstream according to Fig. 1 shown, wherein in a known manner the combed out fibre beard 28 is fed via the feed cylinder 24 to the tear-off roller pair 34 in order to start the soldering process with the end 30 of the already formed fibre fleece 32 by the tear-off roller movement 87 as in Fig. 2 described and in Fig. 7 schematically shown. The tear-off roller pair 34 carries out the so-called pilgrim step movement for the tear-off process and the soldering process in the combing machine, ie, before a further tear-off process, the already formed fiber web 32 is conveyed back one step in the direction of the tongs 10 in order to connect the end 30 protruding from the front side of the tear-off roller pair 34 with the combed fiber end 28 and then the fiber web 32 is moved forward again two steps in the conveying direction T. With reference to Fig. 7 By shifting the phase of the tear-off roller movement 87, a shorter end (dashed line) of the fiber fleece or a longer end (dash-dotted line) of the fiber fleece can be presented to the combed-out fiber tuft 28 for the soldering process. Accordingly, the overlap area between the free end of the fiber fleece 30 at the front end of the tear-off rollers 34 and the combed-out fiber tuft 28 can be optimally adjusted to the respective fiber length presented, whereby, as already explained above, the fiber packages in the fiber fleece 32 exhibit fewer mass fluctuations.

[0044] A technical implementation for the phase shift of the forward and backward movement 87 is carried out either via a separating device as in Fig. 9 described or manual via a sleeve as in Fig. 10 described.

[0045] As from Fig. 9 recognizable, in contrast to Fig. 2 The tear-off roller auxiliary shaft 70 of the second drive train 68 extends outward through the housing 60 and has a first angle of rotation sensor 148a outside the housing 60 at a front end of the tear-off roller auxiliary shaft 70. The gripper auxiliary shaft 100 also extends outward through the housing 60 and has a second angle of rotation sensor 148b outside the housing 60 at a front end of the gripper auxiliary shaft 100. The common motor 128a is controlled via a first frequency converter 129a, and the frequency converter 129a and the two angle of rotation sensors 148a, 148b are connected to a control unit 131.

[0046] In Fig. 9 It can further be seen that the circular comb drive gear 134 has a step 133 in an end region facing the tear-off roller drive gear 130, so that only a partial region of the frontal outer surface of the tear-off roller drive gear 130 interacts with the circular comb drive gear 132, while the circular comb drive gear 132 interacts with the pliers drive gear 134 over the entire frontal outer surface.

[0047] In order to rotate the tear-off roller cam device 72 relative to the gripper cam device 98, a device is provided to separate the operative connection between the tear-off roller drive gear 130 and the gripper drive gear 132 by displacing the gripper drive gear 132 in the direction of a longitudinal axis of the circular comb auxiliary shaft 92. The displacement is in Fig. 9 marked with a double arrow. In the present embodiment, the displacement of the pliers drive gear 132 is achieved with the aid of a hydraulic cylinder 150. The hydraulic cylinder 150 is connected to a hydraulic pump 152 and a reservoir 156 via a directional control valve 154 with two flow paths. The control unit 131 controls the two flow paths of the directional control valve 154 for the reservoir 156 and the hydraulic pump 152 via a valve regulator 155. The hydraulic pump 152 is connected to a pump drive gear 158, with the pump drive gear 158 being operatively connected to a brush drive gear 160 and a motor drive gear 162 via a belt 164. A second frequency converter 129b is connected to a second motor 128b and thus drives the hydraulic pump 152 and the brush 48.The second frequency converter 129b and the valve controller 155 are connected to the control unit 131 together with the two rotation angle sensors 148a, 148b and the first frequency converter 129a.

[0048] The functioning of the present inventive separation of the operative connection between the tear-off roller cam device 72 and the gripper cam device 98 is such that the control unit 131 activates the hydraulic pump 152 and the valve regulator 155, so that the reservoir 156 moves the hydraulic cylinder 150 and this moves the first non-circular gear 96a together with the circular comb auxiliary shaft 92, on which the circular comb drive gear 132 is non-rotatably seated, in the direction of the longitudinal axis of the circular comb auxiliary shaft 92, so that the circular comb drive gear 132 is no longer in engagement with the tear-off roller drive gear 130, but continues to engage with the gripper drive gear 134. Thus, the tear-off roller cam device 72 is separated from the second Gear module 54 and third gear module 56 are decoupled and can be rotated.The rotation of the detachment roller cam disk device 72 is carried out via the first frequency converter 129a in conjunction with the common motor 128a, such that the detachment roller auxiliary shaft 70 is rotated in increments of 0.9° to 4.5°. The first rotation angle sensor 148a is used to detect the rotation angle state of the detachment roller auxiliary shaft 70 and compare it with the unchanged rotation angle state of the gripper auxiliary shaft 100. When the detachment roller auxiliary shaft 70 is rotated, the control unit 131 compares the values ​​of the first rotation angle sensor 148a with the unchanged values ​​of the second rotation angle sensor 148b and can thus determine the number of degrees by which the rotation has occurred with the common motor 128a.Only when the desired rotation is set with the common motor 128a does the control unit 131 again send a signal to the second frequency converter 129b and the valve controller 155 to activate the hydraulic cylinder 150, so that the circular comb drive gear 132 again engages with the tear-off roller drive gear 130. As a result, the tear-off roller movement 87 is now shifted in time relative to the gripper movement 134, as already explained in connection with . Fig. 7 und Fig. 8 explained.

