JPH06185543A - Hydraulic type power transmission coupling - Google Patents

Abstract

PURPOSE:To improve stable controllability and responsiveness by forming an outflow passage such that delivery oil from a hydraulic pump is cut off by a guide part in a manner to cause the outflow of it to an oil chamber provided with a hydraulic pump on the moving magnetic substance side of an actuator. CONSTITUTION:When a solenoid coil 26 is not energized, a return spring 38 is in a non-compression state and a valve hole 30 is closed by a first control valve 29 to disconnect communication between a high pressure chamber 15 and an intake port 12. An orifice 16 is released by a second control valve 36. Thus, oil flow, as shown by an arrow mark E, through a high pressure chamber 15, an orifice 16, and an opening hole 18 and is cut out by a guide part 37 and fed from an outflow passage 21 to an intake port 12. Thus, the oil is prevented from flowing to the oil chamber 22 side where a moving magnetic body 27 is arranged. An oil pressure in a high pressure chamber 15, a delivery port 13, and a plunger chamber 7 is increased through resistance of the orifice 16 to generate a reaction force at a plunger 8, and torque is generated through rotation of a cam 3.

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 has proposed a hydraulic power transmission coupling as shown in FIG. 7 in Japanese Patent Application No. 3-338215. That is, the hydraulic power transmission joint is provided between the input / output shafts that are relatively rotatable, and is driven by the differential rotation of the input / output shafts. A control valve for controlling the flow resistance,
In a hydraulic power transmission joint that includes an actuator that operates the control valve in response to a signal from the outside, and transmits a torque corresponding to the rotational speed difference of the input / output shaft and a control signal from the outside, is fixed to an external member, A magnetic frame 102 that surrounds the solenoid coil 101 and is held in non-contact with the joint, and is supported inside the joint so as to be movable and tiltable in the axial direction, and a magnetic attraction force is generated by energizing the coil 101. The movable magnetic body 103 and the movable magnetic body 103 constitute the actuator.
The first control valve 104 as the control valve and the second control valve 105 are provided at symmetrical positions apart from the center of the joint axis, and they act weakly on the first control valve 104. By providing a return spring for urging the movable magnetic body 103 in a direction opposite to the attraction direction so as to strongly act on the control valve 105 of No. 2, the current to the coil 101 is made non-energized. Both the first and second control valves 104 and 105 are not operated, a second control state in which only the first control valve 104 is operated by setting a weak energization state, and a strong energization state are set. Thus, the control is performed in three stages of the third control state in which both the first and second control valves 104 and 105 are operated.

In the normal state where the solenoid coil 101 is not energized, the movable magnetic body 103 does not generate a magnetic attraction force and is held at the position shown in the figure. Therefore, as shown in FIG. 8, the second control valve 105 includes the high pressure chamber 106 and the suction passage 10.
The valve hole 108 for communicating 7 is closed.
On the other hand, since the first control valve 104 opens the orifice 109, the discharged oil flows out to the side of the movable magnetic body 103 which operates the second control valve 105 as shown by an arrow A.

[0004]

However, in such a conventional hydraulic power transmission joint, since the oil flowing out from the orifice flows toward the movable magnetic body side, the movable magnetic body is driven by a signal from the outside. Suck it to the valve side,
When trying to operate the control valve, the movement of the movable magnetic body was hindered by the force received from the spilled oil.

As a result, stable control performance cannot be ensured and responsiveness is poor. Further, the control valve for locking has a complicated shape, and thus the cost is high. Further, since the tip of the lock control valve and the tapered portion of the orifice outflow passage have variations, the diameter of the seal portion varies greatly, and the relief pressure with respect to the load acting on the lock control valve varies.

As a result, there was a large variation in lock torque. Further, when it is repeatedly used, the control performance changes due to wear or the like. The present invention has been made in view of such conventional problems, and provides a hydraulic power transmission joint that can secure stable control performance, enhance responsiveness, and reduce cost. With the goal.

