JPH0121048Y2 - - Google Patents

Description

[Detailed description of the invention] [Field of industrial application] The present invention relates to a hub clutch, and in particular, to a hub clutch that allows accurate clutch engagement and disengagement even if the braking force of the brake mechanism itself is small. Regarding Kuratsuchi.

[Conventional technology and its problems] As a conventional hub clutch, for example,
There are examples such as those shown in Japanese Patent Application Laid-open No. 54-108315 and Japanese Patent Application Laid-open No. 139527-1983. In these devices, the cam follower (cam follower) is rotated integrally with the axle at the beginning of rotation of the axle, and the cam is moved by the frictional coupling force generated between the spring (multi-turn drag spring) and the nut (sleeve). The brake is applied, causing relative rotation between the cam follower and the cam. This relative rotation causes the cam follower and the sleeve (clutch member) to move axially outward, causing the inner clutch teeth to mesh with the outer clutch teeth. In order to ensure this meshing state, it is necessary to increase the frictional coupling force generated between the spring and the nut so that sufficient relative rotation can be obtained. However, increasing the frictional coupling force causes large wear on the sliding parts that occurs during frictional coupling. Therefore, as the hub clutch is used over time, it becomes impossible to obtain sufficient frictional coupling force, resulting in a problem that the durability of the hub clutch deteriorates.

Also, for example, Japanese Utility Model Application Publication No. 54-27427,
The hub clutch shown in JP-A No. 54-25026 and JP-A No. 54-42728 is normally able to keep the frictional coupling force to a certain level, and large frictional force is generated during meshing operation. It is said that the structure is possible. However, when these items are driven from the axle side, which is the drive side,
The moving cam mechanism for engaging the clutch generates the large frictional engagement force required for engaging the clutch. Therefore, a reaction force of the same magnitude as the thrust force that moves the movable gear in the axial direction generated by the moving cam mechanism is entirely applied to the brake shoe, thereby strongly pressing the brake shoe against the fixed system. Therefore, the brake shoe causes abnormal friction with the fixed system, and the height (fitting position) of the cam mechanism for moving the movable gear increases.
There was a problem that a reliable engagement could not be obtained due to the change in the

The present invention was devised in view of the above-mentioned problems of the conventional technology, and its purpose is to provide a brake mechanism with a small braking force to reduce the amount necessary for engaging and disengaging the cam. It is an object of the present invention to provide a hub/clutch that can provide a thrust force such as that of the brake mechanism and that does not apply the reaction force of the thrust force to the brake mechanism.

[Means and actions for solving the problem]

In order to achieve the above object, the hub clutch of the present invention includes a retainer for the cam whose movement toward the brake mechanism in the axial direction is restricted by at least one of the drive clutch and the driven clutch, and the brake mechanism. A wedge mechanism is provided to generate braking force.

〔Example〕

Hereinafter, the hub clutch according to the present invention will be described in detail with reference to the drawings.

FIG. 1 is an explanatory diagram of the configuration of a hub clutch according to an embodiment of the present invention, in which A is a vertical sectional view showing the clutch engaged state, and B is a portion showing the joint between the brake shoe and the retainer shown in A. FIG.

This hub clutch is disposed outside the drive clutch 3 which is connected to the drive shaft 5 by a snap ring 4, and is engaged with a slide clutch 2 via a spline so as to be movable in the axial direction of the drive shaft 5. , a driven clutch 1 which has a toothed portion 1a that is coupled with the toothed portion 2b of the slide clutch 2, is disposed on the outside of the slide clutch 2, and is connected and disconnected by movement in the axial direction.
The retainer 6 is connected to a brake mechanism that generates a predetermined braking force between the retainer 6 and the fixed system 10, and relative rotation occurs between the retainer 6 and the slide clutch 2 due to drive from the drive side. It is comprised of a cam mechanism that moves the slide clutch 2 in the axial direction to engage the clutch, and releases the clutch engagement when the slide clutch 2 is driven from the driven side in a direction opposite to the drive from the drive side. A pin 2a is driven into the outside of the slide clutch 2, and the retainer 6 is positioned in the driven clutch 1 by being restricted from moving axially inward (towards the brake mechanism) by a snap ring 14. has been done.

