JPS6328918A - Driving gear for detaching roller of comber - Google Patents

Abstract

PURPOSE:To reduce impact in reverse rotation of rotary direction of detaching roller, by using a link mechanism and a differential gear mechanism in a driving gear without using a clutch and a cam. CONSTITUTION:A main shaft 2 is rotated at a uniform speed by revolution of a driving shaft 3 through gears 4 and 5 and a crank plate 14 is rotated by elliptic gears 8 and 12. Consequently, a connecting pin 13 of the plate 14 of four node link crank mechanism is subjected to circular motion around a shaft 6 and a lever 17 is subjected to shaking motion through a rod 18 around the shaft 3 as the center. The rotation of the four node link crank mechanism makes a lever 22 undergo shaking motion through a rod 23 and a sun gear 27 at the input side of a differential gear mechanism 26 is subjected to shaking motion through a sector gear 35 of a shaking shaft 20. Rotary motion of the shaft 2 and normal and reverse rotary motion of the sector gear 35 are synthesized by the differential gear mechanism 26 and detaching rollers 38 and 39 are reversely and normally rotated from a sun gear 30 at the output side through a gear 37 and gears 40 and 41.

Description

DETAILED DESCRIPTION OF THE INVENTION Object of the Invention (Field of Industrial Application) The present invention relates to a detaching roller drive device for a comb, and more particularly to a detaching roller drive device that can cope with high-speed operation of a machine.

(Prior art) The combing action of the wrap in the comber involves combing the tip of the wrap whose rear end is gripped by the nippers with a combing cylinder, and moving the combed fleece toward the detaching roller as the nippers move forward. Corresponding to the advance of this fleece, the detaching roller reverses, retreats the fleece that was picked up earlier, and overlays the freshly sensitized fleece on top of the fleece, and then the detaching roller rotates in the normal direction. The fleece is taken up from the nipper, and the top comb repeatedly sensitizes the rear end of the fleece. In such a series of combing actions, the combing action by the combing cylinder is performed during approximately one-half rotation of the cylinder shaft, so during that time the detaching roller is stationary or slowly rotates in the forward direction, and the remaining combing action of the cylinder shaft is The above-mentioned reverse and forward rotations are performed during approximately one-half rotation.

Conventionally, a device using a grooved cam and a clutch has been employed in the Nasmyth type comber as a drive device for performing forward and reverse movement of the detaching roller. With this device, it is easy to set the normal rotation, reverse rotation, and rest period of the detaching roller.Moreover, the stopping is achieved by disengaging the clutch, so it is in a completely stationary state, and when the detaching roller rotates in the normal direction to send out the fleece, the top comb is reliably set at 71. A north combing action can be performed. If a clutch is used, there is a shock when the clutch is attached and detached, and the clutch is attached and detached every time the detaching roller is switched between forward and reverse rotation, making it extremely difficult to achieve high-speed operation. In addition, the actual public notice of June 28, 1970
Japanese Patent No. 169 proposes a detaching roller drive device which is composed of a combination of a grooved cam and a differential gear mechanism. In this IA setting, a shock occurs due to the attachment and detachment of the clutch (Yona 6S), but when the machine is operated at high speed, the impact when the detaching roller moves direction is reversed due to the collision of the grooved cam and cam ball. In addition to generating noise, there is also the problem of causing damage to cam grooves, cam balls, power transmission gears, bearings, etc.Furthermore, displacement of the detaching roller in a drive device using a grooved cam and differential gear mechanism. As shown in Figure 6 (b), the curve shows that the detaching roller is not in a completely stationary state.
However, there is also the problem that the fleece is fed out, leading to a decrease in the quality of the spun product due to insufficient top combing at the end of the spun fleece, short fibers being brought in, etc. On the other hand, the special public notice No. 53-15178 announced on May 23, 1978
The @ gazette proposes a detaching roller drive device consisting of a combination of a crank mechanism and a differential gear mechanism. Unlike when using a clutch or grooved cam, this device does not have the problem of impact noise or abnormal stress occurring when the direction of movement of the detaching roller is reversed even during high-speed operation, but the displacement curve of the detaching roller is As shown in (b) in the figure, it is the same as when using a grooved cam,
The above-mentioned problems exist.

(Problems to be Solved by the Invention) This invention solves the problem of the above-mentioned conventional equipment, which suffers from noise generation during high-speed operation of the machine, damage to various parts due to generation of abnormal stress, and spun products due to insufficient combing action of the top comb. This solves the problem of quality deterioration.

Structure of the Invention (Means for Solving the Problems) In order to solve the above problems, in this invention, the thick part of the four-bar link crank mechanism is meshed with an elliptical gear disposed so as to be rotatable integrally with the main shaft. Oscillation for inputting a oscillation motion of a predetermined amplitude into a differential gear mechanism, which is arranged so as to be able to rotate integrally on the same axis as an elliptical gear of the same size, and combines the rotational motion of the main shaft with a predetermined forward and reverse rotational motion. A rocking lever that can rotate integrally with the shaft and an extended end of the connecting rod of the four-bar link crank mechanism are connected by a second connecting rod, and the length of the second connecting rod is determined by the movement trajectory of the connecting rod. is approximately equal to the radius of curvature of the circular arc portion, and the detaching roller performs one cycle of reverse rotation, forward rotation, and rest during one rotation of the main shaft, and after the normal rotation is completed, the swing lever moves at a constant speed. The starting point of the standstill period of the detaching roller is set at 160a of the spindle rotation angle.
~200°.

(Function) In the device of the present invention, the rotational motion of the main shaft and the predetermined forward and reverse rotational motion are combined by the differential gear mechanism, and the detaching roller is driven by the output of the differential gear mechanism. The rotational motion of the four-bar link crank mechanism is transmitted as a rocking motion to the rocking link of the rocking shaft that inputs a rocking motion of a predetermined amplitude to the differential gear mechanism via the second connecting rod. The four-bar link crank mechanism is rotated at variable speeds at one cycle per cycle via a pair of elliptical gears of the same size from the main shaft. Then, the rotational motion of the main shaft and the rocking motion of the rocking shaft are combined via a differential gear mechanism, and the output causes the detaching roller to rotate in reverse and forward motion by approximately 18 degrees around the main shaft rotation angle. , it is held almost stationary from around 180° to 360°. Therefore, the fleece is fed out only during the action of the top comb, eliminating the entrainment of short fibers and impurities and improving the quality of the spun product.

(Embodiment) An embodiment embodying the present invention will be described below with reference to FIGS. 1 to 6. As shown in Fig. 2, the gear box frame 1 includes a cylinder shaft 2 and a driving shaft 3.
is rotatably supported, a small gear 4 is fitted on the driving shaft 3 so as to be rotatable together, and a large gear 5 meshing with the small gear 4 is fitted on the cylinder shaft 2 so as to be rotatable as a unit. ing. As shown in FIG. 3, a crankshaft 6 is rotatably supported below the cylinder shaft 2 with respect to the frame 1 via a bearing 7. The crankshaft 2 has a pitch circle with an eccentricity of 0.
The elliptical gear 8 of No. 3 is fitted into the coupling 10, and the other end of the coupling 10 is fastened to the big gear 5 with a bolt 9, and the other end of the coupling 10 is fastened with a bolt 11, and is integrated with the big gear 5, that is, the cylinder shaft 2. It is designed to rotate.

On the other hand, an elliptical gear 12 having the same dimensions as the elliptical gear 8 is fitted onto the crankshaft 6 such that it meshes with the elliptical gear 8 and the major axes of both ellipses are aligned in a straight line. A crank plate 14 having a protruding pin 13 is tightened and fixed with a bolt 15 via a clamp plate 16.

ing. The elliptical gears 8 and 12 are mounted such that the focal point of the pitch circle is the axis of the cylinder shaft 2 and crankshaft 6, respectively.

A swing lever 17 is rotatably supported on the driving shaft 3, and a connecting rod 18 is rotatably connected to a connecting pin 13 protruding from the crank plate 14 at the tip of the swing lever 17. One end is rotatably connected by a pin 19. A four-bar link crank mechanism is formed by the crank plate 14, the connecting rod 18, and the swing lever 17, and the crank plate 14 is the thick part thereof. On the other hand, a swing shaft 20 is rotatably supported on the gear box frame 1 via a bearing 21 for inputting a swing motion of a constant amplitude to a differential gear mechanism to be described later. A swing lever 22 is fitted to one end of the swing shaft 20 so as to be integrally rotatable, and the tip of the swing lever 22 and the extended end of the connecting rod 18 of the four-bar link crank mechanism are connected to a second Each pin 24°2 to the connecting rod 23
5, they are rotatably connected. The length of the second connecting rod 23 is equal to the radius of curvature of the extended end of the connecting rod 18, that is, the portion where the locus of movement of the pin 25 is approximately an arc.

