EP3514272B1 - Dispositif d'entraînement pour cylindres arracheurs d'une machine de peignage - Google Patents

Dispositif d'entraînement pour cylindres arracheurs d'une machine de peignage Download PDF

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Publication number
EP3514272B1
EP3514272B1 EP19150700.3A EP19150700A EP3514272B1 EP 3514272 B1 EP3514272 B1 EP 3514272B1 EP 19150700 A EP19150700 A EP 19150700A EP 3514272 B1 EP3514272 B1 EP 3514272B1
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EP
European Patent Office
Prior art keywords
detaching
drive
gear
detaching roller
shaft
Prior art date
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EP19150700.3A
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German (de)
English (en)
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EP3514272A1 (fr
Inventor
Heribert Weber
Daniel Bommer
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Maschinenfabrik Rieter AG
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Maschinenfabrik Rieter AG
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Publication of EP3514272A1 publication Critical patent/EP3514272A1/fr
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    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01G—PRELIMINARY TREATMENT OF FIBRES, e.g. FOR SPINNING
    • D01G19/00—Combing machines
    • D01G19/06—Details
    • D01G19/26—Driving arrangements
    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01G—PRELIMINARY TREATMENT OF FIBRES, e.g. FOR SPINNING
    • D01G19/00—Combing machines
    • D01G19/06—Details
    • D01G19/14—Drawing-off and delivery apparatus
    • D01G19/18—Roller, or roller and apron, devices, e.g. operating to draw-off fibres continuously

Definitions

  • the present invention relates to a drive device for detaching rollers of a combing machine with a housing enclosing a gear, the gear having a first drive train with a first drive shaft, which transmits a continuous rotational movement to the detaching rollers via a differential gear, and the gear having a second drive train with a detaching roller -Auxiliary shaft, on which a detaching roller cam device is arranged for generating a back and forth movement, wherein the continuous rotary movement of the differential gear together with the back and forth movement of the detaching roller cam device transmits a deep stepping motion to the detaching rollers.
  • each nipper unit which has a lower nipper plate and an upper nipper rotatably mounted thereon, is presented with a sliver from a lap roll to a circular comb arranged below the nipper unit for combing out.
  • the nipper unit moves from a rear open position to a front closed position, during this reciprocating movement of the nipper unit the upper nipper opens and closes, with the lower nipper plate forming a clamping point with the upper nipper in the closed state of the nipper unit a hanging fiber tuft to a combing segment of the circular comb.
  • the nipper unit opens, in which the upper nipper lifts off the lower nipper plate and the combed-out tuft is fed via a rotatably mounted feed cylinder in the nipper unit to a downstream pair of detaching rollers for soldering the combed-out tuft.
  • the combed fiber slivers formed at the individual combing points are then transferred next to one another on a conveyor table to a downstream drafting system, in which they are drawn and then combined to form a common combing machine sliver.
  • the sliver produced during the drafting system is then placed in a can via a funnel wheel.
  • the soldering process on the detaching rollers depends on the position of the tong unit and the position of the detaching rollers.
  • the detaching roller moves, as shown in FIG GB191204425A known, first in the direction of the nipper unit and then in the opposite direction, in order to solder an already combed out fiber end that has been pinched by the detaching rollers to a fiber end combed out by the circular comb.
  • the distance that is not imbricated and soldered is called the soldering distance and can be defined by the movement of the detaching rollers.
  • the soldering of the fiber bundles to form the desired fiber band has in particular the requirement that the fiber bundles laid on top of one another like imbricated tiles have a uniform result.
  • this uniformity of the sliver is determined by capacitive measurement on the sliver, whereby the layering of the individual fiber bundles is measured.
  • a disadvantage for the yarn quality is the folding of the fiber tips by adjusting a control disk on a known combing machine. The consequence of this, however, is that although deep irregularities (CV value) are measured in the sliver, this result results in a yarn quality that is not recommended for further processing.
  • the object of the present invention is therefore to create a drive device for detaching salts of a combing machine which makes it possible to optimize the uniformity of the sliver with regard to the soldering process in such a way that the yarn quality is maintained for a wide range of fiber masses presented.
  • a drive device for detaching rollers of a combing machine with the features of independent claim 1. Proposed is a drive device for detaching rollers of a combing machine with a housing enclosing a gear, the gear having a first drive train with a first drive shaft, which has a ring gear one
  • differential gear transfers a continuous rotational movement to the detaching rollers and wherein the transmission includes a second drive train having an auxiliary detacher shaft on which is disposed a detacher cam mechanism for producing fore and aft movement, the continuous rotary motion of the ring gear being associated with the fore and aft movement of the detacher cams -Contraption transfers a mit stepping motion to the detaching rollers.
  • an adjustment device for adjusting a transmission ratio between the continuous rotary movement and the forward and backward movement.
  • the continuous rotary motion caused by the ring gear of the differential causes linear motion to be transmitted to the detaching rollers and the detaching roller cam mechanism transmits back and forth motion to the differential, the combination of linear motion in conjunction with the back and forth motion resulting in a reciprocating motion transferred to the detaching rollers.
  • the ring gear of the differential gear has a transmission ratio that defines the linear movement that is transmitted to the detaching rollers. Accordingly, the adjusting device according to the invention allows the linear movement of the ring gear of the differential gear to be changed by adjusting the transmission ratio, with the back and forth movement caused by the detaching roller cam device remaining unchanged.
  • soldering gap i.e. the area that does not overlap
  • the soldering distance can therefore advantageously be variably adjusted as a function of the fiber mass presented, with the yarn quality not being adversely affected, since the fiber tips do not have to be folded over at any time, as is the case with the prior art, in order to achieve optimal uniformity of the yarn to get bands.
  • the first drive shaft of the first drive train preferably has a first toothed belt wheel and the detaching roller auxiliary shaft of the second drive train or an auxiliary motor shaft drive-connected to the detaching roller auxiliary shaft has a second toothed belt wheel, with the two toothed belt wheels each being guided through the housing to the outside of the housing and are connected in connection with a toothed belt to a motor and the adjustment device is designed such that the setting of the transmission ratio takes place in that the first toothed belt wheel is designed as an interchangeable toothed belt wheel.
  • the detaching roller auxiliary shaft for moving back and forth is driven by a first drive motor and, independently, the first drive shaft for the ring gear of the differential gear is driven by a second drive motor, with the adjustment device being formed by the second drive motor.
  • the setting of the transmission ratio is particularly preferably stepless.
  • the second drive motor is a servo motor with a servo amplifier.
  • the setting of the transmission ratio between 2.25 and 3.8 is particularly preferred.
  • the gear ratio of the differential gear By adjusting the gear ratio of the differential gear, the linear movement of the ring gear can rotate faster or slower, so that in conjunction with the back and forth movement of the detaching roller cam device, an optimal soldering distance can be set.
  • the second drive motor is preferably synchronized with the first drive motor via a control unit.
  • the synchronization is advantageous so that the forward and backward movement caused by the detaching roller cam device and the linear movement caused by the differential gear are optimally matched to one another.
  • the differential gear is a planetary gear
  • the first drive train driving a sun gear via the ring gear in conjunction with planetary gears in order to transmit the continuous rotational movement of the ring gear to the detaching rollers and, independently of this, the forward and backward movement is formed by the detaching roller cam disk device
  • the detaching roller cam disk device has at least one detaching roller cam disk arranged non-rotatably on the detaching roller auxiliary shaft and interacting with at least one detaching roller cam roller, and the detaching roller cam roller interacting with a planetary carrier of the planetary gear via a detaching roller rocker arm.
  • a combing machine with a drive device for detaching rollers of a combing machine is also provided.
  • each combing point 2 consists of a tong unit 10 (called tongs for short), which executes a reciprocating movement of the tongs 10 via front rockers 12 and rear rockers 14 .
  • the front swingarms 12 (only one shown) are rotatably mounted on a circular comb shaft 16 and on a front tong axle 18 of the tongs 10 .
  • the rear rocker 14, which is rotatably mounted on a rear tongs axis 20 of the tongs 10, is non-rotatably connected to a driven tongs shaft 22.
  • a wad 26 is supplied to a feed cylinder 24 which is rotatably mounted within the tongs 10 .
  • the lap 26 is unwound from a lap roll, not shown, which rests on winding rollers, also not shown, for the unwinding process.
  • the nipper 10 in the in 1 shown position, the nipper 10 is open, i.e. an upper nipper 11 is pivoted relative to a lower nipper 13 via an upper nipper pin 25 and is thus lifted off the lower nipper 13 and the nipper 10 is in a front position in which the fiber tuft protruding from the nipper 10 28 is attached to a fiber end 30 of an already formed fiber web 32 and soldered to it.
