CA2002309A1 - High speed precision yarn winding system - Google Patents
High speed precision yarn winding systemInfo
- Publication number
- CA2002309A1 CA2002309A1 CA002002309A CA2002309A CA2002309A1 CA 2002309 A1 CA2002309 A1 CA 2002309A1 CA 002002309 A CA002002309 A CA 002002309A CA 2002309 A CA2002309 A CA 2002309A CA 2002309 A1 CA2002309 A1 CA 2002309A1
- Authority
- CA
- Canada
- Prior art keywords
- yarn
- package
- spindle
- motor
- tube
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 238000004804 winding Methods 0.000 title claims abstract description 36
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- 230000033001 locomotion Effects 0.000 claims description 18
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- 238000010168 coupling process Methods 0.000 claims 6
- 238000005859 coupling reaction Methods 0.000 claims 6
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- 230000010386 affect regulation Effects 0.000 claims 1
- 210000003128 head Anatomy 0.000 description 14
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- 238000011161 development Methods 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 239000004753 textile Substances 0.000 description 2
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- 230000003068 static effect Effects 0.000 description 1
- 229920002994 synthetic fiber Polymers 0.000 description 1
- 238000012549 training Methods 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H54/00—Winding, coiling, or depositing filamentary material
- B65H54/02—Winding and traversing material on to reels, bobbins, tubes, or like package cores or formers
- B65H54/28—Traversing devices; Package-shaping arrangements
- B65H54/2836—Traversing devices; Package-shaping arrangements with a rotating guide for traversing the yarn
- B65H54/2839—Traversing devices; Package-shaping arrangements with a rotating guide for traversing the yarn counter rotating guides, e.g. wings
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H59/00—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators
- B65H59/40—Applications of tension indicators
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H2553/00—Sensing or detecting means
- B65H2553/20—Sensing or detecting means using electric elements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H2553/00—Sensing or detecting means
- B65H2553/20—Sensing or detecting means using electric elements
- B65H2553/26—Piezoelectric sensors
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H2701/00—Handled material; Storage means
- B65H2701/30—Handled filamentary material
- B65H2701/31—Textiles threads or artificial strands of filaments
Landscapes
- Engineering & Computer Science (AREA)
- Textile Engineering (AREA)
- Winding Filamentary Materials (AREA)
- Tension Adjustment In Filamentary Materials (AREA)
- Spinning Or Twisting Of Yarns (AREA)
- Replacing, Conveying, And Pick-Finding For Filamentary Materials (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A high-speed precision winder for winding a running yarn onto a tube to form a cross wound yarn package, including a spindle for rotating the tube about a spindle axis, a yarn traversing mechanism for guiding running yarn received along an infeed path back and forth across a traverse zone, a bail roller disposed in rolling contact with the peripheral surface of the yarn package being wound, a tensioner for varying tension of the infeed yarn, and a control system for continuously regulating operation of the winder during formation of the package. The control system includes three separate variable speed drive motors and respective associated motor control circuits forming a spindle drive, a traversing means drive, and a down pressure drive providing three independent motor systems which are separately controllable.
Load cells are associated with the bail roller and tensioner and output signals from the load cells and a predetermined set processing condition data applied to a microprocessor provide control signals to activate the motor to position the bail roller and transversing mechanisms and regulate the spindle drive, traversing mechanism drive, and bail roller and traversing mechanism position to maintain a desired yarn density and tension throughout winding of the package.
A high-speed precision winder for winding a running yarn onto a tube to form a cross wound yarn package, including a spindle for rotating the tube about a spindle axis, a yarn traversing mechanism for guiding running yarn received along an infeed path back and forth across a traverse zone, a bail roller disposed in rolling contact with the peripheral surface of the yarn package being wound, a tensioner for varying tension of the infeed yarn, and a control system for continuously regulating operation of the winder during formation of the package. The control system includes three separate variable speed drive motors and respective associated motor control circuits forming a spindle drive, a traversing means drive, and a down pressure drive providing three independent motor systems which are separately controllable.
Load cells are associated with the bail roller and tensioner and output signals from the load cells and a predetermined set processing condition data applied to a microprocessor provide control signals to activate the motor to position the bail roller and transversing mechanisms and regulate the spindle drive, traversing mechanism drive, and bail roller and traversing mechanism position to maintain a desired yarn density and tension throughout winding of the package.
Description
20023~g BACKGROUND AND OBJECTS OF THE INVENTION
The present invention relates in general to the winding of textiles yarns, filaments, or the like of natural, man made or synthetic materials, all referred to herein as "yarns", and more particularly to high speed precision winding of yarn packages on a precision winder machine having a propeller structure for guiding the yarn back and forth between the ends of the package during the winding process, and incorporating sensors and controls for regulating the propeller drive, the spindle drive for the yarn package handle, and down pressure drive to produce a highly uniform package which is free of ribboning effects once injecting to dying processes and the like.
Before the days of the continuous filament extrusion, texturizing, and similar high speed methods of yarn production, traditional mechanisms for producing the traversing mechanism necessary for laying yarn on a package included a grooved scroll with either engaged the yarn directly or drove a yarn guide so as to cause it to carry out a reciprocatory traversing motion. Those mechanisms were limited as to there speed of operation and the uniformity of packages produced by such mechanisms.
Upon the more recent development of high speed yarn production methods, the demand was emphasized for winders having very much higher speeds of operation. One form of traversing mechanism proposed for such high speed winders included slot like yarn guides unted on closely spaced driving members moving in opposite directions across the traverse so that the yarn was carried from one end of the traverse to the other by one yarn guide and was then Z0023~)9 transferred to another yarn guide so as to be carried back in opposite direction. This avoided inertial problems which were incident to use of a single yarn guide which moved in one direction and then the other, but created problems of yarn transfer from one guide to another.
While driving arrangements involving two guide members, one moving in one direction and the other in the opposite direction, have taken forms such as belt or chain drives for the yarn guides moving them in a straight line across the traverse, the use of rotary discs or blades which act as yarn guides moving across the traverse along and arc of a circle having come into wide use. These rotary discs or blade type yarn guides move in a continuous path with no abrupt changes in velocity or direction, so that the only inertia concerns presented are in connection with the inertia of the yarn itself at each reversal point. Care had to be taken, however, to maintain close control of the yarn as it is transferred from one yarn guiding blade or disc to another, in a manner which would avoid nipping action on yarn which may have an adverse effect on its quality. However full control over the yarn ~during transfer from one driving member to another is essential~
One of the widely used types of cross winding systems ~ employed in the textile industry is of the type disclosed in ~ 25 U.S. patent 3,823,886 granted to Maschinenfabrik Scharer, v which involve first and second yarn guides of a propeller or blade type rotatable and opposite directions about respective axes of rotation which are offset f~om each other, associated with respective substantially circular shaped guide members provided for each of the yarn guides, centered on the respective axes of rotation of the yarn guides so that the 20QZ30g guide tracts intersect each other at a pair of diametrically opposite points for overlapping of the thread guides at these points. Other yarn traversing apparatus of this general type ~~ involving rotary blade or propeller type guides are disclosed in U.S. patent no. 4,561,603 of December 31, 1985, no.
4,585,181 of April 29, 1986 and no. 4,6~6,983 of March 3, 1987 all granted to Barmag Barmer Maschinenfabrik A.G.
It has been customary, heretofore, for example in the Scherer winder machines, to attempt control of the winding in an effort to achieve uniformity throughout the wound packages by regulating a drive motor which drives the yarn guide blades or propellers and the package spindle. However, it has been found that this arrangement does not provide sufficient control of the various perimeters affecting uniformity of the density of the yarn package to achieve the desired extent of yarn package uniformity wherein the packages are free of ribboning when subjected to the dying process, and which would have such uniformity all the way to the bottom of the package so that the innermost layers of yarn do not need to be discarded. I have 20 ~ found, however, that by providing separate drive motors providing separately controlled drive systems for the spindle drive, the propeller drive, and a down pressure drive, thus providing three independent motor systems that can be separately controlled, one can properly set and regulate the pitch and the tension during winding of the package so as to maintain the desirable yarn density or tension throughout the whole package, and ensures freedom from development of ribboning patterns during pack~ge winding, which are detrimental to during the dying process.
20~Z3~g BRIEF DESCRIPTION OF THE_PIGURES
FIGURE 1 is a front elevational view of the yarn winding apparatus of the present invention, showing the portions of the frame associated with the components related to production of the yarn package, with lower portions of the frame not shown;
FIGURE 2 is a vertical section view of the apparatus, taken along the line 2-2 of Fig. l;
FIGURE 3 is a horizontal section view showing the underside of the moveable platform supporting the yarn guide propeller members and the drive therefor, taken along the line 3-3 of Fig. 2;
~ IGURE 4 is a top plan view of the propeller supporting platform, the yarn guide propellers and associated stationary guide mem~ers, and the bail roll and supports therefor;
FIGURE 5 is a vertical section view showing the bail roll and the yarn guide propeller drive mechanism and drive motor therefor, taken along the line 5-5 of Fig. 4;
FIGURE 6 is an exploded perspective view of the yarn guide propeller mechanism and supporting platform therefor and the I ! ' 201' `associated drive components;
,¦ FIGURE 7 is a fragmentary front view showing one form of yarn tensioner mechanism for the apparatus;
FIGURUE 8 is a side elevational view of the yarn tensioner;
FIGURE 9 is a horizontal section view taken along line 9-9 of Fig. 8;
FIGURE 10 is a schematic diagram of a typical load cell circuit for processing load cell ~ignals from a load cell associated with one of the sensed conditions in the winder, of the present invention, such as the bail roller load cell;
FIGURE 11 is a block diagram of the control system for the winder;
FIGURE 12 is a block diagram of a typical proportional, integral derivative (PID) motor control section for the winder control system; and FIGUURE 13 is a block fdiagram of a typical Digital to Analog Converter (DAC) section for the winder control system.
DETAILED DESCRIPTION OF A PREFERRE~ EMBODIMENT
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10Referring to the drawings, wherein like reference - characters designated corresponding parts throughout the several figures, and particularly to Figs. 1 and 2, the high speed precision yarn winding apparatus of the present invention is indicated generally by the reference character 10 and comprises, in one preferred embodiment, a supporting frame 11 formed basically of angle iron members, including vertical main frame members 12, and horizonal frame members 13 ~ extending between and fixed to the vertical frame members 12.
