JPH08232122A - Apparatus for changing number of twist in double twister - Google Patents

Abstract

PURPOSE: To enable the changing of the number of twist easily and accurately. CONSTITUTION: A force transmission system 26 connecting between a spindle driving system and a winding drum is provided with an infinitively variable- speed mechanism. The force transmission system 26 is composed of a belt transmission means 84 consisting of a belt and pulleys. As the infinitively variable- speed mechanism, an infinitively variable-speed pulley 90, which changes speed by adjusting its position between the pulleys, is furnished. The pulley 90 is provided with a screw rod 116 screwed into a movable block 110 placed at the end of the pulley shaft 105 and a variable speed motor 113, which suitably rotates the screwed rod 116.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a twisting number changing device for a double twister.

[0002]

2. Description of the Related Art As shown in FIG. 17, a double twister 1
Is configured by arranging a large number of weights 4 provided with the yarn twisting portion 2 and the winding device 3 side by side. An end box 11 accommodating a motor (power source) 5 is provided at one end of the weight row, and the spindle 12 of the yarn twisting portion 2 is moved by frictional contact of an endless belt 6 that is circulated and driven by the rotation of the motor 5. It is designed to rotate at a high speed all at once. Further, the circulation motion of the endless belt 6 is changed to appropriate rotation by the speed reducer 7 and the gear train 8 provided in the case 13 at the other machine end, and the winding drum 9 and the traverse member 10 of the winding device 3 are Driven.

[0003]

By the way, the package P
The number of twists of the yarn Y wound around is determined by the relationship between the rotation speed of the spindle and the winding speed (the rotation speed of the winding drum 9). Conventionally, in order to change the number of twists, the gear train It could only be done by replacing the gear in the middle of 8. For this reason, there is a problem that changing the number of twists takes time and effort, and moreover, fine control cannot be performed.

Therefore, the present invention was devised to provide a twist number changing device of a double twister capable of easily and appropriately changing the twist number.

[0005]

SUMMARY OF THE INVENTION The present invention provides a continuously variable transmission mechanism in a power transmission system connecting a spindle drive system and a winding drum. Further, according to the present invention, a power transmission system for connecting a spindle drive system and a winding drum is constituted by a belt transmission means composed of a belt and a pulley, and a continuously variable pulley for performing gear shifting by position control between the pulleys. Be prepared. It is preferable that the continuously variable transmission pulley is provided with a screw rod screwed to the end of the pulley shaft and a motor that appropriately rotates the screw rod.

[0006]

With the above structure, the power transmission system appropriately transmits the rotation of the spindle drive system to the winding drum to wind the twisted yarn, and to adjust the number of twists corresponding to the rotation ratio.
The continuously variable transmission mechanism changes the number of twists by changing the transmission speed of the power transmission system. The continuously variable pulley changes its position by changing the position between the pulleys of the belt transmission means. The motor changes the position of the continuously variable pulley by appropriately rotating the screw rod.

[0007]

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

FIG. 1 shows an embodiment of a twisting number changing device of a double twister according to the present invention. This twisting number changing device is configured such that a power transmission system 26 connecting a spindle drive system and a winding drum is provided with a continuously variable transmission pulley (variable pitch pulley) 90 as a continuously variable transmission mechanism. In the present embodiment, the power transmission system 26 is mainly constituted by the belt transmission means 84 composed of a belt and a pulley, and the continuously variable transmission pulley 90 is controlled in position between the pulleys so as to change the speed. It has become. In the double twister of this embodiment, the weights are arranged in two rows in the vertical direction and in two rows (back to back), and the power transmission system 26 is arranged above and below the case 25 having a substantially rectangular parallelepiped shape installed at one end of the weight row. The same configuration is stored in.