[0007]

In order to achieve the above-mentioned object, the present invention is provided between input / output shafts capable of relative rotation,
A hydraulic pump driven by the differential rotation of the both shafts;
A control valve provided at the outlet of the hydraulic pump for controlling the flow resistance of the discharged oil; and an actuator for operating the control valve in response to an external signal; a rotational speed difference between the two shafts and an external control signal In a hydraulic power transmission joint that transmits torque according to the above; the oil discharged from the hydraulic pump is the oil provided in the hydraulic pump on the opposite side of the oil chamber provided with the movable magnetic body forming a part of the actuator. An outflow passage communicating with the discharge passage from the hydraulic pump is provided so as to flow into the chamber, and is opened to the oil chamber provided with the hydraulic pump.

Further, the present invention provides the above-mentioned flow resistance.
Larger diameter than the orifice as a means for generating flow resistance
Hold the valve and open vertically to the flat surface of the valve.
Move along the opening of the fiss outlet and the axis of the opening
It is possible to be installed and pushed by the movable magnetic body.
As the control valve for closing the opening hole by
Control valve for locking and guide the control valve to the above state
At the same time, the oil discharged from the orifice is moved by the movable magnet.
It is equipped with a guide part that blocks the flow so that it does not flow to the body side.
The control valve is a circle larger than the diameter of the opening hole at the orifice outlet.
It has a rod-shaped cross section, and closes closely to the opening hole.
The angle between the stopping contact surface and the flat surface is less than a predetermined angle
To have a conical or spherical end surface
It is the one.

[0009]

According to the hydraulic power transmission joint of the present invention having such a structure, the discharge oil from the hydraulic pump is blocked by the guide portion so as not to flow to the movable magnetic body side, and is passed through the outflow passage. Since the oil flows out into the oil chamber provided with the hydraulic pump, the discharged oil does not hit the movable magnetic body and the operation of the movable magnetic body is not hindered. Therefore, stable control performance can be secured with a small current, and responsiveness can be improved.

Further, since the lock control valve can be formed in a simple rod shape, the cost can be reduced. Furthermore, since the control valve for locking has a conical or spherical end face such that the angle between the flat surface and the contact surface is less than a predetermined angle, for example, 45 degrees or less, a small contact angle with respect to the flat surface is obtained. Since the contact is made with, the variation of the lock torque is small, and the change of the control performance is small even if it is repeatedly used.

[0011]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 6 are views showing an embodiment of the present invention.
First, the configuration will be described. In FIG. 1 and FIG.
Is a housing, and the housing 1 is connected to an output shaft (not shown) and rotates integrally with the output shaft.

The housing 1 has a housing non-magnetic portion 1A made of a non-magnetic material and another portion made of a magnetic material including the welded portion 2 integrated with each other. Reference numeral 3 denotes a cam, and the cam 3 is supported on the inner surface of the housing 1 via a thrust needle bearing 4 so as to be rotatable by a predetermined angle. The cam 3 has a cam surface 3A composed of a plurality of cam peaks and cam valleys, and has a plurality of projections 3B for positioning and torque transmission on the outer periphery thereof where the cam peaks are on the side surfaces.

When the projection 3B of the cam 3 engages with the notch 1B formed in the housing 1 to rotate integrally with the housing 1 in the rotation direction of the rotor 5, and when the rotation direction of the rotor 5 changes, the cam 3 Rotates around with the rotor 5, and the cam 3
The protrusion 3B rotates until it contacts the notch 1B of the housing 1, and then rotates integrally with the housing 1. The rotor 5 is rotatably accommodated in the housing 1, is coupled to the input shaft 6, and rotates integrally with the input shaft 6.

A plurality of plunger chambers 7 are formed in the rotor 5 in the axial direction, and a plurality of plungers 8 are slidably accommodated in the plunger chamber 7 via return springs 9. Further, the rotor 5 is formed with a plurality of suction / discharge holes 10 so as to communicate with the respective plunger chambers 7. Reference numeral 11 denotes a valve in which an intake port 12 and a discharge port 13 are formed. The valve 11 is positioned and fixed to the housing 1 by engaging a notch 1B of the housing 1 with a protrusion 14.

