JP2857014B2 - Driving device for detaching roller in comba - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a driving device for a detaching roller in a comber, and more particularly to a driving device for a detaching roller capable of coping with a high speed operation of a machine base.

[0002]

2. Description of the Related Art In a comber as a spinning machine, a needle row (cylinder needle) in which a supplied wrap is gripped at a position where a nipper device is retracted, and a tip of the wrap is implanted in a cylinder half wrap of a combing cylinder. The wrap is combed to remove short fibers and the like (including contaminants such as neps) to obtain a fleece. The fleece is moved toward the detaching roller by the advance of the nipper. In response to the advance of the fleece, the detaching roller is rotated in the reverse direction, and the fleece (leading fleece) pulled out earlier is retracted.
The rear end of the fleece and the front end of the newly carded fleece (following fleece) are overlapped. Thereafter, the detaching roller is rotated forward again to pull out the succeeding fleece joined to the preceding fleece. At this time, the action of the top comb combing the rear end of the fleece is repeated.

The detaching roller repeatedly performs reverse rotation and normal rotation every time combing is performed in order to perform the above-mentioned piecing action. Further, in order to sequentially feed the pieced fleece, it is necessary to apply a rotation to the detaching roller so as to advance the position by a small amount each time one combing is performed.

[0004] In one cycle of the combing operation, the combing operation by the cylinder needle is performed during about 1/2 rotation of the combing cylinder. During this time, the detaching roller stops or slowly rotates close to the stop. The detaching roller performs the above-described reverse rotation and normal rotation during the remaining approximately 1/2 rotation of the combing cylinder.

In order to perform such a movement of the detaching roller, a differential gear mechanism is attached to the input shaft of the detaching roller, and a constant speed input and an unequal speed rotation input are applied to the differential gear mechanism. , And both inputs are combined.
As a means for applying the non-uniform rotation input, there is a mechanism using a cam groove and a cam ball. In this case, an ideal movement curve for joining and pulling out the fleece is obtained by designing the cam groove. However, in the case of the mechanism using the cam groove and the cam ball, the inertia of the drive-related members from the cam ball to the detaching roller is concentrated on the contact portion between the cam groove and the cam ball when the detaching roller reversely rotates and accelerates. Therefore, it is easily worn. In recent years, the speed of the comber has been increased, and the detaching roller needs to be rotated at a high speed. However, in the case of a mechanism using a cam groove and a cam ball, the impact between the cam groove and the cam ball when the detaching roller switches from reverse rotation to normal rotation increases with an increase in speed. As a result, as the speed of the comber increases, the noise and vibration increase, and the cam wears more severely.
Deterioration of sliver quality also occurs. Therefore, a mechanism using a cam groove and a cam ball is not suitable for high speed operation.

In order to cope with the high speed, a so-called camless comber using a link mechanism has been proposed as a means for giving the unequal-speed rotation input. For example, in the device disclosed in Japanese Patent Application Laid-Open No. 3-97921, the constant-velocity rotational motion transmitted from the drive source is divided into two drive systems,
In the first drive system, a non-constant rotational motion is formed from the constant rotational motion via the crank mechanism and the four-bar link mechanism, and the motion is transmitted to the input shaft of the differential gear mechanism. In the second drive system, the constant speed rotational motion is made into a swinging motion by a crank mechanism, and then transmitted to the planetary gear side of the differential gear mechanism as reciprocating motion via a connecting lever and link means. Then, the detaching roller is driven by the output of the differential gear mechanism that combines the movements of both drive systems.

[0007]

In the above device, the link is swung by changing the rotational movement into a reciprocating arc movement by a crank mechanism, and the link connecting pin of the link determines the dead center of the swinging movement by the combination of the links by the combing action. The configuration in which the sheet is passed twice in one cycle causes the detaching roller to stop or to perform slow forward rotation close to the stop. As a result, an ideal motion curve similar to that of a cam comber can be obtained while being a camless comber.

