JPS641540Y2 - - Google Patents

Description

[Detailed description of the invention] This invention combines a movable member that rotates integrally with the input shaft and is movable in the axial direction, and an output rotating member that is idly supported on the input shaft to output output from the input shaft. Negative action type in which torque is transmitted to the rotating member and the movable member moves in the direction of the output rotating member using spring force, while fluid pressure is used to separate the movable member from the output rotating member. This relates to a hydraulic clutch.

As shown in FIG. 1, an example of which is shown in a longitudinal cross-sectional side view, this type of negative-actuation type fluid pressure clutch has a spline 2 formed in the center of a tube shaft 1 serving as an input shaft, and a movable member 3. It is spline fitted.

Further, an output rotating member 4 is provided at one end of the tube shaft 1.
is supported by bearings 5, 5 so as to be freely rotatable.

On opposing end surfaces of the movable member 3 and the output rotating member 4, meshing teeth 6 and 7 that can mesh with each other are arranged in a ring shape.

At the other end of the tube shaft 1, an outer tube body 9 having stepped portions 9A and 9B on its inner peripheral surface is supported via a bearing 8 so as to be freely rotatable.

The outer tube 9 forms a cylinder chamber 11 with the inner tube 10 inserted so as to be movable in the axial direction along the inner peripheral surface of the peripheral wall 9C between the stepped portions 9A and 9B.

The inner tubular body 10 is a piston with a flange portion 10A as a pressure receiving surface, and an outer race 12A of a bearing 12 is fixed to a stepped portion 10B on the inner periphery of the tip portion.

On the other hand, since the inner race 12B of the bearing 12 is fixed to the movable member 3, the movable member 3 moves together with the inner tube body 10 in the axial direction, but is free to rotate.

In the annular gap 13 formed by the input shaft 1 and the inner tubular body 10, there is an annular plate 14 as a spring bearing that comes into contact with the movable member 3, and an inner race 8A of the bearing 8.
A ring plate 16 as a spring receiver that comes into contact with a snap spring 15 that comes into contact with the input shaft 1 is fitted to the input shaft 1, respectively.

Compression coil springs 17 are supported on the ring plates 14 and 16 at equal angle division positions, and the elastic pressing force of these compression coil springs pushes the movable member 3 in the direction of the output rotation member 4, and the meshing teeth 6 is given the habit of meshing with 7.

Fluid pressure (for example, air pressure) for resisting the elastic pressing force of the compression coil spring 17 and separating the movable member 3 from the output rotating member 4 is applied to the peripheral wall portion 9C of the outer tube body 9.
The data is entered and exited from the port 18 provided in the.

In addition, in the figure, the reference numeral 19 is a rotation prevention pin of the inner tube body 10, 20 is a pressure receiving ring member of the cylinder chamber 11, and 2
1 and 22 are O-rings.

Although this type of negative-actuation type fluid pressure clutch has great advantages such as reliable operation and high reliability, the input shaft and movable member are fitted with a spline, so gaps between the teeth of the spline may cause problems. There was a problem with the noise generated.

This invention provides a negative actuation type fluid pressure clutch that solves the above problem.The input shaft and the movable member are not connected by a spline, but are connected by a leaf spring, and the assembly of the movable member to the input shaft is performed with the shaft free. As a fitting assembly, it is characterized by completely eliminating noise generated by collision of spline teeth, and also by making it possible to buffer during load fluctuations.

Next, the negative operation type hydraulic clutch of this invention will be explained by way of an embodiment with reference to the drawings.

FIG. 2 shows an embodiment of the negative actuation type hydraulic clutch of this invention in a longitudinal sectional side view. As shown in the drawings, the input shaft 23 has a flange portion 24 as a radial projecting portion at the center thereof.

On the other hand, the input shaft 23 has a bearing 25 at one end.
An output rotary member 26 is supported through a shaft 25 so as to be freely rotatable, and a movable member 27 is loosely fitted into a portion 23A between the output rotary member 26 and the flange portion 24.

The movable member 27 has a central portion in the axial direction formed in a circumferential groove 29 for fixing the inner race 28A of the bearing 28. In order to enable the inner race 28A to be fitted, the movable member constituent members 27A, 27B, and these movable member constituent members are integrally connected by a plurality of bolts 30.

A large number of meshing teeth 31 are carved radially on the end face of the flange portion 26A of the output rotating member 26, and meshing teeth 32 that can freely mesh with the meshing teeth 31 are carved on the flange portion 27C of the movable member 27. It has been set up.

Three to four fixed point engagement pins 33 are implanted in the movable member 27 in an irregular arrangement.

The fixed-point engagement pins 33 can be fitted into holes 34 provided in the output rotation member 26 in correspondence with these fixed-point engagement pins, and the movable member 27 and the output rotation member 26
However, they are designed so that they can always be coupled in the same phase in the rotational direction.

That is, a pulley, a gear, a chain wheel, etc. (not shown) concentrically fixed to the output rotating member 26 are always connected only at one point during one rotation in the rotational direction, so that the phase does not shift, and each of the fixed point engagement pins 33 Of course, connection is possible only when all the fixed point engagement pins 33 face the dedicated holes, as well as when they are in contact with the output rotating member 26 at a portion other than the hole 34.