The discharge port 13 communicates with the high pressure chamber 15, and an orifice 16 as a flow resistance generating means is formed at the outlet of the high pressure chamber 15. As shown in FIG. 3, the outlet portion of the orifice 16 is formed as a round hole and the flat portion 17 of the valve 11 is formed.
And an opening hole 18 is formed by opening vertically. This opening 1
The diameter of 8 is larger than the diameter of the orifice 16.

Further, as shown in FIG. 4, a groove 19 communicating with the opening 18 is formed in the outer circumference of the valve 11 in the circumferential direction,
A groove 20 communicating with the groove 19 is formed in the horizontal direction, and these grooves 19 and 20 form an outflow passage 21 through which the oil outflow from the orifice 16 flows out. The arrow B indicates the flow of oil outflow from the orifice 16. The arrow C indicates the flow of oil flowing out from the free valve described later.

The outflow passage 21 allows the outflow oil to flow out to the oil chamber 23 provided with a hydraulic pump, without flowing to the oil chamber 22 provided with a movable magnetic body, which will be described later. When the plunger 8 is in the suction stroke, the suction port 12 of the valve 11 and the suction / discharge hole 10 of the rotor 5 are in a positional relationship of communicating with each other, and the orifice 16, the opening hole 18, and the outflow passage 2 are provided.
Oil can be sucked into the plunger chamber 7 through the suction port 1, the suction port 12, and the suction / discharge hole 10 of the rotor 5.

When the plunger 8 is in the discharge stroke, the relationship is the reverse of the suction stroke, and the suction / discharge hole 10 of the rotor 5 communicates with the discharge port 13 of the valve 11 and the high pressure chamber 15. The valve 11 is supported by bearings 24, the valve 11 is fixed to the inner circumference of the housing 1, and rotates integrally with the housing 1.

Reference numeral 25 is a magnetic frame, and the magnetic frame 25 is fixed to an external member and held in a non-contact state with the joint. The magnetic frame 25 is arranged concentrically with respect to the joint shaft,
A solenoid coil 26 is housed inside. A movable magnetic body 27 generates a magnetic attraction force by energizing the solenoid coil 26, and the movable magnetic body 27 is movably accommodated in the housing 1. A screw 28 is provided on the valve 11 as a stopper to the right of the movable magnetic body 27 in the figure. Further, the screw 28 has a function as a detent for the movable magnetic body 27.

Reference numeral 29 denotes a poppet-type first control valve as a free valve. One end side of the first control valve 29 closes the valve hole 30 of the valve 11, and the other end side is formed in the movable magnetic body 27. It is inserted into the insertion notch 31. The first control valve 29 includes a poppet valve portion 32 that closes the valve hole 30 and a space portion 33 that communicates with the high pressure chamber 15.
And a piston portion 34 of the valve hole 30 having substantially the same diameter, and a circumferential groove 35 that engages with the movable magnetic body 27. Movable magnetic body 2
When the first control valve 29 moves to the left in FIG. 1 by 7, the valve hole 30 is opened, and the high pressure chamber 15 communicates with the suction port 12 and becomes free. The first control valve 29 has a good sealing property and opens the valve hole 30 with a small amount of movement.

Reference numeral 36 is a second control valve as a lock valve. The second control valve 36 is a flat portion 17 of the valve 11.
It is slidably inserted into a guide portion 37 formed in the valve 11 so that it can move along an axis that is perpendicular to the axis and is concentric with the opening hole 18, and one end thereof is a movable magnetic body. It is inserted in 27. The guide portion 37 also has a function of guarding the oil flowing out of the orifice 16 from hitting the movable magnetic body 27.

As shown in FIG. 3, the second control valve 3
6 is formed in the shape of a rod having a round cross section that is larger than the diameter of the opening hole 18 at the outlet of the orifice 16, and the angle D between the contact surface 36A that closes in close contact with the opening hole 18 and the flat surface portion 17 is a predetermined angle, For example, it is set to 45 degrees or less. That is,
The other end of the second control valve 36 has a spherical shape or a conical shape.