Il Near the upper end portion of the main frame 11 is a yarn 20l package support assembly, indicated at generally at 14, `~ ' comprising a driven tube-engaging head subassembly 15 and an axially moveable companion head assembly 16 providing a live center for the yarn package tube 17 on which the yarn package 18 is to be wound. The head assemblies 15 and 16 each include a truncated conical head 19 and 20, respectively adapted to ~;partially interfit into the hollow center of the yarn package tube 17 and embraced the tube ,17 and yarn package 18 therebetween. The driven head 19 is fixed on a cylindrical spindle 21 journaled in the bearing block 22 fixed on a support arm 23 carried by the stationary main frame 11, for example by 200Z3~;19 spacer members 24 and bolts 25 connected to upright main framemembers 12 at one side of the main frame or to horizontal cross members extending therebetween. The end of the spindle 21 opposite the drive head 19 projects from the bearing block 22 and carries a pulley 26 driven by a belt 27 trained about the pulley 26 and about an output drive pulley 28 on the output shaft of the spindle drive motor 29. The spindle drive motor 29 may be conveniently supported also from the support arm 23.
The opposite or live center head 20 forms a removable holder for the yarn package tube 17 and is rotatably supported on a retractable and returnable spindle member 30, for example by roller bearings, rotatably supporting a truncated conical tube holder head 20 on the spindle member 30. The spindle member 30 is supported for axially movement between an lS extended, tube holding position as illustrated in Fig. 1, to a retracted tube removal position in a linear slide sleeve 31 housed in a supporting block 32 carried by another support arm 33 extending from the main frame 11, the spindle member 30 having an internal nut 34 threaded on a screw shaft 35 which 20, projects from the support block 32 on the si~e opposite the tube holder head 20. A pulley 36 is provided on the screw , shaft 35, driven through a belt 37 trained about a drive pulley 38 on the output shaft of a DC motor 39 operating in a constant torque mode and forming a doff motor for retracting or doffing a fully wound package 18 and its associated tube 17 when the package is fully wound. Energizing of the doff motor 39 effects rotation of the screw shaft 35 through the system of pulleys 38, 36 and belt 37, causing the screw 34 carried by the spindle member 30 to be driven by the threads on the screw shaft 35 in a airection to axially retract the spindle member 30 and tube holder head 20 through a travel of about 1 1/2 l ZOQZ309 inches, withdrawing the live center tube holder head 2~ from holding relation to the tube, permitting tube 17 and package 18 : to be doffed or withdrawn. A new empty yarn package tube 17 is replaced by fitting one end of the new empty tube 17 on the companion tube holder head 19 and activating the doff motor 39 to rotate the screw shaft 35 and axially drive the spindle member 30 in tube holder head 20 through a return stroke to the tube holding position shown in Fig. 1.
A movable subframe 40 is guided for vertical up and down movement in the main frame 11 between the vertical frame members 12, for example, by vertical guide rods 41 sliding in guide sleeves or brackets 42 fixed to appropriate portions of the main frame 11. The vertically movable subframe 40 comprises a bail roll and yarn guide propeller supporting upper 15¦ platform 43 at the uppermost end of the subframe 40, connected by vertical subframe members 44 with a bottom horizontal subframe member 45 to form a unitary movable subframe which can be raised and lowered as required as the yarn package 18 ¦ is being formed on the tube 17. The upper platform 43 supports a bail roll 46 supported in bearing brackets 47 at its opposite ends, at least one of which is carried on a load cell 48 . mounted on the uppermost surface of the platform 43 and disposed between the upwardly facing surface of the platform 43 and the bottom surfaces of the bail roll bearing brackets 47.
The mounting of the bail roll 46 on load cell 48 and the processing circuitry associated with the output signals from . I these load cells provides a down pressure sensing and control system, as later described in srea4r detail, to maintain proper down pressure properties responsive to pressure of the package on the bail roll and causing the platform 43 to be raised and lowered relative to the spindle axis to maintain proper package ~ Z0023~9 winding. The load cell 48 may be of the kind marketed byTransducer Techniques, Inc. of Rancho, California, described as low profile load cells, which incorporate strain gauge transducers providing an output signal proportional to the load on a member, which in this case is the bail roll 46. This provides a highly accurate and reliable signal output indicative of the down pressure of the yarn package on the bail roll, by proving a beam structure or the like having suitable mounting surfaces for a plurality of electrical strain gauges and utilizing the transducive electrical strain gauges to measure the shear stresses caused by the applied loads. The transducive effect of a strain gauge allows for accurate translation between a given amount of stress imposed on a surface by a load and its electrical equivalent, resulting in an accurate stress measurement. Foil, semiconductor, or other types of strain gauges may be effectively used to provide such shear stress measurements. Typically, the strain gauges are connected into a Wheatstone bridge network to provide the correct output. The principals of the strain gauge employed may be similar to those disclosed in earlier U.S. patents 3,927,560 and 4,127,001, as typical examples.
Also mounted on the vertical translation platform 43 of the movable subframe 40 is a pair of yarn guide blades or propellers 50a, 50b rotating in opposite directions through appropriate paths immediately above the curved yarn guide bar 51 fixed to the vertical translation platform 43 and having a convexly curved working edge 52, spanning a yarn traversing zone of appropriate width between a~pair of end control guide rails 53, 54. As will be well understood by persons skilled in the relevant art, the yarn guide propeller blades 50a, 50b and the stationary yarn guide bar 51 and end control guide rails I ~OOZ30g 53, 54, form a yarn winding station whereby the uppermost yarn Iguiding propeller and blade 50a, as best shown in Fig. 4, i traverses the yarn, indicated at 55, from top to bottom (as l shown in Fig. 4) or from right to left as viewed in Fig. 1, along the length of the package 18 and, after transfer to the guide propeller or blade 50b while the yarn is captured against , outward disengaging movement from the blade system by the end control guide rail 54, at the lower or left and end of the ¦
field of traverse, the yarn 55 is traversed back again to the upper or right hand end where it is again transferred back to the yarn guide propeller or blade 50a.
The dri~ing mechanism for the yarn guide propellers or blades 50a, 50b comprises a propeller shaft 56 supported for rotation in a vertical axis, which is fixed to the uppermost blade or propeller 50a and extends through a center opening in the lower blade or propeller 50b. The lower blade or propeller 50b is fixed to an upper pulley member 57, in the form of a downwardly opening cup or hollow cylinder, having a center j collar portion 57a encircled by roller bearing assemblies 58 whose outer portions are supported in an extension 59a of a bearing housing 59, the lower portion of which supports the outer portion of the roller bearing assembly 60 encircling and mounted on the center post or spindle portion 6la of the lower pulley 61. The bearing assemblies 58, 60 are captured in the bearing housing 59 by retainer rings 62 and the center opening ; 57b in the center collar portion 57a of the upper pulley 57 is of a sufficiently large diameter to accommodate rotation of the upper pulley 57 about an eccentric axis A2 located eccentrically relative to the vertical axis A1 which extends through the centers of the propeller shaft 56 and the lower pulley 61. The lower end of the propeller shaft 56 driving the upper propeller or blade 50a is fixed against relative rotation in the socket formation in the spindle or center post portion 61a of the lower pulley 61, and the pulley 61 is coupled by a locking ring 63 and a lock nut 64 to the drive S sha~t 65 of the propeller or blade drive motor 66. The motor 66 is mounted by a suitable hanger bracket 67 depending from the platform 43, with its vertical legs spaced outwardly from the pe~ipheries of the eccentrically related upper and lower pulleys 57, 61. The outer surfaces of the cylindrical pulleys 57, 58 are provided with teeth interfitted with tooth formations on the toothed endless belt 68 which is trained about the lower pulley 61, driven directly from the output shaft of the propeller drive motor 66, the belt system being arranged to effect rotary drive of the upper pulley 57 in a reverse direction. This is accomplished by training the belt ; 68 about an idler roll or pair of idler pulleys on an interconnecting shaft, shown at 69, journaled for rotation in a mounting block 70 and protruding from both ends thereof providing end portions about which the belt is wrapped, with the upper portion of the belt in a hori~ontal path immediately above the idler roll 69 extending about and interfitting with the teeth on the outer periphery of the upper pulley 57.
The entire subframe assembly 40 is movable upwardly and downwardly responsive to down pressure signals derived from the bail roll 46 and load cells 48, and the associated circuitry, activating a down pressure control motor or platform positioning motor 72 mounted on the main frame 11. Vertical movement of the subframe 40 and ~the vertical translation platform 43 is achieved, in a preferred example, by an Acme screw and nut assembly, as indicated by the vertical lag screw 73 journaled for rotation at its lower end in a bearing bracket . I
.: .
20023~
i, 74 carried by a horizontal stationary beam 75 fixed to and forming part of the main frame 11 and extending through the nut 76 carried by the lower cross frame member 45 of the vertically movable subframe 40. The Acme screw 73 is driven by a pulley 77 fixed against relative rotation on the dxive screw 73, as by keying the pulley to the drive screw, driven by a belt 78 trained about the pulley 77 and about drive pulley 79 fixed to the output shaft of the down pressure control motor It will be apparent fro~ the above description that this apparatus, therefore, provides three motors providing separate control of three principal factors determining the precision winding of the yarn package so as to provide the desired level of uniformity and absence of ribboning. First the down pressure control motor 72 controls the vertical position of the : vertical translation platform 43 carrying the yarn guide propellers or blades 50a, 50b and associated yarn guide structure, as well as carrying the bail roll 46 and its associated load cells 48. Secondly, the propeller drive motor 66 carried by the vertically movable platform 43 determines the speed of drive of the yarn guide propellers or blades 50a, . 50b and thus the speed of traverse of the yarn between the opposite ends of the package being formed. Thirdly, the spindle drive motor 29 carried by the stationary main frame 11 drives the spindle 21 and tube holder head 19 to rotate the I yarn package tube 17 and thus determine the speed of winding of yarn onto the package.
Control of the spindle drive motor 29 is derived from the yarn tensioner assembly, indicated generally at 80, to sense the tension of incoming yarn leading to the winder and provide load cell output signals which are processed to effect yarn Z~OZ3~ .
drive so as to maintain a predetermined yarn tension and preserve uniformity of winding and tracking of the yarn on the package. Alternatively, the owner has the option of having a constant speed drive for the spindle motor 29 instead of a control system which is responsive to sensing of incoming yarn tension.
Referring particularly to Figures 7-9/ there is shown in those figures one preferred embodiment of the yarn tensioner assembly 80 which/ in general may be described as forming a pair of yarn guides 81, 82 which are vertically spaced along the yarn feed path 83, with a sensor arm 84 interposed therebetween bearing against the yarn and deflecting it slightly out of the yarn path defined by the eyes in the yarn guides 81, 82. In this yarn tensioner, the guides 81, 82 are formed as a pair of parallel legs bent from a plate to form a U-shaped bracket 85 having a transverse base portion 86 and ~ outwardly bent legs 86a, 86d defining the guides 81, 82. The I legs 86a, 86b include a projecting finger portion 86c having an inclined surface 86b forming one side of a truncated triangular hook portion of the finger which leads through a throat formation 86e into a generally circular or rounded eye . formation 86f which receives the yarn and defines the yarn path 83 between the two guides 81, 82. The eye formation 86f should be deep enough to prevent yarn escape while running at high speeds, and the inclined surface 86d of the finger portion 86c is so positioned and shaped that the yarn will self thread from s this surface into the eye formation 86f. The transverse base portion 86 is provided with a slot ~6g at its center elongated widthwise of the base portion 86 and receiving the sensor arm 84, which is in the form of a bent rod, for example a ceramic flame coated stainless steel rod having an outer diameter of Il z00~30~
about l/8th inch, extending from a block 87 having bearings 88 pivGting the block on a pivot shaft 88a extending between stationary support arms 89. The block 87 includes a protruding finger ~ormation ~7a bearing against a load cell 90 supported by mounting standoffs or a block from the support plate which also supports the arms or yoke 89 mounting the pivot shaft 88a thereto as well as supporting the U-shaped bracket 85 forming the guides Bl, 82. In practice, this support plate, indicated ; at 9l, which must also be provided with a slot for appropriate movement of the yarn contacting feeler 84, may be bent in a U-shaped as shown in the drawings to support a printed circuit board amplifier and carrier plate 92 for amplifying signals from the load cell 90.
A preferred example of a winder control system for the lS high speed precision winder of the present invention is indicated in block diagram form in Figure ll, wherein the control system is shown as including a motor section MS, a digital to analog section indicated at D/A, and an analog to digital section, indicated at A/D, which are connected to a microprocessor indicated at MP. To describe the overall operation, the microprocessor MP writes command data to the digital proportional, Integral, Derivative (PID) control subsystem. This command data determines the speed, exceleration, and servo response characteristics of each of the three motors, namely the spindle drive motor 29, the propeller or blade drive motor 66, and the carriage positioning or down pressure control motor 72. The resolution of each controller is one in 4,294,967,296 or 32 bits. Consequently, highly precise speed ratios between the spindle motor and the propeller may be achieved. This control technique also allows for the DC motors 29, 66, and 72 to be operated in a position ZOOZ3~9 mode. This is advantageous for the carriage system 40controlled by the carriage motor 72, as the microprocessor is positioning the carriage 40 and platform 43 in response to pressure on the yarn package 18 as measured by the load cell or load cells 48 associated with the bail roll 46. The circuit associated with the load cell 48, to be later described, sends a signal to the microprocessor MP proportional to the pressure on the package. If this value is greater than the programed set point, the microprocessor MP lowers the carriage position of carriage 40 and platform 43 until the setpoint value is received from the load cell 48. The carriage motor 72 is then commanded to halt.
The Digital to Analog subsystem D/A includes two converters, to which the microprocessor MP writes data to establish setpoints for tensioner current to the tensioner assembly 80 and doff motor current to the doff motor 39. The ; D/A output controls the duty cycle of a pulse width modulated (PWM) power stage. This duty cycle may be varied from 0 to 100%. Consequently, the tensioner current and doff motor current maybe varied from 0 to 100~. The tension or current is directly proportional to the amplified yarn tension developed by an electromagnetic tensioning device. The doff motor current for the motor 39 is directly proportional to the force exerted on the dye tube 17 by the live center system (the live center tube holder head 20).
Referring to the Analog to Digital system A/D, the microprocessor MP monitors a variety of analog values in the winder system to maintain system parameters, efficiency, and diagnostics capability. The three system parameters monitored are (1~ the down pressure load cell 48 to establish current pressures, (2) the tensioner current which establishes that the 2~023v9 ii tensioner is functional and that the value is sufficient for the tensiometer to maintain control and (3) the tensiometer load cell 90 which transmits the current yarn tension to the microprocessor. The other five A/D inputs to the Analog to Digital subsystem A/D are used to monitor system power supplies and motor currents for failsafe operation and diagnostic functions.
Also shown in the block diagram of Fig. 11 as part of the overall winder control system is a stop motion system indicated at SM, providing a means to determine if the yarn from the supply package is broken. This stop motion system may be an optical stop motion system of the type presently commercially available which generates a signal applied to the microprocessor as an interrupt signal. This interrupt signal forces the microprocessor to stop current program execution and to immediately implement routines established by the software which appropriately stop the winding process and signal for operator help.
Also, as an additional communication facility to communicate with operators and plant personnel, the microprocessor in the illustrated embodiment is connected to a keyboard and display, indicated at KB/D in Fig. 11, and through a communication link CL through a RS 485 serial transmission line to a host computer. The onboard communications provided to the display and keyboard section KB/D allow the microprocessor MP to relate the machine status to the operator and to receive operator request for activity.
The communications link line allo~s the microprocessor to acquire all operations data, such as yarn speed, max yardage, max diameter, pitch, down pressure, etc. that plant personnel may have programmed into a host computer.
: ~
zOOZ3a)9 Referring now to Fig~ 12, there is shown in block diagram ¦ form an example of the motor control section MS of the ¦ illustrated embodiment, comprising a digital subsystem which receives data from the microprocessor MP and from the motor shaft encoder and is designed to be a real time proportional integral, derivative (PID) controller. The microprocessor write data to the PID controller to establish exceleration rates, velocity, position, error limits, system gain, etc., of the associated motor, either the spindle motor 29, the propeller motor 66, or the carriage motor 72. It will be understood that such a typical motor control section as here described is provided for each of these three motors. The shaft encoder information (sine~cosine/index signals) generate feedback data to the PID controller as the motor velocity and position. The output of the PID controller is a pulse width modulated (PWM) signal which varies from 0 to 100% "ON" to the motor driver, full ON or 100% PWM corresponding to the max speed and/or torque of the DC motor system. PID controllers calculate what encoder signals should be, based on command data from the microprocessor MP and the specialized filter parameters inherent to this type control. Deviations between actual (encoder) and calculated (command) data are monitored to see if they exceed programmed limits. If these limits are exceeded, an error signal is generated to the microprocessor MP
for further action. For example, if the motor shaft is locked and the microprocessor MP requests a speed of 100 rpm, the PID
controller will see a speed error as the shaft is not turning.
The microprocessor MP will respond ~o this error by cancelling the speed command and alerting the operator to a problem with this motor. A level translator and FET driver section, indicated at LT, is provided to convert the PID pulse width ~ Z~OZ3~?9 modulated signal to a power signal of the same duty cycle which will drive the FET's. The current sense assures that neither motor nor FET's will be over-currented and thus damaged. This also provides for torque control of the motor.
Fig. 13 shows in block diagram form a typical Digital to Analog convertor (DAC) section such as the sections indicated at D/A in Fig. 11. The Digital to Analog converter DAC accepts digital information form the microprocessor MP and converts to an analog signal. This particular DAC is an 8 bit;0-5vdc device. This means that the resolution of the output is 1 in 255 or .0196V per bit. Mid scale would be 128 or 128 x .0196 e~ual 2.5 vdc. This analog signal controls a Pulse Width Modulator (PWM): 0 vdc-0~ duty cycle, 5vdc e~ual 100% duty cycle. Consequently, the microprocessor MP may control the Pulse Width Modulator duty cycle to the doff motor 39. In this case, the current is controlled by the PWM. If 50% of the motor torque is required to seat the package tube holder 17, the microprocessor will command 1~8 to the DAC in the direction so that the plunger moves out toward the package tube. To retract the tube holder, the microprocessor will command 60% torque in the opposite direction. Direction is controlled by the microprocessor via the relay.
To summarize the, sensed signals and the control signals for the winder control system include the following:
SENSED "SIGNALS"
Load Cells , I
0.5V from Bail Roller represents 0-53 lbs. force (to A/D) 0.5V from Tensiometer represents 0-125 grams (to A/D) ~ Z002309 Other 0.5VDC represents 0-25 ma in Tensioner - This assures that Tensioner is electrically functional (to A/D).
0-5VDC represents 0-full current in the doff motor - this allows the microprocessor to assure that the doff motor is ~
functional and to e~tablish the value of the motor Torque !
(current) (to A/D) All system power is monitored to be sure that voltages are within specification: +160vdc, +5vdc, +15vdc, 34vdc.
Stop Motion A digital level tells the microprocessor if yarn is moving or not. This allows the MP to sense a broken yarn strand during the winding process.
: CONTROL "SIGNALS"
To Spindle, Propeller & Overfeed 1) Acceleration 2) Velocity 3) Max. position error 4) proportional gain 5) derivative gain 6) integral gain 6 limit Carriage Motor 1) all of above 2) position Tension 1) digital value to establish tension level (D/A) DoffMotor . _ .
1) Digital values toestablish Doff~motor torque and direction (D/A) A summary of the control scheme provided by the winderl control system is as follows: ¦
~I Z~?oz3l?9 WINDER CONTROL SYSTEM SUMMARY
~ A) Spindle motor 29, propeller motor 66, and overfeed or ; carriage motor 72 parameters are derived from operator input and factory settings.
B) Carriage position of carriage 40 is determined by the Bail roller load cell 48. The pressure setpoint is derived from operator input. Whenever the Bail roller load cell 48 1 exceeds this setpoint, the carriage 40 is commanded to a !
new, lower position. The magnitude of the correction is dependent on the magnitude of the load cell signal over the .
setpoint.
C) Two levels of tension control are available.
1) The tension set point is established by operator input. The MP uses the current feedback as a failsafe.
2) The tension setpoint is established by the operator. The MP sets a value to the tensioner which corresponds to this tension during a static condition. However, when the winder begins to run, the MP reads the Tensiometer load cell 90 and compares this value to the command value. This allows the system to be run as fast as the inlet tension will allow - as the tensioner value could be reduced to OVDC and the delivered tension to the winder would be a summation of supply (inlet) tension, friction and windage.
D) The Doff motor 39 is a torque (current~ controlled device.
To assure that the package tube 17 is firmly held, the MP
will command a level of torque which corresponds to a certain axial force on the tube. The MP then monitors the ¦
current to see when this level is attained. This assures I
Z~OZ3~ 1 that the package is firmly seated between the two tube holders and that the current can be lowered to a holding value for running. This also allows the MP to select torque values such that the unseating force is always greater than the seating. Thus, a yarn package should never become stuck.
E~ Package, yardage, pitch, yarn speed are derived mathematlcally yds = ~ circ2 + (legth) / 36 X Turns pitch = 2 sPi prope er rpm yarn speeds = circ x rpm = yds per minute F) Outside diameter of the package is determined by knowing the position of the Bail roller 46. This is accomplished by using the shaft encoder on the carriage motor 72 in conjunction with the PID controller. Resolution is approximately .0000167 inches per pulse of position. This allows the MP to calculate circumference.
lS A typical load cell circuit, for use either with the load cell 4~ associated with the bail roller 46, or the load cell 90 associated with the tensiometer 80 is shown in Fig. 10.
The upper half of the circuit shown in Fig. 10 is simply power suppl~ Both supplies are designed to track so as to minimize system error due to un-symmetrical power supplies.
Typical load cells sensitivities ar~ 2MV/V. Consequently, for a 10V supply (+5; -5) the full scale Load cell signal will be 20MV. This same signal could be provided by a 40 MV drift of one of the power supplies.
Z~Oz31~ ~
The load cell bridge, indicated at LCB, is excited by a i +5V; -5V power supply for a total of 10 VOlts. This also makes the signal lines reference to OVDC - or 1/2 bridge voltage.
This makes for an easy amplifier design which does not require level shifting. The bridge is zeroed by the resistor network across the bridge of 5.lK, lK values.
The first operational amplifier Al has a gain of about 24 1 and a very low frequency response due to the l mfd feedback capacitor. This is to attenuate high frequency signals which are primarily due to vibration.
The second operational amplifier A2 is the full scale !
stage~ System gain is set by the 50K feedback pot. For the ¦
bail roller load cell 48, OVDC output represents the weight of the bail roller 46 and bearings - as these effects are I
purposely zeroed out. A full scale of 5 VDC represents about j 53 pounds of force on the bail roller 46.
The two LM339 comparators Cl and C2 are used as error !
detectors. These devices are designed so that if the load cell goes negative by more than .6V or goes beyond +5VDC the microprocessor MP is sent an error signal. The MP can then stop the process and alert the operator.
The present invention relates in general to the winding of textiles yarns, filaments, or the like of natural, man made or synthetic materials, all referred to herein as "yarns", and more particularly to high speed precision winding of yarn packages on a precision winder machine having a propeller structure for guiding the yarn back and forth between the ends of the package during the winding process, and incorporating sensors and controls for regulating the propeller drive, the spindle drive for the yarn package handle, and down pressure drive to produce a highly uniform package which is free of ribboning effects once injecting to dying processes and the like.
Before the days of the continuous filament extrusion, texturizing, and similar high speed methods of yarn production, traditional mechanisms for producing the traversing mechanism necessary for laying yarn on a package included a grooved scroll with either engaged the yarn directly or drove a yarn guide so as to cause it to carry out a reciprocatory traversing motion. Those mechanisms were limited as to there speed of operation and the uniformity of packages produced by such mechanisms.
Upon the more recent development of high speed yarn production methods, the demand was emphasized for winders having very much higher speeds of operation. One form of traversing mechanism proposed for such high speed winders included slot like yarn guides unted on closely spaced driving members moving in opposite directions across the traverse so that the yarn was carried from one end of the traverse to the other by one yarn guide and was then Z0023~)9 transferred to another yarn guide so as to be carried back in opposite direction. This avoided inertial problems which were incident to use of a single yarn guide which moved in one direction and then the other, but created problems of yarn transfer from one guide to another.
While driving arrangements involving two guide members, one moving in one direction and the other in the opposite direction, have taken forms such as belt or chain drives for the yarn guides moving them in a straight line across the traverse, the use of rotary discs or blades which act as yarn guides moving across the traverse along and arc of a circle having come into wide use. These rotary discs or blade type yarn guides move in a continuous path with no abrupt changes in velocity or direction, so that the only inertia concerns presented are in connection with the inertia of the yarn itself at each reversal point. Care had to be taken, however, to maintain close control of the yarn as it is transferred from one yarn guiding blade or disc to another, in a manner which would avoid nipping action on yarn which may have an adverse effect on its quality. However full control over the yarn ~during transfer from one driving member to another is essential~
One of the widely used types of cross winding systems ~ employed in the textile industry is of the type disclosed in ~ 25 U.S. patent 3,823,886 granted to Maschinenfabrik Scharer, v which involve first and second yarn guides of a propeller or blade type rotatable and opposite directions about respective axes of rotation which are offset f~om each other, associated with respective substantially circular shaped guide members provided for each of the yarn guides, centered on the respective axes of rotation of the yarn guides so that the 20QZ30g guide tracts intersect each other at a pair of diametrically opposite points for overlapping of the thread guides at these points. Other yarn traversing apparatus of this general type ~~ involving rotary blade or propeller type guides are disclosed in U.S. patent no. 4,561,603 of December 31, 1985, no.
4,585,181 of April 29, 1986 and no. 4,6~6,983 of March 3, 1987 all granted to Barmag Barmer Maschinenfabrik A.G.
It has been customary, heretofore, for example in the Scherer winder machines, to attempt control of the winding in an effort to achieve uniformity throughout the wound packages by regulating a drive motor which drives the yarn guide blades or propellers and the package spindle. However, it has been found that this arrangement does not provide sufficient control of the various perimeters affecting uniformity of the density of the yarn package to achieve the desired extent of yarn package uniformity wherein the packages are free of ribboning when subjected to the dying process, and which would have such uniformity all the way to the bottom of the package so that the innermost layers of yarn do not need to be discarded. I have 20 ~ found, however, that by providing separate drive motors providing separately controlled drive systems for the spindle drive, the propeller drive, and a down pressure drive, thus providing three independent motor systems that can be separately controlled, one can properly set and regulate the pitch and the tension during winding of the package so as to maintain the desirable yarn density or tension throughout the whole package, and ensures freedom from development of ribboning patterns during pack~ge winding, which are detrimental to during the dying process.
20~Z3~g BRIEF DESCRIPTION OF THE_PIGURES
FIGURE 1 is a front elevational view of the yarn winding apparatus of the present invention, showing the portions of the frame associated with the components related to production of the yarn package, with lower portions of the frame not shown;
FIGURE 2 is a vertical section view of the apparatus, taken along the line 2-2 of Fig. l;
FIGURE 3 is a horizontal section view showing the underside of the moveable platform supporting the yarn guide propeller members and the drive therefor, taken along the line 3-3 of Fig. 2;
~ IGURE 4 is a top plan view of the propeller supporting platform, the yarn guide propellers and associated stationary guide mem~ers, and the bail roll and supports therefor;
FIGURE 5 is a vertical section view showing the bail roll and the yarn guide propeller drive mechanism and drive motor therefor, taken along the line 5-5 of Fig. 4;
FIGURE 6 is an exploded perspective view of the yarn guide propeller mechanism and supporting platform therefor and the I ! ' 201' `associated drive components;
,¦ FIGURE 7 is a fragmentary front view showing one form of yarn tensioner mechanism for the apparatus;
FIGURUE 8 is a side elevational view of the yarn tensioner;
FIGURE 9 is a horizontal section view taken along line 9-9 of Fig. 8;
FIGURE 10 is a schematic diagram of a typical load cell circuit for processing load cell ~ignals from a load cell associated with one of the sensed conditions in the winder, of the present invention, such as the bail roller load cell;
FIGURE 11 is a block diagram of the control system for the winder;
FIGURE 12 is a block diagram of a typical proportional, integral derivative (PID) motor control section for the winder control system; and FIGUURE 13 is a block fdiagram of a typical Digital to Analog Converter (DAC) section for the winder control system.
DETAILED DESCRIPTION OF A PREFERRE~ EMBODIMENT
.
10Referring to the drawings, wherein like reference - characters designated corresponding parts throughout the several figures, and particularly to Figs. 1 and 2, the high speed precision yarn winding apparatus of the present invention is indicated generally by the reference character 10 and comprises, in one preferred embodiment, a supporting frame 11 formed basically of angle iron members, including vertical main frame members 12, and horizonal frame members 13 ~ extending between and fixed to the vertical frame members 12.
Il Near the upper end portion of the main frame 11 is a yarn 20l package support assembly, indicated at generally at 14, `~ ' comprising a driven tube-engaging head subassembly 15 and an axially moveable companion head assembly 16 providing a live center for the yarn package tube 17 on which the yarn package 18 is to be wound. The head assemblies 15 and 16 each include a truncated conical head 19 and 20, respectively adapted to ~;partially interfit into the hollow center of the yarn package tube 17 and embraced the tube ,17 and yarn package 18 therebetween. The driven head 19 is fixed on a cylindrical spindle 21 journaled in the bearing block 22 fixed on a support arm 23 carried by the stationary main frame 11, for example by 200Z3~;19 spacer members 24 and bolts 25 connected to upright main framemembers 12 at one side of the main frame or to horizontal cross members extending therebetween. The end of the spindle 21 opposite the drive head 19 projects from the bearing block 22 and carries a pulley 26 driven by a belt 27 trained about the pulley 26 and about an output drive pulley 28 on the output shaft of the spindle drive motor 29. The spindle drive motor 29 may be conveniently supported also from the support arm 23.
The opposite or live center head 20 forms a removable holder for the yarn package tube 17 and is rotatably supported on a retractable and returnable spindle member 30, for example by roller bearings, rotatably supporting a truncated conical tube holder head 20 on the spindle member 30. The spindle member 30 is supported for axially movement between an lS extended, tube holding position as illustrated in Fig. 1, to a retracted tube removal position in a linear slide sleeve 31 housed in a supporting block 32 carried by another support arm 33 extending from the main frame 11, the spindle member 30 having an internal nut 34 threaded on a screw shaft 35 which 20, projects from the support block 32 on the si~e opposite the tube holder head 20. A pulley 36 is provided on the screw , shaft 35, driven through a belt 37 trained about a drive pulley 38 on the output shaft of a DC motor 39 operating in a constant torque mode and forming a doff motor for retracting or doffing a fully wound package 18 and its associated tube 17 when the package is fully wound. Energizing of the doff motor 39 effects rotation of the screw shaft 35 through the system of pulleys 38, 36 and belt 37, causing the screw 34 carried by the spindle member 30 to be driven by the threads on the screw shaft 35 in a airection to axially retract the spindle member 30 and tube holder head 20 through a travel of about 1 1/2 l ZOQZ309 inches, withdrawing the live center tube holder head 2~ from holding relation to the tube, permitting tube 17 and package 18 : to be doffed or withdrawn. A new empty yarn package tube 17 is replaced by fitting one end of the new empty tube 17 on the companion tube holder head 19 and activating the doff motor 39 to rotate the screw shaft 35 and axially drive the spindle member 30 in tube holder head 20 through a return stroke to the tube holding position shown in Fig. 1.
A movable subframe 40 is guided for vertical up and down movement in the main frame 11 between the vertical frame members 12, for example, by vertical guide rods 41 sliding in guide sleeves or brackets 42 fixed to appropriate portions of the main frame 11. The vertically movable subframe 40 comprises a bail roll and yarn guide propeller supporting upper 15¦ platform 43 at the uppermost end of the subframe 40, connected by vertical subframe members 44 with a bottom horizontal subframe member 45 to form a unitary movable subframe which can be raised and lowered as required as the yarn package 18 ¦ is being formed on the tube 17. The upper platform 43 supports a bail roll 46 supported in bearing brackets 47 at its opposite ends, at least one of which is carried on a load cell 48 . mounted on the uppermost surface of the platform 43 and disposed between the upwardly facing surface of the platform 43 and the bottom surfaces of the bail roll bearing brackets 47.
The mounting of the bail roll 46 on load cell 48 and the processing circuitry associated with the output signals from . I these load cells provides a down pressure sensing and control system, as later described in srea4r detail, to maintain proper down pressure properties responsive to pressure of the package on the bail roll and causing the platform 43 to be raised and lowered relative to the spindle axis to maintain proper package ~ Z0023~9 winding. The load cell 48 may be of the kind marketed byTransducer Techniques, Inc. of Rancho, California, described as low profile load cells, which incorporate strain gauge transducers providing an output signal proportional to the load on a member, which in this case is the bail roll 46. This provides a highly accurate and reliable signal output indicative of the down pressure of the yarn package on the bail roll, by proving a beam structure or the like having suitable mounting surfaces for a plurality of electrical strain gauges and utilizing the transducive electrical strain gauges to measure the shear stresses caused by the applied loads. The transducive effect of a strain gauge allows for accurate translation between a given amount of stress imposed on a surface by a load and its electrical equivalent, resulting in an accurate stress measurement. Foil, semiconductor, or other types of strain gauges may be effectively used to provide such shear stress measurements. Typically, the strain gauges are connected into a Wheatstone bridge network to provide the correct output. The principals of the strain gauge employed may be similar to those disclosed in earlier U.S. patents 3,927,560 and 4,127,001, as typical examples.
Also mounted on the vertical translation platform 43 of the movable subframe 40 is a pair of yarn guide blades or propellers 50a, 50b rotating in opposite directions through appropriate paths immediately above the curved yarn guide bar 51 fixed to the vertical translation platform 43 and having a convexly curved working edge 52, spanning a yarn traversing zone of appropriate width between a~pair of end control guide rails 53, 54. As will be well understood by persons skilled in the relevant art, the yarn guide propeller blades 50a, 50b and the stationary yarn guide bar 51 and end control guide rails I ~OOZ30g 53, 54, form a yarn winding station whereby the uppermost yarn Iguiding propeller and blade 50a, as best shown in Fig. 4, i traverses the yarn, indicated at 55, from top to bottom (as l shown in Fig. 4) or from right to left as viewed in Fig. 1, along the length of the package 18 and, after transfer to the guide propeller or blade 50b while the yarn is captured against , outward disengaging movement from the blade system by the end control guide rail 54, at the lower or left and end of the ¦
field of traverse, the yarn 55 is traversed back again to the upper or right hand end where it is again transferred back to the yarn guide propeller or blade 50a.
The dri~ing mechanism for the yarn guide propellers or blades 50a, 50b comprises a propeller shaft 56 supported for rotation in a vertical axis, which is fixed to the uppermost blade or propeller 50a and extends through a center opening in the lower blade or propeller 50b. The lower blade or propeller 50b is fixed to an upper pulley member 57, in the form of a downwardly opening cup or hollow cylinder, having a center j collar portion 57a encircled by roller bearing assemblies 58 whose outer portions are supported in an extension 59a of a bearing housing 59, the lower portion of which supports the outer portion of the roller bearing assembly 60 encircling and mounted on the center post or spindle portion 6la of the lower pulley 61. The bearing assemblies 58, 60 are captured in the bearing housing 59 by retainer rings 62 and the center opening ; 57b in the center collar portion 57a of the upper pulley 57 is of a sufficiently large diameter to accommodate rotation of the upper pulley 57 about an eccentric axis A2 located eccentrically relative to the vertical axis A1 which extends through the centers of the propeller shaft 56 and the lower pulley 61. The lower end of the propeller shaft 56 driving the upper propeller or blade 50a is fixed against relative rotation in the socket formation in the spindle or center post portion 61a of the lower pulley 61, and the pulley 61 is coupled by a locking ring 63 and a lock nut 64 to the drive S sha~t 65 of the propeller or blade drive motor 66. The motor 66 is mounted by a suitable hanger bracket 67 depending from the platform 43, with its vertical legs spaced outwardly from the pe~ipheries of the eccentrically related upper and lower pulleys 57, 61. The outer surfaces of the cylindrical pulleys 57, 58 are provided with teeth interfitted with tooth formations on the toothed endless belt 68 which is trained about the lower pulley 61, driven directly from the output shaft of the propeller drive motor 66, the belt system being arranged to effect rotary drive of the upper pulley 57 in a reverse direction. This is accomplished by training the belt ; 68 about an idler roll or pair of idler pulleys on an interconnecting shaft, shown at 69, journaled for rotation in a mounting block 70 and protruding from both ends thereof providing end portions about which the belt is wrapped, with the upper portion of the belt in a hori~ontal path immediately above the idler roll 69 extending about and interfitting with the teeth on the outer periphery of the upper pulley 57.
The entire subframe assembly 40 is movable upwardly and downwardly responsive to down pressure signals derived from the bail roll 46 and load cells 48, and the associated circuitry, activating a down pressure control motor or platform positioning motor 72 mounted on the main frame 11. Vertical movement of the subframe 40 and ~the vertical translation platform 43 is achieved, in a preferred example, by an Acme screw and nut assembly, as indicated by the vertical lag screw 73 journaled for rotation at its lower end in a bearing bracket . I
.: .
20023~
i, 74 carried by a horizontal stationary beam 75 fixed to and forming part of the main frame 11 and extending through the nut 76 carried by the lower cross frame member 45 of the vertically movable subframe 40. The Acme screw 73 is driven by a pulley 77 fixed against relative rotation on the dxive screw 73, as by keying the pulley to the drive screw, driven by a belt 78 trained about the pulley 77 and about drive pulley 79 fixed to the output shaft of the down pressure control motor It will be apparent fro~ the above description that this apparatus, therefore, provides three motors providing separate control of three principal factors determining the precision winding of the yarn package so as to provide the desired level of uniformity and absence of ribboning. First the down pressure control motor 72 controls the vertical position of the : vertical translation platform 43 carrying the yarn guide propellers or blades 50a, 50b and associated yarn guide structure, as well as carrying the bail roll 46 and its associated load cells 48. Secondly, the propeller drive motor 66 carried by the vertically movable platform 43 determines the speed of drive of the yarn guide propellers or blades 50a, . 50b and thus the speed of traverse of the yarn between the opposite ends of the package being formed. Thirdly, the spindle drive motor 29 carried by the stationary main frame 11 drives the spindle 21 and tube holder head 19 to rotate the I yarn package tube 17 and thus determine the speed of winding of yarn onto the package.
Control of the spindle drive motor 29 is derived from the yarn tensioner assembly, indicated generally at 80, to sense the tension of incoming yarn leading to the winder and provide load cell output signals which are processed to effect yarn Z~OZ3~ .
drive so as to maintain a predetermined yarn tension and preserve uniformity of winding and tracking of the yarn on the package. Alternatively, the owner has the option of having a constant speed drive for the spindle motor 29 instead of a control system which is responsive to sensing of incoming yarn tension.
Referring particularly to Figures 7-9/ there is shown in those figures one preferred embodiment of the yarn tensioner assembly 80 which/ in general may be described as forming a pair of yarn guides 81, 82 which are vertically spaced along the yarn feed path 83, with a sensor arm 84 interposed therebetween bearing against the yarn and deflecting it slightly out of the yarn path defined by the eyes in the yarn guides 81, 82. In this yarn tensioner, the guides 81, 82 are formed as a pair of parallel legs bent from a plate to form a U-shaped bracket 85 having a transverse base portion 86 and ~ outwardly bent legs 86a, 86d defining the guides 81, 82. The I legs 86a, 86b include a projecting finger portion 86c having an inclined surface 86b forming one side of a truncated triangular hook portion of the finger which leads through a throat formation 86e into a generally circular or rounded eye . formation 86f which receives the yarn and defines the yarn path 83 between the two guides 81, 82. The eye formation 86f should be deep enough to prevent yarn escape while running at high speeds, and the inclined surface 86d of the finger portion 86c is so positioned and shaped that the yarn will self thread from s this surface into the eye formation 86f. The transverse base portion 86 is provided with a slot ~6g at its center elongated widthwise of the base portion 86 and receiving the sensor arm 84, which is in the form of a bent rod, for example a ceramic flame coated stainless steel rod having an outer diameter of Il z00~30~
about l/8th inch, extending from a block 87 having bearings 88 pivGting the block on a pivot shaft 88a extending between stationary support arms 89. The block 87 includes a protruding finger ~ormation ~7a bearing against a load cell 90 supported by mounting standoffs or a block from the support plate which also supports the arms or yoke 89 mounting the pivot shaft 88a thereto as well as supporting the U-shaped bracket 85 forming the guides Bl, 82. In practice, this support plate, indicated ; at 9l, which must also be provided with a slot for appropriate movement of the yarn contacting feeler 84, may be bent in a U-shaped as shown in the drawings to support a printed circuit board amplifier and carrier plate 92 for amplifying signals from the load cell 90.
A preferred example of a winder control system for the lS high speed precision winder of the present invention is indicated in block diagram form in Figure ll, wherein the control system is shown as including a motor section MS, a digital to analog section indicated at D/A, and an analog to digital section, indicated at A/D, which are connected to a microprocessor indicated at MP. To describe the overall operation, the microprocessor MP writes command data to the digital proportional, Integral, Derivative (PID) control subsystem. This command data determines the speed, exceleration, and servo response characteristics of each of the three motors, namely the spindle drive motor 29, the propeller or blade drive motor 66, and the carriage positioning or down pressure control motor 72. The resolution of each controller is one in 4,294,967,296 or 32 bits. Consequently, highly precise speed ratios between the spindle motor and the propeller may be achieved. This control technique also allows for the DC motors 29, 66, and 72 to be operated in a position ZOOZ3~9 mode. This is advantageous for the carriage system 40controlled by the carriage motor 72, as the microprocessor is positioning the carriage 40 and platform 43 in response to pressure on the yarn package 18 as measured by the load cell or load cells 48 associated with the bail roll 46. The circuit associated with the load cell 48, to be later described, sends a signal to the microprocessor MP proportional to the pressure on the package. If this value is greater than the programed set point, the microprocessor MP lowers the carriage position of carriage 40 and platform 43 until the setpoint value is received from the load cell 48. The carriage motor 72 is then commanded to halt.