In this embodiment, the movable member 27 and the output rotating member 26 are coupled by meshing the meshing teeth 32 and 31, but they may be coupled by bringing the opposing surfaces of the flanges 27C and 26A into frictional contact. Note that the fixed point engagement pin 33 is unnecessary when there is no need to couple the movable member 27 and the output rotating member 26 only in one phase.

The movable member 27 is the flange portion 2 of the input shaft 23.
A plurality of compression coil springs 35 arranged in equiangular division between the output rotary member 26 and the output rotary member 26 are always pressed in the direction of the output rotating member 26, and the meshing teeth 32 have a habit of meshing with the output rotating member 31.

On the other hand, the flange portion 24 of the input shaft 23 and the flange portion 27D of the movable member 27 are connected by a plurality of plate springs 36 stacked one on top of the other.

The plate spring 36 has bolts 37 attached to the flange portion 24.
The flange portion 27D is fixed with bolts 38, and the flange portion 24 has a hole 39 into which the head 38A of the bolt 38 is inserted, and the flange portion 27D has a hole 39 into which the head of the bolt 37 is inserted. 40 are provided.

The leaf spring 36 may be annular, semicircular, arcuate, or strip-shaped; if it is semicircular, it may be two sets;
If the strips are shaped like strips, it is desirable to use three sets.

An annular block 42 is supported at the other end of the input shaft 23 via a bearing 41 so as to be freely rotatable.

The annular block 42 is provided with a flange portion 42A and an inwardly directed flange portion 42B on the inner circumference, and together with an annular member 44 fixed to the inner circumferential surface of one end of the outer tube body 43, serves as a fluid pressure receiving portion. A cylinder chamber 45 is formed.

The outer race 28B of the bearing 28 is fixed to the inner circumferential surface of the other end of the outer tube body 43, and when pressure is supplied to the cylinder chamber 45, the meshing teeth 32 move away from the movable member 27 together with the movable member 27. do.

In the figure, reference numeral 46 is a thrust bearing provided between the flange 24 of the input shaft 23 and the flange 42B of the annular block 42, 47 and 48 are O-rings, 49 is a fluid pressure communication port, and 50 is a sealing member. It is.

The negative actuation type fluid pressure clutch of this invention having the above-mentioned configuration always uses the compression coil spring 35.
The movable member 27 pushed by is coupled to the output rotating member 26, and torque is transmitted from the input shaft 23 to the output rotating member 26 via the flange portion 24, the leaf spring 36, and the movable member 27.

Next, when a high-pressure fluid (for example, pressurized air) is supplied into the cylinder chamber 45, the annular block 42 remains in a fixed position on the input shaft 23 and cannot move in the axial direction.
Since high-pressure fluid enters between the annular member 43 and the outer tube body 43, the movable member 27 moves in the direction of compressing the compression coil spring 35, disengaging the meshing teeth 32 and 31, and transmitting torque. It will be terminated.

When the fluid pressure in the cylinder chamber 45 is released, the torque transmission state is restored again.

During operation during this period, the input shaft 23 and the movable member 27 do not have any parts that collide with each other in the rotational direction due to load fluctuations during rotation, starting, or stopping, so no collision or banging noises are generated. Not only,
Since the load is absorbed by the leaf spring 36, torque transmission is always buffered.

As is clear from the above description, since the negative actuation type hydraulic clutch of this invention does not have a spline fitting portion, noise caused by the spline portion can be completely eliminated, and it is also possible to provide damping in the rotational direction. Also,
In a power system equipped with this type of device, by eliminating the spline fitting part, the drive side and
Practical advantages such as less variation in the amount of rotation with the driven side connected via this type of device and improved angular accuracy can be obtained.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional side view showing an example of a conventional negative operating type hydraulic clutch, and FIG. 2 is a longitudinal sectional side view showing an embodiment of the negative operating type hydraulic clutch of the present invention. In the drawings, 23...input shaft, 24...flange portion, 26...output rotating member, 27...movable member, 3
1, 32...meshing tooth, 33...fixed point meshing pin, 34...
Hole, 35... Compression coil spring, 36... Leaf spring, 42
...Annular block, 43...Outer tubular body, 44...Annular member, 45...Cylinder chamber, 49...Fluid pressure communication port.

Claims (1)

[Scope of utility model registration request] an output rotating member that is concentrically supported on the input shaft so as to freely rotate; a movable member that rotates integrally with the input shaft, is movable in the axial direction and has a coupling habit to the output rotating member; and the output rotating member is connected to the movable member. In a negative actuation type fluid pressure clutch comprising a spring that gives a tendency to move in the direction, and a fluid pressure receiving part that causes the movable member to move away from the output rotating member, the input shaft is connected to the radial projecting part. What is claimed is: 1. A negative actuation type fluid pressure clutch comprising an input shaft having an input shaft and a movable member connected to the projecting portion by a leaf spring.