JP3207903B2 - Hydraulic power transmission coupling - Google Patents

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 coupling used for distributing driving force of a vehicle.

[0002]

2. Description of the Related Art The present applicant has proposed the following hydraulic power transmission coupling in Japanese Patent Application No. 1-154228. In other words, the hydraulic power transmission joint has a hydraulic pump driven by a rotational speed difference between the first and second rotatable members that can rotate relative to each other, and a hydraulic pump in response to an external control signal to a discharge path of the hydraulic pump. A control means for generating flow resistance;
In a hydraulic power transmission joint in which a transmission torque between the first and second rotating members is controlled by an external control signal, a movable magnetic body accommodated in a central portion of the one rotating member so as to be movable in an axial direction. And the magnetic frame fixed to the third member that does not rotate and the solenoid coil are kept out of contact with each other to form an electromagnetic actuator as a whole, and the actuator directly operates the flow resistance control means. It was made.

[0003]

However, such a conventional hydraulic power transmission coupling is provided with a valve that opens on the suction side and a valve that closes on the discharge side for generating hydraulic pressure by differential rotation. This requires a complicated structure. In addition, since the movable magnetic body, the magnetic frame, and the solenoid coil need to be provided at the rear end side of the joint, there is a problem that the mounting on the vehicle is greatly restricted and the size of these actuators is increased.

[0004] The present invention has been made in view of such conventional problems, and has a simple structure that does not require a one-way valve.
It is an object of the present invention to provide a hydraulic power transmission coupling capable of reducing the size of an actuator.

[0005]

In order to achieve the above object, the present invention is provided between input / output shafts which are rotatable relative to each other,
A cam housing connected to the one shaft and having a cam surface having two or more peaks on an inner surface; and a plurality of plans connected to the other shaft and rotatably housed in the cam housing. A rotor forming a jar chamber;
A plurality of plungers are housed in each of the plurality of plunger chambers so as to be reciprocally movable under the pressure of a return spring, and are driven by the cam surface when the two shafts rotate relative to each other, and formed in the rotor. And a suction / discharge port communicating with the plunger chamber, and positioned so as to be rotatable by a predetermined angle between the cam housing and the suction / discharge port when the relative rotation directions of the two shafts are switched, and Acts as a suction valve or a discharge valve depending on the positional relationship, and has flow resistance generating means,
An axially movable valve body, and an actuator provided on the other axis for controlling movement of the valve body in the axial direction, wherein the valve body is made of a movable magnetic body, and has a notch on its outer periphery.
The cylindrical part formed by projecting the valve body has multiple cuts.
Form a notch, discharge port on the front surface of the cylinder, and oil on the back surface
The flow resistance forming a groove and communicating the discharge port with the oil groove
An orifice is formed as generating means .

[0006]

According to the present invention, when the relative rotation direction of the input / output shaft is switched, it is positioned so as to be rotatable by a predetermined angle with the cam housing, and the suction valve or the suction valve depends on the positional relationship with the suction and discharge holes of the rotor. It has the function of a discharge valve, has flow resistance generating means, and is provided with a valve element (rotary valve) that can move in the axial direction, eliminating the need for a one-way valve required for each plunger chamber, thus simplifying the structure. become.

[0007] Further, since an actuator for controlling the movement of the valve element can be provided on the outer periphery of the other shaft (input shaft), restrictions on mounting on the vehicle are reduced. Further, since the actuator only operates the valve body directly, the size can be reduced.

[0008]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 6 are views showing one embodiment of the present invention.
First, the structure will be described. In FIGS. 1 to 3, reference numeral 1 denotes an input shaft having an oil passage 2 formed therein. A sprocket 3 is rotatably supported on the input shaft 1 via a needle bearing 4. . A chain 5 is provided between the sprocket 4 and a sprocket (not shown).

A front body 7 is fitted to a spline 6 integrally formed with the sprocket 3, and the front body 7
Is welded with a cam housing 8 having a cam surface 8A having two or more cam ridges on the inner diameter surface at 8B. Reference numeral 9 denotes a rear cover. The rear cover 9 is fixed to the cam housing 8 and is provided with two stopper bolts 10.

Reference numeral 11 denotes a rotor rotatably housed in the cam housing 8, and the rotor 11 has a hollow shaft 45.
, And is rotated integrally with the input shaft 1. A plurality of plunger chambers 12 are formed in the rotor 11 in the radial direction, and a plurality of plungers 13 are slidably housed in the plunger chamber 12 via a return spring 14. Further, a plurality of suction / discharge holes 15 are formed in the rotor 11 so as to communicate with each plunger chamber 12.