The Digital to Analog subsystem D/A includes two converters, to which the microprocessor MP writes data to establish setpoints for tensioner current to the tensioner assembly 80 and doff motor current to the doff motor 39. The ; D/A output controls the duty cycle of a pulse width modulated (PWM) power stage. This duty cycle may be varied from 0 to 100%. Consequently, the tensioner current and doff motor current maybe varied from 0 to 100~. The tension or current is directly proportional to the amplified yarn tension developed by an electromagnetic tensioning device. The doff motor current for the motor 39 is directly proportional to the force exerted on the dye tube 17 by the live center system (the live center tube holder head 20).
Referring to the Analog to Digital system A/D, the microprocessor MP monitors a variety of analog values in the winder system to maintain system parameters, efficiency, and diagnostics capability. The three system parameters monitored are (1~ the down pressure load cell 48 to establish current pressures, (2) the tensioner current which establishes that the 2~023v9 ii tensioner is functional and that the value is sufficient for the tensiometer to maintain control and (3) the tensiometer load cell 90 which transmits the current yarn tension to the microprocessor. The other five A/D inputs to the Analog to Digital subsystem A/D are used to monitor system power supplies and motor currents for failsafe operation and diagnostic functions.
Also shown in the block diagram of Fig. 11 as part of the overall winder control system is a stop motion system indicated at SM, providing a means to determine if the yarn from the supply package is broken. This stop motion system may be an optical stop motion system of the type presently commercially available which generates a signal applied to the microprocessor as an interrupt signal. This interrupt signal forces the microprocessor to stop current program execution and to immediately implement routines established by the software which appropriately stop the winding process and signal for operator help.
Also, as an additional communication facility to communicate with operators and plant personnel, the microprocessor in the illustrated embodiment is connected to a keyboard and display, indicated at KB/D in Fig. 11, and through a communication link CL through a RS 485 serial transmission line to a host computer. The onboard communications provided to the display and keyboard section KB/D allow the microprocessor MP to relate the machine status to the operator and to receive operator request for activity.
The communications link line allo~s the microprocessor to acquire all operations data, such as yarn speed, max yardage, max diameter, pitch, down pressure, etc. that plant personnel may have programmed into a host computer.
: ~
zOOZ3a)9 Referring now to Fig~ 12, there is shown in block diagram ¦ form an example of the motor control section MS of the ¦ illustrated embodiment, comprising a digital subsystem which receives data from the microprocessor MP and from the motor shaft encoder and is designed to be a real time proportional integral, derivative (PID) controller. The microprocessor write data to the PID controller to establish exceleration rates, velocity, position, error limits, system gain, etc., of the associated motor, either the spindle motor 29, the propeller motor 66, or the carriage motor 72. It will be understood that such a typical motor control section as here described is provided for each of these three motors. The shaft encoder information (sine~cosine/index signals) generate feedback data to the PID controller as the motor velocity and position. The output of the PID controller is a pulse width modulated (PWM) signal which varies from 0 to 100% "ON" to the motor driver, full ON or 100% PWM corresponding to the max speed and/or torque of the DC motor system. PID controllers calculate what encoder signals should be, based on command data from the microprocessor MP and the specialized filter parameters inherent to this type control. Deviations between actual (encoder) and calculated (command) data are monitored to see if they exceed programmed limits. If these limits are exceeded, an error signal is generated to the microprocessor MP
for further action. For example, if the motor shaft is locked and the microprocessor MP requests a speed of 100 rpm, the PID
controller will see a speed error as the shaft is not turning.
The microprocessor MP will respond ~o this error by cancelling the speed command and alerting the operator to a problem with this motor. A level translator and FET driver section, indicated at LT, is provided to convert the PID pulse width ~ Z~OZ3~?9 modulated signal to a power signal of the same duty cycle which will drive the FET's. The current sense assures that neither motor nor FET's will be over-currented and thus damaged. This also provides for torque control of the motor.
Fig. 13 shows in block diagram form a typical Digital to Analog convertor (DAC) section such as the sections indicated at D/A in Fig. 11. The Digital to Analog converter DAC accepts digital information form the microprocessor MP and converts to an analog signal. This particular DAC is an 8 bit;0-5vdc device. This means that the resolution of the output is 1 in 255 or .0196V per bit. Mid scale would be 128 or 128 x .0196 e~ual 2.5 vdc. This analog signal controls a Pulse Width Modulator (PWM): 0 vdc-0~ duty cycle, 5vdc e~ual 100% duty cycle. Consequently, the microprocessor MP may control the Pulse Width Modulator duty cycle to the doff motor 39. In this case, the current is controlled by the PWM. If 50% of the motor torque is required to seat the package tube holder 17, the microprocessor will command 1~8 to the DAC in the direction so that the plunger moves out toward the package tube. To retract the tube holder, the microprocessor will command 60% torque in the opposite direction. Direction is controlled by the microprocessor via the relay.
To summarize the, sensed signals and the control signals for the winder control system include the following:
SENSED "SIGNALS"
Load Cells , I
0.5V from Bail Roller represents 0-53 lbs. force (to A/D) 0.5V from Tensiometer represents 0-125 grams (to A/D) ~ Z002309 Other 0.5VDC represents 0-25 ma in Tensioner - This assures that Tensioner is electrically functional (to A/D).
0-5VDC represents 0-full current in the doff motor - this allows the microprocessor to assure that the doff motor is ~
functional and to e~tablish the value of the motor Torque !
(current) (to A/D) All system power is monitored to be sure that voltages are within specification: +160vdc, +5vdc, +15vdc, 34vdc.
Stop Motion A digital level tells the microprocessor if yarn is moving or not. This allows the MP to sense a broken yarn strand during the winding process.
: CONTROL "SIGNALS"
To Spindle, Propeller & Overfeed 1) Acceleration 2) Velocity 3) Max. position error 4) proportional gain 5) derivative gain 6) integral gain 6 limit Carriage Motor 1) all of above 2) position Tension 1) digital value to establish tension level (D/A) DoffMotor . _ .
1) Digital values toestablish Doff~motor torque and direction (D/A) A summary of the control scheme provided by the winderl control system is as follows: ¦
~I Z~?oz3l?9 WINDER CONTROL SYSTEM SUMMARY
~ A) Spindle motor 29, propeller motor 66, and overfeed or ; carriage motor 72 parameters are derived from operator input and factory settings.
B) Carriage position of carriage 40 is determined by the Bail roller load cell 48. The pressure setpoint is derived from operator input. Whenever the Bail roller load cell 48 1 exceeds this setpoint, the carriage 40 is commanded to a !
new, lower position. The magnitude of the correction is dependent on the magnitude of the load cell signal over the .
setpoint.
C) Two levels of tension control are available.
1) The tension set point is established by operator input. The MP uses the current feedback as a failsafe.
2) The tension setpoint is established by the operator. The MP sets a value to the tensioner which corresponds to this tension during a static condition. However, when the winder begins to run, the MP reads the Tensiometer load cell 90 and compares this value to the command value. This allows the system to be run as fast as the inlet tension will allow - as the tensioner value could be reduced to OVDC and the delivered tension to the winder would be a summation of supply (inlet) tension, friction and windage.
D) The Doff motor 39 is a torque (current~ controlled device.
To assure that the package tube 17 is firmly held, the MP
will command a level of torque which corresponds to a certain axial force on the tube. The MP then monitors the ¦
current to see when this level is attained. This assures I
Z~OZ3~ 1 that the package is firmly seated between the two tube holders and that the current can be lowered to a holding value for running. This also allows the MP to select torque values such that the unseating force is always greater than the seating. Thus, a yarn package should never become stuck.
E~ Package, yardage, pitch, yarn speed are derived mathematlcally yds = ~ circ2 + (legth) / 36 X Turns pitch = 2 sPi prope er rpm yarn speeds = circ x rpm = yds per minute F) Outside diameter of the package is determined by knowing the position of the Bail roller 46. This is accomplished by using the shaft encoder on the carriage motor 72 in conjunction with the PID controller. Resolution is approximately .0000167 inches per pulse of position. This allows the MP to calculate circumference.
lS A typical load cell circuit, for use either with the load cell 4~ associated with the bail roller 46, or the load cell 90 associated with the tensiometer 80 is shown in Fig. 10.
The upper half of the circuit shown in Fig. 10 is simply power suppl~ Both supplies are designed to track so as to minimize system error due to un-symmetrical power supplies.
Typical load cells sensitivities ar~ 2MV/V. Consequently, for a 10V supply (+5; -5) the full scale Load cell signal will be 20MV. This same signal could be provided by a 40 MV drift of one of the power supplies.
Z~Oz31~ ~
The load cell bridge, indicated at LCB, is excited by a i +5V; -5V power supply for a total of 10 VOlts. This also makes the signal lines reference to OVDC - or 1/2 bridge voltage.
This makes for an easy amplifier design which does not require level shifting. The bridge is zeroed by the resistor network across the bridge of 5.lK, lK values.
The first operational amplifier Al has a gain of about 24 1 and a very low frequency response due to the l mfd feedback capacitor. This is to attenuate high frequency signals which are primarily due to vibration.
The second operational amplifier A2 is the full scale !
stage~ System gain is set by the 50K feedback pot. For the ¦
bail roller load cell 48, OVDC output represents the weight of the bail roller 46 and bearings - as these effects are I
purposely zeroed out. A full scale of 5 VDC represents about j 53 pounds of force on the bail roller 46.
The two LM339 comparators Cl and C2 are used as error !
detectors. These devices are designed so that if the load cell goes negative by more than .6V or goes beyond +5VDC the microprocessor MP is sent an error signal. The MP can then stop the process and alert the operator.
Claims (30)
1. In a high-speed precision winder for winding a running yarn onto a tube to form a cross wound yarn package, including spindle means for rotating the tube about a spindle axis, yarn traversing means for guiding running yarn received along an infeed path back and forth across a traverse zone adjacent said tube to form the cross wound package, a bail roller disposed in rolling contact with the peripheral surface of the yarn package being wound, and tensioner means for varying tension of the infeed yarn approaching said traversing means; the improvement comprising a control system for continuously regulating operation of the winder during formation of the package comprising first, second and third separate variable speed drive motors and respective associated motor control circuits forming a spindle drive, a traversing means drive, and a down pressure drive, the three drive motors and associated motor control circuits providing three independent motor systems which are separately controllable, means coupling the first drive motor with the spindle for rotating the package tube about the spindle axis to wind the yarn thereon, means connecting the second drive motor with the traversing means for variably driving the traversing means in accordance with the speed of the second drive motor, said down pressure drive including down pressure adjusting means for positioning said bail roller and transversing means relative to the spindle axis, and means coupling said third drive motor with said adjusting means for regulating the position of said bail roller and traversing means.
2. In a high-speed precision winder for winding a running yarn onto a tube to form a cross wound yarn package, including spindle means for rotating the tube about a spindle axis, yarn traversing means for guiding running yarn received along an infeed path back and forth across a traverse zone adjacent said tube to form the cross wound package, a bail roller disposed in rolling contact with the peripheral surface of the yarn package being wound, and tensioner means for varying tension of the infeed yarn approaching said traversing means; the improvement comprising a control system for continuously regulating operation of the winder during formation of the package comprising first, second and third separate variable speed drive motors and respective associated motor control circuits forming a spindle drive, a traversing means drive, and a down pressure drive, the three drive motors and associated motor control circuits providing three independent motor systems which are separately controllable, means coupling the first drive motor with the spindle for rotating the package tube about the spindle axis to wind the yarn thereon, means connecting the second drive motor with the traversing means for variably driving the traversing means in accordance with the speed of the second drive motor, said down pressure drive including down pressure adjusting means for positioning said bail roller and transversing means relative to the spindle axis, means coupling said third drive motor with said adjusting means to position the same, means for continuously sensing package down pressure on the bail roller during winding of the package, and means responsive to sensing of the down pressure for activating the motor control circuit associated with said third drive motor to vary the position of said bail roller and traversing means relative to the tube being driven by said spindle means.
3. In a high-speed precision winder for winding a running yarn onto a tube to form a cross wound yarn package, including spindle means for rotating the tube about a spindle axis, yarn traversing means for guiding running yarn received along an infeed path back and forth across a traverse zone adjacent said tube to form the cross wound package, a bail roller disposed in rolling contact with the peripheral surface of the yarn package being wound, and tensioner means for varying tension of the infeed yarn approaching said traversing means; the improvement comprising a control system for continuously regulating operation of the winder during formation of the package comprising first, second and third separate variable speed drive motors and respective associated motor control circuits forming a spindle drive, a traversing means drive, and a down pressure drive, the three drive motors and associated motor control circuits providing three independent motor systems which are separately controllable, means coupling the first drive motor with the spindle for rotating the package tube about the spindle axis to wind the yarn thereon, means connecting the second drive motor with the traversing means for variably driving the traversing means in accordance with the speed of the second drive motor, said down pressure drive including down pressure adjusting means for positioning said bail roller and transversing means relative to the spindle axis, means coupling said third drive motor with said adjusting means to position the same, means for continuously sensing package down pressure on the bail roller during winding of the package for producing down pressure status signals, means for continuously sensing yarn tension at said tensioner means for providing tension status signals, and regulating means responsive to a predetermined set of processing conditions and to said status signals to continuously regulate activation, acceleration, speed and position of said three motors to secure selected yarn density and tension conditions throughout winding of a package.
4. A high-speed precision yarn winder as defined in claim 1, including a main frame providing a stationary support for said spindle means, said down pressure adjusting means including a movable carriage forming a sub-frame movable toward and away from said spindle axis and supporting said bail roller and traversing means thereon, said third drive motor forming a carriage motor for moving said carriage and the bail roller and traversing means carried thereby toward and away from said spindle axis, and the motor control circuit associated with said carriage means to including means responsive to applied control signals to energize the carriage motor and vary the speed thereof in accordance with applied signals.
5. A high-speed precision yarn winder as defined in claim 2, including a main frame providing a stationary support for said spindle means, said down pressure adjusting means including a movable carriage forming a sub-frame movable toward and away from said spindle axis and supporting said bail roller and traversing means thereon, said third drive motor forming a carriage motor for moving said carriage and the bail roller and traversing means carried thereby toward and away from said spindle axis, and the motor control circuit associated with said carriage motor to including means responsive to applied control signals to energize the carriage motor and vary the speed thereof in accordance with applied signals.
6. A high-speed precision yarn winder as defined in claim 3, including a main frame providing a stationary support for said spindle means, said down pressure adjusting means including a movable carriage forming a sub-frame movable toward and away from said spindle axis and supporting said bail roller and traversing means thereon, said third drive motor forming a carriage motor for moving said carriage and the bail roller and traversing means carried thereby toward and away from said spindle axis, and the motor control circuit associated with said carriage motor to including means responsive to applied control signals to energize the carriage motor and vary the speed thereof in accordance with applied signals.
7. A high-speed precision yarn winder as defined in claim 4, wherein said traversing means comprises a pair of rotatable yarn guide blades forming a yarn traversing propeller assembly for guiding the yarn back and forth across the traverse zone to wind the yarn package on the tube, the yarn guide blades of said propeller assembly being rotatable in closely adjacent parallel propeller planes located below the spindle axis and rotatable about a propeller assembly axis projecting downwardly substantially perpendicular to the spindle axis, and said second drive motor forming a propeller motor located below said propeller planes and being rigidly mounted in suspended relation therebelow by supporting members extending from said carriage.
8. A high-speed precision yarn winder as defined in claim 5, wherein said traversing means comprises a pair of rotatable yarn guide blades forming a yarn propeller assembly for guiding the yarn back and forth across the traverse zone to wind the yarn package on the tube, the yarn guide blades of said propeller assembly being rotatable in closely adjacent parallel propeller planes located below the spindle axis and rotatable about a propeller assembly axis projecting downwardly substantially perpendicular to the spindle axis, and said second drive motor forming a propeller motor located below said propeller planes and being rigidly mounted in suspended relation there below by supporting members extending from said carriage.
9. A high-speed precision yarn winder as defined in claim 6, wherein said traversing means comprises a pair of rotatable yarn guide blades forming a yarn propeller assembly for guiding the yarn back and forth across the traverse zone to wind the yarn package on the tube, the yarn guide blades of said propeller assembly being rotatable in closely adjacent parallel planes located below the spindle axis and rotatable about a propeller assembly axis projecting downwardly substantially perpendicular to the spindle axis, and said second drive motor forming a propeller motor located below said propeller planes and being rigidly mounted in suspended relation therebelow by supporting members extending from said carriage.
10. A high-speed precision yarn winder as defined in claim 1, wherein support means are provided for rotatably supporting said bail roller including a load cell in the support structure for at least one end of said bail roller for responding to variations in pressure thereon and producing load cell output signals.
11. A high-speed precision yarn winder as defined in claim 2, wherein support means are provided for rotatably supporting said bail roller including a load cell forming parts of the support structure for at least one end of said bail roller for responding to variations in pressure thereon and producing load cell output signals, and said means for continuously sensing package down pressure including means responsive to said load cell output signals for generating activation and speed control signals for said third drive motor.
12. A high-speed precision yarn winder as defined in claim 3, wherein support means are provided for rotatably supporting said bail roller including a load cell forming part of the support structure for at least one end of said bail roller for responding to variations in pressure thereon and producing load cell output signals, and said means for continuously sensing package down pressure including means responsive to said load cell output signals applied to said regulating means for generating activation and speed control signals for said third drive motor.
13. A high-speed precision yarn winder as defined in claim 5, wherein support means are provided for rotatably supporting said bail roller including a load cell forming part of the support structure for at least one end of said bail roller for responding to variations in pressure thereon and producing load cell output signals, and said means for continuously sensing package down pressure including means responsive to said load cell output signals for generating activation and speed control signals for said third drive motor.
14. A high-speed precision yarn winder as defined in claim 1, including means for generating sensing signals continuously indicating variations in down pressure of said bail roller and variations in tension of yarn at said tensioner means, and microprocessor means responsive to input signals including said sensing signals and predetermined data for activating the motor control circuits associated with said three drive motors to regulate yarn winding so as to maintain selective yarn density and tension conditions throughout the yarn package.
15. A high-speed precision yarn winder as defined in claim 2, including means for generating sensing signals continuously indicating variations in tension of yarn at said tensioner means, and microprocessor means responsive to input signals including said sensing signals and predetermined processing condition data for activating the motor control circuits associated with said three drive motors to regulate yarn winding so as to maintain selective yarn density and tension conditions throughout the yarn package.
16. A high-speed precision yarn winder as defined in claim 3, wherein said regulating means includes microprocessor means responsive to input signals including said status signals and predetermined processing data for activating the motor control circuits associated with said three drive motors to regulate yarn winding so as to maintain selective yarn density and tension conditions throughout the yarn package.
17. A high-speed precision yarn winder as defined in claim 1, including live center means coactive with said spindle means mounted for reciprocative movement along said spindle axis for releasable receiving and holding a package tube between said live center means and said spindle means in driven engagement with the latter, and electric motor forming a doff motor coupled to said live center means for retracting the same to a release position for removal of the package tube and projecting the same to a tube holding position relative to the spindle means, and a motor control circuit associated with said doff motor for activating the same to retract and project the live center means upon completion of winding of a yarn package.
18. A high-speed precision yarn winder as defined in claim 2, including live center means coactive with said spindle means mounted for reciprocative movement along said spindle axis for releasable receiving and holding a package tube between said live center means and said spindle means in driven engagement with the latter, and electric motor forming a doff motor coupled to said live center means for retracting the same to a release position for removal of the package tube and projecting the same to a tube holding position relative to the spindle means, and a motor control circuit associated with said doff motor for activating the same to retract and project the live center means upon completion of winding of a yarn package.
19. A high-speed precision yarn winder as defined in claim 3, including live center means coactive with said spindle means mounted for reciprocative movement along said spindle axis for releasable receiving and holding a package tube between said live center means and said spindle means in driven engagement with the latter, and electric motor forming a doff motor coupled to said live center means for retracting the same to a release position for removal of the package tube and projecting the same to a tube holding position relative to the spindle means, and a motor control circuit associated with said doff motor for activating the same to retract and project the live center means upon completion of winding of a yarn package.
20. A high-speed precision yarn winder as defined in claim 16, including live center means coactive with said spindle means mounted for reciprocative movement along said spindle axis for releasable receiving and holding a package tube between said live center means and said spindle means in driven engagement with the latter, and electric motor forming a doff motor coupled to said live center means for retracting the same to a release position for removal of the package tube and projecting the same to a tube holding position relative to the spindle means, and a motor control circuit associated with said doff motor for activating the same to retract and project the live center means upon completion of winding of a yarn package.
21. A high-speed precision winder as defined in claim 1, wherein said tensioner means includes a movable contact member engaging the infeed yarn, a load cell forming part of support structure for said contact member for responding to variations in tension of infeed yarn engaging said contact member and producing load cell output signals, and means responsive to said load cell output signals for activating said drive motors in predetermined relation to variations in such yarn tension.