First, the case 25 accommodating the power transmission system 26 will be described with reference to FIGS. 9 to 16. The case 25 includes a lower plate 45 serving as a bottom surface thereof, a side plate 46 defining a side surface on the weight side S, a box plate 47 defining a side surface on the opposite side, and an upper plate 48 defining a ceiling surface. Board 48
And a lower plate 45 and a middle plate 49 provided in parallel with each other. That is, the power transmission system 26 for the upper weight is accommodated above the middle plate 49, and the power transmission system 26 for the lower weight is accommodated below the middle plate 49. The left and right sides of the lower plate 45 and the middle plate 49 (on the front side of each weight) are bent upward at a right angle, and a pair for joining the side plate 46 and the box plate 47 to both ends of these bent portions 50, 51. The holes 52 and 53 are formed respectively. The upper plate 48 is bent downward, and the bent portion 54 has a similar assembly hole 55. The left and right sides and the upper and lower sides of the side plate 46 are bent inward, and the left and right bent portions 56 are overlapped with the end portions of the bent portions 54, 51, 50 of the upper plate 48, the middle plate 49, and the lower plate 45. The upper and lower bent portions 57 are overlapped with the ends of the surface portions of the upper plate 48 and the lower plate 45, respectively. Then, on the bent portion 56, the upper plate 48,
Assembling holes 58 are formed so as to match the assembling holes 55, 53, 52 of the middle plate 49 and the lower plate 45. The box board 47 is
The left and right sides and the upper and lower sides are bent deeper than the side plate 46,
It is formed so that only the side opposite to the weight side S is opened. The middle plate 49 is formed to have a size shorter than the upper plate 48 and the lower plate 45 so as to be fitted to the surface portion of the box plate 47, and the front and rear sides thereof are bent downward. The upper plate 48 and the lower plate 45 are also attached to the bent portion 60 of the box plate 47.
Also, an assembling hole 61 corresponding to the assembling holes 55, 52, 53 of the intermediate plate 49 is formed. In addition, a partition plate 62 that doubles as an oil pan is provided inside the bent portion 60 of the box plate 47. The four edges of the partition plate 62 are the box plate 47.
Is bent so as to be surface-bonded to the surface portion and the bent portion 60. In addition, at the four corners of the lower plate 45, a pedestal 63 made of a bolt rod and a columnar hem member 64 extending outside in the weight direction are formed.
And are attached.

To assemble these plates, a monobolt (blind rivet) 65 as shown in FIG. 11 is used. The monobolt 65 includes a rivet 67 having a shaft portion 66 corresponding to the diameter of the assembling hole, and a pin 68 inserted into the shaft hole formed in the rivet 67. Then, the rivet 67 is inserted into the assembling holes 52, 61 from the outside of the lower plate 45 and the box plate 47, for example (b), and the pin 68 is pulled out in this state, whereby the enlarged diameter portion 6 of the tip of the pin 68 is
9 is for swelling the shaft portion 66 of the rivet 67 in the radial direction (c) and fastening the plates together by crimping. The base end side of the pin 68 is bent and removed from the rivet 67. Further, as shown in FIG. 15, the exterior plate 7 that can be freely opened and closed is provided on the outside of the case 25 (three sides except the weight side S).
0, 71, 72 are provided. Brackets 73, 74 and vertical pins 75, 76 are provided above and below both sides of the box plate 47 to support the exterior plates 71 ... 72 (see FIGS. 13 and 14). That is, this vertical pin 75,
By fitting the holes formed at the ends of the exterior plates 70, 71, 72 to 76, the hem member 64 can be opened and closed like a door. Further, on one side of the box plate 47, a magnet 77 that is attracted when the facing exterior plate 70 is closed is provided.

Next, the power transmission system 26 will be described. As shown in FIG. 1, the power transmission system 26 is provided with a worm speed reducer 83 for reducing the rotation of the endless belt 87, which is a spindle drive system, to an appropriate rotation, and a belt transmission means 84 is provided on the output side thereof. It is connected. The worm speed reducer 83 has a main body attached to the surface of the box plate 47, and the input side pulley 8 attached to the input shaft 85 protruding to the lower portion of the main body.
1 are located above the middle plate 49 or the lower plate 45, respectively. An output pulley 82 attached to the horizontal output shaft 86 is located inside the box plate 47. A pair of guide pulleys (not shown) for guiding the endless belt 87 is provided on both sides of the input side pulley 81 and at positions appropriately separated from the weight side S. The box plate 47 and the side plate 46 are provided with rectangular notches 88 and 89 for avoiding interference with the input side pulley 81 and the endless belt 87.

The belt transmission means 84 is a worm speed reducer 8.
No. 3 output side pulley 82, a continuously variable transmission pulley 90 and a belt 91 connected thereabove, and a first relay pulley 92 and a belt 93 connected to the continuously variable transmission pulley 90 above that.
And a pair of take-up drum pulleys 94 and 95 and a belt 96 that are connected to the first relay pulley 92 at the left and right positions thereof (see FIGS. 4 and 8).

As shown in FIGS. 2 and 3, the continuously variable transmission pulley 90 includes a pair of fixed pulley plates 106 and 107 mounted at a predetermined interval in the axial direction of the pulley shaft 105, and these fixed pulley plates. And a movable pulley plate 108 which is provided between the movable pulley plate 108 and the fixed pulley plates 106 and 107 so as to be wound between the movable pulley plate 108 and the fixed pulley plates 106 and 107, respectively. Has become. Pulley shaft
A base end portion of 105 is supported by a moving block 110 engaged with a guide 109 in a substantially vertical direction via a bearing 111.
A nut portion 112 is formed on the moving block 110, and is screwed into a screw rod (ball screw) 116 connected to an output shaft 114 of a speed change motor 113 via a coupling 115. That is, the rotation of the transmission motor 113 causes the moving block 110 to move in a substantially vertical direction along the guide 109, changing the position of the pulley shaft 105 between the output pulley 82 and the first relay pulley 92. ing. By this position control, the tension of the belts 93, 91 wound between them is changed, and the movable pulley plate 108 is changed.
The diameter of the pulley formed between the fixed pulley plates 106 and 107 is substantially increased or decreased to adjust the rotation ratio. In this embodiment, by raising the pulley shaft 105, the diameter of the pulley connected to the output pulley 82 is reduced to increase the rotational speed of transmission, and by lowering the pulley shaft 105, the rotational speed is decreased. It is designed to let you. Further, the guide 109 and the screw rod 116 are provided on the belts 91 and 93.
Is slightly inclined with respect to the traveling surface of the movable pulley plate 108.
The belt 91, 93 is kept in a constant traveling position by absorbing the deviation of the belt engagement position due to the movement of the belt.
Then, the guide 109, the screw rod 116, and the transmission motor 113
A housing 117 for supporting the housing 117 is attached to the surface of the box plate 47 by a bracket 118 surrounding the housing 117 in a U shape. A rectangular opening 78 is formed in the box plate 47 at this position so as not to prevent the moving block 110 and the pulley shaft 105 from moving. A sensor 119 for detecting the position of the moving block 110 is provided in the housing 117.

The first relay pulley 92 comprises a large diameter pulley 92a and a small diameter pulley 92b which are coaxial with each other.
The variable pulley a is opposed to the continuously variable transmission pulley 90, and the small diameter pulley 92b is opposed to the take-up drum pulleys 94 and 95. FIG.
As shown in FIG. 6, the belt 96 wound around the winding drum pulleys 94 and 95 from the first relay pulley 92 is the tension roller 12 adjacent to the right winding drum pulley 94.
The pulleys 94 and 95 for the take-up drum are also wound around 0 to rotate in the opposite directions. As shown in FIG. 4, the pulley shafts of the take-up drum pulleys 94 and 95 extend toward the weight side S as drum drive shafts 121 and 122, and are supported by the box plate 47 and the side plate 46 on both sides via bearings 123. ing. A fifth relay pulley 124 is attached near the side plates 46 of the drum drive shafts 121 and 122, and a shaft 12 of a feed roller (not shown) provided on each weight is provided.
5, it is connected via its pulley 126 and belt 127. In the middle of this belt 127, the tension roller 12
9 is engaged. The feed roller shaft 125
Has an end portion penetrating the side plate 46 and supported by a bearing 128, and a pulley 126 is attached to the extending end thereof.

Further, as shown in FIG. 5, the belt transmission means is configured to drive the traverse device 21 for reciprocating the traverse bar 37 supporting the traverse member of each weight. That is, as a structure following the right winding drum pulley 95, a second relay pulley 97 and a belt 98 connected below the pulley 95 and a second relay pulley 9 are connected.
7, a third relay pulley 99 and a belt 100 that are connected obliquely downwardly thereof, a traverse cam drive shaft 101 that is a pulley shaft of the third relay pulley 99, and a fourth relay pulley 102 attached to the other end side. And a cam pulley 103 and a belt 104 attached to the rotary shaft 22 of the traverse device 21 so as to be connected to the fourth relay pulley 102. A tension roller 134 attached to the side plate 46 is engaged with the belt 104.

