JPH05296262A - Hydraulic power transmission coupling - Google Patents

Abstract

PURPOSE:To prevent a hydraulic power transmission coupling used in distributing the driving force of a vehicle from interfering with ABS and reduce the weight of the coupling. CONSTITUTION:A hydraulic power transmission coupling comprises a valve body 32 located between a first rotary member connected to either input or output shaft, and, a second rotary member connected to the other shaft, and a frictional member 26 provided between the valve body 32 and the first rotary member for providing friction resistance, the valve body 32 being provided in such a manner as to be freely turned to a predetermined position according to the direction of rotation by locking a protrusion 33 to the cam face 17 of the first rotary member, having a flywheel portion 34 and an open hole 35, and used to block a high pressure line 31 provided in the coupling when torque is transmitted and communicate the high pressure line 31 to the open hole 35 by means of the flywheel portion 34 when the vehicle is decelerated sharply.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic power transmission joint used for distributing a driving force of a vehicle.

[0002]

2. Description of the Related Art The applicant of the present invention filed Japanese Patent Application No. 63-204043.
In this issue, the following hydraulic power transmission joint is proposed. That is, this hydraulic power transmission joint is provided between the input and output shafts that are relatively rotatable, and has a flow rate generating means for flowing an amount of fluid according to the rotational speed difference between the two shafts and a flow passage for the fluid. In a torque transmission joint including means for generating resistance, the transmission torque between the input and output shafts being controlled by the flow resistance of the fluid, an orifice, a protrusion, and a flywheel rotatably housed in the opening of the discharge passage. A rotary valve having an opening hole and an opening hole to detect the angular acceleration of the joint at the time of sudden acceleration of the vehicle to close the discharge passage and open the discharge passage at the time of sudden deceleration; And a lid member for positioning the return spring via the protrusion thereof.

[0003]

However, in such a conventional hydraulic power transmission joint, when the vehicle with ABS is in a sudden braking state, the joint located at the position where the lock tire is joined is in the rotational direction. A large deceleration occurs in the rotary valve, which has inertia and overcomes the force of the return spring, opens the hydraulic circuit, reduces the torque transmission characteristics, and reduces the interference torque transmitted to the joint of the braking force.
The ABS system repeats loosening and strengthening the brakes to avoid tire lock.

Therefore, when the hydraulic valve is loosened, the deceleration in the rotational direction of the hydraulic coupling is also reduced, and the rotary valve is returned to its original position by the force of the spring. For this reason, the transmission characteristic of the hydraulic joint becomes stronger, and the interference torque transmitted to the joint increases. Further, in order to operate the high pressure rotary valve in order to operate the high pressure rotary valve by overcoming the friction generated on the side surface due to the spring force and the inertia of the rotary valve at the deceleration of the brake of the vehicle, the friction due to the unbalanced load of each part caused by the spring force, etc. Requires a large inertial weight,
When put in the lid member, the finished product as a whole has a very large structure.

The present invention has been made in view of such conventional problems, and an object thereof is to provide a hydraulic power transmission joint which can prevent interference with ABS and can reduce the weight. I am trying.

[0006]

In order to achieve the above-mentioned object, the present invention is provided between input / output shafts capable of relative rotation,
In a hydraulic power transmission joint for flowing an amount of fluid according to a difference in rotational speed of both shafts and controlling a transmission torque between the input and output shafts by a flow resistance of the fluid, a first power transmission joint connected to one of the input and output shafts. Between the rotating member and the second rotating member connected to the other of the input / output shaft, a protrusion is engaged with the cam surface of the first rotating member to be rotatably provided at a predetermined position in the rotating direction.
A valve body having a flywheel portion and an open hole, closing the high pressure passage inside the joint during torque transmission, and communicating the high pressure passage to the open hole by the flywheel portion during rapid deceleration; And a friction member provided between one rotating member to provide frictional resistance.

[0007]

In the present invention, the valve body having the flywheel portion is not positioned by the spring, but is provided by providing a slight friction resistance to the extent that it can be provided with the first rotating member. In this way, the cam surface provided on the second rotating member has a protrusion protruding from the valve body, and is rotated so that the flow resistance generating means always produces a flow resistance during normal driving.

On the other hand, when the vehicle is braked, the valve body having the flywheel section overcomes a slight friction resistance and rotates the valve body relative to the first rotating member, thereby generating a flow resistance. Avoid flow resistance in the means. That is, the joint should not transmit torque. In this state, even if the deceleration of the brake decreases, or if the rotation from the tire is in the acceleration direction, that is, by weakening the braking force of the locked tire, the rotation increases due to the frictional force with the road surface. However, until the rotation of the tire side where the braking force is loosened and the rotation speed rises faster than the rotation of the wheel side where the brake is working, the joint maintains the state where no flow resistance occurs, that is, the state where torque is not transmitted. ing.