22. A high-speed precision winder as defined in claim 2, wherein said tensioner means includes a movable contact member engaging the infeed yarn, a load cell forming part of support structure for said contact member for responding to variations in tension of infeed yarn engaging said contact member and producing load cell output signals, and means responsive to said load cell output signals for activating said drive motors in predetermined relation to variations in such yarn tension.
23. A high-speed precision winder as defined in claim 16, wherein said tensioner means includes a movable contact member engaging the infeed yarn, a load cell forming part of support structure for said contact member for responding to variations in tension of infeed yarn engaging said contact member and producing load cell output signals, and means applying said load cell output signals to said microprocessor means to affect regulation of the three motors responsive to variation in infeed yarn tension.
24. A down pressure sensing and control system for high-speed precision winder for winding a running yarn onto a tube to form a cross wound yarn package wherein the winder includes spindle means for rotating the tube about a spindle axis, traversing means, and a bail roller disposed in rolling contact with the peripheral surface of the yarn package being wound, the down pressure sensing and control system comprising means for continuously regulating down pressure on the bail roller during formation of the package comprising a variable speed drive motor, an associated motor control circuit therefor, a stationary support frame for the spindle means, a carriage movable relative to said frame supporting the bail roller, support structure on said carriage for an end of the bail roller including a load cell arranged to respond to variation in down pressure on the bail roller and produce load cell output signals responsive thereto, and means responsive to said load cell output signals representing variations for activating a motor control circuit associated with said drive motor to vary the position of said bail roller relative to said spindle axis and relative to the tube being driven by said spindle means.
25. A tension sensing and control system for a high-speed precision winder for winding a running yarn onto a tube to form a cross-wound package wherein the winder includes a spindle station having spindle means and coactive yarn package tube holding means and means associated therewith for traversing running yarn being fed to said station back and forth along a traversed zone of the tube, and a tensioner station through which infeed yarn is fed along a yarn feed path to the spindle station comprising a tension mechanism including a yarn engaging finger, support bracket means for the yarn engaging finger supporting the finger for pivotal movement with a portion of the finger engaging the infeed yarn, a load cell supported adjacent a movable portion of said finger, means for applying force from the movable portion of the finger to the load cell bearing predetermined relation to the tension of infeed yarn engaged by said finger to sense variations in the infeed yarn tension and effect power lated variations in the load cell, a load cell producing load cell output signals responsive to said infeed yarn tension and variations thereof, and means responsive to said load cell output signals representing variations in infeed yarn tension for activating infeed yarn tension regulating means to adjust infeed yarn tension to predetermined tension conditions.
26. A tension sensing and control system as defined in claim 25, wherein said support bracket means includes a generally U-shaped thin bracket member having a pair of leg portions extending in parallelism with each other perpendicular to the yarn feed path at said tensioner station and a bridge portion extending between said leg portions, means supporting said load cell from one of said leg members to dispose said load cell between said leg portions, pivot shaft means for said yarn engaging finger supported for pivotal movement about a shaft axis at a location between said leg portions and adjacent said load cell, and abutment means movable with said yarn engaging finger extending from said pivot shaft means in a direction opposite the direction at which the yarn engaging finger extends therefrom and having a portion disposed in abutment with said load cell to exert a force thereon related to tension of the infeed yarn engaged by said finger.
27. A tension sensing and control system as defined in claim 26, including a guide yoke member extending from said bridge portion of said support bracket in a direction opposite the direction of extension of said leg portions therefrom, said guide yoke member having a pair of parallel outwardly projecting guide legs located above and below the location of said yarn engaging finger, said guide legs each having a truncated triangular hook portion and an inclined surface forming one side of said hook portion, the inclined surface extending to a throat formation adjoining a generally circular eye formation to guide yarn into said eye formation and define the yarn path between said two guide legs.
28. A tension sensing and control system as defined in claim 25, including a guide yoke member having a pair of parallel outwardly projecting guide legs located above and below the location of said yarn engaging finger, said projecting guide legs having a truncated triangular hook portion and an inclined surface forming one side of said hook portion, the inclined surface extending to a throat formation ajoining a generally circular eye formation to guide yarn into said eye formation and define the yarn path between said two guide legs.
29. A movable carriage frame structure for a high speed precision winder for winding a running yarn onto a tube to form a cross wound yarn package, the winder including a stationary spindle and tube holding station where running yarn is wound onto the tube, the carriage frame structure including an upper platform member, a pair of rotatable yarn guide blades forming a yarn traversing propeller assembly rotatably supported for movement about a substantially vertical axis perpendicular to the horizontal platform for guiding the yarn back and forth across a traverse zone at the spindle station to wind a yarn package on a tube supported and driven at the spindle station, the yarn guide blades being rotatable inclusive adjacent parallel planes located closely adjacent and above said platform member and below a spindle axis defined at said spindle station, a drive motor forming a propeller motor carried in depending relation below said platform member and rigidly mounted in suspended condition therebelow by supporting members extending from the carriage, drive means for said yarn guide blades including a first drive member driven directly from the motor for rotating one of said guide blades in a first direction and direction reversing means driven therefrom rotatably driving the other said guide blades in an opposite direction to said first mentioned guide blade, guide means for guiding said carriage and platform member thereof for reciprocative movement upwardly and downwardly parallel to said vertical axis, a carriage drive motor, and drive screw and worm drive means driven from said carriage motor and coupled to said carriage for moving the carriage upwardly and downwardly, and a bail roller rotatably supported on said platform member in a position above the same to be disposed in rolling contact with a peripheral surface of a yarn package being wound onto the tube.
30. A yarn package down pressure sensing and control system for a high-speed precision winder for winding a running yarn onto a tube to form a cross-wound package wherein the winder includes a spindle station having spindle means and coactive yarn package tube holding means and means associated therewith for traversing running yarn being fed to said station back and forth along a traversed zone adjacent said tube to form the cross-wound package, comprising a bail roller disposed in rolling contact with the peripheral surface of the yarn package being wound, a main frame providing a stationary support for said spindle means, down pressure adjusting means including a movable carriage forming a sub-frame movable toward and away from said spindle axis and supporting said bail roller and traversing means thereon, support means for rotatably supporting said bail roller including a load cell forming part of the support structure for at least one end of said bail roller for responding to variations in pressure thereon and producing load cell output signals, motor means for moving said carriage and the bail roller and traversing means carried thereby toward and away from said spindle axis, and a motor control circuit associated with said carriage means including means responsive to said load cell output signals for generating activation and speed control signals for said motor means.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US27081388A | 1988-11-07 | 1988-11-07 | |
| US270,813 | 1988-11-07 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2002309A1 true CA2002309A1 (en) | 1990-05-07 |
Family
ID=23032912
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002002309A Abandoned CA2002309A1 (en) | 1988-11-07 | 1989-11-06 | High speed precision yarn winding system |
Country Status (9)
| Country | Link |
|---|---|
| JP (1) | JPH02178174A (en) |
| CA (1) | CA2002309A1 (en) |
| CH (1) | CH682560A5 (en) |
| DE (1) | DE3936718A1 (en) |
| FR (1) | FR2638726B1 (en) |
| GB (1) | GB2224520B (en) |
| IT (1) | IT1237177B (en) |
| NL (1) | NL8902745A (en) |
| SE (1) | SE8903707L (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4208393A1 (en) * | 1992-03-16 | 1993-09-23 | Sahm Georg Fa | METHOD FOR REWINDING CONTINUOUSLY WITH PREFERRED, CONSTANT SPEED OF A THREADED DEVICE, THREAD-SHAPED GOODS IN STEPPED PRECISION CROSSWINDING, AND REEL DEVICE FOR IMPLEMENTING THIS |
| AT502728B1 (en) * | 2003-08-20 | 2008-10-15 | Starlinger & Co Gmbh | COIL WINDING DEVICE |
| CN108998914B (en) * | 2018-10-18 | 2024-01-30 | 广东溢达纺织有限公司 | Broken yarn detection device and sizing machine system |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2972450A (en) * | 1957-12-05 | 1961-02-21 | Leesona Holt Ltd | Textile winding machine |
| US3860186A (en) * | 1968-12-09 | 1975-01-14 | Rieter Ag Maschf | Method and apparatus for winding yarn from open end spinning devices |
| GB1441821A (en) * | 1973-03-20 | 1976-07-07 | Barmag Barmer Maschf | Winding machine |
| US4033519A (en) * | 1974-06-06 | 1977-07-05 | Teijin Limited | Method and apparatus for automatically changing bobbins and winding yarn continuously |
| CH618401A5 (en) * | 1975-06-12 | 1980-07-31 | Barmag Barmer Maschf | |
| US4009839A (en) * | 1975-10-06 | 1977-03-01 | Leesona Corporation | Winding apparatus |
| JPS6023065B2 (en) * | 1978-02-16 | 1985-06-05 | 東レ株式会社 | Yarn winding device |
| DE3176821D1 (en) * | 1981-05-08 | 1988-09-01 | Toray Industries | Yarn winding apparatus |
-
1989
- 1989-10-27 GB GB8924268A patent/GB2224520B/en not_active Expired - Fee Related
- 1989-11-02 CH CH3964/89A patent/CH682560A5/en not_active IP Right Cessation
- 1989-11-03 IT IT04851789A patent/IT1237177B/en active IP Right Grant
- 1989-11-03 DE DE3936718A patent/DE3936718A1/en not_active Withdrawn
- 1989-11-06 SE SE8903707A patent/SE8903707L/en not_active Application Discontinuation
- 1989-11-06 CA CA002002309A patent/CA2002309A1/en not_active Abandoned
- 1989-11-06 FR FR898914524A patent/FR2638726B1/en not_active Expired - Fee Related
- 1989-11-07 NL NL8902745A patent/NL8902745A/en not_active Application Discontinuation
- 1989-11-07 JP JP1289827A patent/JPH02178174A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| CH682560A5 (en) | 1993-10-15 |
| DE3936718A1 (en) | 1990-05-10 |
| FR2638726A1 (en) | 1990-05-11 |
| GB8924268D0 (en) | 1989-12-13 |
| JPH02178174A (en) | 1990-07-11 |
| GB2224520B (en) | 1993-06-23 |
| SE8903707L (en) | 1990-05-08 |
| GB2224520A (en) | 1990-05-09 |
| IT1237177B (en) | 1993-05-24 |
| SE8903707D0 (en) | 1989-11-06 |
| FR2638726B1 (en) | 1993-01-22 |
| NL8902745A (en) | 1990-06-01 |
| IT8948517A0 (en) | 1989-11-03 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |