EP0271115B1 - Procédé et appareil de compensation automatique des variations de poids des rubans sur les machines textiles telles que cardes, bancs d'étirage et similaires - Google Patents

Procédé et appareil de compensation automatique des variations de poids des rubans sur les machines textiles telles que cardes, bancs d'étirage et similaires Download PDF

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Publication number
EP0271115B1
EP0271115B1 EP87118414A EP87118414A EP0271115B1 EP 0271115 B1 EP0271115 B1 EP 0271115B1 EP 87118414 A EP87118414 A EP 87118414A EP 87118414 A EP87118414 A EP 87118414A EP 0271115 B1 EP0271115 B1 EP 0271115B1
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Prior art keywords
feed
nip
groove
signal
roll
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EP87118414A
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German (de)
English (en)
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EP0271115A2 (fr
EP0271115A3 (en
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Paul Stäheli
Robert Demuth
Peter Fritzsche
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Maschinenfabrik Rieter AG
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Maschinenfabrik Rieter AG
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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
    • D01G23/00—Feeding fibres to machines; Conveying fibres between machines
    • D01G23/06—Arrangements in which a machine or apparatus is regulated in response to changes in the volume or weight of fibres fed, e.g. piano motions

Definitions

  • the invention relates to a method and a device for automatically compensating strip density fluctuations in textile machines, such as cards, draw frames and the like, as defined in the preamble of the first method and the first device claim.
  • the homogenization of the fiber wadding - also called the fiber mat - at the entrance to a textile machine that processes the wadding is an essential prerequisite for the uniformity of the fiber sliver emitted by this machine. With increasing processing speed, this prerequisite becomes even more important, since fewer machines are used for the same amount of fiber wadding to be processed, so that the possibility of duplication from a larger number of machines and the resultant equalization of the product becomes smaller.
  • a feed means of a card consisting of a fixedly arranged feed plate and a drivable feed roller movably arranged above it. This feed roller is pressed at both ends by means of springs against the fiber wadding located between the feed roller and the trough plate.
  • a similar arrangement is known from DE-A-32 05 776.
  • the movements of the feed roller resulting from the unevenness in the fiber wool are emitted by sensors provided at both ends of the feed roller as signals to a control unit, which calculates the necessary speed change of the feed roller in order to compensate for these unevenness as far as possible.
  • the main disadvantage of this system is that the feed roller to be driven is also used to scan the unevenness in the fiber wadding, which inevitably leads to interference in the measurement signals, even if precautions are taken in the arrangement of the drive of the feed roller to the directions of the To obtain driving force of the feed roller drive perpendicular to the direction of movement of this roller during the scanning.
  • a disadvantage of this system is not the measuring principle, but the type of fiber transfer to a subsequent licker-in roller (also called a beater), in that the fiber transfer point on the trough plate (or pedals) moves due to the swiveling of the trough plate relative to the stationary licker-in roller, which means that the position of the transfer point of the fiber wadding from the trough plate (or pedals) to the licker-in roller also moves alternately in the direction of rotation of the licker-in roller and against it, which creates an unrest in the transfer of the fibers to the licker-in roller.
  • the disadvantage of this system is that the density of the fiber wadding is measured before it is drawn in between the trough plate and the feed cylinder, so that changes in the fiber wadding can occur until it is drawn in between the trough plate and the feed cylinder, which then no longer match the measured values would match.
  • a trough plate and a feed plate as well as a feed cylinder and a feed roller are each the same elements acts.
  • the aforementioned examples relate to essential, but not all, prerequisites for the uniformity of the sliver delivered by this machine.
  • the invention is therefore based on the object of finding a system which detects and corrects the inequalities in the sliver simply and yet sufficiently precisely without accepting the disadvantages mentioned.
  • the measuring point or the measuring plane, respectively. the measuring direction can be provided such that the determination of the change in thickness of the fiber mat can be carried out close to the narrowest nip between the feed plate and the feed roller, i.e. essentially close to the point at which the fiber mat is taken over by the licker-in roller. This creates a very small distance between the measuring point and the fiber transfer point, i.e. the time of the measurement is very close to the time of the necessary speed correction.
  • FIG. 1 shows a longitudinal view of a card with a sliver compensation according to the invention, shown schematically, 2 the fiber sliver compensation according to the invention from FIG. 1, shown enlarged, 3 shows a variant of the sliver compensation of FIG. 2, 4 parts of the sliver compensation of FIG. 1, shown enlarged, 5 is a plan view of part of FIG. 4, 6 to 29 each variant of the fiber feed means, in a representation with a longitudinal view and floor plan analogous to FIGS. 4 and 5, 30 shows a drafting system with the sliver compensation according to the invention, shown schematically, 31 the part of FIG. 4 with further details, shown schematically, 32 shows part of the device of FIG. 4, enlarged and shown in section along lines I of FIG. 33, FIG. 33 shows part of the device from FIG. 4, enlarged and shown in viewing direction II (FIG. 31).
  • a card 1 comprises from left to right, as seen in FIG. 1, at the card entry a fiber feed means 2, a licker-in roller 3, also called a beater, a reel 4 with a cover 5, a fiber pile removal roller 6, also called a doffer roller, one Fiber pile compression unit 7 for forming a card sliver 8.