However, since the link connecting pin passes through the dead center twice, the swing range of the link performing the swinging motion becomes large. For example, in the case of a comb with 350 nips per minute, the link reciprocates 11.7 times per second, and the greater the swing range of the link, the more easily the abrasion of the connection pin proceeds. In the above-mentioned conventional apparatus, there is not much problem in the operation up to about 350 nips per minute, but in the case of high-speed operation of 400 nips per minute or more, when the operation is performed for a long time, the connection pin-related wear is remarkable. Become. as a result,
Since the detaching roller rotates incorrectly, there is a problem that a high-quality fleece may not be produced.

The present invention has been made in view of the above problems, and has as its object to reduce wear of a drive mechanism for inputting unequal speed rotation to a detaching roller by using a link mechanism. An object of the present invention is to provide a driving device for a detaching roller in a comber which can cope with a higher speed of a machine base.

[0010]

In order to achieve the above object, according to the present invention, the constant speed rotary motion transmitted from the drive source is divided into two drive systems, and the first drive system includes a crank mechanism and a four-wheel drive.
A non-uniform rotational motion is formed from the uniform rotational motion through the joint link mechanism, and the motion is transmitted to the input shaft of the differential gear mechanism. In the second drive system, the uniform rotational motion is performed by the crank mechanism. After the swinging motion, the reciprocating motion is transmitted to the planetary gear side of the differential gear mechanism via the connecting lever and the link means, and the detaching roller is driven by the output of the differential gear mechanism that combines the motions of both driving systems. A first double link that swings around a shaft in front of a crank lever that swings by the crank mechanism of the second drive system; A second double link swinging about a support shaft is provided above the link, and a third double link swinging about the pin is provided on a pin supported near the base end of the first double link. And the first
The front end of the double link is connected to the base end of the second double link via a link, and the front end of the second double link is connected to the crank lever via a link. A third double link is connected via a pin to a second end of the connecting link whose end is connected to a shaft on the planetary gear side of the differential gear mechanism, and the second end is connected via a pin. A third double link via a pin to a first end of the link connected to the crank lever, and an end of a reciprocating locus of a pin connecting the link and the third double link. The straight line connecting the swing center of the crank lever is located near the end of the reciprocating locus of the pin connecting the crank lever and the link, and the latter reciprocating locus does not intersect the straight line. Reciprocating rail of pin supported near the base of double link And a straight line connecting the position of the shaft on the planetary gear side farthest from the trajectory is near the end of the reciprocating trajectory of the pin connecting the connecting link and the third double link, The reciprocating locus of the latter does not cross the straight line.

[0011]

In the driving device according to the present invention, the constant speed rotary motion transmitted from the driving source is divided into two driving systems. In the first drive system, a non-constant rotational motion is formed from the constant rotational motion via the crank mechanism and the four-bar link mechanism, and the motion is transmitted to the input shaft of the differential gear mechanism. In the second drive system, the constant speed rotational motion is made into a swinging motion by the crank mechanism, and then transmitted as reciprocating motion to the planetary gear side of the differential gear mechanism via the connecting lever and the link means. Then, the movements of both drive systems are combined by the differential gear mechanism, and the output thereof drives the detaching roller.

A crank lever that swings by the crank mechanism of the second drive system is connected to a connecting link connected to the planetary gear side of the differential gear mechanism via a link and a third double link. Have been. The swing center of the third double link is supported by the first double link, and the first double link and the crank lever are connected to the second double link via the respective links. By using the three double links, the swing range of the crank lever and the swing range of the second double link do not exceed the dead center, and the swing ranges thereof are narrowed. as a result,
Wear of the connecting part is reduced.

[0013]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. As shown in FIG. 1, a V-belt 2 is wound around a driving pulley 1 and a driving source (not shown). A gear 4 is fixed to an end of the drive shaft 3 to which the drive pulley 1 is fixed. The cylinder shaft 5 constituting the first drive system D ₁ is arranged in parallel with the drive shaft 3. A gear 6 meshing with the gear 4, a gear 7, and a pair of eccentric wheels 8 are fixed to the cylinder shaft 5, and the base end of a crank link 9 constituting a crank mechanism is rotatable on each eccentric wheel 8. Mated. Double crank link 9
The shaft 10 is fixed between the tips of the shafts. A pair of links 11 are rotatably supported at the base end of the cylinder shaft 5 with the gear 7 interposed therebetween, and a shaft 12 is supported at the tip of both links 11. A gear 13 meshing with the gear 7 and a first end of a pair of links 14 are rotatably supported on the shaft 12. The shaft 10 has second ends of both links 14 and a gear 15 meshing with the gear 13.
Are rotatably supported.

The shaft 1 is located above the cylinder shaft 5.
6 is rotatably supported at a predetermined position by a bearing (not shown). The shaft 10 has a first link 17
The ends are rotatably supported, and the second ends of both links 17 are rotatably supported by the shaft 16. Shaft 1
A gear 18 meshing with the gear 15 and a gear 19 meshing with a gear of a differential gear mechanism described later are fixed to 6.
The gears 7, 13, 15, and 18 always mesh in this order. The links 11, 14, and 17 constitute a four-bar link mechanism L.

In the vicinity of the shaft 16, a shaft 20 constituting a differential gear mechanism G is rotatably supported at a predetermined position in parallel with the shaft 16 by a bearing (not shown).
A lever 21 having a pair of arms integrally connected to the shaft 20 is fixed at a base end thereof. Shafts 22 and 23 are fixed to the lever 21 in parallel with the shaft 20. The shaft 20 has a gear 24 meshing with the gear 19,
The gear 25 is rotatably supported. The gear 25 is composed of gears 28, 2 fixed to detaching rollers 26, 27.
9 is engaged. A first end of the connecting link 30 and a gear 31 meshing with the gear 24 are rotatably supported on the shaft 22. The shaft 31 has a gear 31
A long gear 32 meshing with the gear 25 is rotatably supported. That is, the rotation of the shaft 16
9, 24, 31 to the gear 32,
Is rotated by the detaching rollers 26, 2 via the gear 25.
7 are transmitted to the gears 28 and 29. The above configuration is basically the same as the configuration disclosed in Japanese Patent Application Laid-Open No. 3-97921.

A crankshaft 33 constituting the _second drive system D2 is disposed in parallel with the drive shaft 3, and a gear 34 having the same number of teeth as the gear 6 is fixed to the crankshaft 33. An intermediate gear shaft 35 is provided between the drive shaft 3 and the crankshaft 33, and a gear 36 meshing with the gear 4 and the gear 34 is fixed to the intermediate gear shaft 35. The base end of the crank 37a is fixed to the crankshaft 33. A support shaft (not shown) rotatably provided via a bearing 38 on an extension of the crankshaft 33.
, A base end of a crank 37b paired with the crank 37a is fixed. Crank pins 39 are supported at the tips of both cranks 37a and 37b.

As shown in FIGS. 1-3, the crankpin 3
A support bracket 40 is fixed to a frame (not shown) behind the rotation range 9 (rightward in FIGS. 1 to 3). A pin 41 is supported by the support bracket 40, and a first end of a crank lever 42 is rotatably supported by the pin 41. Near the second end of the crank lever 42, a first end of a crank rod 43 is connected to a crank lever pin 44.
Is rotatably connected via a. Crank rod 4
The second end 3 is rotatably supported by a crank pin 39. Therefore, the crank lever 42 swings about the pin 41 by the rotation of the cranks 37a and 37b.

A pair of support shafts 45a and 45b are fixed to a frame (not shown) at a position higher than the pin 41 in front of the rotation range of the crank pin 39 (left side in FIGS. 1 to 3). A lever 46a as a first double link is rotatably supported at the base end of the support shaft 45a.
A lever 46b is rotatably supported by 45b.
A pin 47 is provided between the levers 46a and 46b at a position eccentric to the support shafts 45a and 45b near the base ends of the levers 46a and 46b.
(Shown in FIGS. 2, 4, and 5), and the base end of a lever 48 is rotatably supported by a pin 47. Lever 48
Supports the second end of the connecting link 30 rotatably via a pin 49 and the first end of the link 50.
It is rotatably connected to the end via a pin 51. A second end of the link 50 is rotatably connected to a second end of the crank lever 42 via a pin 52. Lever 4
8 constitutes a third double link, lever 48
Swings about the pin 47 in a state where the angle between the straight line connecting the pin 47 and the straight line connecting the pin 51 and the pin 47 is always constant.

A support bracket 53 is fixedly mounted on a frame (not shown) above the support shafts 45a and 45b, and a base end of a lever 55 pivots on a support shaft 54 projecting from the support bracket 53. Supported as possible. Lever 5
A first end of a link 57 is rotatably connected to a distal end of the link 5 via a pin 56, and a second end of the link 57 is
Is rotatably supported. A first end of a link 59 is rotatably connected to a base end of the lever 55 via a pin 58, and a second end of the link 59 is rotatably connected to a distal end of the lever 46a via a pin 60. Are linked. Pin 5
The position 8 is set to be lower than a straight line connecting the center of the pin 56 and the support shaft 54. Lever 55 is the second
The lever 55 comprises a pin 56 and a support shaft 5
4 and the straight line connecting the pin 58 and the support shaft 54 make an angle around the support shaft 54 at a constant angle.

The lever 4 constituting the first double link
6a is a straight line connecting the pin 47 and the support shaft 45a, and the pin 6
It swings around the support shaft 45a in a state where the angle between the zero and the straight line connecting the support shaft 45a is always constant.

The lengths of the crank 37a, the crank lever 42, the crank rod 43, the levers 46a, 48, 55 and the links 50, 57, 59 are set so as to satisfy the following conditions. The end of the reciprocating locus of the pin 51 (FIG. 7)
A line connecting the swing center of the crank lever 42, that is, the pin 41, is near the end of the reciprocating locus of the pin 52, and the reciprocating locus of the pin 52 does not intersect the straight line. A straight line connecting the end of the reciprocating locus of the pin 47 (shown as a47 in FIG. 7) and the position of the shaft 22 on the planetary gear side farthest from the locus (shown as a22 in FIG. 7) is It is near the end of the reciprocating locus, and the reciprocating locus of the pin 49 does not intersect the straight line.

Next, the operation of the device configured as described above will be described. First explaining the first operation of the driving system D _1. The constant velocity circular motion transmitted from the driving source to the driving pulley 1 via the V-belt 2 is transmitted to the first driving system D ₁ via the gears 4 and 6. As the gear 6 rotates, the cylinder shaft 5
When it rotates in the direction of the arrow in FIG. 1, the eccentric wheel 8 also rotates in the same direction. Then, the eccentric wheel 8 moves from f8 to g8 to h shown in FIG.
As the shaft rotates from 8 to f8, the shaft 10 becomes f10
reciprocating between h10, the shaft 12 is f12 to h12
Reciprocating between Also, the rotation of the gear 7 is
5 and 18 and transmitted to the shaft 16.
Of the input gear 2 of the differential gear mechanism G via the gear 19
4 is transmitted. Since a rotational force is applied to the gears 13, 15, and 18 even when the shaft 10 and the shaft 12 move, the rotational force of the gear 5 and the rotational force based on the movement of the shaft 10 and the shaft 12 are not combined on the shaft 16. A constant rotational movement is transmitted.

The rotation of the gear 24 is transmitted to the gear 25 via the gears 31 and 32, and the rotation of the gear 25 causes the gears 28 and 2 to rotate.
9 and the detaching rollers 26 and 27 are rotated. If the shaft 22 does not move, the detaching rollers 26, 2
The amount of movement of the surface 7 is represented by a curve M indicated by a broken line in FIG.

Next, the operation of the _second drive system D2 will be described.
The rotation of the driving pulley 1 is rotated by the second gear via the gears 4, 36, 34.
It is transmitted in the drive system D _2. Since the gears 6 and 34 have the same number of teeth, the crankshaft 33 rotates in the opposite direction, that is, in the direction of the arrow in FIG. With the rotation of the crankshaft 33, the crank 37
a, 37b rotate in the same direction as the crankshaft 33,
The crank lever 42 swings about the pin 41 via the crank pin 39, the crank rod 43, and the crank lever pin 44. Then, when the crank pin 39 rotates in the order of a39 → b39 → c39 → d39 → a39 in FIG. 7, the crank lever pin 44 moves to a44 → b44 → c
It reciprocates 44 → b44 → a44. The pin 52 reciprocates in the order of a52 → b52 → c52 → b52 → a52. FIG. 3 is a view corresponding to a state where the pin 44 is at the position of c44.

When the pin 52 reciprocates between a52 and c52, the lever 55 swings about the support shaft 54 via the link 57, and the pin 56 is moved from a56 to b56 to c56 in FIG.
→ b56 → a56 reciprocating, the pin 58 is a58 → b
It reciprocates in the order of 58 → c58 → b58 → a58. Then, the lever 46a connected to the lever 55 via the link 59 is swung about the support shaft 45a, and the pin 60 is moved to the position shown in FIG.
Reciprocatingly moves in the order of a60 → b60 → c60 → b60 → a60, and the pin 47 moves from a47 → b47 → c47 → b47 in FIG.
→ Reciprocate with a47.

The pivot center of the lever 48 to which the connecting link 30 is connected via the pin 49 is a pin 47,
A pin 51 connecting the link 50 and the lever 48 moves with the swing of the crank lever 42. Then, with the swing of the crank lever 42, the pin 51 is moved to the position a51 in FIG.
The pin 49 reciprocates in the order of b51 → c51 → b51 → a51, and the pin 49 reciprocates in the order of a49 → b49 → c49 → b49 → a49. As a result, the connecting link 30 is reciprocated, and the motion is input to the planetary gear side of the differential gear mechanism G as reciprocating motion.

While the crank pin 39 moves in the vicinity of the position a39, the pin 49 moves in the vicinity of a49, and the shaft 22 slightly moves in the vicinity of a22, and is practically almost stationary. As is apparent from FIG. 7, the crank pin 39 is moved from b39 through c39 to d39.
The amount of movement of the shaft 22 during the movement of the crank pin 39 is smaller than the amount of movement of the shaft 22 during the movement of the crank pin 39 from d39 to b39 via a39. Then, the shaft 22 reciprocates between the vicinity of a22 and c22 while the crank 37a rotates substantially 180 °.

The gear 31 is rotatable with respect to the shaft 22, and the gears 24, 31, 32, and 25 are differential gear mechanisms G.
Is composed. Therefore, if the gear 24 is fixed, the gear 25 moves at a constant speed ratio by the movement of the shaft 22, and the detaching rollers 26, 27 are rotated by the gears 28, 29 meshing with the gear 25. As a result, the amount of movement of the surfaces of the detaching rollers 26 and 27 by one rotation of the cranks 37a and 37b becomes a curve K shown by a solid line in FIG.

Since the rotational forces of both drive systems D ₁ and D ₂ are combined and transmitted to the detaching rollers 26 and 27 by the differential gear mechanism G, the amount of movement of the surfaces of the detaching rollers 26 and 27 is shown in FIG. 8 is a curve N obtained by combining the two curves M and K.

When the crank lever 42 is rotated in the counterclockwise direction in FIG. 7, that is, when the shaft 22 moves toward the c22 side, the detaching rollers 26 and 27 are reversed, and the leading fleece is fed out. . When the crank lever 42 is rotated clockwise in FIG. 7, that is, when the shaft 22 moves toward the a22 side, the detaching rollers 26 and 27 are rotated forward, and the joining of the preceding fleece and the succeeding fleece and the succeeding fleece are performed. The fleece is pulled out.

Each of the levers 46a, 48 and 55 constitutes a double link having a constant angle formed by a straight line connecting the center of connection with the link and the swing center of the lever 46a, 48 and 55. The movement of the link 50 is restricted. As shown in FIG. 7, a pin 49 connecting the connecting link 30 and the lever 48 and a pin 52 connecting the link 50 and the crank lever 42 are different from the conventional device, and cannot move beyond the dead center. Absent. Therefore, the swing amount of the connecting link 30, the crank lever 42, and the like during one rotation of the crank 37a is smaller than that of the conventional configuration in which the reciprocating motion exceeds the dead center,
The wear related to the connection shaft during high-speed operation is reduced, and the durability is improved.

The present invention is not limited to the above-described embodiment. For example, the crank pin 39 may be supported only by the crank 37a without the crank 37b forming a pair with the crank 37a. Further, a pair of arms may be used instead of the lever 21 that supports both shafts 22 and 23 of the differential gear mechanism G.