The cylinder shaft 2 is provided with a differential gear mechanism 2 for combining the rotational motion of the cylinder shaft 2 as a main shaft and the rocking motion of a constant amplitude input via the rocking shaft 20.
6 are arranged. The input side thick @ gear 27 constituting the differential gear single machine M426 is formed integrally with the first sun gear 28 and is rotatably supported by the cylinder shaft 2.
The second sun gear 29 is formed integrally with the output thick PA gear 30 and is also rotatably supported on the cylinder shaft 2. Further, a pair of support shafts 32 are supported on a casing 31 that is rotatably attached to the cylinder shaft 2 between both sun gears 28 and 29, and
The support shaft 32 has a planetary gear 33 that meshes with the first sun gear 28 and a planetary gear 34 that meshes with the second sun gear 29.
are integrally formed and rotatably supported.

The input side sun gear 27 is meshed with a sector gear 35 that is supported so as to be integrally rotatable with respect to the swing shaft 20.
Along with the oscillating motion of 0, a oscillating motion of a constant amplitude is inputted to the differential gear mechanism 26 by the sector gear 35. Further, an intermediate gear 37 that meshes with the output thick FiA wheel 30 is rotatably supported on a support shaft 36 disposed on the gear box frame 1, and a detaching roller 38° 39 is attached to the intermediate gear 37. Detaching roller gears 40 and 41, which rotate integrally with each other, are meshed with each other.

Next, the operation of the apparatus configured as described above will be explained. When the driving shaft 3 is driven, the cylinder shaft 2 as the main shaft is rotated at a constant speed via the small gear 4 and the large gear 5, and the crank plate 14 is rotated integrally with the elliptical gear 12 via the elliptical gear 8°12. rotate. Crank plate 1 that constitutes a four-bar link crank mechanism.
The connecting pin 13 of No. 4 performs a circular motion around the crankshaft 6, and the swing lever 17 connected via the connecting rod 18 performs a swinging motion around the driving shaft 3. As the four-bar link crank structure rotates, the swing lever 22 connected to the four-bar link crank mechanism via the second connecting rod 23 swings, causing the sector gear attached to the swing shaft 20 to rotate. 35 is oscillated and the input side sun gear 2 of the differential gear mechanism 26
A constant amplitude motion is input to 7. The rotational motion of the main shaft, that is, the cylinder shaft 2, and the predetermined forward and reverse rotational motion input from the sector gear 35 are combined by the differential gear mechanism 26 and transmitted from the output side sun gear 30 to the intermediate gear 37. Meshing detaching roller gear 40.4
1, the detaching rollers 38 and 39 are driven forward or reverse in accordance with the direction of rotation of the sector gear 35. In the device of this embodiment, when the sector gear 35, that is, the swing lever 22, rotates clockwise, the detaching rollers 38, 39 are rotated in the normal direction, and when the sector gear 35 rotates counterclockwise, the detaching rollers 38, 39 are rotated in the normal direction. Rollers 38, 39 are driven in reverse.

The connecting pin 13 of the crank mechanism is connected to both oval gears 8.12.
It rotates at a speed ratio determined by the eccentricity of. FIG. 4 shows movement trajectories representing the positions of the connecting pin 13 and pins 24 and 25 corresponding to every 9 degrees of rotation angle of the cylinder shaft 2. Connecting pin 1
3 is a trajectory P moving on the circumference centered on the crankshaft 6, pin 25 is an elliptical trajectory Q approximating an egg shape, pin 2 is
4 draws an arc locus R centered on the swing axis 20. The point in time when the pin 25 is positioned at q3 in FIG. 4 is the position where the rotation angle of the cylinder shaft 2 is Oo in the motion curve diagrams of FIGS. 5 and 6, and the cylinder shaft 2 is
rotates 360°, the four-bar link crank mechanism performs one cycle of movement, and the detaching rollers 38 and 39 perform one cycle of reverse rotation, forward rotation, and stationary movement.

