JPS6047370B2 - Combing cylinder speed change mechanism in coamer - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a transmission mechanism for a combing cylinder in a comb.

Generally, the combing sill of a comb is rotated at a constant speed, but it is effective to increase the circumferential speed of rotation of the cylinder in the same operating period and time of the nipper holding the wrap, so that the cylinder needle can comb the wrap held by the nipper. By increasing the length of the cylinder to increase the number of cylinder needles that pass through the lap, or by increasing the circumferential rotational speed of the cylinder, the forward distance of the nipper while the combing action is being performed is made relatively short.

In order to perform effective combing work by reducing the gap between the cylinder needle and the nipper, that is, the change in the cylinder gauge, and making the gauge uniform, it was necessary to rotate the cylinder once. On the other hand, during combing, by slowing down the circumferential rotational speed of the cylinder, the impact when the cylinder needle enters the wrap is reduced, reducing fluctuations in the load acting on the cylinder, and the speed at which the wrap is combed is slowed down. As a result, it was necessary to change the speed of the cylinder in order to perform the combing work effectively.

By the way, the circumferential rotational speed of the cylinder should be increased depending on the type and fineness of the raw cotton, for example, if the fineness is thick and the fiber strength is strong, the speed should be increased, and if the fineness is thin and the fibers are 1', it should be slowed down. As shown in FIG. 9, the conventional transmission mechanism for this cylinder is a gear 21 that is eccentrically attached to the drive shaft 20, and a gear 24 that is eccentrically attached to the rotating shaft 23 of the cylinder 22. The constant speed rotation of the drive shaft 20 is transmitted to the cylinder 22 as variable speed rotation via the gears 21, 24 and the rotating shaft 23.
However, in the conventional mechanism using the eccentric gears 21 and 24, the backlash of the gears 21 and 24 not only causes vibration and noise, but also causes rapid wear of the gears 21 and 24, which is an obstacle to increasing speed. I was getting used to it.

Further, during the combing operation using the cylinder needle, the load increases, and this load variation acts on the eccentric gears 21 and 24, resulting in local wear of the gears 21 and 24. Incidentally, this local wear of the eccentric gears 21 and 24 can be solved by using a circular gear (not shown) in which the meshing position and force nucleus changes each time, but there is another problem that manufacturing a circular gear is extremely difficult. There is. The object of the present invention is to prevent vibration, noise, or local wear by interposing a double crank mechanism that forms a non-parallel four-bar link mechanism between the rotating shafts that support the cylinders, and to It is an object of the present invention to provide a speed change mechanism for a combing cylinder in a comb that can perform a proper combing operation by taking out a smooth speed change rotational motion and can further increase the speed.

Hereinafter, one embodiment of the present invention will be described with reference to FIGS. 1 and 2. In the drawings, reference numeral 1 denotes a drive shaft rotatably mounted horizontally to a drive gear mechanism storage case 2 via a bearing 3. The rotation of a motor (not shown) is transmitted to the drive shaft 1 via a gear mechanism, and the drive shaft 1 is configured to actively rotate in synchronization with the nipper motion.

4 is a cylinder shaft supported on a combing machine stand (not shown) in parallel with the drive shaft 1, and 5 is a combing cylinder mounted on the same shaft 7, which is connected to the nipper by a cylinder needle 6 on a part of its outer circumference. It is designed to comb the sandwiched plastic wrap.

Reference numeral 7 indicates the entire transmission mechanism articulated with the left end of the drive shaft 1 and the right end of the cylinder shaft 4 which is eccentric with respect to this, and 8
10 is a drive lever whose base end is fitted and fixed to the drive shaft 1 via a key 9; 10 is a drive lever whose base end is fitted and fixed to the right end of the cylinder shaft 4 via a key 11; 12 is a drive lever on both ends. The connecting link is rotatably connected to the tips of the drive and driven levers 8 and 10 by pins 13 and 14, respectively, so that the rotation of the drive lever 8 can be transmitted to the driven lever 10 at a variable speed. I have to.

By the way, in this embodiment, the lengths of the four sides AB, BC, CD, and AC connecting the centers A, B, C, and D of the drive shaft 1, the cylinder shaft 4, and the pins 13 and 14 are, for example, 25.4 and 25.4, respectively. 78, 103, and 82 Tmm, which constitutes a double crank mechanism that can transmit the rotation of the drive shaft 1 to the cylinder shaft 4, and has opposite sides. AB, CD or A
It is a non-parallel four-bar link mechanism in which at least one of C and BD has a different length on opposite sides, and it can be set to any size as long as it satisfies the three requirements necessary for a double crank mechanism. be able to.

Next, the operation of the transmission mechanism of the combing cylinder 5 constructed as described above will be explained.

Now, in FIG. 2, the drive lever 8 is on the vertical axis y, and the driven lever 10 is in a position rotated about 30 degrees counterclockwise from the horizontal axis X. When the drive shaft 1 is rotated in the counterclockwise direction in FIG. Rotated in the same direction around the center. At this time, the drive lever 8 and the pin 1 of the connecting link 12
Since the drive shaft 1 is in a fixed position, the center C of the drive shaft 1 moves on a circular locus P with a radius AC centered on the center A of the drive shaft 1, and the center D of the connecting link 12 and the pin 14 of the driven lever 10 is ,
Since the cylinder shaft 4 is in a fixed position, it moves on a circular locus Q having a radius BD and centering on the axis B of the cylinder shaft 4. When the rotation angle θ of the drive lever 8 reaches 45 degrees as shown by the two-dot chain line in FIG. 2 from the position shown by the solid line in FIG.
The rotation angle θ″ at zero is approximately 46 degrees.

Furthermore, when the drive lever 8 is rotated 90 degrees as shown by the solid line in FIG. Movement angle 0
becomes 135 degrees, the rotation angle θ5 of the driven lever becomes approximately 11
It will be 6 degrees.

Similarly, as is clear from FIGS. 4 and 5, when the rotation angle θ of the drive lever 8 becomes 180, 225, 270 and 315 degrees, the rotation angle 0'' of the driven lever 10 becomes 146 degrees, respectively. , 180, 233 and 302 degrees.

The relationship between the rotation angles θ and θ″ of the driving lever 8 and the driven lever 10 with respect to time is expressed in a graph as shown in FIG. 6. According to the graph of FIG. In a range T1 where the angle θ is approximately 95 to 180 degrees, the angular velocity of the driven lever 10 becomes slow, and the rotational circumferential speed of the needle 6 of the combing cylinder 5 becomes slow.

On the other hand, the rotation angle θ of the drive lever 8 is approximately 180 to 34
In the range T2 of 0 degrees, the angular velocity of the driven lever 10 becomes faster, and the rotational peripheral speed of the needle 6 of the combing cylinder 5 becomes faster. Therefore, the timing of the combing operation by the needle 6 of the cylinder 5 is set to a range T2 where the angular velocity of the driven lever 10 is high and the rotational speed of the cylinder 5 is fast, or a range T1 where the angular velocity of the driven lever 10 is slow and the rotational speed of the cylinder 5 is slow. By matching, a proper combing operation is performed that matches the type and fineness of the raw cotton. Now, in the embodiment of the present invention, a drive lever 8 is fixed to the drive shaft 1, a driven lever 10 is fixed to the cylinder shaft 4, and a connecting link 12 is connected between the tips of both levers 8 and 10 by pins 13 and 14. Since the constant speed rotation of the drive shaft 1 is transmitted as non-uniform speed rotation to the cylinder shaft 4 via the double crank mechanism, vibration and noise due to backlash that exist in conventional transmission mechanisms using eccentric gears can be eliminated. Combing cylinder 5
can be rotated smoothly, and the combing operation can be performed at high speed. In the embodiment of the present invention, the transmission mechanism 7 is connected between the drive shaft 1 and the cylinder shaft 4, but in this way, the transmission mechanism 7 can function as a coupling between the drive shaft 1 and the cylinder shaft 4. This makes it possible to simplify the mechanism by omitting couplings that are normally required for assembly.

Further, as shown in FIGS. 7 and 8, the present invention forms the drive lever 8 in a disk shape, and provides a plurality of connecting holes 15, 15a, 15b near the outer periphery of the drive lever 8. By changing the articulation position of the pin 13, that is, the rotational phase of the drive lever 8, the timing at which the needle 6 of the combing cylinder 5 starts and ends combing can be made to match the range T or T2 in FIG. 6 described above. It can also be made adjustable.

That is, when the needle 6 of the combing cylinder 5 starts combing, it can be confirmed by the position of a scale called an index (not shown), so when this position is confirmed, the pin 13 is inserted into the connecting hole 15a. The rotational speed of the combing cylinder 5 can be adjusted to slow down or speed up during the combing operation by changing the position of the connecting hole 15b or the position of the connecting hole 15b. The rotational position of the drive lever 8 can be adjusted using the key 9.
This can also be achieved by providing two or more fitting positions on the drive shaft 1 and changing the mounting position of the drive lever 8 with respect to the drive shaft 1.

As described in detail above, the present invention has a driving shaft that rotates at a constant speed in synchronization with the nipper motion, and a driven shaft that is connected to a combing cylinder, which are disposed parallel to each other and eccentrically. In order to change the speed and transmit rotation to the driven shaft, a double crank mechanism is provided for both shafts that forms a non-parallel four-bar link mechanism using them as a pair of fixed fulcrums, thereby preventing vibration, noise, and local wear. In addition, it is possible to smoothly drive the combing cylinder, which has the effect of increasing the speed of the combing operation.

[Brief explanation of the drawing]

FIG. 1 is a plan view showing an embodiment of the transmission mechanism for a combing cylinder of the present invention, FIG. 2 is a front view of the transmission mechanism, and FIGS. 3 to 5 are schematic front views each illustrating the operation of the transmission mechanism. 6 is a graph showing the relationship between the rotation angles of the drive shaft and the driven shaft, FIG. 7 is a front view showing another embodiment of the present invention, and FIG.
The figure is a sectional view taken along the line FF in FIG. 7, and FIG. 9 is a front view showing a conventional combing cylinder speed change mechanism. Drive shaft 1, cylinder shaft 4, transmission mechanism 7, drive lever 8,
Driven lever 10, connection link 12.

Claims (1)

[Claims] 1. A drive shaft that rotates at a constant speed in synchronization with the Nitzpa motion and a driven shaft connected to a combing cylinder are arranged parallel to each other and eccentrically, and the rotation of the drive shaft is changed in speed. A speed change mechanism for a coaming cylinder in a coamer, characterized in that a double crank mechanism is provided for both shafts to form a non-parallel four-bar link mechanism using them as a pair of fixed fulcrums in order to transmit the information to the driven shaft. 2. The drive lever connected to the drive shaft and forming part of the double crank mechanism is formed in a disc shape, and the drive lever has a plurality of connecting holes for changing the rotational phase. A speed change mechanism of a combing cylinder in the comb described in Section 3.