The right winding drum pulley 95 is coaxially provided with a pulley 130 having a diameter smaller than that of the right winding drum pulley 95. The second relay pulley 97 includes a large-diameter pulley 97a and a small-diameter pulley 97b, and a belt 98 is provided between the small-diameter pulley 97a and the small-diameter pulley 130 of the left winding drum pulley 95.
Is wound. The traverse cam drive shaft 101 of the third relay pulley 99 penetrates the box plate 47 and the side plate 46.
It is extended to and is supported on both ends thereof by bearings 123. The fourth relay pulley 102 is attached to the traverse cam drive shaft 101 at a position appropriately separated from the side plate 46, and faces the cam pulley 103 of the rotary shaft 22. The fourth relay pulley 102 and the cam pulley 103 are two pulleys (102a, 102b, 103a, 103) arranged side by side.
b), and the fourth relay pulley 102 has a slightly different pulley diameter. The small-diameter relay pulley 102b is located on the side close to the side plate 46, and the one cam pulley 103b facing this is fixed to the rotary shaft 22 via a boss 131. One end of the rotary shaft 22 is parallel to the traverse cam drive shaft 101 and one end of the side plate 46 is provided.
The other end to the bracket 118 of the continuously variable pulley 90.
Each is supported through 123. In the above belt transmission means 84, especially the drum drive shafts 121, 122
It is desirable that the components related to the rotation of (1) are composed of a toothed belt and a toothed belt wheel. In the illustrated example, two belts (96, 98) and six pulleys (92b, 94, 9) are used.
5,97b, 120,130) are toothed.
Further, the small-diameter second relay pulley 97a and the third relay pulley 99 are formed as stepped pulleys (pulleys having different diameters) so that the transmission speed can be switched between them. The tension roller 143 engaged with the belt 100 is formed with a length corresponding to the entire width of the pulley.

The traverse device 21 is mainly constituted by a traverse cam 23, which is a press-formed cam member attached to the rotary shaft 22, and a traverse lever 24, which is a lever member that engages with the traverse cam 23 and swings. There is. The traverse levers 24 are provided on the left and right sides with the traverse cam 23 interposed therebetween, and the base ends thereof are pivotally supported near both ends of a rod 35 that is horizontally installed in the case 25.
The rod 35 is formed by bending the middle plate 49 and the lower plate 45.
The holes 59 are formed in the holes 1, 50. A traverse bar 37 is connected to a tip end portion of the traverse lever 24, which is a swing end, via a connecting member 36. Further, at a position substantially in the middle of the traverse lever 24, a roller 38 which is a cam follower, and a spring 3 which urges the roller 38 to contact the engagement surface 28 of the traverse cam 23.
9 and 9 are attached. The connecting member 36 is formed by a small rod 41 having one end loosely fitted in a long hole 40 formed at the tip of the traverse lever 24, and a connecting plate 42 connecting the other end of the small rod 41 and the traverse bar 37. ing. A screw 43 is engraved on the other end of the small rod 41, and a pair of nuts 44 screwed into the screw 43 are provided on both sides of the connecting plate 42. That is, by rotating the nut 44, the swing angle of the traverse bar 24 and the traverse bar 3
The relationship with the reciprocating position of 7 can be adjusted.