Numeral 16 denotes a rotary valve (valve element) made of a movable magnetic material. As shown in FIG. 4, the rotary valve 16 has a valve body 16A and a cylindrical body formed integrally with the valve body 16A and curved. It has a plurality of projecting portions 16B which are portions. A long hole-shaped discharge port 17 is formed in each of the protruding portions 16B, and each of the discharge ports 17 is formed with an orifice 18 as a flow resistance generating means.

An oil groove 19 communicating with the orifice 18 is formed on the back side of the projection 16B.
Notches 20 communicating with the oil grooves 19 are respectively formed between 6B. The oil groove 19 and the notch 20 constitute a suction passage 21, and the suction passage 21 communicates with the plunger chamber 12 through the suction / discharge hole 15. A notch 16C is formed on the outer periphery of the rotary valve 16, and a stopper bolt 10 screwed into the rear cover 9 is engaged with the notch 16C (see FIG. 3).

The rotary valve 16 constitutes a timing member for determining the opening / closing timing of the suction / discharge port 15, and the notch 16C and the stopper bolt 10 constitute a positioning mechanism for regulating the phase relationship between the cam housing 8 and the rotary valve 16. ing. When the plunger 13 is in the suction stroke, there is a positional relationship between the suction passage 21 of the rotary valve 16 and the suction / discharge hole 15 of the rotor 11, so that the notch 20,
Oil can be sucked into the plunger chamber 12 through the oil groove 19 and the suction and discharge holes 15 of the rotor 11.

When the plunger 13 is in the discharge stroke, the relationship is opposite to that of the suction stroke. The suction and discharge holes 15 of the rotor 11 communicate with the discharge port 17 of the rotary valve 16 and the suction passage 21 is closed. Become. When the direction of the differential rotation changes, the rotary valve 16 rotates together with the rotor 11 due to the friction of the O-ring 22, and rotates until the notch 16 C of the rotary valve 16 hits the stopper bolt 10 of the rear cover 9. It rotates as one. Accordingly, the suction / discharge port 15 is forcibly opened and closed at a predetermined timing even in the normal rotation or the reverse rotation.

A retainer 23 is provided between the rotary valve 16 and the input shaft 1, and the retainer 23 is positioned by a snap ring 24 provided on the rotary valve 16. Input shaft 1 in contact with retainer 23 and bearing 25
A spring 27 is provided between the plate 26 and the plate 26 fixed thereto, and the rotary valve 16 is pressed against the rear cover 9 by the spring 27.

Numeral 28 denotes a solenoid coil for attracting the rotary valve 16 when energized.
Are stored in a magnetic frame 29. The magnetic frame 29 is attached to a transfer casing 31 by a bracket 30. The solenoid coil 28 and the magnetic frame 29 constitute an actuator for controlling the movement of the rotary valve 16 in the axial direction. The actuator is provided on the outer periphery of the input shaft 1.

Numeral 32 denotes a communication passage formed in the rotor 11. The suction passage 2 is formed through a communication hole 35 formed in the communication passage 32 and a cover member 34 supported by a bearing 33.
1 and the hydraulic chamber 36 communicate with each other. The accumulator piston 3 is connected to the hydraulic chamber 36 via a return spring 37.
8 is slidably provided. The accumulator piston 38 absorbs the thermal expansion of the oil inside the joint.

Reference numerals 39 and 40 denote oil seals and 41 and 40, respectively.
42 is an O-ring, and 43 and 44 are stopper rings.
Next, the operation will be described. First, a normal operation will be described. At the normal time when the solenoid coil 28 is not energized, the rotary valve 16 is not attracted by the solenoid coil 28 and presses the rear cover 9 by the force of the spring 27.

Therefore, the orifice 18 of the rotary valve 16 communicates with the suction / discharge hole 15. In this state, if a rotation difference occurs between the input and output shafts, the plunger 13 in the discharge stroke is pushed in the axial direction by the cam surface 8A of the cam housing 8. For this reason, plunger 1
3 pushes the oil in the plunger chamber 12 from the suction and discharge hole 15 to the discharge port 17 of the rotary valve 16.

The oil pushed out to the discharge port 17 is
The gas is supplied to the suction passage 21 through the orifice 18. At this time, the oil pressure in the discharge port 17 and the plunger chamber 12 rises due to the resistance of the orifice 18, and the plunger 13
A reaction force is generated. By rotating the rotor 11 against this plunger reaction force, a torque is generated, and the torque is transmitted between the cam housing 8 and the rotor 11.

This torque characteristic becomes a torque T proportional to the square of the differential rotation speed ΔN, as shown in FIG. 5A.
Further, when the rotor 11 is rotated, a suction stroke is performed,
Since the suction / discharge port 15 and the suction path 21 communicate with each other, the suction path 21
Of oil flows through the plunger chamber 12 through the suction / discharge port 15.
The plunger 13 returns along the cam surface 8A of the cam housing 8.

Next, the free state will be described. When power is supplied to the solenoid coil 28, the solenoid coil 2
8 shows the rotary valve 16 against the spring 27 in FIG.
Suction in the middle right direction. Therefore, the rotary valve 16 moves rightward until it comes into contact with the bearing 25. As a result, the orifice 18 of the rotary valve 16 moves away from the suction / discharge port 15, and the oil in the plunger chamber 12 escapes from the suction / discharge port 15 to the suction passage 21. Thus, the joint is free. The torque characteristic at this time is shown in FIG.

In this embodiment, the rotary valve 16 having the suction passage 21, the discharge port 17 and the like is used, so that the one-way valve required for each plunger chamber as in the related art is not required. Can be.
As a result, the structure was simplified. Since an actuator for controlling the operation of the rotary valve 16 can be provided on the outer periphery of the input shaft 1, restrictions on mounting on the vehicle are reduced. Furthermore, since the solenoid coil 28 only operates the rotary valve 16 directly, the size of the actuator can be reduced.

[0024]

As described above, according to the present invention, since a rotary valve is used, a conventional one-way valve is not required, and the structure is simplified. Further, since the actuator can be provided on the outer periphery of the input shaft, restrictions on mounting on the vehicle are reduced. Further, the size of the actuator can be reduced.

[Brief description of the drawings]

FIG. 1 shows an embodiment of the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG. 1;

FIG. 3 is a sectional view taken along arrows BB in FIG. 1;

FIG. 4 is a perspective view of a rotary valve.

FIG. 5 is a graph showing torque characteristics.

FIG. 6 is an explanatory diagram of an operation in a free state.

[Explanation of symbols]

 1: Input shaft 2: Oil path 3: Sprocket 4: Needle bearing 5: Chain 6: Spline 7: Front body 8: Cam housing 8A: Cam surface 9: Rear cover 10: Stopper bolt 11: Rotor 12: Plunger chamber 13: Plunger 14: Return spring 15: Suction / discharge hole 16: Rotary valve 16A: Valve body 16B: Projection 16C: Notch 17: Discharge port 18: Orifice (flow resistance generating means) 19: Oil groove 20: Notch 21: Suction path 22: O-ring 23: Retainer 24: Snap ring 25: Bearing 26: Plate 27: Spring 28: Solenoid coil 29: Magnetic frame 30: Bracket 31: Casing 32: Communication path 33: Bearing 34: Cover member 35: Communication Hole 36: Hydraulic chamber 37: Return spring 38: Accumulator piston 39, 40: Oil seal 41, 42: O-ring 43, 44: Stopper ring 45: Hollow shaft

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F16D 31/02

Claims (1)

(57) [Claims] 1. A cam housing provided between input and output shafts rotatable relative to each other and connected to the one shaft and having a cam surface having two or more peaks on an inner surface, and connected to the other shaft. And a rotor rotatably housed in the cam housing and forming a plurality of plunger chambers; and a plurality of plunger chambers, each of which is housed in a reciprocating manner under the pressure of a return spring. A plurality of plungers driven by the cam surface at the time of relative rotation of the two shafts, a suction and discharge hole formed in the rotor and communicating with the plunger chamber, and when the relative rotation direction of the two shafts is switched, It is positioned so as to be rotatable by a predetermined angle with the cam housing, and acts as a suction valve or a discharge valve depending on the positional relationship with the suction and discharge holes of the rotor. Together, has a flow resistance generating means, and movable valve element in the axial direction, is provided on the other axis, an actuator for moving control the valve body in the axial direction, the valve body is movable magnetic body
With a notch on the outer circumference and protruding valve body
A plurality of notches are formed in the cylindrical part
An oil groove is formed on the back of the discharge port, and the discharge port and the oil groove
Orifice as the flow resistance generating means for communicating
A hydraulic power transmission joint characterized by being formed .