  • the fiber feed means 2 comprises a rotatable and drivable feed roller 9, also called feed cylinder, a feed plate 10, also called trough plate, which cooperates with the feed roller and is pivotally mounted about a pivot axis 11.
  • the feed roller 9 is arranged stationary, and the pivotability of the feed plate 10 is limited by an adjusting screw 12, in the direction of movement away from the feed roller 9, and by a stop mentioned later in the opposite direction.
  • the feed roller 9 is driven by a gear motor 13.
  • a fiber mat 15 is fed to the fiber feed means 2 on a feed plate 14.
  • the fiber mat is fed in a manner known per se to the much faster rotating licker-in roller than the compressed fiber mat.
  • the nonwoven fabric processed between the drum 4 and the lid 5 is removed from the doffer roller 6 and passed on to the nonwoven compression unit 7, in which the nonwoven fabric is compressed into the card sliver 8.
  • a device 110 known from EP-A-0 078 393 determines the mass or density of the sliver and outputs a signal 111 corresponding to the density to a controller 17.
  • the ratio of the peripheral speed of the doffer roller 6 to the peripheral speed of the feed roller 9 gives the so-called draft ratio of the card.
  • the food plate 10 is pivoted away from the feed roller 9 until the food plate contacts the set screw 12. This position of the food plate 10 is referred to as the operating position.
  • two signals 16A, 16B from left to right on the pivot axis 11 of the feed plate 10 are attached strain gauges, which sense the transverse force of the bearing journal of the feed trough.
  • These signals 16A, 16B are applied to a measuring amplifier 16C, which first adds the signals and then amplifies them, so that the signal 16 is produced, which represents an amplified mean signal.
  • the measuring amplifier 16C converts the signals from the strain gauge transducers into a DC voltage which is between -10 and +10 V.
  • the signal 16 is input to a controller 17, together with a manipulated variable signal 18, a rotational speed signal 19 of the doffer roller 6 and a rotational speed signal 20 of the geared motor shaft 21, as well as the already mentioned signal 111, the manipulated variable signal 18 and the speed signal 19 of the doffer roller 6 have a predetermined value.
  • the value of the signal box signal 18 can be selected at a decade switch 18A and finally determines the desired band number.
  • the controller "processes" the aforementioned signals into an output signal 22, by means of which the speed of the geared motor 13 is corrected in accordance with the deviations in the density of the fiber mat 15 in a clamping gap area 23 and the deviations determined by the device 110, that the density of the sliver 8 when leaving the card 1 is substantially balanced.
  • the controller 17 essentially consists of a microcomputer 17a from Texas Instr. Type 990 / 100MA with the necessary number of EPROM's type TMS 2716, also from Texas Instr., For programming the control functions, as well as a control unit 17b type D 10 AKN RV419D-R from AREG (Federal Republic of Germany, Gemrigheim).
  • the control unit 17B amplifies a speed signal emitted by the microcomputer to the output signal 22 and receives the signal 20 for checking and regulating the feed roller speed.
  • the run-in signal 16 is first processed in a stage 17C.
  • the mean value of the incoming signal is recalculated from a fixed number of the last read values. In this way, the long-term deviation of the fiber template can be eliminated.
  • the averaging process that is carried out again and again has an effect as if there was a drift filter.
  • the instantaneous value of the incoming signal is compared with the most recently determined mean value in stage 17C in such a way that the quotient mean value / instantaneous value is formed in order to obtain a signal y which shows whether the fiber density in the nip is currently increasing or decreasing.
  • the signal y can be understood as a "trend signal".
  • the signal y is multiplied by a control signal x from the microcomputer 17A and the result of this multiplication, possibly taking into account a further constant, is supplied to the AREG controller 17B as a setpoint. This is shown schematically by means of the corresponding arrow between the blocks 17D and 17B.
  • the AREG controller represents independent control electronics connected upstream of the control motor 13.
  • the setpoint value determined by the stage 17D is compared in the control electronics with the tachometer actual value 20, the difference is amplified and fed to the motor via the power circuits.
  • the control electronics 17B works as a voltage metering and only supplies the motor with as much voltage 22 as is required to apply the required torque and maintain the speed.
  • the value of the control value signal 18, which is selected at the decade switch 18, represents the desired band number.
  • This setpoint signal 18 together with the actual value signal for the band number or band density is fed to the stage 17E, which subtracts the two signals to determine the deviation.
  • This deviation, that is, the deviation Proportional signal e is supplied to the microcomputer 17A, which in this example is formed by corresponding EPROMS and PI controllers.
  • the tachometer initiator 19A measures the speed of the pickup 6. This speed, which should be constant during operation and is regulated to a constant value during operation, is an important value for the microcomputer 17A, especially when the arrangement is started up, since the value is not constant here and a corresponding start-up control must be carried out .
  • stages 17C and 17B and 17E can be performed in the microcomputer as needed, if programmed accordingly.
  • the present description shows how the entire arrangement is regulated, starting from the absolute value of the strip measured on the step roller block.
  • the nip area 23 is defined by the interaction of the feed roller 9 and the feed plate 10 by the fiber mat 15 in this area of the original thickness D is compressed to a thickness (not shown), which has this immediately before leaving the area 23.
  • the clamping gap region 23 thus ends at the edge of the food plate 10, referred to as the fiber delivery edge 24, at which the fiber mat 15 is no longer clamped by the food plate 10.
  • the directions of rotation of the feed roller 9, the breeze 3, the reel 4 and the doffer roller 6 are each identified by the arrows U.
  • the fiber material moves through the card in accordance with these directions of rotation.
  • FIG. 2 shows the fiber feed means 2 from FIG. 1 in an enlarged representation and in somewhat more detail, for which reason the same elements are provided with the same reference symbols.
  • pivot axis 11 is accommodated in a stationary bearing housing 26 belonging to the machine housing 25 (only indicated with hatching).
  • a stop 27 which prevents the feed plate 10 from resting on the feed roller 9 when there is no fiber mat 15.
  • a carrier 28 receiving the set screw 12 and the gear motor 13 are fastened to the machine housing 25.
  • FIG. 3 shows a variant 2.1 of the fiber feed means from FIGS. 1 and 2, so that the same elements are provided with the same reference symbols.
  • This variant has a feed plate 29 arranged below the feed roller 9, as seen in FIG. 3, which is pivotably mounted by means of a pivot axis 31 accommodated in a bearing housing 30 fastened to the machine housing 25.
  • a set screw 32 limits the pivoting movements of the feed plate 29 in a direction away from the feed roller 9, while a stop 33 prevents the feed plate 29 from coming into contact with this roller in one direction of movement against the feed roller 9, the latter direction of movement of the feed plate 29 is caused by a compression spring 34.
  • the set screw 32 is received by means of a carrier 35 and the spring 34 by means of a carrier 36 each from the machine housing 25.
  • the stop 33 is the end face of a feed plate 37, which is also attached to the machine housing 25.
  • the clamping gap area 23.1 corresponds to the clamping gap area 23 of FIGS. 1 and 2.
  • measuring means are defined which are used to generate the signal 16 emitted by the feed means 2.
  • FIGS. 6, 10, 14, 18 and 22 show elements of the feed means of FIG. 3. Accordingly, the same elements are provided with the same reference numerals in the figures mentioned.
  • FIG. 5 shows the feed plate 10, the pivot axis 11 and the bearing housing 26 as well as a second bearing housing 26.1 which also receives the pivot axis 11.
  • the feed plate 10 has two bearing legs 38, by means of which the feed plate 10 is pivotably mounted on the pivot axis 11.
  • the pivot axis 11 each has a surface 39 (FIGS. 32 and 33) for receiving one strain gauge 90 each.
  • These strain gauges are arranged in such a way that they each generate a signal corresponding to the magnitude of a force F (FIGS. 4, 31 to 33) generated during operation on the feed plate 10, both signals 16A, 16B in a mean value generator 16C (not shown here) ) are converted into the previously mentioned signal 16.
  • the force F is determined by two force components together, on the one hand from a force component which is caused by the pressure forces generated by the fiber mat in the wedge gap between the feed plate and the feed roller and on the other hand from a force component which arises from the friction forces occurring in the wedge gap.
  • the total resulting force F R (is equal to compressive force + frictional force) can be broken down into two components, namely a horizontal component F H and a vertical component F V.
  • the vertical force component is relatively small, since the corresponding contributions of the pressure and friction forces point in opposite directions. This component thus changes only slightly when the density of the fiber template changes.
  • the horizontal force component on the other hand, the corresponding contributions of the pressure and friction forces add up, so that there is a pronounced dependency here between F M and the change in density of the fiber template in the clamping gap area.
  • This dependency is exploited according to the invention in that the strain gauges 90 are likewise placed essentially in a horizontal plane and thus most sensitively determine changes in density of the fiber template in the clamping gap area.
  • the optimal direction of the force F is roughly horizontal and can be determined by experiment. However, an approximation to this optimal direction is enough to make a sensitive measurement.
  • this type of measurement also represents a significant difference from the prior art, in which a relative movement between the feed plate and feed cylinder is used for the measurement.
  • the compressive forces increase with increasing density of the fiber template, but so do the frictional forces, which are due to the indispensable curvature of the food plate work against the pressure forces around the feed cylinder so that the measurement cannot be carried out sensitively.
  • the horizontal direction is only the preferred direction for the force measurement if the card is designed as in FIG. 1.
  • the direction of force had to be chosen accordingly.
  • FIGS. 32 and 33 it is enlarged and thus shown in more detail than with FIG. 5 that the surface 39 with the strain gauges 90 is the flat base surface of a bore 91 and that by means of a further bore 92, which is arranged in mirror image relative to the aforementioned bore 92 emerges as the weakest point.
  • This measurement practice is known in the art and is used, for example, by the Reglus firm in Adliswil, Switzerland.
  • FIG. 7 shows the feed plate 29, the pivot axis 31 and the bearing housing 30 as well as a second bearing housing 30.1 which also receives the pivot axis 31 as a floor plan of FIG. 6.
  • the feed plate 29 has two bearing legs 40 which receive the pivot axis 31.
  • the pivot axis 31 has in the spaces between the bearing legs 40 and the bearing housings 30 and 30, respectively. 30.1, each have a surface 39 for receiving a strain gauge (not shown).
  • strain gauges for this variant are also arranged in such a way that they each generate a signal corresponding to the magnitude of a force F.1 (FIG. 6) generated during operation on the feed plate 29, with both signals in a mean value generator (not shown) in the Signal 16 mentioned earlier can be converted.
  • the force F.1 builds up in an analogous manner to the force F described for FIGS. 4 and 5.
  • the optimal direction of the force F.1 is also determined by experiments, an approximation to this optimal direction also being sufficiently precise.
  • FIGS. 8 and 9, 12 and 13, 16 and 17, 20th and 21, as well as 24 and 25, with the exception of the measuring means for determining the signal 16, show the same elements as were shown with FIGS. 4 and 5, for which reason the same reference symbols are used for the same elements.
  • FIGS. 10 and 11, 14 and 15, 18 and 19 and 22 and 23 with respect to the elements shown in FIGS. 6 and 7.
  • the measuring means of FIGS. 8 and 9 is a load cell 41 assigned to the adjusting screw 12 such that it outputs a signal 16 corresponding to the size of a force F.2 (FIG. 8).
  • This force F.2 is a force resulting from the forces generated in operation by the fiber mat 15 (not shown in FIG. 8) in the clamping gap region 23, which acts in the direction of the longitudinal axis (not shown) of the adjusting screw 12.
  • the set screw 12 is arranged in the middle of the length L of the feed plate 10.
  • the horizontal distance H, as seen in FIG. 8, of the above-mentioned longitudinal axis up to the fiber delivery 24 is not particularly critical, nevertheless the smallest possible distance H should be aimed for.
  • a load cell 41.1 assigned to the set screw 32 (FIG. 10), to which a force F.3 acts analogously to the force F.2 of FIG. 8.
  • the set screw 32 is in the middle of the length L and with a horizontal distance H.1, as viewed in FIG. 10, from a fiber deflecting nose 44 on the feed plate 29 to that in the direction of the longitudinal axis (not shown) Set screw 32 acting force F.3.
  • Fig. 12 respectively. 13 and 14 resp. 15 each show a variant in the use of load cells to determine the density of the fiber mat in the wedge gap area 23 or. 23.1 (not shown in FIGS. 12 and 14) force generated during operation.
  • the dining plate 10 of FIGS. 12 and 13 in the end face 42 facing the beater 3 has a depth T and a height B (FIG. 12) having groove 43.
  • the height B is selected in such a way that load cells 41.2 can be pushed into the groove 43 without play in a position shown in FIGS. 12 and 13 and held in place (not shown).
  • the fiber mat 15 located in the wedge gap between the feed plate 10 and the feed roller 9 generates forces which tend to have a feed plate part 60 located between the groove 43 and the fiber-dispensing edge 24 around an inner groove edge 61 to pivot in a direction R. These forces result in a force F.4 acting over the entire length L, which generates a corresponding signal in the load cells 41.2.
  • the signals of the individual load cells are averaged to signal 16 in an averager (not shown).
  • FIGS. 14 and 15 functions with respect to the generation of the signal 16 essentially the same as described with reference to FIGS. 12 and 13, which is why it is for the generation of the signal 16 necessary elements are provided with the same reference numerals as in FIGS. 12 and 13, with the exception of the force F.5, which already has a different size than that because of the different type of fiber transfer via the nose 44 of the feed plate 29 to the briseur 3 Force F.4 of FIG. 12, in which the fibers are transferred in a so-called synchronous fashion from the feed roller 9 to the beater 3.
  • the synchronism arises from the fact that the feed roller 9 and the beater 3 have the same direction of movement at the fiber transfer point (see FIG. 1).
  • the force component F.5 can play a role in the formation of the force component F.5, such as the shape of the food plate 10 or. 29 in the area 23 resp. 23.1 and the distance of the groove edge 61 from the fiber mat 15 leading surface of the food plate 10, respectively. 29.
  • the invention is not restricted to the number and arrangement of the load cells shown in FIGS. 13 and 15. It is understood that, for example, depending on the strength of the groove 43 to the fiber release edge 24 (FIG. 12) or. one, two or more load cells 41.2 extending up to the nose 44 (FIG. 14) can be provided.
  • the measuring means consists of three load cells 41.3 which are arranged in a groove 45 which is embedded in the feed plate 10 and opens into the clamping gap region 23 (FIGS. 1 and 2) in the clamping gap.
  • the signals emitted by the individual load cells 41.3 are converted into signal 16 in an averager (not shown).
  • the distribution of the aforementioned load cells in the groove 45 is essentially as shown in FIG. 17.
  • the number of load cells is not limited to the three shown.
  • only two load cells can be used, while if a more precise determination of the force components over the length L (FIG. 17) of the feed plate 10 is to be carried out, a larger number of load cells can be distributed.
  • 18 and 19 is composed of a membrane 47 inserted into the feed plate 29, a pressure converter 48 and a pressure fluid system 49 connecting the membrane 47 to the pressure converter 48.
  • a force component F.7 (FIG. 18) analogous to the force F.6 of FIG. 16 causes a pressure on the diaphragm 47, as a result of which a force transmission is transmitted via the hydraulic fluid system 49 to the pressure converter 48, which is a force F. 7 corresponding signal 16 is generated.
  • This overpressure is detected with the measuring means shown in FIGS. 20 and 21, in that a measuring groove 50 is let into the food plate 10, which is connected to a pressure transducer 53 within the food plate 10 via a pressure line 51 and a pressure line 52 connected to the food plate 10 is.
  • This pressure converter 53 converts the excess pressure determined in the measurement groove 50 into the signal 16.
  • the measurement groove 50 is not continuous over the entire length L, i.e. the length L.1 of the measuring groove 50 is shorter than the length L of the feed plate 10, so that the measuring groove 50 is a groove located in the clamping gap area 23 and only open against the clamping gap.
  • the measurement groove forms an acute angle ⁇ with an imaginary plane E, which includes the mouth edge 54 of the wall 55 of the groove 50 as a tangential plane. This arrangement avoids that a fiber jam occurs in the groove 50.
  • the angle ⁇ has a maximum of 30 degrees.
  • FIGS. 20 and 21 show one of the measurement grooves 50 of FIGS. 20 and 21 analog measurement groove 50.1 with a pressure line 51.1 connected to it and a pressure line 52.1.
  • the measuring means of FIGS. 22 and 23 not only measure the pressure which, as described, arises from the pressing out of the air from the fiber mat, but it also becomes a constant one from a compressed air source 56
  • the amount of compressed air is pressed into the compacting fiber mat using measuring groove 50.1.
  • This predetermined amount of compressed air is passed through the fiber mat against the resistance of the fiber mat, so that a pressure corresponding to this resistance is transmitted from the pressure lines 51.1 and 52.1 to a pressure transducer 53.1 connected to the pressure line 52.2.
  • the pressure converter 53.1 converts these pressure variations into the signal 16.
  • the measurement groove 50.1 also has the angle ⁇ described for FIG. 20.
  • FIGS. 24 and 25 show a variant of the measuring means of FIGS. 22 and 23, in that the quantity of compressed air which remains constant from the compressed air source 56.1 by means of a Blow-in groove 58 is blown into the fiber mat located in the wedge gap area 23. This air travels in this fiber mat in a direction W opposite to the direction of rotation of the feed roller until it can escape into the atmosphere through a ventilation groove 59 and a ventilation line 57 connected to it.
  • a pressure transducer 53.2 is connected to the pressure line 52.2. This pressure converter 53.2 converts the pressure existing in the pressure line 52.2 into the signal 16.
  • a resistance range can be defined with the distance M between the injection groove 58 and the ventilation groove 59.
  • FIGS. 26 and 27 show a variant 2.2 of the fiber feed means from FIG. 2, in that the feed plate 10 can not only be pivoted about the pivot axis 11, but that it can also be pivoted about a pivot axis 62, which is coaxial with the axis of rotation of the feed roller 9 lies. This pivotability is shown schematically with the radius arrow S.
  • a holding bracket 63 which has two legs 64 (only one visible in FIG. 26), in which the pivot axis 11 is mounted.
  • the legs 64 each have a guide slot 66, the lower guide surface 67 (with 26)) has a curvature with the radius S.
  • the upper guide surface 68 opposite the lower guide surface 67 is provided parallel to the guide surface 67.
  • These guide slots 66 each serve to receive two guide pins 69, which are fixedly arranged in a machine housing part 70.
  • the distance (not marked) of these two guide bolts 69 is selected in relation to the length (not marked) of the guide slot 66 such that the holding bracket 63 can be pivoted about the pivot axis 62 for a given pivot length (not marked).
  • the holding bracket 63 In order to hold the holding bracket 63 in a selected pivot position, it is held in place by means of two screws 71 screwed into the machine housing part and projecting through the guide slot 66.
  • set screw 12 is arranged on an end part 63.1 of the holding bracket 63 directed against the licker-in roller 3.
  • this variant can also be used to combine all of the elements shown in FIGS. 4 to 25 in order to generate the signal 16. The application of these elements in connection with this variant is therefore not repeated.
  • This mobility of the feed roller 9 is given by the fact that the free ends 73 of the feed roller 9 projecting on both sides (only one shown with FIG. 28) of the feed roller 9 are accommodated in a bearing bush 74, which is between two stationary sliding guides 75 and. 76 are guided.
  • the displacement range of the feed roller 9 is limited on the one hand by a stationary stop 77 and by an adjusting screw 78 which is received in a carrier 79 which in turn is attached to the machine housing 25.
  • the stop 77 has the same function as the stop 27 described earlier.
  • the fiber mat 15 on the feed plate 72 is slidably moved from the feed roller 9 into the wedge gap between the feed roller 9 and the feed plate 72, whereby the feed roller 9 from its starting position, in which the bearing bushes 74 each rest on the corresponding stop 77, until they enter the operating position are raised, in which the bearing bushes 74 each abut the adjusting screws 78.
  • FIG. 30 shows a drafting system in which the method described so far is also used.
  • a counter roller 101 is used instead of the feed plate 10 shown in FIG. 1. This counter roller 101 forms together with the Feed roller 9 the nip.
  • the counter roller 101 is not driven, i.e. is freely rotating and is dragged through the fiber mat 15 lying between the counter roller and the feed roller.
  • the counter roller 101 is rotatably attached to a pivot lever 102.
  • pivot lever 102 is pivotally mounted by means of the pivot axis 11 and the bearing housing 26.
  • the load cell 41 described with FIGS. 8 and 9 is used as the measuring means for generating the signal 16. Reference is therefore made to the description for FIGS. 8 and 9.
  • roller pairs identified by reference numerals 103 and 104 are very well known from drafting technology and are therefore not described further. It should only be mentioned in connection with the function of the feed means that the two lower rollers (seen with a view of FIG. 30) of the roller pairs 103 and 104 are driven at a fixed speed which results in the draft in the drafting system. The upper rollers of the roller pairs 103 and 104 are also dragged from the fiber mat in an analogous manner to the roller 104.