  • the nonwoven fabric 32 is held by a pair of detaching rollers 34, which perform a rotary motion indicated by the arrows for the soldering and detaching process and thus move the nonwoven fabric 32 or its fiber end 30 in the transport direction T.
  • the pliers 10 are closed, with the fiber tuft 28 protruding from the pliers 10 being combed out by a combing segment 36 or by a combing set of a rotatably mounted circular comb 38 .
  • the combing segment 36 is located in an upper position during the combing process Position.
  • the combing segment 36 is usually provided with clothing teeth which engage in the tuft 28 during the combing process.
  • the circular comb 38 which is rotatably mounted in the machine frame via the circular comb shaft 16 , is located within a suction shaft 40 which is essentially closed all around and which opens into a channel 42 .
  • 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).
  • the separated material consists of short fibers, shell 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 material is transferred directly to the channel 42 by the vacuum applied via the vacuum source 44 and the resulting air flow.
  • the remaining part, in particular the combed-out fibers, remains in the combing segment 36 or settles between the clothing teeth and is drawn down into the in 1 promoted position shown.
  • the combing segment 36 comes within the range of action 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 over its circumference.
  • In 2 is a combination 51 of a first gear 52 for generating a mit-step movement for the detaching rollers 34 (see 1 ), a second gear 54 for non-uniform driving of the circular comb 38 (see 1 ), a third gear 56 for reciprocating the tongs 10 (see 1 ) and a fourth gear 58 for opening and closing the upper gripper 11 (see 1 ) intended.
  • the four gears 52, 54, 56, 58 are provided in a modular design, with the combination 51 of the four gear modules 52, 54, 56, 58 being enclosed by a housing 60.
  • the first transmission module 52 has a first drive train 62 with a first drive shaft 64 which transmits a continuous rotational movement to a ring gear 74 via a differential gear 66 .
  • the transmission module 52 also has a second drive train 68 with a detaching roller auxiliary shaft 70 on which a detaching roller cam disc device 72 for generating a forward and backward movement 87 is arranged.
  • the differential gear 66 is designed as a planetary gear, with the first drive train 62 driving a sun gear 78 via the ring gear 74 in conjunction with planet wheels 76 in order to transmit the continuous rotary motion of the ring gear 74 to the detaching rollers 34 .
  • the forward and backward movement 87 is formed by the detaching roller cam disc device 72, the detaching roller cam disc device 72 having two detaching roller cam discs 80 which are non-rotatably arranged on the detaching roller auxiliary shaft 70 and which interact with two detaching roller cam rollers 82 interact.
  • the two detaching roller cam rollers 82 are connected to a planetary carrier 86 of the differential gear 66 via a detaching roller rocker arm 84, so that the forward and backward movement 87 of the detaching roller cam discs 80 is superimposed via the planetary carrier 86 with the continuous rotational movement of the ring gear 74 in order to to transfer a mit stepping motion to the detaching rollers 34.
  • the first drive train 62 is drive-connected to a table calender 88 and to transport rollers 90, and in this way is part of the first transmission module 52. It is of course also possible to connect the table calender 88 and transport rollers 90 via a separate drive the powertrain.
  • the second transmission module 54 has a crested auxiliary shaft 92, which is connected to the crested shaft 16 via a non-circular gear stage 94 made up of two intermeshing non-circular gears 96a, 96b, the non-circular gear stage 94 converting a continuous rotational movement of the crested auxiliary shaft 92 into a non-uniform rotational movement for the comb shaft 16 converts.
  • the diameter of the circular comb shaft according to the prior art is 30 mm and 35 mm.
  • the multiples of the natural frequency and the speed of the combing machine are superimposed, so that an undesired resonance of the circular comb shafts is stimulated.
  • the third transmission module 56 is designed for the reciprocating movement of the tongs 10 with a tongs cam device 98, wherein in the embodiment according to 2 the tong cam assembly 98 includes two tong cams 102 (only one shown) non-rotatably mounted on an auxiliary tong shaft 100, which interact with two tong cams 104 (only one shown).
  • the two tong cam rollers 104 are connected to the driven tong shaft 22 via a tong rocker arm 106 (see Fig 1 ) connected so that the movement profile, in particular the reciprocating movement of the tong cams 102 on the tong 10 (see 1 ) is transmitted.
