JPS6039538Y2 - Clutch mechanism in power transmission - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a clutch mechanism in a power transmission machine that reduces the clutch disengagement load at hand at the initial stage of clutch body sliding.

Conventionally, in agricultural machines and the like, as shown in Fig. 1, a clutch body spline-fitted to a power take-off shaft a is removably engaged with a drive sprocket c via engagement teeth d. A pin g, which is eccentrically provided at a certain distance (sliding distance of the clutch body) with respect to the center of rotation of the shifter f, is engaged in the engagement groove e. Since the mounting position was on the straight line connecting the rotation center of shifter f and the tip of the arm attached to shifter f, the length from the rotation center of shifter f to pin g was 11, and it was installed on shifter f. If the length of the arm is 12, the lever ratio of 11:12 is not very large, and therefore, the clutch disengagement load at hand becomes heavy at the beginning of clutch sliding, where sliding resistance is extremely large. The drawback was that smooth latch operation was not possible.

The purpose of the present invention is to eliminate the above-mentioned drawbacks, and its feature is that, in particular, when the clutch body and the sliding rotating body are engaged, the rotational center of the shifter is The position of the pin installed at an eccentric position is approximately equal to the straight line connecting the pivot center of the shifter and the pin with respect to the straight line connecting the pivot center of the shifter and the tip of the arm attached to the chic. The pin is placed at a right angle toward the locking position of the clutch body, ensuring the sliding distance of the clutch body while minimizing the length of the arm of the acting force that slides the clutch body. The lever ratio with the chicly arranged arm can be significantly increased, and the clutch disengagement load on the hand at the initial stage of clutch body sliding can be significantly reduced.

An embodiment of the present invention will be described with reference to the drawings. Reference numeral 1 denotes a drive sprocket of a drive rotary body provided in the center of a case 2, and a chino 3 for transmitting power from an engine or the like is stretched over the drive sprocket.

The drive sprocket 1 is loosely fitted into the small diameter portion 4a of the power take-off shaft 4, and is connected to the power take-off shaft 4 and the power take-off shaft 5 opposite thereto.
are fitted into bearings 6 and 7, respectively, and spline-fitted to clutch bodies 8 and 9.

Further, coil springs 10 and 11 are provided on the backs of the clutch bodies 8 and 9 to press them.

The clutch bodies 8 and 9 each have engagement teeth 8a at the front.
, 9a are provided, and these can be freely engaged and disengaged from a plurality of engagement holes 1a provided in the drive sprocket 1.

Further, shifters 14.15 are arranged above 112.13 provided in the circumferential direction on the sides of the clutch bodies 8 and 9, respectively, and the tips of these shifters 112. Eccentrically provided integral pins 16 and 17 engage with the above-mentioned 912 and 13, respectively.

Further, the shifters 14 and 15 are rotatably supported by the case 2, and arms 18 and 19 each connected to a clutch operating lever (not shown) are fixed to their upper ends.

That is, the mounting positions of the pins 16 and 17 with respect to the shifters 14 and 15 are, for example, as shown in FIGS.
is engaged with the drive sprocket 1, the rotation center of the shifters 14, 15 and the pin 16 are 1 with respect to the straight line connecting the rotation centers of the shifters 14, 15 and the tips of the arms 18 and 19. The condition is that the pins 16 and 17 are arranged at a substantially right angle with the straight line connecting the pins 16 and 17, and in a direction close to the engagement position of the clutch body.

Note that C is a rotation center line passing through the rotation center of the shifter 15.

Next, to explain the operation, first, when cutting off the power transmission to the power take-off shaft 5 by disengaging the clutch, applying a counterclockwise force to the arm 19 causes the shifter 1 to
5 is rotated like the shifter 14 shown symmetrically in FIG. 2, and the clutch body 9 slides like the clutch body 8 to disengage the engagement tooth 9a from the engagement hole 1a.

At the initial stage of sliding of the clutch body 9, the pin 17 is located almost on the rotation center line C of the shifter 15, so that
When the arm 19 is rotated by a force F, the acting force W of the pin 17 on the clutch body 9 acts in the direction of the arrow along the sliding direction of the clutch body 9 as shown in FIG. The moment M with respect to this becomes M=W11.

Here, 11 is the arm length of the acting force W passing on the center line C1 of the pin 17, which is smaller as the position of the pin 17 is closer to the rotation center line C of the shifter 15, and becomes zero on the line C.

Therefore, the magnitude of the acting force W at the initial stage of sliding of the clutch body 9 is W" 1 t when the lengths of the arms 18 and 19 are 12 and 12, and since 11 is extremely small, the so-called leverage ratio is extremely large. Even if the clutch disengagement load F at hand is small, W is very large, so the clutch body 9 slides easily, and the initial clutch operation is performed extremely smoothly.

As mentioned above, the present invention has latch bodies 8, 9 which are spline-fitted to the power take-off shafts 4, 5 and are removable from the drive rotary body.
In a clutch mechanism in which pins 16, 17 that engage the clutch bodies 8, 9 are provided at eccentric positions with respect to the rotation centers of the shifters 14, 15, the engagement between the clutch bodies 8, 9 and the drive rotating body is When adjusting the position of the pin 16.17, the rotation of the shifters 14, 15 is set with respect to the straight line connecting the center of rotation of the shifter 14.15 and the tip of the arm 18.19 attached to the chic 14.15. Since the pins 16 and 17 are arranged in a direction close to the engagement position of the clutch body, with the straight line connecting the center of motion and the pins 16 and 17 being almost at right angles, the clutch body of the pins arranged in a chic manner can be slid easily. Since the arm length of the acting force is extremely small, the lever ratio for the clutch operation force is extremely large, and the clutch disengagement load on the hand at the initial stage of clutch body sliding is significantly reduced, allowing for smooth latch operation. There is an effect.

[Brief explanation of drawings]

Fig. 1 is a plan view of a conventional clutch mechanism, Fig. 2 is a plan sectional view showing an embodiment of the present invention, Fig. 3 is a side sectional view of the main part of Fig. 2, and Fig. 4 is a main part of the mechanism. FIG. 2 is an enlarged plan view. 1: Drive sprocket, 4, 5: Power take-off shaft, 8.9:
Clutch body, 12, 13: groove, 14, 15 lid, 1
6, 17: Pin, 18.19: Arm

Claims (1)

[Scope of utility model registration request] The latch bodies 8, 9 which are spline-fitted to the power take-off shaft 4.5 and can be engaged with and disengaged from the drive rotary body, and the pins 16.17 that engage the clutch bodies 8, 9 are set as the center of rotation of the shifter 14.15. In a clutch mechanism installed at an eccentric position relative to
When the clutch body 8.9 is engaged with the drive rotating body, the position of the pin 16.17 is adjusted between the center of rotation of the shifters 14 and 15 and the tip of the arm 18.19 attached to the chic 14.15. The straight line connecting the rotation center of the shifter 14°15 and the pin 16.17 is almost perpendicular to the straight line connecting the pin 16.17, and the pin 16.17 is arranged in a direction close to the engagement position of the clutch body. The clutch mechanism in the power transmission machine is characterized by: