JPH04151022A - Clutch device - Google Patents

Abstract

PURPOSE:To prevent transmission of rotation torque which exceeds the predetermined value and provide torque limiter function by releasing engagement when relative rotation torque on the input and output sides exceeds the predetermined value. CONSTITUTION:A groove 3 which has the V-shaped cross section is formed on the outer peripheral face of an input disk 1, and a recessed section 4 which tilts for radius direction is formed on the inner peripheral face of an output disk 2. A roller 8 is supported at one end of a claw member 7, and it forms an engaging means together with a claw support member 6 and a spring 5 which is in the recessed section 4. When the input disk 1 rotates clockwise, the roller 8 fits in the groove 3 to transmit power to the output disk 2. When overload is applied to the output disk, the spring 5 is compressed, the roller 8 comes out of the groove 3, and the input disk 1 performs idle running. Consequently, one-way clutch is provided with the function of a torque limiter.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention This invention relates to a clutch device that transmits rotation in only one direction.

2. Description of the Related Art Conventional one-way clutches include, for example, Japanese Patent Application Laid-open No. 58-5
There is one shown in Publication No. 537.

FIG. 15 is a sectional view of the one-way clutch described above,
41 is a drive shaft, 42 is a ratchet wheel, 43 is a key, and the drive shaft 41 and ratchet wheel 4 are connected via this key 43.
2 are designed to rotate together. 42a is a ratchet tooth of the ratchet wheel 42, 44 is a cylindrical outer peripheral metal fitting for driving a load, 45 is four pawl storage parts formed on the inner peripheral surface of the cylindrical outer peripheral metal fitting 44, and 46 is stored in the pawl storage recess 45. It is a ratchet pawl. Further, 47 is a spring, and 48 is a spring holder that supports the spring 47. The spring 47 presses the ratchet pawl 46 against the ratchet wheel 42.

When the drive shaft 41 and the ratchet wheel 42 rotate clockwise in the figure, the ratchet teeth 42a and the ratchet pawl 46 engage with each other, so that the ratchet wheel 42
Along with the rotation, the cylindrical outer peripheral fitting 44 rotates. On the other hand, when the drive shaft 41 and the ratchet wheel 42 rotate counterclockwise in the figure, the ratchet teeth 42a and the ratchet pawl 46 do not engage, and the rotation of the ratchet wheel 42 is not transmitted to the cylindrical outer peripheral metal fitting 44. It looks like this.

By the way, in the above-described one-way clutch, when an overload is applied to the cylindrical outer peripheral metal fitting 44, the ratchet wheel 4
2. Overload also acts on the drive shaft 41 and a motor (not shown).

Therefore, in the past, a torque limiter such as that disclosed in Japanese Patent Application Laid-Open No. 142028/1984 has been arranged separately from the one-way clutch.

FIG. 16 is a cross-sectional view of the torque limiter described above,
51 is a transmission shaft, 52 is a rotary disk, and 56 is a key, through which the transmission shaft 51 and the rotary disk 52 are rotated together.

Further, 54 is an engagement portion formed on the outer circumference of the rotary disk 52;
53 is a transmission plate, 55 is an engaging body, 57 is a bolt, 58 is a nut, and 59 is a spring. The bolt 57 is screwed into a hole formed in the transmission disc 53 and supports a spring 59, and the spring 59 moves the engaging body 55 to the rotary disc 53.
2.

If the load on the transmission disc 53 is normal, the engagement body 55 and the engagement part 54 are maintained in a retained state by the spring force of the spring 59, and the transmission disc 53 rotates as the rotary disc 52 rotates. be done. When the load on the transmission disc 53 becomes excessive, the engagement between the engaging body 55 and the engaging portion 54 is released, and the rotary disc 52 rotates without rotation of the transmission disc 53. .

In this way, overload is prevented from being applied to each member.

Problems to be Solved by the Invention As mentioned above, conventionally, in order to protect a one-way clutch from overload, a torque limiter must be provided separately from the one-way clutch. There are problems in that space is required and the amount of electricity required increases, resulting in an increase in cost.

Means for Solving the Problems Therefore, in order to solve the above problems, the present invention includes a rotation input means, a rotation output means, and a rotation input means supported by either one of the rotation input means and the rotation output means. A clutch device comprising an engagement means that engages the rotation input means and the rotation output means so as to transmit torque only when the rotation input means and the rotation output means rotate relative to each other in a predetermined direction, the engagement means comprising: A transmission torque limiter that releases the engagement between the rotation input means and the rotation output means when the relative rotation torque between the rotation input means and the rotation output means exceeds a predetermined value, and prevents transmission of rotation torque exceeding the predetermined value. It is characterized by having a part.

The rotational torque of the rotational input means or the rotational output means in a predetermined direction is transmitted to the rotational output means or the rotational input means by the operational engagement means. Furthermore, the transmission torque limiting portion of the engagement means prevents transmission of rotational torque exceeding a predetermined value. Therefore, one Kurasochi device can have both the function of a one-way clutch and the function of a torque limiter.

Embodiment FIG. 1 is a sectional view of a clutch device which is an embodiment of the present invention.

In the same figure, ■ is an input disk (rotation input means), and the outer peripheral surface of this input disk 1 has a groove 3 having a V-shaped cross section.
is formed. 2 is a cylindrical output disk 7 (rotational output means); 4 is a recess formed on the inner peripheral surface of the output disk 2 so as to be inclined with respect to the radial direction of the output disk 2; Further, 7 is a claw member, 6 is a claw support member, 8 is a roller, and 5 is a spring (transmission torque limiting part). A roller 8 is rotatably supported at one end of the claw member 7, and the other end of the claw member 7 is a spring. is rotatably supported by the claw support member 6.

These springs 5, support members 6, claw members 7, and rollers 8 constitute an engaging means. The spring 5 is housed in the recess 4, and the claw support member 6 is attached to the output disk 2.
It is pressed against the inner peripheral surface side. Note that the end surface of the claw member 7 supported by the claw support member 6 is inclined with respect to the longitudinal direction of the claw support member 6, and this inclined surface is such that when the claw member 7 is in the state shown in FIG. , comes into contact with the side surface of the recess 4 and prevents the claw member 7 from rotating in the counterclockwise direction. Further, the roller 8 has a size that allows it to fit into the groove 3.

In the above configuration, when the input disk 1 rotates clockwise and the roller 8 fits into the groove 3, the rotation of the input disk 1 is transmitted to the output disk 2 via the claw member 7, and the output disk 2 is rotated. .

When an overload is applied to the output disk 2, the rotation of the input disk 1 presses the pawl support member 6 toward the outer circumference of the output disk 2, compressing the spring 5. Finally, the roller 8 is released from the groove 3, and the input disk 1
will end up idling.

Further, when the input disk 1 rotates counterclockwise as shown by the arrow in the figure, even if the roller 8 and the groove 3 are fitted,
The claw member 7 rotates clockwise, as shown in FIG.
It is designed to easily escape from the groove 3. Therefore, when the human-powered disk I rotates counterclockwise, the rotation of the input disk 1 is not transmitted to the output disk 2.

FIG. 4 is a sectional view of another embodiment of the present invention, and FIG.
The figure is a cross-sectional view taken along line -V.

In the figure, 9 is an input disk (rotary input means), and as shown in FIG. 5, this input disk 9 is constructed by combining two members 9g and 9b. and,
A housing portion 11 is formed between these two members 9a and 9b, and a rod 13 and a spring 12 (transmission torque control portion) that presses the rod 13 toward the center of the input disk 9 are provided in the housing portion 11. It is accommodated. 14 is a roller, and this roller 14 is rotatably supported at the end of the rod 13.

Further, 10 is an output disk (rotation output means), and this output disk 10 is constructed by combining two members 10a and 10b as shown in FIG. Also,
An arm 15 is attached to the output disk 10 and is rotatably supported around a support portion I6. In addition,
Spring 12, rod 13, roller 14, arm 1
5. The support portion 16 constitutes an engaging means.

In the above configuration, when the input disk 9 rotates clockwise in the figure, the roller 14 rides on the arm I5 and the spring 12 is compressed, as shown in FIG. Then, due to the reaction force of this spring 12, the input disk 9
is transmitted to the output disk 10, and the rotation of the output disk 1 is transmitted to the output disk 10.
0 rotates.

When the output disk 10 is overloaded, the roller 14 further rides on the arm 15, and finally this arm 1
I'll get over 5. Therefore, in case of overload, the input disk 9 is designed to idle.

Further, as shown in FIG. 7, when the input disk 9 rotates counterclockwise, the roller 14 passes under the arm 15 and does not engage with this arm 15. therefore,
When the input disk 9 rotates counterclockwise, the rotation of the input disk 9 is not transmitted to the output disk 10.

FIG. 8 is a sectional view of still another embodiment of the present invention, in which 17 is an input shaft (rotation input means), 18 is an output shaft (rotation output means), and 19 is a cloth-wrapped coil spring (with a torque limiter). engagement means).

The diameter of the input shaft 17 is slightly larger than the inner diameter of the coil spring 19, and the inner diameter of the output shaft 18 is approximately the same as the outer diameter of the coil spring 19.

When the input shaft 17 rotates in the direction shown by the arrow in the figure, that is, clockwise, a force acts on the coil spring 19 in the opposite direction to the winding direction due to the frictional force between the coil spring 19 and the inner peripheral surface of the output shaft 18. tends to expand in the radial direction, and the frictional force between the coil spring 19 and the inner peripheral surface of the output shaft 18 increases. Thereby, the rotation of the input shaft 17 is transmitted to the output shaft 18, and the output shaft 18 is rotated. If an overload is applied to the output shaft 18, the coil spring 1
9 tries to expand further in the radial direction, the frictional force between the coil spring 19 and the input shaft 17 decreases, and the input shaft 17 and the coil spring 19 begin to slip. Therefore, if an overload is applied to the output shaft 18, the input shaft 17 will idle.

Furthermore, when the input shaft 17 rotates in the direction opposite to the arrow in the figure, the radius of the spring 19 is reduced, so the frictional force between the coil spring 19 and the inner peripheral surface of the output shaft 18 is reduced. The output shaft 18 is not rotated.

Note that if you want to rotate the output shaft when the input shaft 17 rotates to the left, and let the input shaft 17 idle when the input shaft 17 rotates to the right, the winding direction of the coil spring 19 should be reversed from the example in FIG. , it may be left-handed.

FIG. 9 is a schematic cross-sectional view of still another embodiment of the present invention, and FIG. 10 is an enlarged cross-sectional view of the main part of the example shown in FIG.

In the figure, 20 is an input shaft, 21 is an input disk (rotary input means), 22 is an output shaft, 23 is an output disk (rotary output means), and 24 is an input disk 2
This is a spring that presses it to 1. Then, as shown enlarged in FIG. 10, the input disk 21 and the output disk 2
A thrust bearing 30 is disposed between the two. Further, concave portions 25 and 27 and an inclined concave portion 26 are formed between the concave portions 25 and 27 on the surface of the input disk 21 facing the output disk 23, and a spring 22 is provided in the concave portion 27.
9 and a ball 28 are provided.

A plurality of these four parts 25, 26, 27, balls 28, and springs 29 are arranged on the input disk 21. The depth of the recess 25 is smaller than the depth of the recess 27, and the depth of the recess 27 is smaller than the depth of the ball 28.
is slightly smaller than the diameter of Note that the springs 24, 29, the recesses 25, 26, 27, and the ball 28 constitute an engaging means.

In the above configuration, when the input disk 21 rotates in the direction indicated by the arrow in FIG. 10, the ball 28 moves upward in the figure and is compressed between the output disk 23 and the input disk 21. Therefore, as the input disk 21 rotates, the output disk 23 rotates.

If an overload is applied to the output disk 23, the ball 28 and the output disk 23 will slip.

Therefore, if an overload is applied to the output disk 23, the input disk 21 will idle.

When the input disk 21 rotates in the direction opposite to the arrow shown in FIG. 10, the ball 28 moves downward in the figure,
Since the ball 28 is located within the recess 27, the ball 28 is not pressed between the input disk 21 and the output disk 23, and the output disk 23 is not rotated.

FIG. 11 is a sectional view of a configuration of still another embodiment of the present invention.

In the figure, 31 is an input shaft, 32 is an input disk (rotary input means), 35 is a roller, 34 is a claw member, 33 is a claw member support part, 36 is an output shaft, 37 is an output disk (rotary output means), 38 is a spring, and 39 is a groove formed in the output disk 37 and having a V-shaped cross section. The claw member support portion 33 is disposed on the side of the input disk 32 facing the output disk 37, and the claw member 34 is supported by the claw member support portion 33. Note that the claw member 34 is rotatable only within one side of the connection point between the claw member 34 and the support portion 33. That is, for example, in the state shown in FIG. 12, the claw member 34 can only rotate within the range indicated by the broken line arrow in the figure, and cannot rotate to the left from the state shown. Further, the roller 35 is rotatably supported by the claw member 34 and can be fitted into the groove 39. Note that the claw member support portion 33. Claw member 34. Roller 35. spring 38
The coupling means is constituted by:

In the above configuration, the input disk 32 is the output disk 3
7 in the direction indicated by the solid arrow in FIG. 12, the roller 35 fits into the groove 39, thereby causing the output disk 37 to also rotate. When an overload is applied to the output disk 37, as shown in FIG.
5 escapes from full 39. Therefore, when the output disk 37 is overloaded, the input disk 32 is idled. In addition, the input disk 32
When the roller 35 rotates in the direction indicated by the arrow in FIG. 14, the claw member 34 rotates to the left as shown, so even if the roller 35 fits into the groove 39, it immediately escapes. . Therefore, in this case, the output disk 37 is not rotated.

The clutch device of the present invention described above can be applied to various things, for example, it can be used as a forward/reverse motion detection device in the toroidal continuously variable transmission described in Japanese Patent Application Laid-Open No. 2-163562, which was previously proposed by the present applicant. is possible.

As detailed in the above-mentioned publication, the forward/reverse motion detection device is a device for detecting whether the vehicle is in a forward or reverse state, and based on the detected result, performs forward-only gear change control. The device and the reverse gear shift control device are switched.

Effects of the Invention As described above, according to the present invention, the rotation input means, the rotation output means, and the rotation input means and the rotation output means are supported by either one of the rotation input means and the rotation output means. In the clutch device, the engagement means engages the rotation input means and the rotation output means so as to transmit torque only when the rotation input means and the rotation output means rotate relative to each other in a predetermined direction. When the relative rotational torque with the means exceeds a predetermined value, the rotation input means and the rotation output means are disengaged from each other to prevent transmission of rotational torque exceeding the predetermined value. Therefore, it is possible to realize a clutch device that combines the functions of a one-way clutch and a torque limiter. Therefore, by arranging this one clutch device, there is no need to separately arrange a one-way clutch and a torque limiter.
Weight saving.

This saves space and reduces costs.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of one embodiment of the present invention, FIGS. 2 and 3 are explanatory diagrams of the operation of the example in FIG. 1, FIG. 4 is a sectional view of another embodiment of the invention, and FIG. 5 is a sectional view taken along the line V-V in FIG. 4, FIGS. 6 and 7 are explanatory diagrams of the operation of the example in FIG. 4,
8 is a sectional view of still another embodiment of the invention, FIG. 9 is a schematic sectional view of still another embodiment of the invention, FIG. 10 is a partially enlarged detailed view of the embodiment of FIG. 9, and FIG. 11 12, 13, and 14 are explanatory views of the operation of the example shown in FIG. 11, FIG. 15 is a sectional view of a conventional one-way clutch, and FIG. 16 is a sectional view of still another embodiment of the present invention. is a sectional view of the torque limiter. 1.9, 21.32... Input disk, 2, 10°2
3.37...Output disk, 3,39...Groove, 4゜25.26.27...Concavity, 5.12.24,29゜38...Spring, 6.33...Claw support member, 7
゜34...Claw member, 8,14.35...Roller,
DESCRIPTION OF SYMBOLS 11... Accommodation part, 13... Rod, 15... Arm, 17°20.31... Input shaft, 18.22.36
...output shaft, 28...ball. Figure 4 Figure 5 Figure 6 Figure 7 Figure 1 et al.

Claims (1)

[Claims] (1) A rotation input means, a rotation output means, supported by either one of the rotation input means and the rotation output means, and only when the rotation input means and the rotation output means rotate relative to each other in a predetermined direction. In a clutch device comprising an engagement means that engages the rotation input means and the rotation output means in a torque transmittable manner, the engagement means is configured such that the relative rotation torque between the rotation input means and the rotation output means is equal to or greater than a predetermined value. 1. A clutch device comprising a transmission torque limiting section that releases engagement between the rotational input means and the rotational output means to prevent rotational torque exceeding a predetermined value from being transmitted when the rotational torque is reached.