  • the fourth gear module 58 is for opening and closing the upper gripper 11 (see 1 ) formed with a top jaw cam device 108, wherein in the embodiment according to 2 the top tong cam mechanism 108 includes two top tong cams 110 (only one shown) non-rotatably mounted on the tong auxiliary shaft 100 and interacting with two top tong cam followers 112 (only one shown).
  • the two upper nipper cam rollers 112 are rotatably mounted on an upper nipper rocker arm 114 via a screw connection, with the upper nipper rocker arm 114 being connected to the upper nipper shaft 27 via a coupling rod 116 in conjunction with an upper nipper shaft clamp 118 .
  • the upper tong rocker arm 114 and the upper tong shaft clamp 118 are connected to the coupling rod 116 via screw connections 122, the coupling rod 116 being formed from three elements 116a, 116b, 116c and thus the auxiliary tong shaft 100 being connected via a four-joint 124 to the Upper gripper shaft 27 connects.
  • the combination 51 of transmission modules 52, 54, 56, 58 is controlled by a common motor 128.
  • a detaching roller drive gear wheel 130 is seated in a torque-proof manner on the detaching roller auxiliary shaft 70 of the second drive train 68, a round comb drive gear wheel 132 is seated in a torque-proof manner on the circular comb auxiliary shaft 92 and a gripper drive gear wheel is seated in a torque-proof manner on the auxiliary gripper shaft 100 134, all of the drive gears 130, 132, 134 being of the same size and meshing with each other.
  • the drive gears 130, 132, 134 By designing the drive gears 130, 132, 134 with the same dimensions, the same speed is transmitted to all transmission modules via the common motor 128.
  • An intermediate gear 136 which meshes with the detaching roller drive gear 130, is fixed in a rotationally fixed manner on an auxiliary motor shaft 138, and the auxiliary motor shaft 138 is guided to the outside through the housing 60, and an intermediate motor gear 140 sits there in a rotationally fixed manner -Intermediate gear 140 is drivingly connected to a motor gear 144 via a toothed belt 142, the motor gear 144 being non-rotatably fastened to a motor shaft 146 of the common motor 128.
  • a toothed belt drive can be used instead of the drive gears 130, 132, 134.
  • At least one sensor in the form of a speed sensor is fitted outside the housing 60 on a shaft (e.g. 70, 92, 100) with a constant combing machine speed.
  • a control unit 131 is connected to a first sensor 133a, a second sensor 133b and a frequency converter 129, with the frequency converter 129 controlling the common motor 128.
  • the first sensor 133a is a speed sensor and is mounted outside the housing 60 on the tong auxiliary shaft 100 to determine absolute machine position.
  • the second sensor 133b is preferably an induction sensor or speed sensor and is mounted outside of the housing 60 on the rear tong shaft 22.
  • the second sensor 133b is designed to measure the distance between the lower pliers 13 in the front end position 1 to determine the detaching rollers 34, this being the so-called ecartement in combers.
  • FIG 3 shows an embodiment of a first combination 51a with the first gear module 52 for the vocational step movement of the detaching rollers 34 and the second gear module 54 for the non-uniform movement of the circular comb shaft 16, the gear modules 52, 54 being surrounded by a first housing 60a are.
  • a first frequency converter 129a in connection with a first drive motor 128a is connected to the first combination 51a in the same way as in FIG 2 described drive-connected.
  • the third gear module 56 for the reciprocation of the driven tong shaft 22 and the fourth gear module 58 for the movement of the upper tong shaft 27 are combined in a second combination 51b and enclosed by a second housing 60b.
  • the tongs auxiliary shaft 100 is guided through the second housing 60b and drive-connected from the outside directly to a second drive motor 128b.
  • the tong cam assembly 98 and the upper tong cam assembly 108 are mounted on the auxiliary tong shaft 100 in the same manner as discussed in connection with FIG 2 described.
  • the first drive motor 128a and the second drive motor 128b are synchronized with one another via the control unit 131, with the drive motors 128a, 128b being asynchronous motors which are drive-connected to a corresponding frequency converter 129a, 129b.
  • the drive motors 128a, 128b are servo motors which are each connected to a servo amplifier 129a, 129b.