[0049] As from Fig. 10 recognizable, in contrast to Fig. 2 , the tear-off roller auxiliary shaft 70 of the second drive train 68 is provided with an adjusting device 165. The adjusting device 165 has a sleeve 166, which is non-rotatably mounted on the tear-off roller auxiliary shaft 70 and releasably connected to the tear-off roller auxiliary shaft 70. The sleeve 166 is connected to the tear-off roller cam disk 80 via a drag drive. The adjusting device 165 is arranged outside the housing 60.

[0050] In Fig. 11 is an enlarged view of the adjusting device 165 according to Fig. 10 shown. The housing 60 is shown in simplified form only by the dot-dash line. For the dragging of the sleeve 166 with the tear-off roller cam disc 80, one end of the sleeve 166 facing the tear-off roller cam disc 80 is formed as an annular shoulder, in which a plurality of receptacles 168 are formed radially outwardly. The tear-off roller cam disc 80 has inserted pins 170 that interact with the receptacles 168.

[0051] The tear-off roller cam disc 80 is coupled to the tear-off roller auxiliary shaft 70 via a spring element package 174, wherein a clamping effect is created when the sleeve 166 is tensioned in the axial direction via the tear-off roller auxiliary shaft 70, in that a mandrel 176 protruding from the sleeve 166 displaces the spring element package 174 inserted in the tear-off roller cam disc 80 into a transverse position such that the tear-off roller cam disc 80 presses against the tear-off roller auxiliary shaft 70 via the spring element package 174. The sleeve 166 is connected to the tear-off roller auxiliary shaft 70 by screw connections 178, wherein an end of the sleeve 166 facing away from the tear-off roller cam disc 80 has blind hole-like holes 180 through which the screw connections 178 extend.

[0052] At the end of the sleeve 166 facing away from the tear-off roller cam disc 80, an annular receptacle 182 is formed, on which an adjusting disc 184 is detachably arranged. This conceals the screw connections 178, which are screwed into the blind-hole-like holes 180. The adjusting disc 184 has a pointer 186 on its circumference, which serves to indicate the position of the tear-off roller cam disc 80 relative to the tear-off roller auxiliary shaft 70 by means of a scale 188 attached to the housing 60.

[0053] To monitor the presence of the adjusting disc 184 on the sleeve 166, a sensor 190, preferably a reed contact sensor, is provided on the housing 60. This sensor is connected to a control unit (not shown) and thus indicates to the operator of the combing machine whether the adjusting disc 184 has been removed after adjustment.

[0054] In Fig. 12 An alternative embodiment of the adjustment device 165 is shown, wherein the sleeve 166 is connected to the tear-off roller cam disc 80 via screw connections 178. The dragging of the sleeve 166 with the tear-off roller cam disc 80 and the fastening of the sleeve 166 to the tear-off roller auxiliary shaft 70 are in the same way as already described in connection with Fig. 11 explained. The mounting of the adjusting disc 184 on the sleeve 166 and the pointer 186 on the circumference of the adjusting disc 184 for indicating the rotation of the detachment roller cam disc 80 relative to the detachment roller auxiliary shaft 70 via the scale 188 are also of the same design. Likewise, the sensor 190 is arranged on the housing 60 to detect the presence of the adjusting disc 184.

[0055] Alternatively, the tear-off roller cam disc 80 can be releasably attached to the tear-off roller auxiliary shaft 70 using a hydraulic clamping set. For this purpose, a HYD shrink disc from STÜWE could be used, for example. In this context, the HYD shrink disc has a pressure chamber into which hydraulic oil can be introduced via a hydraulic pump to enable the shrink disc to be tightened or loosened between the tear-off roller cam disc and the tear-off roller auxiliary shaft. Legende