The ABS brake repeats the strength of the braking force, but by installing this joint, the condition that the front wheel rotates faster than the rear wheel rotates, especially the interference at the initial stage, which is the most important in the ABS brake, Since it can be largely avoided, the characteristics of the ABS system can be improved.
Also, the valve body is positioned by the cam surface, but since the cam surface is designed near the maximum diameter that determines the size of this joint, the valve body can accommodate the maximum diameter design.
As a result, the most advantageous design structure can be obtained in order to increase the inertia weight and reduce the total weight.

The ABS system is still an expensive system and may or may not be attached by the user. This joint can be replaced with a conventional ordinary joint by removing only the flywheel part and stopping drilling of the hydraulic circuit, so it is extremely easy to handle and the configuration of the production line can be simplified. ..

[0011]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 5 are views showing an embodiment of the present invention.
First, the configuration will be described. In FIG. 1 and FIG.
Is the case of the final drive unit,
One end of the output shaft 3 is rotatably supported by the case 1 via a bearing 2. The output shaft 3 has a male spline section 4
And the threaded portion 5 is formed.

Reference numeral 6 is a rotor shaft (first rotary member) of a joint 7 connected to the output shaft 3, and a hollow portion 8 is formed in the rotor shaft 6. A step portion 9 is formed in the hollow portion 8, and a female spline portion 1 that fits into the spline portion 4 of the output shaft 3 is provided in the small diameter portion 10 on the right side of the step portion 9.
1 is formed. The rotor shaft 6 and the output shaft 3 are spline-fitted by the spline portions 11 and 4, and the washer 12 is inserted into the screw portion 5 until the step portion 9 abuts.
Fasten with the nut 13.

The cylindrical surface of the outer diameter portion 14 of the rotor shaft 6 is precision-finished, and an oil seal 15 is interposed between the outer diameter portion 14 and the case 1. Reference numeral 16 is an end block connected to an input shaft (not shown).
6 is welded together to a housing 18 having a cam surface 17 so that the end block 16 and the housing 18 are
It constitutes a rotating member.

The end block 16 is formed with a flat surface portion 19, a spigot portion 20, and a bolt hole 21, respectively. A plurality of plunger chambers 22 are formed in the rotor shaft 6 in the radial direction, and a plurality of plungers 23 are slidably accommodated in the plunger chamber 22 via return springs 24.

The plunger 23 is provided with a suction / discharge hole 25, and inside the plunger 23, the suction / discharge hole 2 is formed.
5 is provided with a check valve 26, and the check valve 26 is held by a retainer 28 via a spring 27. The check valve 26 has an orifice 29 as a flow resistance generating means. Further, the rotor shaft 6 has a high pressure chamber 3 communicating with the plunger chamber 22.
0 and a high pressure passage 31 communicating with the high pressure chamber 30 are formed.

Reference numeral 32 denotes a rotary valve as a valve element, and the rotary valve 32 is provided between the housing 18 and the rotor shaft 6 so as to be rotatable at a predetermined position in the rotational direction. That is, the rotary valve 32 has a positioning projection 33 that engages with the cam surface 17 formed on the inner circumference of the housing 18. The rotary valve 32 has a flywheel portion 34 formed integrally therewith, and also has a high pressure passage 31.
Has an open hole 35 that can communicate with the.

Reference numeral 36 denotes a dish (or wave) type friction member provided between the rotary valve 32 and the rotor shaft 6, and the friction member 36 does not position the rotary valve 32 but gives a slight friction resistance. By giving it, it has a function to rotate together with the rotor shaft 6. Reference numeral 37 denotes an accumulator piston that rotates together with the housing 18, and the accumulator piston 37 moves according to the internal pressure and absorbs the thermal expansion of the enclosed oil. A return spring 39 is provided between the accumulator piston 37 and the retainer 38, and an oil seal 40 is provided between the accumulator piston 37 and the rotor shaft 6.

Reference numeral 41 is an oil seal, 42 is a needle bearing, 43 is a snap ring, and 44 is an O-ring. Next, the operation will be described. First, the normal operation will be described. When a difference in rotation occurs between the housing 18 and the rotor shaft 6, the plunger 23 in the discharge stroke is pushed radially by the cam surface 17 of the housing 18.

The oil in the plunger chamber 22 is supplied to the low pressure chamber from the suction / discharge hole 25 through the orifice 29. At this time, the hydraulic pressure in the plunger chamber 22, the high pressure chamber 30, and the high pressure passage 31 rises due to the resistance of the orifice 29, and a reaction force is generated in the plunger 23. A torque is generated by rotating the housing 18 against the plunger reaction force, and the torque is transmitted between the housing 18 and the rotor shaft 6.

That is, as shown by A in FIG. 5, torque proportional to the square of the relative rotation between the rotor shaft 6 and the housing 18 is transmitted. In this case, as shown in FIG. 3, the housing 18 rotates to the right relatively faster than the rotor shaft 6, but the rotary inertia force does not act on the flywheel portion 34 during normal operation, and the rotary valve 3
2 and the rotor shaft 6 are in the positional relationship shown in the drawing, and when the plunger 23 is in the phase of tightening the oil, the high pressure passage 31
Is closed by the rotary valve 32 and does not communicate with the open hole 35.

Next, the case of sudden deceleration will be described. When the vehicle is suddenly braked so that the ABS works, the housing 18 moves the rotor shaft 6 as shown in FIG.
Although it is rotating to the right relatively faster than the rotary valve 32 is rotated by the rotary inertia force due to the flywheel portion 34, when the plunger 23 is in the phase of tightening the oil,
The high pressure path 31 and the open hole 35 communicate with each other.

The torque characteristic at this time is as shown in FIG. 5B, and the interference of the front and rear braking forces can be avoided. Regarding the state at the time of reverse rotation under normal use conditions, the arrow in FIG. 4 is viewed in reverse, and torque can be transmitted as in normal operation. Further, the rotary valve 32 is positioned by the cam surface 17, but since the cam surface 17 is designed near the maximum diameter that determines the joint size, the rotary valve 32 can correspond to the maximum diameter design. Therefore, the flywheel unit 34
The total weight can be kept small even if the inertia of is increased.

Next, FIGS. 6 to 8 are views showing a second embodiment of the present invention. 7 is a cross-sectional view taken along the line AA of FIG.
FIG. 8 is a sectional view taken along the line BB of FIG. 6 to 8, reference numeral 51 is a rotary valve, and the rotary valve 5
1, an open passage 53 is formed which can communicate with a high pressure passage 52 communicating with the plunger chamber 22, and an open hole 54 is communicated with the open passage 53. The outlet of the open path 53 is a lid member 55.
The lid member 55 is provided with a thrust needle bearing 56, a retaining plate 57, and a snap ring 58.

A groove 59 is formed around the outlet of the open passage 53, and an O-ring 60 is inserted in the groove 59.
Further, the rotary valve 51 has a flywheel portion 61 formed integrally therewith, and has a protrusion 62 that engages with the cam surface 17 of the housing 18. During normal operation, the high pressure passage 52 is closed by the rotary valve 51, and the orifice 29 causes flow resistance. As a result, the torque characteristic shown by A in FIG. 5 is obtained.

At the time of sudden deceleration, the rotary valve 51 is rotated by the flywheel portion 61 so that the high pressure path 52 communicates with the open path 53 and the open hole 54, and the torque shown by B in FIG. 5 is obtained. Also in this embodiment, the same effect as that of the above embodiment can be obtained. Next, FIGS. 9 to 12 show a third embodiment of the present invention.
It is a figure which shows an Example.

In FIGS. 9 and 10, reference numeral 22 denotes a plunger chamber formed on the rotor shaft 6, and a plurality of plungers 71 are slidable in the plunger chamber 22 in a radial direction via return springs 72. Is stored in. A high pressure chamber 73 communicating with the plunger chamber 22 is formed in the rotor shaft 6, and a high pressure passage 74 is formed in the high pressure chamber 73.
Are in communication.

Reference numeral 75 is a rotary valve having a projection 76 that engages with the cam surface 17 of the housing 18, and the rotary valve 75 is rotatably provided between the housing 18 and the rotor shaft 6. A flywheel portion 77 is formed integrally with the rotary valve 75, and an orifice 78 and an open hole 79 that can communicate with the high pressure passage 74 are formed. Reference numeral 80 denotes a friction member provided between the rotor shaft 6 and the rotary valve 75. The friction member 80 gives a slight frictional resistance so that the rotary valve 75 and the rotor shaft 6 rotate together.

During normal operation, as shown in FIG. 11, the high pressure passage 74 communicates with the orifice 78 in the phase in which the plunger 71 tightens the oil, and the torque indicated by A in FIG. 5 is obtained. On the other hand, at the time of sudden deceleration in which the vehicle is suddenly braked so that ABS acts, the rotary valve 75 is rotated by the flywheel unit 77, and as shown in FIG. The high pressure passage 74 communicates with the open hole 79. As a result, the torque characteristic becomes as shown by B in FIG.

Also in this embodiment, the same effect as that of the above embodiment can be obtained.

[0030]

As described above, according to the present invention, the oil is released to the open hole and the torque is not transmitted at the time of sudden deceleration, so that the interference with the ABS can be prevented. Further, the inertial weight can be increased and the total weight can be reduced.

[Brief description of drawings]

FIG. 1 is a diagram showing a first embodiment of the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG.

3 is a sectional view taken along the line BB of FIG.

FIG. 4 is a sectional view taken along the line BB of FIG.

FIG. 5 is a graph showing torque characteristics

FIG. 6 is a diagram showing a second embodiment of the present invention.

7 is a sectional view taken along the line AA of FIG.

8 is a sectional view taken along the line BB of FIG.

FIG. 9 is a diagram showing a third embodiment of the present invention.

10 is a sectional view taken along the line AA of FIG.

11 is a sectional view taken along the line BB of FIG.

12 is a cross-sectional view taken along the line BB of FIG.

[Explanation of symbols]

 1: Case 2: Bearing 3: Output shaft 4: Spline part 5: Screw part 6: Rotor shaft 7: Joint 8: Hollow part 9: Step part 10: Small diameter part 11: Spline part 12: Washer 13: Nut 14: Outer Diameter part 15: Oil seal 16: End block 17: Cam surface 18: Housing 19: Flat part 20: Inlay part 21: Bolt hole 22: Plunger chamber 23: Plunger 24: Return spring 25: Suction / discharge hole 26: Check Valve 27: Spring 28: Retainer 29: Orifice 30: High pressure chamber 31: High pressure path 32: Rotary valve (valve body) 33: Protrusion 34: Flywheel part 35: Open hole 36: Friction member 37: Accumulator piston 38: Retainer 39 : Return spring 40: Oil seal 41: Oil seal 42: Needle bearing 43: Snap ring 44: O-ring 51: Rotary valve 52: High pressure passage 53: Open passage 54: Open hole 55: Lid member 56: Thrust needle bearing 57: Retaining plate 58: Snap ring 59: Groove 60 : O-ring 61: Flywheel 62: Protrusion 71: Plunger 72: Return spring 73: High pressure chamber 74: High pressure passage 75: Rotary valve 76: Protrusion 77: Flywheel 78: Orifice 79: Open hole 80: Friction member

Claims (3)

[Claims] 1. A hydraulic system which is provided between input / output shafts which can rotate relative to each other, and which causes an amount of fluid to flow in accordance with a rotational speed difference between the shafts and controls transmission torque between the input / output shafts by a flow resistance of the fluid. In the power transmission joint, a protrusion is engaged with the cam surface of the first rotating member between the first rotating member connected to one of the input / output shafts and the second rotating member connected to the other of the input / output shafts. It is rotatably provided at a predetermined position depending on the rotation direction, has a flywheel part and an opening hole, and closes the high pressure path inside the joint during torque transmission,
When the vehicle is suddenly decelerated, the flywheel unit is provided with a valve body that communicates the high-pressure passage with the opening hole, and a friction member that is provided between the valve body and the first rotating member to provide frictional resistance. Hydraulic power transmission coupling. 2. A hydraulic system which is provided between relatively rotatable input / output shafts and which causes a quantity of fluid to flow according to the rotational speed difference between both shafts and controls the transfer torque between the input / output shafts by the flow resistance of the fluid. In the power transmission joint, a protrusion is engaged with the cam surface of the first rotating member between the first rotating member connected to one of the input / output shafts and the second rotating member connected to the other of the input / output shafts. It has a flywheel part, an open path, and an open hole that communicates with the open path.The flywheel part, the open path, and the open hole communicating with the open path are closed.The high-pressure path inside the joint is closed during torque transmission, and during rapid deceleration. A valve member that connects the high-pressure chamber to the open passage and the open hole by the flywheel portion; a lid member that closes the outlet portion of the open passage; and a seal member that is provided around the outlet portion. A hydraulic power transmission joint characterized by. 3. A hydraulic system which is provided between relatively rotatable input / output shafts and causes a quantity of fluid to flow according to the difference in rotational speed between the two shafts, and controls the transfer torque between the input / output shafts by the flow resistance of the fluid. In the power transmission joint, a protrusion is engaged with the cam surface of the first rotating member between the first rotating member connected to one of the input / output shafts and the second rotating member connected to the other of the input / output shafts. It has a flywheel part, an orifice, and an open hole so that it can be rotated at a predetermined position depending on the direction of rotation, and when the torque is transmitted, the high-pressure path inside the joint is communicated with the orifice. A hydraulic power transmission joint comprising: a valve body that connects a high-pressure passage to the open hole; and a friction member that is provided between the valve body and the first rotating member to provide frictional resistance.