  • the circular comb auxiliary shaft 92 is guided to the outside through the housing 60a and a third sensor 133c in the form of a speed sensor is attached to the circular comb auxiliary shaft 92 outside of the housing 60a.
  • the third sensor 133c is drive-connected to the control unit 131 and has the task of transmitting the rotational position of the circular comb auxiliary shaft 92 to the control unit 131, so that the second frequency converter 129b, in conjunction with the second drive motors 128b, can determine the position of the tongs via the control unit 131 10 and the upper pliers 11 in relation to the rotational position of the detaching rollers 34 and the circular comb auxiliary shaft 92 can be optimally adjusted for the combing process and soldering process.
  • each individual transmission module 52, 54, 56, 58 is surrounded by its own housing 60c, 60d, 60e, 60f.
  • the first gear module 52 for generating the mit step movement for the detaching rollers 34 and the second gear module 54 for driving the circular comb shaft 16 in a non-uniform manner are designed in the same way as in FIG 2 described.
  • the tong auxiliary shaft 100 is provided only for the tong cam device 98, and for the upper tong cam device 108, an upper tong auxiliary shaft 148 is provided.
  • the third gear module 56 with the pincer cam device 98 includes two tong cams 102 (only one shown) non-rotatably mounted on the tong auxiliary shaft 100, which interact with two tong cam followers 104 (only one shown).
  • the two tong cam rollers 104 are connected to the driven tong axis 22 via the tong rocker arm 106, so that the movement profile, in particular the reciprocating movement of the tong cam discs 102 on the tong 10 (see Fig 1 ) is transmitted.
  • the fourth gear module 58 with the upper gripper cam disk device 108 has two upper tong cams 110 (only one shown) non-rotatably mounted on the upper tong auxiliary shaft 148, which interact with two upper tong cam followers 112 (only one shown).
  • the two upper nipper cam rollers 112 are connected directly to the upper nipper shaft 27 via the upper nipper rocker arm 114, so that the movement profile, in particular the back and forth movement of the upper nipper cam discs 110 on the upper nipper 11 (see 1 ) is transmitted.
  • the detaching roller auxiliary shaft 70 of the second drive train 68 is through the housing 60c
  • the circular comb auxiliary shaft 92 is through the housing 60d
  • the nipper auxiliary shaft 100 through the housing 60e
  • the top nipper auxiliary shaft 148 through the housing 60f to the outside of the housing 60c, 60d, 60e, 60f out, where the respective auxiliary shaft 70, 92, 100, 148 in the form of a drive shaft from a corresponding drive motor 128c, 128d, 128e, 128f arranged outside the housings 60c, 60d, 60e, 60f.
  • the drive motors 128c, 128d, 128e, 128f are asynchronous motors or alternatively servomotors, which are each controlled via a frequency converter or alternatively servo amplifiers 129c, 129d, 129e, 129f, with the drive motors 128c, 128d, 128e, 128f being synchronized with one another via the control unit 131 .
  • the drive motors 128c, 128d, 128f in conjunction with the respective cam disc devices 72, 98, 108, can continuously adjust the desired transmission ratio on the detaching rollers 34, the driven tong shaft 22 and the upper tong shaft 27.
  • FIG 5 is enlarged the tongs 10 and downstream the pair of detaching rollers 34 according to 1 shown, with the combed-out fiber package 28 being fed in a known manner via the feed cylinder 24 to the pair of detaching rollers 34 in order to complete the soldering process with the end 30 of the fiber web 32 already formed by the back and forth movement 87 as in FIG 2 to perform as described.
  • the pair of detaching rollers 34 carries out the so-called crawl movement for the detaching process and the soldering process in the combing machine, i.e.
  • the already formed fiber fleece 32 is transported back by one step in the direction of the tongs 10 in order to take the end 30 protruding from the front side of the pair of detaching rollers 34 with it to connect the combed-out fiber end 28 and then the non-woven fabric 32 is again moved forward by two steps in the conveying direction T.
  • this leads to a roof tile-like structure of the fiber fleece 32 as in 6 very simplified and shown schematically.
  • Each bundle of fibers 28 supplied by the tongs 10 is attached to the free end 30 of the non-woven fabric 32 and connected to one another via the reciprocating movement of the detaching rollers 34, this process being generally referred to as a soldering process.