As shown in FIG. 6, the traverse cam 23
Is formed by bending the outermost edge portion 27 of a circular plate in the axial direction, and has an engaging surface 28 that engages with the traverse lever 24 inside (outer peripheral portion) thereof. Between the engagement surface 28 and the shaft center portion 29, eight ribs 31 which are slightly projected from the surface portion 30 and radially extend in the radial direction are integrally formed. Further, the traverse cam 23 is slightly bent at the position of the line segment in the radial direction, and as shown in FIG. 7, the engaging surface 28 has a peak portion 32 and a valley portion 33, each of which is 180 degrees. Are formed in the phase. The refraction points of these portions 32 and 33 have a slightly rounded shape so that the center locus 34 of the roller 38 can be smoothly connected. The traverse cam 23 is attached to the rotary shaft 22 by the key groove 132 in the axial direction.
It is attached by welding to the sliding body 133 fitted through the above in an appropriately inclined state. That is, the engagement surface 28 is held so as to be orthogonal to the axial direction of the rotary shaft 22 over the entire circumference. Then, by the inclination angle of this attachment, the refraction angle α, and the axial distance H between the crests 32 and 33,
The engagement surface 28 is formed to have a predetermined cam profile. That is, the rotary shaft 22 is the drum drive shaft 121.
, 122 to rotate at a predetermined rotation ratio with respect to the winding rotation speed. By this rotation, the traverse cam 23 swings the traverse lever 24 at an appropriate cycle.

Further, the traverse device 21 of the present embodiment is provided with a creeping mechanism 135 for preventing the height of the winding package from rising. This creeping mechanism 135
Is the other cam pulley 103a facing the large-diameter pulley 102a of the fourth relay pulley 102, and a creeping cam 136 for sheet metal processing attached to the end of the sliding body 133 by welding.
The creeping cam 136 includes a roller 137 that engages with the profile surface of the creeping cam 136, and a bracket 138 for attaching the roller 137 to the other cam pulley 103a. The profile surface of the creeping cam 136 is formed so as to be slightly reciprocally displaced in the axial direction by one rotation. Therefore, as the rotation is transmitted, the fourth relay pulleys 102a, 102b
Of the other cam pulley 103a
Shifts in phase with respect to one of the cam pulleys 103b (rotating shaft 22). Due to this phase shift, the roller 137 rotates relative to the creeping cam 136,
The sliding body 133 and the traverse cam 23 are periodically moved in the axial direction little by little. That is, the traverse width is set to be the same and the winding position is moved to the left and right to reduce the density of both ends of the winding package.

As shown in FIGS. 12 and 16, the side plate 46 and the box plate 47 have bearing holes 139 and 140 for mounting the bearings 123 and 128, and the traverse bar 3.
7, through holes 141, 142, tension pulleys 120, and elongated holes 144, 145 for attaching the tension rollers 129, 134, 143 are formed. Also sensor 11
Since it is desirable that the cables connecting the 9 and the variable speed motor 113 and the like to the control panel (not shown) are arranged along the surface of the side plate 46 or the box plate 47, a string locking hole 146 for passing a string for bundling them. Are formed. In addition, the side plate 46,
A fixing hole 147 for fixing one end of the spring 39 for pulling the traverse lever 24 is formed, and the box plate 4
7 has a mounting hole 14 for mounting the worm reducer 83
8 are formed.

As described above, since the continuously variable transmission pulley 90 is provided in the power transmission system 26 connecting the worm speed reducer 83 and the drum drive shafts 121 and 122, it is possible to replace the speed change gears in the conventional gear train. This eliminates the troublesome work, and the twist number can be easily and accurately changed. Power transmission system 2
6 is constituted by the belt transmission means 84, and the worm speed reducer 8
Since the continuously variable transmission pulley 90 is provided between the output side pulley 82 of No. 3 and the first relay pulley 92 and the position of the continuously variable transmission pulley 90 is controlled in the vertical direction, the gear shifting can be performed with the minimum required simple structure. It can be carried out. Then, as a mechanism for moving the continuously variable pulley 90 up and down, a screw rod 116 and a variable speed motor 11 are provided.
Since 3 is provided, it is possible to quickly and precisely control the number of twists. Further, continuously variable transmission pulley 90 and transmission motor 11
Since the bracket 118 for mounting the 3 etc. is used for supporting the rotary shaft 22 of the traverse cam 23, it is possible to contribute to simplification and compactification of the overall configuration.

Further, in the present embodiment, the power transmission system 26
A traverse cam 23 formed by press molding is attached to a rotary shaft 22 which is driven to rotate by a traverse bar 37 by a traverse lever 24 that engages with and swings.
Since it is made to reciprocate, the processing time and the manufacturing cost can be shortened as compared with the configuration using the cam of the conventional heavy casting. Further, by bending the outside of the engaging surface 28 of the traverse cam 23 and press-forming the rib 31 on the surface portion 30, sufficient strength for swinging the traverse lever 24 can be obtained. Further, the creeping cam 136 attached to the traverse cam 23
Since it is composed of a press-molded product, further weight reduction and cost reduction can be achieved.