[0033]

As described above in detail, according to the present invention, although it is a camless comber, an ideal motion curve similar to that of a cam comber can be obtained, and a differential gear mechanism for transmitting a rotational force to a detaching roller. The durability of the link mechanism for giving an input to the planetary gear side is improved, and higher speed operation is possible.

[Brief description of the drawings]

FIG. 1 is a perspective view of a main part of a driving device according to the present invention.

FIG. 2 is a side view of a main part.

FIG. 3 is a side view of a main part in a state where a crank lever is arranged at a lowermost position.

FIG. 4 is a partial plan view.

FIG. 5 is a partially enlarged view of FIG. 2;

FIG. 6 is an explanatory view of the movement of the first drive system.

FIG. 7 is an explanatory diagram of movement of a second drive system.

FIG. 8 is a movement curve diagram of a detaching roller.

[Explanation of symbols]

3 ... drive shaft, 5 ... cylinder shaft, 8 ... eccentric wheel forming a crank mechanism, 9 ... also crank link,
Reference numeral 11 denotes a link that forms a four-bar linkage, 14 denotes a link, 17 denotes a link, 19 denotes a gear, 22 denotes a shaft that forms a differential gear mechanism, 26 and 27 denotes a detaching roller, and 30 denotes a connecting link. 41 ... pin, 4
2 ... Crank lever, 45a ... Support shaft, 46a ... Lever as first double link, 47 ... Pin, 48 ... Lever as third double link, 49 ... Pin, 50 ... Link,
51, 52 ... pin, 54 ... support shaft, 55 ... lever as a second double link, 57, 59 ... link, 60 ... pin,
D ₁ : first drive system, D ₂ : second drive system, G: differential gear mechanism, L: four-node link mechanism.

Claims (1)

(57) [Claims] 1. A constant speed rotary motion transmitted from a drive source is divided into two drive systems (D ₁ , D ₂ ), and a first drive system (D ₁ ) includes a crank mechanism and a four-bar link mechanism (L). To form an unequal-speed rotation from the constant-speed rotation, which is transmitted to the input shaft of the differential gear mechanism (G), and the second drive system (D ₂ ) performs the constant-speed rotation. After the swing motion by the crank mechanism, the reciprocating motion is transmitted to the planetary gear side of the differential gear mechanism (G) via the connecting lever and the link means, and the motions of both drive systems (D ₁ , D ₂ ) are combined. Detaching rollers (26, 27) by the output of the differential gear mechanism (G)
A driving device for a detaching roller in a comber for driving a shaft (4) in front of a crank lever (42) that swings by a crank mechanism of the _second drive system (D ₂ ).
A first double link (46a) swinging about 5a) is provided, and a second double link (55) swinging about the support shaft (54) above the double link (46a). And the first
Pin (4) supported near the base end of the double link (46a) of
7) is provided with a third double link (48) swinging around the pin (47), and the tip of the first double link (46a) and the base of the second double link (55) are provided. The near end is connected via a link (59), and the near end of the second double link (55) and the crank lever (42) are linked (57).
And a third double link to a second end of the connecting link (30), the first end of which is connected to the shaft (22) on the planetary gear side of the differential gear mechanism (G). (4
8) is connected via a pin (49) and a third end is connected to a first end of a link (50) whose second end is connected to a crank lever (42) via a pin (52). The heavy link (48) is connected via a pin (51), and the end (a51) of the reciprocating locus of the pin (51) connecting the link (50) and the third double link (48) is connected to the crank. A straight line connecting the swing center of the lever (42) is near the end of the reciprocating locus of the pin (52) connecting the crank lever (42) and the link (50), and the latter reciprocates.
Locus is configured so as not to cross the straight line, and the first doubly linked end of the reciprocating path of the pin which supports the base end side of the (46a) (47) (a47 ), farthest from the locus A straight line connecting the position (a22) of the shaft (22) on the planetary gear side is a connecting link (3).
0) and the third double link (48).
9) A driving device for a detaching roller in a comber, wherein the driving device is arranged near the end of the reciprocating locus of 9) and the latter reciprocating locus does not intersect the straight line.