  • the detaching roller cam device 72 as in connection with 2 described in detail, the detaching roller movement 87 can be adjusted in such a way so that the uncovered area 152, which is referred to as the so-called solder gap, can be precisely defined.
  • the variable setting of the soldering distance has the advantage that an optimal uniformity of the non-woven fabric 32 can be achieved. The important thing here is that no fiber tips have to be folded over in order to achieve an expedient uniformity of the fiber fleece 32 .
  • detaching roller cam device 72 As already in connection with 2 discussed shown.
  • Two detaching roller cam disks 80a, 80b are seated in a rotationally fixed manner on the detaching roller auxiliary shaft 70.
  • the detachment roller rocker arm 84 shown purely schematically, has two detachment roller cam rollers 82a, 82b, which are spaced apart from one another at an angle ⁇ , the first detachment roller cam disk 80a being connected to the first detachment roller cam roller 82a and the second detachment roller cam disk 80b to the second detaching roller cam roller 80b acts together.
  • the second detach cam follower 82b prevents the first detach cam follower 82a from lifting off the first detach cam follower 80a.
  • the detaching roller cam rollers 82a, 82b have a diameter of 90 mm and the detaching roller cam discs 80a, 80b each have a disc width of 15 mm to 30 mm, preferably 20 mm.
  • the detaching roller cam discs 80 can be supported either by roller bearings or plain bearings. When using rolling bearings, their diameters are in the range of 90 mm to 120 mm. When plain bearings are used, their diameters are preferably in the range from 60 mm to 90 mm. Particularly when space is limited, slide bearings are preferably used.
  • the detaching roller cam discs 80a, 80b each have a specific outer circumference on which the respective detaching roller cam roller 82a, 82b rests.
  • the mechanical connection of the respective cam roller 82a, 82b to the detaching roller auxiliary shaft 70 results in a detaching roller movement profile 87 of the detaching roller cam disk 80 transferred to the detaching rollers 34, as in connection with 2 executed in detail.
  • In 8 is on the abscissa axis (horizontal X-axis) a single rotation, i.e. from 0° to 360°, of the detaching roller cam 80 and on the ordinate axis (vertical Y-axis) is a cam disc deflection angle of 0° to 35° for the detaching rollers - Cam 80 shown.
  • the solid line is the fore and aft motion profile 87 as related to FIG 2 and figure 5 explained. From 0° to about 60° there is a negative course of movement, between about 60° and 110° there is no change in the course of movement, from about 110° to about 290° there is a positive course of movement and from 290° to 360° it is again a negative course of movement is provided.
  • This detaching roller movement pattern corresponds to the back and forth movement 87 for the detaching rollers, which is caused by the detaching roller cam device 72 .
  • FIG 9 illustrates purely schematically a first linear movement 154 caused by the ring gear 74 of the differential gear 66 according to FIG 2 and 10 shows a first resulting U stepping movement 156 at the detaching rollers 34 caused by the forward and backward movement 87 according to FIG 8 in connection with the first linear movement 154 according to 9 .
  • FIG 11 shows a first transmission module 51a according to the invention in comparison to FIG 3 for the inside 10 shown resulting harvest movement 156 of the detaching rollers 34, wherein the first drive train 62 for the inventive variable soldering distance 152 in comparison to the versions according to 2 , 3 and 4 is adjusted.
  • an adjusting device 158 is provided for adjusting a transmission ratio between the continuous rotational movement, in the sense of the linear movement 154 of the ring gear 74 of the differential gear 66, and the forward and backward movement 87 caused by the detaching roller cam disc device 72.
  • the first drive shaft 64 is connected via a connecting wheel 160 and a double toothed wheel 162a, 162b arranged on an axis of rotation 161 to an adjustment shaft 164, the adjustment shaft 164 being guided through the housing 60a to the outside of the housing 60a and there fixed against rotation with a first toothed belt wheel 166 is attached.
  • the adjusting shaft 164 has an external toothing 168, so that a first part 162a of the double gear wheel interacts with the external toothing 168 and a second part 162b of the double gear wheel interacts with the connecting wheel 160.
  • the detaching roller drive gear 130 is seated in a rotationally fixed manner on the detaching roller auxiliary shaft 70 of the second drive train 68, with an intermediate gear 136, which meshes with the detaching roller drive gear 130, being fixed in a rotationally fixed manner on the motor auxiliary shaft 138 and the motor auxiliary shaft 138 being through the housing 60a to the outside, where the intermediate motor gear 140 sits in a rotationally fixed manner.
  • the intermediate motor gear 140 and the first toothed belt wheel 166 are drive-connected to the motor gear 144 via the toothed belt 142, with the motor gear 144 being non-rotatably mounted on the motor shaft 146 of the motor 128a.
  • the motor 128a is preferably connected to a control unit (not shown) via a frequency converter 129a.
  • the setting device 158 is designed in such a way that a transmission ratio is set by the first toothed belt wheel 166 is an interchangeable toothed belt wheel (shown in phantom).
  • a setting of the transmission ratio between 2.25 and 3.8 is preferably provided with the interchangeable toothed belt wheels.
  • the changed gear ratio causes a change in the continuous linear movement 154 of the ring gear 74, as in FIG 9 explained.
  • a frequency converter 129g in connection with an asynchronous motor 128g is connected to the setting shaft 164 outside of the housing 60a.
  • the stepless setting of the transmission ratio between 2.25 and 3.8 is preferably possible with the frequency converter 129g in connection with the asynchronous motor 128g and the control unit 131.
  • the third sensor 133c in the form of the speed sensor is fastened outside of the housing 60a on the circular comb auxiliary shaft 92 and is connected to the control unit 131 . In this way, the speed of the circular comb and the variable setting of the soldering distance can be optimally coordinated using the detaching rollers. All other elements are designed identically as in connection with 11 described.

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  • Textile Engineering (AREA)
  • Preliminary Treatment Of Fibers (AREA)

Claims (10)

  1. Dispositif d'entraînement pour des rouleaux d'arrachage (34) d'une peigneuse (4), comportant un boîtier (60a) entourant une transmission (51a), dans lequel la transmission (51a) présente une première chaîne cinématique (62) comportant un premier arbre d'entraînement (64) qui transmet un mouvement rotatif continu, par le biais d'une roue à denture intérieure (74) d'un engrenage différentiel (66), sur les rouleaux d'arrachage (34) et dans lequel la transmission (51a) présente une seconde chaîne cinématique (68) comportant un arbre auxiliaire (70) de rouleaux d'arrachage, sur lequel un dispositif de cames de rouleaux d'arrachage (72) pour la production d'un mouvement de va-et-vient est agencé, le mouvement de rotation continu de la roue à denture intérieure (74), conjointement avec le mouvement de va-et-vient du dispositif de cames de rouleaux d'arrachage (72) transmettant un mouvement à pas de pèlerin sur les rouleaux d'arrachage (34), caractérisé en ce qu'un dispositif de réglage (158) est prévu pour le réglage d'un rapport de transmission entre le mouvement de rotation continu et le mouvement de va-et-vient.
  2. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que le premier arbre d'entraînement (64) de la première chaîne cinématique (62) présente une première roue de courroie dentée (166) et l'arbre auxiliaire (70) de rouleaux d'arrachage de la seconde chaîne cinématique (68), ou un arbre auxiliaire (138) de moteur relié en entraînement à l'arbre auxiliaire (70) de rouleaux d'arrachage présente une seconde roue de courroie dentée (140), les deux roues de courroie dentée (166, 140) étant respectivement guidées à travers le boîtier (60a) pour traverser jusqu'à l'extérieur du boîtier (60a) et étant reliées à un moteur (128a) conjointement avec une courroie dentée (142) et le dispositif de réglage (158) étant conçu de sorte que le réglage du rapport de transmission découle du fait que la première roue de courroie dentée (166) est formée comme une roue de courroie dentée alternée.
  3. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que l'arbre auxiliaire (70) de rouleaux d'arrachage est entraîné pour le mouvement de va-et-vient par le biais d'un premier moteur d'entraînement (128a) et, indépendamment de cela, le premier arbre d'entraînement (64) pour la roue à denture intérieure (74) de l'engrenage différentiel (66) est entraîné par le biais d'un second moteur d'entraînement (128g), le dispositif de réglage (158) étant formé par le second arbre d'entraînement (128g).
  4. Dispositif d'entraînement selon la revendication 3, caractérisé en ce que le réglage du rapport de transmission est continu.
  5. Dispositif d'entraînement selon la revendication 4, caractérisé en ce que le second moteur d'entraînement (128g) est un servomoteur comportant un servo-amplificateur (129g).
  6. Dispositif d'entraînement selon l'une des revendications 1 à 5, caractérisé en ce que le réglage du rapport de transmission est prévu entre 2,25 et 3,8.
  7. Dispositif d'entraînement selon l'une des revendications 4 à 6, caractérisé en ce que le second moteur d'entraînement (128g) est synchronisé avec le premier moteur d'entraînement (128a) par le biais d'une unité de commande (131).
  8. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que l'engrenage différentiel (66) est un engrenage planétaire, la première chaîne cinématique (62) entraînant, par le biais de la roue à denture intérieure (74) en conjonction avec des roues planétaires (76), une roue solaire (78), afin de transmettre le mouvement de rotation continu de la roue à denture intérieure (74) sur les rouleaux d'arrachage (34) et, indépendamment de cela, le mouvement de va-et-vient étant formé par le dispositif de cames de rouleaux d'arrachage (72), le dispositif de cames de rouleaux d'arrachage (72) présentant au moins une came de rouleaux d'arrachage (80) agencée sur l'arbre auxiliaire (70) de rouleaux d'arrachage solidaire en rotation en interaction avec au moins un galet de came de rouleaux d'arrachage (82) et le galet de came de rouleaux d'arrachage (82) coopérant, par le biais d'un culbuteur de rouleaux d'arrachage (84), avec le porte-satellites (86) de l'engrenage planétaire (66).
  9. Dispositif d'entraînement selon la revendication 2 et 8, caractérisé en ce que, en complément du réglage du rapport de transmission entre le dispositif de cames de rouleaux d'arrachage (72) et la roue à denture intérieure (74) de l'engrenage différentiel (66), une rotation manuelle ou automatique de la came de rouleaux d'engrenage (80) par rapport à l'arbre auxiliaire de rouleaux d'engrenage (70) est prévue.
  10. Peigneuse comportant au moins un dispositif d'entraînement selon l'une des revendications 1 à 9.
EP19150700.3A 2018-01-23 2019-01-08 Dispositif d'entraînement pour cylindres arracheurs d'une machine de peignage Active EP3514272B1 (fr)

Applications Claiming Priority (1)

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CH00070/18A CH714582A1 (de) 2018-01-23 2018-01-23 Antriebsvorrichtung für Abreisswalzen einer Kämmmaschine.

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EP3514272B1 true EP3514272B1 (fr) 2023-06-07

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Publication number Priority date Publication date Assignee Title
DE102020117233A1 (de) * 2020-06-30 2021-12-30 Trützschler GmbH & Co Kommanditgesellschaft Getriebeeinheit für eine Kämmmaschine und Kämmmaschine mit Getriebeeinheit

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191204425A (en) * 1912-02-22 1913-01-09 Robert Howard Lunn Improvements in Combing Machines.
US3479699A (en) * 1966-10-10 1969-11-25 Maremont Corp Combers
DE1685575C3 (de) * 1967-09-30 1973-11-22 Maschinenfabrik Rieter Ag., Winterthur (Schweiz) Antriebsvorrichtung für Abreiß walzen an einer Flachkammaschine
US3604063A (en) * 1969-05-02 1971-09-14 Maremont Corp Textile comber detaching roll drive
JP2642201B2 (ja) * 1989-09-08 1997-08-20 株式会社原織機製作所 コーマに於けるデタッチングローラの駆動装置
DE19527950B4 (de) * 1995-08-01 2005-11-10 Maschinenfabrik Rieter Ag Kämmaschine mit wenigstens einem Kämmkopf
DE69514806T2 (de) * 1995-11-02 2000-08-03 Vouk S P A Officine Meccanotes Vorrichtung für einen Hin- und Herdrehantrieb von Abreisszylindern einer Kämmaschine
JP5609530B2 (ja) * 2010-10-22 2014-10-22 株式会社豊田自動織機 コーマのデタッチングローラ動作設定装置
CN102115928A (zh) * 2011-04-11 2011-07-06 东华大学 数字化独立驱动精梳机分离罗拉运动装置
CH711419A2 (de) * 2015-08-05 2017-02-15 Rieter Ag Maschf Antriebsvorrichtung für eine Kämmmaschine.

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CH714582A1 (de) 2019-07-31
CN110067046B (zh) 2023-05-23
CN110067046A (zh) 2019-07-30

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