The movable magnetic body 27 allows the second control valve 36
Moves to the left in FIG. 1 and closes the opening hole 18,
The orifice 16 is closed and locked. The movable magnetic body 27, the solenoid coil 26, and the magnetic frame 25 constitute an actuator as a whole, and the actuator controls the operation of the first and second control valves 29, 36.

As shown in FIG. 5, return springs 38 and 39 are respectively interposed between the valve 11 and the movable magnetic body 27 at the lower two places. The return springs 38 and 39 are provided at positions symmetrical with respect to a vertical line passing through the joint shaft center of the movable magnetic body 27, and the first control valve 29 is provided between the return springs 38 and 39. ing. That is, the return springs 38 and 39 are housed in the housing holes 40 and 41 formed in the valve 11, respectively.

In FIG. 1, reference numeral 42 denotes an accumulator piston that rotates integrally with the housing 1. The accumulator piston 42 is provided to absorb thermal expansion of the enclosed oil. A return spring 44 is interposed between the accumulator piston 42 and the cover 43 fixed to the housing 1. In addition, 45 is a spline, 4
6, 47 are oiling holes, 48, 49 are oil seals, 50 is a needle bearing, 51 is a seal ring, 52-54.
Is a stopper ring.

Next, the operation will be described. First, the normal characteristics will be described. When the solenoid coil 26 is not energized, the movable magnetic body 27 does not generate a magnetic attraction force and is held at the position shown in FIG. Therefore, the return spring 3
8,39 are not compressed.

Therefore, the first control valve 29 is connected to the high pressure chamber 15
The valve hole 30 that connects the suction port 12 with the suction port 12 is closed. On the other hand, the second control valve 36 is the orifice 16
Is open, the oil flows as indicated by arrow E in FIG. That is, the oil pushed out to the discharge port 13 passes through the high pressure chamber 15, the orifice 16 and the opening hole 18, is blocked by the guide portion 37, and is supplied to the suction port 12 via the outflow passage 21.

In this way, the oil does not flow out to the oil chamber 22 side where the movable magnetic body 27 is provided, and therefore flows to the oil chamber 23 side where the hydraulic pump is provided. Then, due to the resistance of the orifice 16, the hydraulic pressure of the high pressure chamber 15, the discharge port 13 and the plunger chamber 7 rises, and the plunger 8
A reaction force is generated. By rotating the cam 3 against the plunger reaction force, torque is generated, and the torque is transmitted between the cam 3 and the rotor 5.

The torque characteristic at this time is shown in F of FIG. 6, and becomes the torque T proportional to the square of the differential rotation speed ΔN.
Next, the characteristics of the lock will be described. When the solenoid coil 26 is weakly energized, the return spring 38,
The upper side of the movable magnetic body 27 not provided with 39 is in contact with the valve 11.

Therefore, the first control valve 29 is connected to the high pressure chamber 15
The valve hole 30 that connects the suction port 12 and the suction port 12 remains closed, but the second control valve 36 is
Close. That is, as shown in FIG.
The control valve 36 of (3) is in close contact with the opening hole 38 on the spherical surface thereof and closes the orifice 16. The angle between the contact surface 36A and the flat surface portion 17 is 45 degrees or less, and the flat surface portion 17 contacts the flat surface portion 17 at a small contact angle.

At this time, the torque characteristic is shown by G in FIG. 6, and the locked state is achieved. Next, the free characteristics will be described. When the solenoid coil 26 is energized strongly,
The movable magnetic body 27 compresses the return springs 38 and 39 to move, and the entire body comes into contact with the valve 11. Therefore, the second control valve 36 keeps the orifice 16 closed, and the first control valve 29 keeps the high pressure chamber 15 closed.
The valve hole 30 that communicates with the suction port 12 is opened.
Therefore, the oil in the high pressure chamber 15 does not pass through the orifice 16 and flows into the suction port 12 as it is.