The brake mechanism includes a cylindrical nut 11a coupled to a cylindrical fixed shaft 10 which is a fixed system disposed on the outside of the drive shaft 5, and a plurality of cylindrical nuts 11a arranged at predetermined intervals on the outer peripheral surface of the nut 11a. The brake shoe 8a includes a brake shoe 8a, a brake shoe receiving member 20 fixedly arranged in contact with the left side of the brake shoe 8a, and a garter spring 7 provided on the brake shoe 8a.

A cam portion 6b integrally formed with the retainer 6 and projecting to the right is held radially outward of the slide clutch 2 at a predetermined distance. This retainer 6 is formed with an arcuate cam groove 6a, as shown in the perspective view of FIG. 1C.

The wedge mechanism includes each brake shoe 8 having a rectangular cross section.
a wedge-shaped recess provided on the right side surface of the retainer 6; and wedge-shaped protrusions 16, each of which is a V-shaped cam that projects from the end side wall of the retainer 6 and is fitted into the wedge-shaped recess.
Consists of a.

In the operation of the hub clutch having the above configuration, when switching to four-wheel drive by operating a select bar (not shown) and applying rotation to the drive shaft 5, the drive clutch 3 and slide clutch 2 shift to the drive shaft 5. rotates with.
Since the rotation of the retainer 6 is suppressed by the action of the brake shoe 8a, relative rotation occurs between the retainer 6 and the slide clutch 2, and the pin 2a driven into the slide clutch 2 is caused by the action of the arcuate cam groove 6a. is moved from the position A shown in FIG. 1C to the position B or B'. That is, the slide clutch 2 moves to the left. Therefore, the drive shaft 5 and the driven clutch are coupled to provide four-wheel drive. Also, when switching from four-wheel drive to two-wheel drive by operating the select bar, after cutting off the power to the drive shaft 5, the drive wheels can be used to move the car a little in the opposite direction of the car's current direction. to rotate the driven clutch 1 in the opposite direction. The slide clutch 2 and drive shaft 5 are rotated by the driven clutch 1, but the rotation of the retainer 6 is suppressed by the resistance of the brake shoe 8a. Therefore, relative rotation occurs between the retainer 6 and the slide clutch 2, and the pin 2a is moved from the position B or B' to the position A shown in FIG. 1C by the action of the arcuate cam groove 6a. Therefore, the slide clutch 2 is moved to the right in the axial direction, and the drive shaft 5 is disengaged from the driven clutch 1, and the drive shaft 5 is stopped, and only the driven clutch 1 idles, resulting in two-wheel drive.

During the above action, the action of the wedge mechanism is as follows. That is, when attempting to move the slide clutch 2 in the axial direction for the operation of engaging and disengaging the clutch, the retainer 6 attempts to rotate the brake shoe 8a. Therefore, the brake shoe 8a slides and rotates with respect to the nut 11 on the sliding surface 21a. However, as shown in FIG.
Therefore, when rotational torque is applied from the V-shaped cam portion 16a to the brake shoe 8a, the brake shoe 8a
A thrust force is generated to the left in the axial direction, and the brake shoe 8a is pushed to the left. Friction is generated at the contact surface between the receiving member 20 and the brake shoe 8a, and this frictional force causes the retainer 6 to brake. used for Therefore, even if the braking force of the brake mechanism itself is small,
It is possible to provide the cam with a thrust force that enables reliable clutch engagement and disengagement.

Note that, since the retainer 6 is restricted from moving axially inward (towards the brake mechanism) by the snap spring 14, the reaction force of the thrust force is not applied to the brake mechanism.

The brake mechanism in another embodiment of the present invention shown in FIGS. 2A and 2B includes a cylindrical nut 11b connected to the fixing system 10, and the nuts 11b are arranged at 90° intervals on the outer circumferential surface of the nut 11b, and have a cross section. It consists of a semi-cylindrical brake shoe 8b and a garter spring 7b fitted on the outer surface of the brake shoe. The retainer 6 is axially positioned on the drive clutch 3 by a snap spring 9. In this case, the wedge mechanism consists of the arcuate outer surface of each brake shoe 8b and the protrusion 16 of the retainer 6.
It consists of a V-shaped inner surface 22 provided on the radially inner side of b.

In the case of this wedge mechanism, when the retainer 6 rotates, its V-shaped inner surface 22 contacts the garter spring 7b and the brake shoe 8b;
A thrust force is generated in the direction of the shaft center, and the brake shoe 8b is pushed toward the shaft center, and a frictional braking force is generated on the contact surface 21b with the nut 11b. This increases the brake torque of the retainer 6.

Furthermore, the brake mechanism in another embodiment of the present invention shown in FIGS. It consists of a truncated conical cone thrust member 8c that is fitted together. The wedge mechanism in this case consists of a wedge-shaped fitting portion provided between the truncated cone-shaped cone thrust member 8c and the protruding portion 16c of the retainer 6.

In the case of this wedge mechanism, the retainer protrusion 1
6c and the cone thrust member 8c, when the rotational torque as described in FIG. ) and the conical inner surface (inclined surface) 21c of the cone thrust member 8c becomes stronger, so that a predetermined braking force can be applied to the retainer 6.

[Effect of idea]

As described above, the present invention generates braking force by providing a wedge mechanism between the brake and the cam retainer whose movement toward the axial brake mechanism is restricted by at least one of the drive clutch or the driven clutch. As a result, the thrust force required for engaging and disengaging the clutch can be applied by a brake mechanism with a small braking force, and the reaction force of the thrust force is not applied to the brake mechanism. Therefore, a hub clutch with good operability and durability can be obtained.

[Brief explanation of the drawing]

FIG. 1 is an explanatory diagram of the configuration of a hub clutch according to an embodiment of the present invention, in which A is a longitudinal cross-sectional view showing a state in which the clutch is engaged, B is a partial perspective view of A, C is a perspective view of a cam portion, and FIG. Figure 2 is an explanatory diagram of the configuration of a hub clutch according to another embodiment of the present invention, in which A is a longitudinal sectional view showing the clutch engaged state, and B is an arrow A-A shown in A.
FIG. 3 is an explanatory view of the configuration of a hub clutch according to yet another embodiment of the present invention, in which A is a vertical cross-sectional view showing the clutch in the disengaged state, and B shows the clutch in the engaged state. FIG. Explanation of symbols, 1... Driven clutch, 2...
Slide clutch, 2a...pin, 3...drive clutch, 4,9,14...snap spring,
5... Drive shaft, 6... Retainer, 6a
...Cam groove, 6b...Retainer cam part, 7a,
7b... Garter spring, 8a, 8b... Brake shoe, 8C... Cone thrust member, 1
0... Fixed shaft, 11a, 11b, 11c... Nut, 12... Hub, 13... Bolt, 16a, 1
6b, 16c... Retainer protrusion, V-shaped cam part (or wedge-shaped fitting part), 20... Thrust force receiving member, 21a, 21b, 21c... Brake shoe friction surface, 22... Brake shoe and Contact surface of retainer protrusion.

Claims (1)

[Claims for Utility Model Registration] 1: a drive clutch coupled to a drive shaft; a slide clutch that engages with the drive clutch and is movable in the axial direction of the drive shaft; a brake mechanism that exerts a braking force between the driven clutch that is connected and disconnected and a fixed system when the drive shaft rotates; and at least one of the drive clutch or the driven clutch restricts inward movement in the axial direction. , a retainer that receives braking force from the brake mechanism and generates relative rotation with the driven clutch; and a retainer that is provided between the retainer and the slide clutch, and is provided with a retainer that rotates the slide clutch in the axial direction by driving from the drive side. A hub clutch having a cam mechanism for releasing the clutch engagement when the slide clutch is moved from the driven side in a direction opposite to the driving direction, the retainer and the brake being moved to engage the clutch. 1. A hub clutch, characterized in that a wedge mechanism is provided between the hub clutch and the retainer and increases the braking force received by the retainer when the retainer receives rotational torque. 2. The wedge mechanism is provided between the brake mechanism and the retainer, and comprises a wedge portion that generates the thrust force in the axial direction when the retainer receives rotational torque. The hub clutch described in item 1. 3. The wedge mechanism is provided on the inner circumferential surface of the retainer and includes a V-shaped inclined surface that comes into contact with the brake mechanism and generates a thrust force toward the axial center. Hub Clutch. 4. The brake mechanism includes a brake member that is locked to a fixed system and has an inclined surface, and a cone thrust member that has an inclined surface that contacts the inclined surface of the brake member, and the wedge mechanism is configured to connect the retainer and the cone. Claims for Utility Model Registration consisting of a wedge portion provided between the retainer and the thrust member, which generates an axial thrust force when the retainer receives rotational torque to increase the frictional braking force on both of the inclined surfaces. Hubs listed in scope 1
Clutch.