JPS61226094A - Speed variable clutch apparatus of sewing machine - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a clutch device for changing speed in a cycle sewing machine.

[Conventional technology]

Conventionally, as a clutch device for changing speed of a cycle sewing machine,
Various methods are used.For hole sewing machines, there are flat heel shift, ball change motor, and electromagnetic clutch types, and for bar tacking machines, there are 2 zero V hel.
These include the Cheeba Crunch and the planetary ball method.

[Problem that the invention seeks to solve]

However, with the flat belt shift type, the transmission is located under the table, which makes maintenance difficult and the heald tension is strong.
Not only is the bearing load large, but it also has the disadvantage of being prone to malfunction. In addition, for the ball change motor type,
Only three-phase AC power can be used, and although the stability is good, the cost is high. In addition, even the electromagnetic clutch type has an MfE point in the alignment MA property, since it is installed under the table, making it difficult to adjust the gap between the clutches.

On the other hand, with the planetary ball system, the mechanism is multi-flL and is expensive.Also, with the conventional mechanism of the two-way V-heald taper clutch type, the heddle tension is applied directly to the upper shaft of the sewing machine, making it difficult to step up to high speeds when changing gears. As a result, the pedal pressure is high, and the operation of the shutoff mechanism is 90 degrees different from the direction in which the pressing plate that operates the mechanism is operated, making it difficult to adjust. Furthermore, since the part where the switching clutch is pressed to change gears is the shaft of the end-to-end cam itself, it slides and stops rotating at the same time, and as it twists while applying force in the axial direction, deflection occurs. The coil spring interposed between the low-speed pulley and the low-speed pulley could not be fully compressed, and as a result, the elasticity of the pressing plate for shifting operations was reduced. Currently, we are facing the problem that it is difficult to produce the shape even though it has to be transformed into a new shape.

[Means for solving problems]

The present invention was made in view of the above-mentioned circumstances, and adopts the two-wood V-herl to Theba clutch type as its original form from among the various methods mentioned above, and integrates high and low speed pulleys into the body of the sewing machine. Equipped with one fixed pulley on a pedestal.
To provide a clutch device for shifting configured to prevent these heald tensions from being directly applied to the shaft, match the operating direction of a cutoff mechanism with the operating direction of a cutoff frame, and reduce the operating force of stepping on a pedal. The aim is to solve these problems.

〔Example〕

An embodiment of the present invention will be described below with reference to FIGS. 1 to 3.

First, I will explain the configuration.

The gear shifting clutch device of this embodiment mainly consists of a transmission E consisting of an operating means, a pulley support mechanism B, a transmission means C, and a driving means.

In the operating means A, a cutoff frame 2 is rotatably supported by a pin 1p on a V-shaped side arm 1y of a support stand whose base I is fixed to a body K of the sewing machine. The frame 2 becomes an upper arm 211 formed into an I shape from the pin 1p, and a biaxial stopper 2s protrudes from one end of the upper arm 211. Also, in the middle of 1 part arm 21J,
A cam plate 3 in the shape of a cam plate 3 is fixed with a set screw 3t, whose inclination angle can be adjusted by set screws 3n fitted into elongated holes 3a and 3a', and an eccentric shaft 3n'. 1
The cam portion 3C extending to the side has a high-speed cam 3H1 from its tip.
A clutch switching cam including a low-speed cam 3T and a cutoff cam 3s protruding toward - is formed. On the other hand, below the corresponding part of the pin 1p of the cutoff frame 2 is a lower arm 2d which has a passive part 2J formed at the lower end that receives the pedal pressing force from the direction of the arrow M, and this arm 2d has a low speed surface 4T on the upper part and a high speed surface 4T on the upper part. A hook 4 with a stepped shape forming a surface 4H is provided. A shutoff spring 5 is hooked between the middle of the two-part arm 213 and the fuselage body, and is biased by l=J so that the biaxial stopper 2s is always pressed against the shutoff cam 35.

As shown in FIG. 2, the clutch lifter 6 includes a pair of curved arms 6u that project inwardly from each other and have at their tips a pin 6p that fits into a groove 25e carved on the outer periphery of the movable body 25. is formed into a 7-shape, and a claw 6t is protruded from the center thereof to be slidably inserted into the square groove 25 carved in the lower part of the movable body 25. As shown in FIG. 2, the base 6 is rotatably supported by the upper arm 1 (1) of the support base 1, and the base 6 is equipped with a roller 6C that engages the clutch switching cam of the cam plate 3C. A side arm 6y is formed.The side arm 6y is connected to the side arm 1y of the support base 1 by a high speed spring 7, and is always urged to rotate downward.

In addition, a switching arm 9 having a hook 8 that engages with the stepped shape of the hook 4 fixed to its tip is rotatably supported by the body K, and a compression coil spring 10 ensures that the lower surface of the hook 8 is always connected to the hook. It is biased so that it is in contact with the two sides of No. 4.

As shown in FIG.
A single pulley holder 12 is connected to a fixed disc 11 fixed to the machine body K by passing through the holder 12, and a low speed pulley 13 is connected to the holder 12 for integration. A stand 14 is provided to the needle via an link 15.

The transmission means C is equipped with a low-speed pulley 22 on one low-speed pulley 13 via a roller bearing 21, a high-speed pulley 24 on one high-speed pulley 14 via a rolling bearing 23, and an end face of the transmission E. A movable body 25 with a groove 25e carved in the outer peripheral part 25g of one end, which protrudes from the fixed disk II and is located so as to cover the outer periphery of the fixed disk II, is attached to the single pulley holder 12.
A switching clutch 26 is externally inserted into the sliding portion 25s so as to be able to reciprocate in the axial direction, and is integrally connected to the sliding portion 25s between one low-speed pulley 13 and one high-speed pulley 14. and the clutch pawl 27 are connected to the rolling bearing 28
．． 28. In addition, mobile body 2
The outer peripheral portion 25g of one end of the pulley 5 and the cylindrical sliding portion 25s are connected by a pair of arm portions 2511 that pass through a notch 13s carved symmetrically around the center of one low-speed pulley 13.

Further, on the outward conical friction surface of the switching clutch 26, a friction material 26z that is in pressure contact with the inward circular 1fc friction surface 22m of the low speed pulley 22 is in contact with the outward conical friction surface of the high speed pulley 24.
J, a friction material 24Z that comes into pressure contact with the inward conical friction surface 26m of the switching clutch 26, and a friction material '24z that comes into contact with the child end friction surface 33m of the drive pulley 33 on the child end friction surface.
' is each taken a (1 game).

Although not shown, the clutch pawl 27 is capable of sliding in the -1 axial direction, and the drive pulley 33
A protruding pawl is provided that is always engaged with.

Driving means D 41: A driving pulley 33 is fitted to the tip of the -1 shaft 31 supported by the rear metal 32 and fixed by a fixing screw 34.
A known cutoff cam 35 is attached to the end face of the high-speed pulley 14 (1ffl), and a plurality of low-speed springs 36 are provided between the drive pulley 33 and the clutch pawl 27. 37 is inserted into the shaft 31 and is interposed between the drive pulley 33 and the single pulley holder 12. 38 is a counter spring that is interposed between the J pulley 33 and the rolling bearing 23 to keep the high speed pulley 24 in the neutral position.

Further, 40 is a low-speed V heel l-141 and a high-speed heald ■.

Next, select the action.

In FIG. 1, when the low-speed pulley 22 and high-speed pulley 24 are freely rotating via the morph pulley due to the drive of a sewing machine drive motor (not shown), when the pedal is depressed, the cutoff frame 2 resists the cutoff spring 5. The clutch lifter 6 rotates in the direction of the arrow N against the high speed spring 7, and the roller 6C rides on the low speed cam portion 3T of the plate 3 due to the force J. move. At this time, the switching arm 9 is biased in the direction of the arrow p (=j) by the compression coil spring 10, so the lower end inner corner 8 of the hook 8 engages with the low speed surface 4T of the hook 4 and the low speed of the cutoff frame 2 The attitude of the movable body 25 is determined by the pin 6p engaged with the circle a25e.
As seen in Fig. 3, moves to the left (arrow ■ - force direction), and along with this, due to the stretching force of the low-speed spring 36,
The switching clutch 26 is pushed in the same direction via the clutch pawl 27, and the friction material 26z comes into pressure contact with the inward circular tflI friction surface 22m, but since the pawl (not shown) of the clutch pawl 27 is always engaged, the above-mentioned The driving force is transmitted to the drive pulley 33 via the clutch 26 and the clutch pawl 27, and the upper shaft 31, which is integrally connected, begins to rotate at a low speed. When the pedal is roughly depressed, the inner corner 8K of the lower end of the hook 8 engages with the high-speed surface 4+1 of the hook 4 to establish the high-speed posture of the cutoff frame 2, and the roller 6C moves to the high-speed cam portion 3T.
The clutch lifter 6 is rotated in the opposite direction of arrow N by the restoring force of the high-speed spring 7 (see Figure 1), and the pin 6p pushes the movable body 25 in the opposite direction of arrow 7 (see Figure 1). (see figure). Therefore, the switching clutch 26 separates from the low-speed boot υ-22 while compressing the low-speed spring 36, and this time presses the inward conical friction surface 26m against the friction material 24Z, and at the same time deforms the high-speed pulley 24 slightly by deforming the leaf spring 38. The friction material 242' is brought into pressure contact with the child end friction surface 33m. Of course, the high-speed pulley 24 is pressed and held between the switching clutch 26 and the drive pulley 33, so the driving force of the high-speed pulley 24 is
1, and the upper shaft 31 becomes one with these surfaces and moves to high speed rotation.

One cycle of sewing is spun, and the switching arm 9 applies a pressure of 1 (h) to the FE compression coil thread 10 using the two notches set in the feed force J, L:'' (not shown) and in the opposite direction of the arrow P. When the hook 4 is rotated, the hook 8 moves up from the high speed surface 4H to the low speed surface 4T to the top blocking position along the stepped shape of the hook 4, and is synchronized with this by the restoring force of the blocking spring 5. Clutch switching force J8: Engagement with Iro 6c is also low speed utility 1, part 3
Clutch IJ '7 ter 6 moves to 3s for cutoff via T
are linked. Therefore, mobile 25 from peer 6p
is operated, the switching clutch 26 returns to the low speed pulley 22 side in the first stage and decelerates the rotation of the 1-shaft 301 to a low speed, and in the second stage, the switching clutch 26 returns to the neutral position and the cutoff flap 1. The upper shaft stopper 2s of 2 corresponds to the cam shape (not shown) of the cut-off cam 35, and fits into the rotating clamping opening to stop the drive pulley 33, and the upper shaft 31.
to stop.

In addition, adjustment of the neutral positioning of the switching clutch 26,
For example, this can be done by changing the force J appearing on the shield 1jIi frame 2 and the mounting angle of the plate 3.

In addition, the one high-speed pulley 14 and the needle ring 15 of the above embodiment are removed, and as shown in FIG. Slide stand 44 between I2
It is also possible to insert and insert a hole, and the same effect can be achieved.

〔Effect of the invention〕

As described above, the present invention has a structure in which a heddle hook pulley is mounted on a pulley support mechanism fixed to the body of a sewing machine, and a movable body equipped with a switching clutch is inserted into the support mechanism. Therefore, the 2-zero V-bell 1-taber crane system can be adopted even in sewing machines where the breaking force 1 is provided at the outer end of the upper shaft. Since it is received by the aircraft, it does not affect the two axes at all, so the rotation of the axes is stabilized, the load on the rear metal is also reduced, and the durability is improved, as well as clutch switching. The 931 work also has the effect of being easily and reliably executed.

In addition, since the clutch lifter that operates the movable body is configured to set the rotational posture by the clutch switching force 1 of the cam plate provided on the cutoff frame 1 and the engagement of the rollers, the movement position of the switching clutch is determined. Not only can this be carried out accurately, but the neutral position can also be adjusted easily and easily, especially by selecting the mounting angle of the cam plate.Furthermore, the low-speed cam part is shaped to protrude higher than the high-speed cam part. When the pedal is depressed to a high speed, the clutch lifter is rotated as required by the tensile force of the high-speed spring, resulting in an advantage that the pedal pressure is reduced.

[Brief explanation of drawings]

FIG. 1 is a side view of a partially omitted transmission and operating means according to an embodiment of the present invention, and FIG. 2 is a view of the clutch lifter and transmission taken along the line ■-■ in FIG. FIG. 3 is an enlarged half-box sectional view of the transmission, and FIG. 4 is an enlarged half-box sectional view showing another example of the transmission. A Operating means B Pulley support mechanism C Transmission means D Drive means K Sewing machine body 2 Shutoff frame 2s Upper shaft stopper 3 Cam plate 3 F (High speed cam section 3T Low speed cam section 3S Shutoff cam section 6 Clutch lifter 22 Low speed pulley 24 High-speed pulley 25 Moving body 26 Switching clutch 27 Clutch pawl 33 Drive pulley 33m Child end friction surface 35 Cutoff cam patent applicant Tokyo Heavy Equipment Industry Co., Ltd. -14=

Claims (1)

[Claims] A driving means is formed by holding a shaft in a bearing, which has a blocking cam attached to the outer end surface and a drive pulley having a friction surface on the inner end surface fixed to one end, and the shaft is fixed to the body of the sewing machine and the shaft is rotatably inserted. between a pulley support mechanism equipped with the mechanism, and a high-speed pulley that can be pressed against the friction surface of the low-speed pulley and the drive pulley, the mechanism is engaged with the support mechanism and is rotatable to a movable body that slides in the axial direction. A transmission means equipped with a clutch pawl that slides in the axial direction with respect to the drive pulley and is rotatable integrally with the drive pulley, and is provided with a switching clutch that is press-connected to the low-speed pulley or the high-speed pulley, respectively; and a pedal. Rotates by stepping on the
A cam plate on which a clutch switching cam is formed is attached to a cutoff frame having an upper shaft stopper that operates the cutoff cam,
1. A clutch device for changing the speed of a sewing machine, comprising an operating means, comprising a clutch lifter that engages and interlocks with the switching cam to position the movable body.