The torque characteristic at this time is shown by H in FIG. 6 and is in a free state. In this way, the orifice 16
The spilled oil from the outlet is blocked by the guide portion 37, and the outflow passage 21
Through the suction port 12 through the movable magnetic body 27
Therefore, the operation of the movable magnetic body 27 is not limited, stable control performance can be secured with a small current, and responsiveness can be improved.

Further, since the second control valve 36 for locking can be formed in a simple rod shape, the cost can be reduced. Furthermore, since the contact surface 36A of the second control valve 36 contacts the flat surface portion 17 of the valve 11 with a small contact angle, the variation of the lock torque is reduced,
Further, even if it is repeatedly used, there is little change in shape, and stable control performance can be obtained.

[0034]

As described above, according to the present invention, the oil flowing out from the orifice is prevented from hitting the movable magnetic body, so that the operation of the movable magnetic body is not hindered and stable control performance is obtained. Can be secured, and responsiveness can be improved. Further, since the lock control valve can be formed in a simple rod shape, the cost can be reduced.

Further, since the control valve for locking contacts the flat surface of the valve with a small contact angle, there is no variation in the lock torque, and even if it is repeatedly used, the change in control performance is small.

[Brief description of drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

[Figure 2] Side view

FIG. 3 is a sectional view of a main part

FIG. 4 is a perspective view of a valve.

FIG. 5 is a diagram showing a valve and a movable magnetic body.

FIG. 6 is a graph showing torque characteristics

FIG. 7 is a sectional view showing a conventional example.

FIG. 8 is an explanatory diagram of problems

[Explanation of symbols]

 1: Housing 1A: Non-magnetic part 1B: Notch 2: Welded part 3: Cam 3A: Cam surface 3B: Protrusion 4: Thrust needle bearing 5: Rotor 6: Input shaft 7: Plunger chamber 8: Plunger 9: Return spring 10: Suction / discharge hole 11: Valve 12: Suction port 13: Discharge port 14: Protrusion 15: High pressure chamber 16: Orifice (flow resistance generating means) 17: Flat part 18: Opening hole 19, 20: Groove 21: Outflow Lines 22 and 23: Oil chamber 24: Bearing 25: Magnetic frame 26: Solenoid coil 27: Movable magnetic body 28: Screw 29: First control valve 30: Valve hole 31: Notch for insertion 32: Poppet valve part 33 : Space part 34: Piston part 35: Circumferential groove 36: Second control valve 36A: Contact surface 37: Guide part 38, 39: Return spring 4 , 41: receiving hole 42: accumulator piston 43: Cover 44: return spring 45: Spline 47: Lubrication holes 48, 49: oil seal 50: needle bearing 51: sealing ring 52 to 54: stop ring

Claims (2)

[Claims] 1. A hydraulic pump provided between relatively rotatable input and output shafts and driven by differential rotation of the both shafts; a control provided at an outlet of the hydraulic pump for controlling flow resistance of discharged oil. A valve and; an actuator for actuating the control valve in response to an external signal; a hydraulic power transmission joint for transmitting a torque according to a rotational speed difference between the two shafts and an external control signal; The discharge passage communicating with the discharge passage from the hydraulic pump so that the discharge oil flows into the oil chamber provided with the hydraulic pump on the opposite side of the oil chamber provided with the movable magnetic body forming a part of the actuator. A hydraulic power transmission joint characterized by being provided with an opening to an oil chamber provided with the hydraulic pump. 2. A diameter larger than an orifice as a flow resistance generating means for generating the flow resistance,
An opening hole of an orifice outlet that opens perpendicularly to the plane part of the valve, and a control valve that is provided so as to be movable along the axis of the opening hole and that is closed by being pushed by the movable magnetic body. And a guide portion for guiding the control valve to the above state and blocking the oil discharged from the orifice so as not to flow to the movable magnetic body side, the control valve being the orifice outlet. The rod-shaped end surface has a circular cross section larger than the diameter of the opening hole, and the angle between the contact surface that closes in close contact with the opening hole and the flat surface portion is equal to or less than a predetermined angle. The hydraulic power transmission joint according to claim 1, wherein