When the connecting pin 13 rotates clockwise from the state shown in FIG. 4, the pin 25, that is, one end of the second connecting rod 23, moves clockwise on the elliptical trajectory Q.
The swinging lever 22 connected to the second connecting rod 23 by the pin 24 is operated while the pin 25 moves from point q3 to point q5, that is, when the cylinder shaft 2 changes from the rotation angle O to 9.
While rotating to 0'', it is rotated counterclockwise from the position shown by the solid line in FIG. 4. As the bar 22 rotates counterclockwise, the sector gear 35 also rotates counterclockwise. The detaching rollers 38 and 39 are rotated in the reverse direction via the differential gear mechanism 26 and the intermediate gear 37.While the cylinder shaft 2 further rotates at a rotation angle of 18o0, the pin 25 moves from the position of point q5 to the position of point q1, and the swing lever 22 is accordingly rotated clockwise, and its tip, that is, the pin 24, moves from the position shown at point r5 to the position shown at point r1. During this time, since the sector gear 35 is rotated clockwise, the detaching rollers 38 and 39 are driven to rotate in the normal direction in the opposite direction.

While the cylinder shaft 2 further rotates from a rotation angle of 180'' to 360°, the pin 25 moves from point ql to point q3.
This movement locus forms a circular arc with a substantially constant radius, and the length of the second connecting rod 23 is formed to be substantially the same as the radius of curvature of the circular arc. If pin 24 is located at the center of curvature of the arc when pin 25 is at point q1, the position of pin 24 does not change even if pin 25 moves from point q1 to point q3.

Therefore, during this time, the sector gear 35 is not rotated and only the rotation of the cylinder shaft 2 is input to the differential gear mechanism 26.

The movements of the detaching rollers 38 and 39 are shown in Figure 5 (a
) is the momentum based on the rotation of the cylinder shaft 2, and
This is a synthetic movement with the momentum based on the movement of the sector gear 35 shown in (b), and the cylinder shaft 2 is rotationally driven at a constant speed, and the accompanying momentum is always a constant and positive value. Therefore, when the motion component caused by the sector gear 35 is 0, the output from the differential gear mechanism 26 is only the output based on the rotation of the cylinder shaft 2, and the detaching rollers 38 and 39 are driven in normal rotation as in the conventional device. ,ru.

However, in the device of the present invention, when the pin 25 moves to the point q1, the tip of the swinging lever 22, that is, the pin 2
Since the quality of the swinging lever 22 and the second connecting rod 23 is selected so that the pin 25 moves to the point r1 to the left of the center of curvature of the circular arc, the pin 25 moves to the point q.
1 to point q3, the pin 24 moves from the position of point r1 to the position of point r3. That is, while the cylinder shaft 2 rotates from a rotation angle of 180° to 360°,
The swing lever 22 is rotated counterclockwise, and the differential gear mechanism 26 includes a sector gear 35 and a detaching roller 38.
．． 39 in the reverse direction is input, and the motion component caused by the cylinder shaft 2 and the motion component caused by the sector gear 35 are combined by the differential gear mechanism 26, as shown in FIG.
As shown in a), the amount of displacement of the detaching roller 38.39 is almost O, and the detaching roller 38.3
9, the rotation angle of the cylinder shaft 2 is from 180° to 360°.
It remains almost stationary between '.

Therefore, in this device, the rotation angle of the cylinder shaft 2 is 18
Detaching roller 38.39 from 0° to 360°
is held almost stationary, and the detaching rollers 38, 39 are driven in normal rotation only during the period in which the top comb is acting, so that the detaching rollers 38, 39 are rotated in the normal direction when the top comb has finished acting on the fleece. Continued introduction of short fibers, impurities, etc. into the spun product is reliably prevented. That is, as shown in (b') in FIG. 6, in the conventional device, when the detaching roller shifts from normal rotation to slow normal rotation, the normal rotation of the detaching roller 38, 39 gradually changes. During the action of the top comb, the fleece drawing speed decreases, and the fleece ends are no longer restrained, resulting in poor separation performance. However, in this device, as shown in FIG. 6(a), the detaching roller 38. The normal rotation speed of the cylinder shaft 2 is approximately constant until the rotation angle of the cylinder shaft 2 is around 180 degrees, and the fleece drawing speed is maintained constant during the top comb operation, so that the separation ability is improved.