In the present embodiment, the plate members (45 ... 49) processed by sheet metal processing are assembled to form the case 25 for accommodating and supporting the power transmission system 26 and the traverse device 21. It can be stronger and lighter than the case, and improved durability and reliability are achieved. In addition, the mono bolt 65 that fastens and fixes each plate material,
Since the case 25 is simply inserted from one side, the case 25 can be easily assembled only by the operation from the outer surface, and the assembling work can be performed in a shorter time and easier than when welding or using bolts and nuts. And the middle plate 49 and the lower plate 4
5, the bent portions 50, 51, the side plate 46, and the box plate 47
Since the surface portion of (1) is made to function as a mounting portion for each component of the power transmission system 26, a separate mounting plate and brackets are not required, and the number of components can be greatly reduced. And assembling holes 52, 53, 55, 58, 6
1 and the bearing holes 139, 140, etc., can be opened in advance before assembly, and there is no room for error in the mutual positional relationship, and the assembling accuracy is improved.

In this embodiment, the continuously variable pulley 90 is shown as the continuously variable transmission mechanism. However, as long as it can be applied to the structure of the power transmission system 26, for example, a friction wheel type machine, a chain type machine, or the like. Besides the type continuously variable transmission, a hydraulic or electric continuously variable transmission may be adopted. Further, although the double twister composed of the upper and lower two-stage weights is shown, the present invention is naturally applicable to the single-stage double twister.

[0025]

In summary, according to the present invention, the following excellent effects are exhibited.

(1) According to the configuration of claim 1, the twist number can be easily and accurately changed.

(2) According to the structure described in claim 2, the gear shift can be performed with a simple structure.

(3) According to the third aspect of the invention, it is possible to quickly perform a fine and precise twist number control.

[Brief description of drawings]

FIG. 1 is a side sectional view showing an embodiment of a twisting number changing device of a double twister according to the present invention.

FIG. 2 is a front view showing a main part of FIG.

FIG. 3 is a plan sectional view of FIG.

FIG. 4 is a side sectional view showing a configuration following the belt transmission means of FIG.

5 is a perspective view showing a main part of FIG.

FIG. 6 is a front view showing the traverse cam of FIG.

FIG. 7 is a profile diagram for explaining the operation of FIG.

8 is a front view showing the power transmission path of FIGS. 1 and 4. FIG.

9 is an exploded perspective view showing the case of FIG.

10 is a perspective view showing a state where the case of FIG. 9 is assembled.

11 is a diagram showing a main part of FIG. 9, in which FIG.
0 is an enlarged view of part A, and (b) and (c) are perspective views showing the operation.

12 is a front view of FIG.

FIG. 13 is a top view of FIG.

FIG. 14 is a side view of FIG.

15 is a top view showing an exterior plate provided in the case of FIG.

16 is a rear view of FIG.

FIG. 17 is a side view of a conventional double twister.

[Explanation of symbols]

 26 power transmission system 84 belt transmission means 87 endless belt (spindle drive system) 90 infinitely variable pulley (infinitely variable transmission mechanism) 105 pulley shaft 110 moving block (end of pulley shaft) 113 variable speed motor (motor) 116 screw rod 121, 122 drum drive shaft

Claims (3)

[Claims] 1. A twisting number changing device for a double twister, wherein a continuously variable transmission mechanism is provided in a power transmission system connecting a spindle drive system and a winding drum. 2. A continuously variable transmission pulley, wherein a power transmission system connecting a spindle drive system and a take-up drum is constituted by belt transmission means composed of a belt and a pulley, and a speed is changed by position control between the pulleys. A double twister twisting number changing device characterized by being equipped. 3. The twist number change of a double twister according to claim 2, wherein the continuously variable pulley includes a screw rod screwed onto an end of a pulley shaft of the continuously variable pulley, and a motor for appropriately rotating the screw rod. apparatus.