  • the draft ratio of the spinning machine shown with this figure lies between the peripheral speed of the feed roller 9, given by the speed of the geared motor shaft 21 and the peripheral speed of the lower roller 104, given by its speed generating the speed signal 19.2.
  • the signal 19.2 has the same function as the signal 19 of FIG. 1.
  • EP-A-0 078 393 Device 110 for determining the density of the sliver is provided immediately after a fiber compression funnel.
  • This device 110 is a pair of rollers that can be pressed against one another, the peripheries of which engage in one another in such a way that a time-limited clamping zone that guides the sliver is created.
  • One roller 113 is stationary and the other roller 114 is arranged to be movable in order to carry out a movement corresponding to the fluctuations in the density of the fiber sliver. In the practical application of this device, these movements are sensed by a so-called proximity switch (not shown) and the signal 111 corresponding to the density fluctuations is generated.
  • the movement of the roller 114 can be limited in a manner analogous to the counter-roller 101 by an adjusting screw 12.1 provided with a load cell 41.
  • the roller 114 is rotatably mounted on a pivot lever 115 which functionally corresponds to the pivot lever 102, while the pivot lever 115 is pivotally mounted by means of a pivot axis 11.1 in a bearing housing 26.1 fixedly arranged on the machine housing 25.
  • the sliver 8 opens the rollers 113 and 114 by a predetermined amount (not marked), i.e. until the pivot lever 115 is in contact with the set screw 12.1.
  • the resulting different forces in the fixed nip of the rollers 113 and 114, which correspond to the different density of the fiber sliver 8, are detected by the load cell 41 and sent to the controller 17 as a signal 116.
  • Another advantage is that the hysteresis inherent in the displacement measurements is eliminated in the force measurement.

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

Claims (30)

  1. Procédé pour égaliser automatiquement les variations de densité de ruban dans les machines textiles, comme les cardes, les bancs d'étirage et similaires, dans lequel, à l'entrée de la machine textile, un signal (16) est produit en fonction de la densité d'une nappe de fibres (15) respectivement d'un ruban de fibre (15.1) se trouvant dans un moyen d'alimentation (2; 2.1; 2.2; 2.3; 2.4), et, à la sortie de la machine textile, un signal (111; 116) est produit en fonction de la densité d'un ruban de fibres (8) se trouvant dans un dispositif (110) servant à la détermination de la densité d'un ruban de fibres, ainsi que dans lequel ces signaux (16 et 111; 116) sont utilisés pour influencer les vitesses d'alimentation en fonction des deux signaux (16 et 111),
    caractérisé par le fait
    qu'au moins le moyen d'alimentation (2; 2.1; 2.2; 2.3; 2.4) comprend une fente de serrage prédéterminée, restant constante pendant la marche, et que le signal (16) est produit en fonction de la densité de fibres dans cette fente de serrage.
  2. Procédé selon revendication 1,
    caractérisé par le fait
    que, en plus, le dispositif cité (110) possède une fente de serrage prédétermineé et stationnaire pendant la marche, et que le signal (111; 116) est produit en fonction de la densité de fibres dans cette fente de serrage.
  3. Procédé selon revendication 1,
    caractérisé par le fait
    que le moyen d'alimentation (2; 2.1; 2.2; 2.3; 2.4) comprend un rouleau d'alimentation (9) et un élément d'alimentation (10, 29, 63, 72, 101) agissant conjointement avec ce rouleau, et que la vitesse d'alimentation est la vitesse de rotation du rouleau d'alimentation (9).
  4. Procédé selon revendication 3,
    caractérisé par le fait
    que l'élément d'alimentation comprend une plaque d'alimentation (10, 29, 63, 72).
  5. Procédé selon revendication 3,
    caractérisé par le fait
    que l'élément d'alimentation comprend un contre-rouleau (101) tournant librement.
  6. Procédé selon revendication 1,
    caractérisé par le fait
    que le signal (16) est produit par la résistance que rencontre un courant d'air s'écoulant à travers et dans le sens contraire à la nappe de fibres (15) respectivement le ruban de fibres (15.1) qui se trouve dans la fente de serrage.
  7. Procédé selon revendication 6,
    caractérisé par le fait
    que le courant d'air est produit par le refoulement de l'air contenu dans la nappe de fibres (15) respectivement le ruban de fibres (15.1) se déplaçant vers l'endroit le plus étroit de la fente de serrage.
  8. Procédé selon revendication 7,
    caractérisé par le fait
    que le courant d'air est produit en plus par un courant d'air insufflé à travers la nappe de fibres (15) respectivement le ruban de fibres (15.1) se déplaçant vers l'endroit le plus étroit de la fente de serrage.
  9. Procédé selon revendication 6,
    caractérisé par le fait
    que le signal (16) est produit par la résistance d'une partie de la section de nappe se trouvant dans la fente de serrage.
  10. Procédé selon revendications 4 et 9,
    caractérisé par le fait
    que la section de nappe est donnée par un trajet prédéterminé dans le sens circonférentiel du rouleau d'alimentation, et par la longueur du rouleau d'alimentation.
  11. Procédé selon revendications 2 et 5,
    caractérisé par le fait
    que le signal est produit par une force produite par la densité de fibres dans la fente de serrage.
  12. Procédé selon revendication 11,
    caractérisé par le fait
    que la force est transmise mécaniquement à un moyen de mesure de force, dans lequel un signal électrique est produit.