Note that the present invention is not limited to the above-mentioned embodiment, and the shapes of both elliptical gears 8 and 12 may be changed to a shape having an eccentricity other than 0.3. In this case, the eccentricity is 0.25-0.
A range of 35 is preferable, and by changing the eccentricity within that range, the starting position of the stopping period of the detaching roller 38 and 39 can be adjusted to a rotation angle of 160° to 200° of the cylinder shaft 2.
Changed within a range of °. Also, contrary to the above embodiment, when the sector gear 35 rotates clockwise, the detaching roller 3
The differential gear mechanism 26 may be configured so that the pin 8.39 is driven in reverse, and in that case, the symmetrical position on the opposite side to the arc portion qlq2q3 of the locus Q of the pin 25 is set to the stationary position of the detaching roller 38.39. It will be used as a movement trajectory for the period.

Effects of the Invention As detailed above, according to the present invention, during the period of normal rotation of the detaching roller when the top comb acts on the fleece, the entire normal rotation of the detaching roller is completed and its rotational speed is maintained constant. Therefore, unlike conventional equipment, during the action of the top comb, the fleece drawing speed decreases and the end of the fleece is no longer restrained, and the fleece is fed out, causing short fibers to be brought in with the fleece and reducing the separation ability. This improves the quality of the spun product.

In addition, since the drive I71 device does not use a clutch or cam structure and is composed of a link mechanism and a differential gear mechanism, noise generation due to impact noise or impact stress occurs when changing the rotation direction of the detaching roller. This has the excellent effect of avoiding damage to parts due to

[Brief explanation of drawings]

Fig. 1 is a front sectional view of a drive device embodying this invention, Fig. 2 is a plan sectional view, Fig. 3 is a sectional view taken along line A-A in Fig. 1, and Fig. 4 is a four-bar link crank mechanism. The fifth factor is a diagram showing the change in the motion component of the sector gear input to the differential gear mechanism and the motion component of the cylinder shaft as the cylinder shaft rotates. FIG. 3 is a diagram showing the amount of displacement of the detaching roller as the cylinder shaft rotates. Cylinder shaft 2 as main shaft, elliptical gear 8゜12,
Connection pin 13, crank plate 14, swing lever 17, connecting rod 18, swing shaft 20. Swing lever 22, second connecting rod 23, differential gear mechanism 26, sector gear 35, detaching rollers 38, 39
゜Patent applicant Tsukahisa Toyota Industries Corporation Agent Patent attorney On 1) Hironobu Figure 1-A Drawing 1 Figure 3

Claims (1)

[Claims] 1. A four-bar link crank mechanism in a coma that combines the rotational motion of the main shaft and a predetermined forward and reverse rotational motion using a differential gear mechanism and transmits the forward and reverse rotational motions to a detaching roller. is arranged so as to be able to rotate integrally on the same axis as an elliptical gear of the same size that meshes with an elliptical gear that is arranged so as to be able to rotate integrally with the main shaft, and to apply a rocking motion of a predetermined amplitude to the differential gear mechanism. A rocking lever that can rotate integrally with a rocking shaft for input and an extended end of the connecting rod of the four-bar link crank mechanism are connected by a second connecting rod, and the length of the second connecting rod is determined. The movement locus of the connecting rod is made equal to the radius of curvature of the approximately circular arc portion, and one rotation of the main shaft causes the detaching roller to perform one cycle of reverse rotation, forward rotation, and rest, and after the normal rotation is completed, the above-mentioned Comber detaching roller drive in which a swinging lever moves at a constant speed in a direction away from the connecting point of both connecting rods, and the starting point of the detaching roller's rest period is in the range of 160° to 200° of the main shaft rotation angle. Device. 2. The combed detaching roller according to claim 1, wherein the second connecting rod is pin-coupled to the connecting rod of the four-bar link crank mechanism so as to be movable in the same plane as the connecting rod. Drive device.