JPS61103019A - Centrifugal clutch - Google Patents

Abstract

PURPOSE:To facilitate changing a clutch characteristic by disposing a weight element capable of freely moving in the peripheral direction in a garter spring in a garter spring type centrifugal clutch. CONSTITUTION:A garter spring 15 for controlling the contact and separation of a clutch plate 11 and a friction plate 12 is disposed on the inside of a housing side wall 18 of a clutch housing 10. A weight element 19 such as a steel ball or the like having a little smaller diameter than the inside diameter of the spring is disposed in the garter spring 15. Accordingly, the number and unit weight of weight elements 39 and the turns of the garter spring 15 are changed variously, and these weight elements and the garter spring are combined to change the clutch IN, the rotating stall and the slide range depending upon these factors can be changed in various modes.

Description

DETAILED DESCRIPTION OF THE INVENTION (& Field of Industrial Application) The present invention relates to a centrifugal clutch that increases or decreases transmitted torque depending on the magnitude of centrifugal force.

(Prior Art) For example, in a small two-wheeled motor vehicle or three-wheeled iV, there is a centrifugal clutch between the end of the engine crankshaft (input shaft) and the output gear. There is something set up.

In this case, as a centrifugal clutch, for example,
There is a ball type shown in FIG. 1 of Japanese Patent No. 6-75331.

In order to eliminate the drawbacks of this ball-type centrifugal clutch, the applicant has published the second publication of the above-mentioned publication prior to filing this application.
The technology related to the garter spring type centrifugal clutch shown in the figure has been disclosed.

This garter spring type centrifugal clutch is advantageous in that it has the unique effects described in the above publication;
Since the conventional type was constructed so as to be operated only by the garter spring, there was another problem in the following points.

In other words, the above-mentioned garter spring is formed by connecting the ends of one coil spooling to form an annular shape, but since the intermediate change in the circumferential direction is constant, the centrifugal force is uniform over the entire circumference. occurs.

The diameter and weight of the garter spring can be determined by determining its specifications, that is, the wire diameter and number of turns of the garter spring. If the rotational speed of is arbitrarily selected, a balanced stall state (maximum rotational state where the clutch plate and friction plate are in contact and slip) is automatically determined for a constant clutch capacity and engine generated torque.

Therefore, the rotational speed range from clutch IN to stall (hereinafter abbreviated as slip range) is also determined naturally.

Here, the rotation speed of the clutch IN is:

This is the rotational speed at which the garter spring receives centrifugal force and expands its diameter, reducing the gap between the clutch plate and friction plate to zero.

Force - Geometrically determined from the spring diameter and coil diameter, the initial clearance between the above two plates, etc.1
It is something.

On the other hand, the stall rotation speed is the rotation speed at which the garter spring receives a larger centrifugal force, increases the clutch plate pressing force, and the transmission torque of the clutch balances with the torque generated by the engine. It depends on the size of the quality. For this reason, if a garter spring with specific specifications is installed, it is possible to always provide a constant driving feeling, but in reality, the characteristics of the engine installed are not constant, and the torque generation speed etc. There is a desire to change the driving feeling depending on the characteristics of the vehicle to be provided or the user's preferences.

To meet these demands, it is necessary to change the above slip range.

However, if the conventional type uses only garter springs, the only way is to increase or decrease the spring wire diameter or the number of spring turns. By increasing the diameter of the ring, the rotation speed of the clutch IN, which is determined geometrically, can be lowered than normal, but since the spring ff1ffi itself is larger, the centrifugal force increases and the stall rotation speed increases. will go down as well.

As a result, the slip range from clutch IN to stall remains almost unchanged regardless of whether the number of turns is increased.As a result, the above-mentioned request can be met, that is, the slip range can be freely selected as well as the rotation speed of clutch IN. I am unable to fully satisfy my desire to do so.

(Object of the invention) The second invention was made in view of the above problem, and
The purpose is to fully satisfy the user's desire for feeling not only between different models but also between the same model.

(Structure of the Invention) In order to achieve the above object, the present invention provides a weight body movable in a circumferential direction within a coil spring.

(Example) An example of the present invention will be described below with reference to the drawings.

FIG. 1 shows an example of a small two-wheeled motor vehicle.

In FIG. 1, 1 is a crankcase, and one side of this crankcase 1 is illustrated. A crankshaft (man-powered shaft) 2 is rotatably supported in the crankcase 1, and a countershaft 3 and a power take-off shaft 4 are each rotatably supported in parallel with the crankshaft 2.

In the above-mentioned countershaft 3, variable speed drive gears 5A, 5B, and 5C from 1st stage to 3rd stage are arranged in one drawing, and a 1487 spring 6 is installed at the end of the countershaft 3 corresponding to the outside of the crankcase 1. A second output extraction gear 7 is attached.

On the other hand, the power take-off shaft 4 includes the speed change drive gears 5A, 5.
Shift driven gears 8A and 8B mesh with B and 5C, respectively.
, 8C are arranged, thus forming a transmission capable of changing speeds including gears (not shown).

Here, a kicking device (not shown) is connected to the first variable driven gear 8A disposed at the right end of the power take-off shaft 4 in the drawing.

On the other hand, a clutch cover 9 is attached to one side of the crankcase 1, and a centrifugal clutch C, which will be described below, is disposed within this clutch force 8-9.

The centrifugal clutch C is provided at the end of the crankshaft 2, and in this case, its main parts are as follows.

That is, 10 is a clutch housing (a member that rotates in synchronization with a clutch plate described later), 11 is a clutch plate, 12 is a friction plate, 13 is a clutch hub, 14 is an internal gear, and 15 is a garter spring.

(' Among the main members mentioned above, the clutch/X Ujifugu 10 has its inner periphery connected to the end of the crack shaft 2 with a spline, and the four nuts 16
Extraction is stopped by.

This clutch housing 10 consists of a central /@tsu/fuguhosu 1f, an outer peripheral side wall 18, and @
It also has an outer peripheral wall 19 of the housing, and on the inside of the housing side wall 18 there is a spring receiver 2' for setting the Carter spring 15.
0 protrudes, and a cam surface 21 is formed at a location corresponding to the outer periphery of the spring receiving sleeve 20 that is inclined toward the outer periphery in the direction of the clutch plate it. The cam surface 21 forms a conical portion as a whole.

On the other hand, as shown in FIG. 2, projections 22 are provided on the inner peripheral portion of the housing outer peripheral wall 19 in an intermittent arrangement in the circumferential direction.

As shown in Figure 1, from the garter spring 15 side, the first end clutch plate 23.2 intermediate clutch plates)
LL, 11. The second end clutch plates 25 are arranged so as to be engaged with each other with the above-mentioned one-head pressure, and each is slidable only in the axial direction. Here, a snap ring 26 is provided on the protrusion 22, and a disc spring 27 for biasing the clutch in the ON direction is disposed between the snap ring 26 and the second end clutch plate 25. In order to bias the second end clutch plate 25 in the direction of clutch OFF against the disc spring 27, a release pin 29 is provided on the guide post 28 between the projections 22, and the release pin 29 can be operated with one foot. It is operated by a clutch operating mechanism 30 that moves forward and backward in response to the movement.

Furthermore, locking claws 31 are formed on the outer periphery of the clutch hub 13, and the friction plates 12 are arranged on these locking claws 31 so as to be slidable in the axial direction. This tension play) 12 uses 5PCC as a core material, and its both sides and outer peripheral end surface;
It has been established.

Here, on the outer periphery of the clutch hub 13,
Push 7 langes 33 facing the friction plate 12
As shown in Figure A2, the inner circumference of the clutch hub 13 is divided into three equal parts in the circumferential direction.
A four-stroke notch 1134 is formed.

Seven connection cam grooves 35 are formed between the phases 1L of this buffer notch groove 34, and each connection cam 11η35 has an engagement cam 3 protruding from the outer periphery of the internal gear 14.
6 are slidably engaged. In this case, by the activation operation using the above-mentioned kick device.

:jAs shown in figure S1, the first shift driven gear 8A and the first
The operating force is transmitted to the output extraction gear 37 on the outer periphery of the crankshaft 2 via the variable drive gear 5A and the second output extraction gear 7, and the rotational force is transmitted from the 1751 output extraction gear 37 to the internal gear 14. As a result, the engaging cam 36 formed on the internal gear 14 rides on the riding surface 38 of the connecting cam tR35 as it rotates. As a result, the state shown in Fig. 3 changes to the state shown in Fig. 2, so that the clutch hub 1
3 is moved to the left in FIG.
3 presses the 2-reaction plate 12,
The clutch is turned on and activated.

On the other hand, when the engine is started, the power transmission direction force is reversed from the crankshaft 2 force 1 through the clutch housing 10, so that the starting state shown in FIG. 2 returns to the normal transmission state shown in FIG. 3.

As described above, the centrifugal clutch C is configured, but here, the configuration of the garter spring 15 is particularly featured.

In other words, the garter spring LSL± in this case.

As shown in FIG. 4, the spring has a regular weight body 39 having a diameter slightly smaller than the inner diameter of the spring. In this case, the weight bodies 39 are made of steel ball acid, and there are five weight bodies in this embodiment.

This weight body 39 rotates in a direction opposite to that of the garter spring 15 as it rotates together with the clutch housing 10 . For example, since the joint part 40 provided at one end of the spring to connect the garter spring 15 has a small diameter, the joint part 40 is always moved in front of the joint part 40. It can be stopped.

Therefore, in the above structure, the ffi weight body 39 is provided inside the garter spring 15.

The following becomes possible.

In other words, when the weight body 39 is separately provided in the garter spring 15, the weight body 39 moves to the front of the joint portion 40 as the garter tin 1 nong 15 rotates, and as a result, when looking at the garter spring 15 as a whole, Only at a specific point in the circumferential direction, force < ffi 3 Due to the presence of the 3Φ body 39, the body 39 is biased and becomes heavy.

Therefore, this part of the FFI weight body 39 generates a centrifugal force larger than that of the Nakakukuiya part and expands in the radial direction.

As a result, the clutch plates 11, 23, 25 and the friction plate 12 are partially damaged! However, the clutch is engaged at a lower rotational speed than the rotational speed when only the garter spring 15 is used.

In this case, the clutch IN rotation speed decreases! IS! body 39
Enlargement of only one part of the garter spring 1 of other parts
5, it is much larger than the case where the number of turns of the garter spring 15 is increased by the same amount as the IT weight body 39.

On the other hand, when the clutch is turned on, the clutch plates 11, 23, 25 and the friction plate 12 in FIG.
Corresponding to the R-view increment, the stall rotational speed is lower than when only the garter spring 15 is used. However, the stall condition is only obtained when the entire circumference of the garter spring 15 expands in the radial direction and the clutch play) 11°23.25 and the 7-reaction plate 12 are brought into strong contact with all of their levers. The presence of the weight body 39 in the garter spring 15 does not affect the stall rotational speed other than the mass increase, and as a result, a centrifugal clutch C having operating characteristics with a longer slip range can be obtained.

Using this specific relationship, the number of single weight bodies 39,
By variously changing the unit weight and the number of turns (diameter) of the garter spring 15 and combining these, the clutch IN, the stall rotational speed, and the slip range based on these can be changed in various ways.

For this reason, it is possible to provide a vehicle with various types of feeling depending on the characteristics of the engine, the characteristics of the vehicle, and the user's preferences.

In particular, the fact that this can be achieved by a very simple method of just providing the weight body 39 is also very advantageous in practice.

In addition, the present invention provides, for example, a drive plate separate from the clutch housing as shown in FIG. garter spring 15
It can also be applied to those with . Further, the weight body 39 may have a shape other than a ball shape.

(Effects of the Invention) As explained above, according to the present invention, the claw needle and body which are movable in the circumferential direction are provided in the coil spring nog.
The user's desire for a good feeling has been fully satisfied not only between different models but also when using the same model.

[Brief explanation of the drawing]

Fig. 1 is a sectional view of a power transmission system showing an embodiment of the present invention, Fig. 2 is a sectional view of Fig. 1 I-II8 during kicking, and Fig. 3 is a sectional view of Fig. 1 II-II in a normal transmission state. II
FIG. 4 is a cross-sectional view showing the garter spring and the weight body inside the seven. 10... Clutch housing (member that rotates in synchronization), 11, 23. 25... Clutch plate. 12... Friction plate, 15... Garter spring, 39... Weight body, C... Centrifugal clutch.

Claims (2)

[Claims] (1) A clutch plate and a friction plate are arranged to face each other in the axial direction, and the clutch plate is provided with a member that faces in the axial direction and rotates in synchronization with the clutch plate, and The centrifugal clutch includes a coil spring formed in an annular shape between a member that rotates by the clutch plate and the clutch plate, characterized in that a weight body movable in the circumferential direction is provided within the coil spring. centrifugal clutch. (2) The centrifugal clutch according to claim 1, wherein the weight body is ball-shaped.