  13. Procédé selon revendication 11,
    caractérisé par le fait
    que la force est transmise hydrauliquement à un moyen de mesure de force, dans lequel un signal électrique est produit.
  14. Procédé selon l'une des revendications précédentes,
    caractérisé par le fait
    que les signaux (16 et 111) sont évalués dans une commande (17) donnant un signal (22) commandant le nombre de tours du rouleau d'alimentation (9).
  15. Dispositif pour réaliser le procédé selon revendication 1,
    - avec un moyen d'alimentation (2; 2.1; 2.2; 2.3; 2.4) qui comprend un rouleau d'alimentation (9) commandable transportant la nappe de fibres (15) respectivement le ruban de fibres (15.1) dans la machine textile, et un élément d'alimentation (10, 29, 63, 72, 101) agissant conjointement avec ce rouleau d'alimentation et formant ainsi une fente de serrage pour la nappe de fibres, ainsi qu'avec un dispositif (110) situé à la sortie de la machine textile, qui comprend un rouleau (113) commandable, transportant le ruban de fibres (8) hors de la machine textile, et un rouleau (114) tournant librement et agissant conjointement avec le rouleau de transport en formant une fente de serrage pour le ruban de fibres (8), et
    - chacun avec un moyen de mesure pour déterminer la densité de la nappe de fibres entrante (15) respectivement du ruban de fibres entrant (15.1) ainsi que du ruban de fibres (8) passant à travers la machine, et donner un signal de mesure (16 respectivement 111; 116) correspondant à chaque densité,
    caractérisé par le fait
    - qu'au moins le rouleau d'alimentation (9) ou
    - l'élément d'alimentation (10, 29, 63, 72, 101) est mobile depuis une position de départ dans une position de marche, laquelle est donnée par
    - un membre de réglage ajustable (12, 78), alors que l'élément d'alimentation (10, 29, 63, 72, 101) ou le rouleau d'alimentation (9) est stationnaire, afin de former, pendant la marche, une fente de serrage restant constante entre le rouleau d'alimentation (9) et l'élément d'alimentation.
  16. Dispositif selon revendication 15,
    caractérisé par le fait
    que, en plus, ledit rouleau tournant librement (114) est mobile depuis une position de départ dans une position de marche qui est donnée par un membre de réglage (12.1) ajustable, alors que le rouleau commandable (113) est stationnaire afin de former, pendant la marche, une fente de serrage stationnaire entre les deux rouleaux cités (113 et 114).
  17. Dispositif selon revendication 15,
    caractérisé par le fait
    que l'élément d'alimentation (10, 29, 63) comprend une plaque d'alimentation (10, 29) oscillant autour d'un axe de pivotement (11, 31), et que le membre de réglage ajustable comprend au moins une vis de réglage (12) contre la laquelle la plaque d'alimentation vient buter pendant la marche, afin de délimiter la fente de serrage.
  18. Dispositif selon revendication 15,
    caractérisé par le fait
    - que l'élément d'alimentation comprend une plaque d'alimentation stationnaire (72), et
    - que le rouleau d'alimentation (9) est mobile depuis une position de départ dans une position de marche qui est donnée par un membre de réglage ajustable (78).
  19. Dispositif selon revendication 15,
    caractérisé par le fait
    que l'élément d'alimentation comprend un contre-rouleau (101) oscillant autour d'un axe de pivotement (11), et que le membre de réglage ajustable comprend au moins une vis de réglage (12) qui délimite le mouvement d'oscillation du contre-rouleau (101) pour délimiter la fente de serrage.
  20. Dispositif selon revendication 16,
    caractérisé par le fait
    que le rouleau tournant librement (114) est disposé oscillant autour d'un axe de pivotement (11.1) et que le membre de réglage comprend au moins une vis de réglage (12.1) qui délimite le mouvement oscillant du rouleau tournant librement (114).
  21. Dispositif selon revendication 17,
    caractérisé par le fait
    que le moyen de mesure est constitué de deux bandes de mesure d'allongement (non montrées) qui sont fixées à une distance l'une de l'autre sur l'axe de pivotement, et qui déterminent la force transversale provoquée par la plaque d'alimentation sur l'axe de pivotement, et donnent un signal électrique correspondant (16).
  22. Dispositif selon revendication 17, 19 ou 20,
    caractérisé par le fait
    que le moyen de mesure est au moins une boîte dynamométrique (41, 41.1) qui, en tant que partie intégrante de la vis de réglage (12, 12.1, 32), détermine la force produite dans la fente de serrage et transmise à la vis de réglage (12, 12.1, 32), et en donne un signal électrique correspondant (16).
  23. Dispositif selon revendication 17 ou 18,
    caractérisé par le fait
    que le moyen de mesure est au moins une boîte dynamométrique (41.2) qui est introduite sans jeu dans une rainure (43) prévue dans la plaque d'alimentation (10, 29) de telle manière que la force produite dans la fente de serrage est transmise à la boîte dynamométrique (41.2) avec au moins une partie proportionnelle, et que celleci donne, en conséquence, un signal électrique correspondant (16).
  24. Dispositif selon revendication 17 ou 18,
    caractérisé par le fait
    que le moyen de mesure est constitué au moins de deux boîtes dynamométriques (41.3) qui reposent sur le fond d'une rainure (45) prévue dans la plaque d'alimentation (10) et débouchant dans la fente de serrage, et qui sont recouvertes par une barre de transmission de force (46) reposant sur ces boîtes dynamométriques (41.3), barre qui forme, avec sa face dirigée vers la fente de serrage, une partie intégrante de la surface de la plaque d'alimentation formant la fente de serrage, et ceci de telle manière que la force transmise aux boîtes dynamométriques (41.3) par le barre de transmission de force (46) produit un signal électrique correspondant (16).
  25. Dispositif selon revendication 17 ou 18,
    caractérisé par le fait
    que le moyen de mesure comprend premièrement une membrane (47) qui est intégrée essentiellement sur la longueur de la plaque d'alimentation (29) dans celle-ci et dans la surface formant la fente de serrage, et deuxièmement comprend un convertisseur de pression (48) auquel la force reçue par la membrane (47) est transmise hydrauliquement, et qui donne un signal électrique correspondant (16).
  26. Dispositif selon revendication 17 ou 18,
    caractérisé par le fait
    que le moyen de mesure comprend une rainure (50) prévue dans la plaque d'alimentation (10), débouchant dans la fente de serrage et s'étendant essentiellement sur la longueur (L) de la plaque d'alimentation, parallèle à l'axe de pivotement (11) de la plaque d'alimentation (10), ainsi qu'un convertisseur de pression (53) relié avec cette rainure, et où la rainure (50) fait un angle de maximum 30 degrés, compris entre la paroi de rainure (55) faisant face à l'axe de pivotement et la surface de la fente de serrage de la plaque d'alimentation (10), et que le convertisseur de pression (53) donne un signal (16) correspondant à la pression régnant dans la rainure.
  27. Dispositif selon revendication 17 ou 18,
    caractérisé par le fait
    que le moyen de mesure comprend
    - une rainure (50.1) prévue dans la plaque d'alimentation (29), débouchant dans la fente de serrage et s'étendant essentiellement sur la longueur (L) de la plaque d'alimentation (29), parallèle à l'axe de pivotement (31) de la plaque d'alimentation (29) ou à l'axe de rotation du rouleau d'alimentation (9),
    - ainsi qu'un convertisseur de pression (53.1) relié avec cette rainure (50.1),
    - ainsi qu'une source d'air comprimé (56) donnant une quantité d'air constante, reliée avec la rainure (50.1),
    - et où la rainure (50.1) fait un angle de maximum 30 degrés, compris entre la paroi de rainure (55.1) faisant face à l'axe de pivotement (31) et la surface de la fente de serrage de la plaque d'alimentation, et que
    - le convertisseur de pression (53.1) donne un signal (16) correspondant à la pression régnant dans la rainure (50.1).
  28. Dispositif selon revendication 17 ou 18,
    caractérisé par le fait
    que le moyen de mesure comprend une première et une seconde rainure, prévue chacune dans la plaque d'alimentation (10), débouchant chacune dans la fente de serrage et s'étendant essentiellement sur la longueur (L) de la plaque d'alimentation (10), parallèle à l'axe de pivotement (11) de la plaque d'alimentation (10), et où la première rainure est une rainure de soufflage (58) et la deuxième est une rainure d'aération (59), et que les deux rainures font un angle de maximum 30 degrés, compris entre leur paroi de rainure faisant face à l'axe de pivotement et la surface de fente de serrage de la plaque d'alimentation,
    que la première rainure est prévue éloignée de la deuxième rainure, d'une distance (M) prédéterminée, et
    que la première rainure (58) est reliée à une source d'air comprimé (56.1) donnant une quantité d'air constante, et à un convertisseur de pression (53.2) qui donne un signal (16) correspondant à la pression, alors que la deuxième rainure (59) est reliée à l'atmosphère.
  29. Dispositif selon les revendications précédentes 15 et 17,
    caractérisé par le fait
    que l'axe de pivotement (11) de la plaque d'alimentation (10), dans une zone prédéterminée, est pivotable et arrêtable autour de l'axe de rotation (62) du rouleau d'alimentation (9).
  30. Procédé selon revendication 3,
    caractérisé par le fait
    que le signal est déterminé près de, cependant avant le lieu ou l'élément d'alimentation délivre la nappe de fibres à l'élément recevant la nappe de fibres.
EP87118414A 1986-12-12 1987-12-11 Procédé et appareil de compensation automatique des variations de poids des rubans sur les machines textiles telles que cardes, bancs d'étirage et similaires Expired - Lifetime EP0271115B1 (fr)

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Application Number Priority Date Filing Date Title
CH495186 1986-12-12
CH4951/86 1986-12-12

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EP0271115A3 EP0271115A3 (en) 1988-07-27
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US (2) US4854011A (fr)
EP (1) EP0271115B1 (fr)
JP (1) JPS63159528A (fr)
DE (1) DE3769610D1 (fr)
IN (1) IN170275B (fr)

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DE3769610D1 (de) 1991-05-29
US5014395A (en) 1991-05-14
JPS63159528A (ja) 1988-07-02
IN170275B (fr) 1992-03-07
EP0271115A2 (fr) 1988-06-15
US4854011A (en) 1989-08-08
EP0271115A3 (en) 1988-07-27

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EP3052681B1 (fr) Étaleur-nappeur et procédé de fabrication d'une nappe à partir de rubans de fibres

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