[0056] 2Combing station 4Combing machine 10Tong unit (short tong) 11Upper tong 12Front rocker 13Lower tong 14Rear rocker 16Circular comb shaft 18Front tong shaft 20Rear tong shaft 22Driven tong shaft 24Feed cylinder 26Wadded wool 27Upper tong shaft 28Fiber tuft 30Fiber end 32Fiber fleece 34Pair of detaching rollers 36Combing segment 38Circular comb 40Suction shaft 42Channel 44Vacuum source 46Brush shaft 48Brush 50Bristles 51Combination of gear modules 52First gear module 54Second gear module 56Third gear module 58Fourth gear module 60Housing 62First drive train 64First drive shaft 66Differential gear (planetary gear) 68Second drive train 70Tear-off roller auxiliary shaft 72Tear-off roller cam device 74Ring gear 76Planet gear 78Sun gear 80Tear-off roller cam 82Tear-off roller cam roller 84Tear-off roller rocker arm 86Planet carrier 87Forward and backward movement 92Circular comb auxiliary shaft 94Circular comb differential gear 96Non-circular gear98Clamp cam assembly 100Clamp auxiliary shaft 102Clamp cam 104Clamp cam follower 106Clamp rocker arm 128Common motor, drive motor 129Frequency converter 130Tear-off roller drive gear 131Control unit 132Circular drive gear 133Step 134Clamp drive gear 136Intermediate gear 138Motor auxiliary shaft 140Motor intermediate gear 142Timing belt 144Motor gear 146Motor shaft 148Angle sensor 150Hydraulic cylinder 152Hydraulic pump 154Directional control valve 155Valve regulator 156Reservoir 158Pump drive gear 160Brush drive gear 162Motor drive gear 164Belt 165Adjusting device 166Sleeve 168Receptacle 170Pin 174Spring element package 176Mandrel 178Screw connections 180Blind holes 182Annular receptacle 184Adjusting disc 186Pointer 188Scale 190Sensor

Claims

1. Gear mechanism for a pilger motion of tear-off rollers (34) of a combing machine (4), the gear mechanism comprising a housing (60), a tear-off roller cam disk (80) and a tear-off roller auxiliary shaft (70) for transmitting a forward and backward movement to the tear-off rollers (34), characterized in that an adjusting device (165) is provided for adjusting the tear-off roller cam disk (80) relative to the tear-off roller auxiliary shaft (70), wherein the adjusting device (165) has a sleeve (166) which is rotationally fixedly mounted on the tear-off roller auxiliary shaft (70) and is detachably connected to the tear-off roller auxiliary shaft (70), wherein the sleeve (166) is connected to the tear-off roller cam disk (80) by means of an entrainment means.

2. Gear mechanism according to claim 1, characterized in that the adjusting device (165) is arranged outside the housing (60).

3. Gear mechanism according to either claim 1 or claim 2, characterized in that for the entrainment means, an end of the sleeve (166) facing the tear-off roller cam disk (80) is designed as an annular shoulder, in which a plurality of receptacles (168) are introduced radially on the outside and cooperate with pins (170) inserted in the tear-off roller cam disk (80).

4. Gear mechanism according to any of claims 1 to 3, characterized in that the sleeve (166) is connected to the tear-off roller cam disk (80) via screw connections (178).

5. Gear mechanism according to claim 1, characterized in that the tear-off roller cam disk (80) is coupled to the tear-off roller auxiliary shaft (70) via a spring element (174), a clamping effect being produced when the sleeve (166) is fastened to the tear-off roller auxiliary shaft (70), in that a mandrel (176) protruding from the sleeve (166) moves the spring element (174) inserted in the tear-off roller cam disk (80) into a transverse position such that the tear-off roller cam disk (80) presses against the tear-off roller auxiliary shaft (70) via the spring element (174).

6. Gear mechanism according to any of claims 1 to 5, characterized in that the sleeve (166) is connected to the tear-off roller auxiliary shaft (70) via screw connections (178).

7. Gear mechanism according to claim 6, characterized in that an end of the sleeve (166) facing away from the tear-off roller cam disk (80) has blind holes (180) for mounting the sleeve (166) on the tear-off roller auxiliary shaft (70) via screw connections (178).

8. Gear mechanism according to either claim 6 or claim 7, characterized in that at the end of the sleeve (166) facing away from the tear-off roller cam disk (80), an annular receptacle (182) is formed, on which an adjusting disk (184) is detachably arranged to cover the screw connections (178) in the assembled state, and the adjusting disk (184) has a pointer (186) on the circumference for indicating a position of the tear-off roller cam disk (80) relative to the tear-off roller auxiliary shaft (70) by means of a scale (188) attached to the housing (609).

9. Gear mechanism according to claim 8, characterized in that a sensor (190) is provided on the housing (60) for monitoring the presence of the adjusting disk (184) on the sleeve (166).

10. Gear mechanism according to any of claims 1 to 9, characterized in that the rotation of the tear-off roller cam disk (80) by means of the sleeve (166) is provided in increments of 9° or 18° relative to the tear-off roller auxiliary shaft (70).

11. Combing machine comprising a gear for a pilger motion of tear-off rollers of a combing machine according to any of claims 1 to 10.