JPH05187461A - Hydraulic power transmission joint - Google Patents

Abstract

PURPOSE:To provide a hydraulic power transmission joint used for distributing the driving force of a vehicle, which can eliminate the need of a one-way valve to be simple in structure and reduce the limit in loading on a vehicle, and can reduce the size of an actuator. CONSTITUTION:A hydraulic power transmission joint comprises; an intake and discharge hole 15 which is formed on a rotor 11 and communicates with a plunger chamber 12; a valve element 16 which is positioned in such a manner as to rotate only in designated degrees of arc with a cam housing 8 when the relative rotating direction of both shafts is switched, functions as an intake valve or as a discharge valve according to the positional relation to the intake and discharge hole 15 of the rotor 11, includes a flow resistance generating means 18, and is capable of moving in the axial direction; and an actuator provided on the other shaft to control the valve element 16 to move in the axial direction.

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 the following hydraulic power transmission joint in Japanese Patent Application No. 1-154228. That is, this hydraulic power transmission joint responds to a hydraulic pump driven by the rotational speed difference between the first and second rotating members which are relatively rotatable, and a control signal from the outside to the discharge passage of the hydraulic pump. Equipped with 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 housed in a central portion of the one rotating member so as to be axially movable. And a magnetic frame fixed to the non-rotating third member and the solenoid coil are held in a non-contact state to constitute an electromagnetic actuator as a whole, and the actuator directly operates the flow resistance control means. It is the one.

[0003]

However, such a conventional hydraulic power transmission joint 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. There is a problem in that the structure becomes complicated because it must be done. Further, since it is necessary to provide the movable magnetic body, the magnetic frame, and the solenoid coil on the rear end side of the joint, there are problems that mounting restrictions on the vehicle are large and that these actuators are large.

The present invention has been made in view of the above-mentioned problems of the prior art, and has a simple structure that does not require a one-way valve, and has less restrictions on vehicle mounting, and
It is an object of the present invention to provide a hydraulic power transmission joint that can downsize an actuator.

[0005]

In order to achieve the above-mentioned object, the present invention is provided between input / output shafts capable of relative rotation,
A cam housing that is connected to the one shaft and has a cam surface having two or more peaks on the inner surface, and a cam housing that is connected to the other shaft and is rotatably housed in the cam housing. A rotor forming a jar chamber,
A plurality of plunger chambers are formed in the rotor, each of which is housed in each of the plurality of plunger chambers so as to be reciprocally movable under the pressure of a return spring and driven by the cam surface when the two shafts relatively rotate. The intake / discharge hole communicating with the plunger chamber and the intake / discharge hole of the rotor are rotatably positioned by a predetermined angle between the cam housing and the cam shaft when the relative rotation directions of the shafts are switched. It acts as a suction valve or a discharge valve depending on the positional relationship, and has a flow resistance generating means,
It is provided with a valve body that is movable in the axial direction and an actuator that is provided on the other shaft and that controls the movement of the valve body in the axial direction.

[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 respect to the cam housing, and the intake valve or In addition to acting as a discharge valve, it has a flow resistance generating means and an axially movable valve element (rotary valve) is provided, so a one-way valve, which was required for each plunger chamber, is not required and the structure is simple. become.

Further, since the actuator for controlling the movement of the valve element can be provided on the outer circumference of the other shaft (input shaft), restrictions on mounting on a vehicle are reduced. Further, since the actuator only directly operates the valve body, it can be downsized.

[0008]

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.
1 to 3, reference numeral 1 denotes an input shaft having an oil passage 2 formed therein, and a sprocket 3 is rotatably supported on the input shaft 1 via a needle bearing 4. .. A chain 5 is installed between the sprocket 4 and a sprocket (not shown).

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

Reference numeral 11 denotes a rotor rotatably housed in the cam housing 8, and the rotor 11 is a hollow shaft 45.
It is fixed to the input shaft 1 via and rotates 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 accommodated in the plunger chamber 12 via return springs 14. Further, the rotor 11 is formed with a plurality of suction / discharge holes 15 so as to communicate with the respective plunger chambers 12.

Reference numeral 16 is a rotary valve (valve body) of a movable magnetic body. As shown in FIG. 4, the rotary valve 16 is a valve body 16A, and a cylinder which is formed integrally with the valve body 16A and is curved. It has a plurality of protrusions 16B which are parts. Elongated hole-shaped discharge ports 17 are formed in the protrusions 16B, and orifices 18 are formed in the discharge ports 17 as flow resistance generating means.

Oil grooves 19 communicating with the orifices 18 are formed on the back side of the protrusions 16B, respectively.
A notch 20 communicating with the oil groove 19 is formed between 6B. The oil groove 19 and the notch 20 form a suction passage 21, and the suction passage 21 communicates with the plunger chamber 12 via the suction / discharge hole 15. A notch 16C is formed on the outer circumference 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 which determines the opening / closing timing of the intake / discharge hole 15, and the notch 16C and the stopper bolt 10 constitute a positioning mechanism which regulates the phase relationship between the cam housing 8 and the rotary valve 16. ing. When the plunger 13 is in the intake stroke, there is a positional relationship in which the intake passage 21 of the rotary valve 16 and the intake / discharge hole 15 of the rotor 11 communicate with each other, and the notch 20,
Oil can be sucked into the plunger chamber 12 through the oil groove 19 and the suction / discharge hole 15 of the rotor 11.

When the plunger 13 is in the discharge stroke, the relationship opposite to that of the suction stroke occurs, and the suction / discharge hole 15 of the rotor 11 communicates 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 friction of the O-ring 22 causes the rotary valve 16 to rotate with the rotor 11, and the notch 16C of the rotary valve 16 rotates until it contacts the stopper bolt 10 of the rear cover 9, and then the cam housing 8 Rotate as one. As a result, the intake / discharge hole 15 is forcibly opened / closed at a predetermined timing even during normal rotation or 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, and the spring 27 presses the rotary valve 16 against the rear cover 9.

Reference numeral 28 is a solenoid coil for attracting the rotary valve 16 by energization.
Are housed in a magnetic frame 29. The magnetic frame 29 is attached to a casing 31 of the transfer by a bracket 30. The solenoid coil 28 and the magnetic frame 29 constitute an actuator that controls the movement of the rotary valve 16 in the axial direction, and the actuator is provided on the outer circumference of the input shaft 1.

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

Incidentally, 39 and 40 are oil seals, 41 and
42 is an O-ring, and 43 and 44 are stopper rings.
Next, the operation will be described. First, the normal operation will be described. In a normal state where the solenoid coil 28 is not energized, the rotary valve 16 is not attracted to 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 intake / 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 by the cam surface 8A of the cam housing 8 in the axial direction. Therefore, the plunger 1
Reference numeral 3 pushes the oil in the plunger chamber 12 from the suction / discharge hole 15 to the discharge port 17 of the rotary valve 16.

The oil pushed out to the discharge port 17 is
It is supplied to the suction passage 21 through the orifice 18. At this time, the hydraulic pressure of 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. A torque is generated by rotating the rotor 11 against the plunger reaction force, and the torque is transmitted between the cam housing 8 and the rotor 11.

As shown in A of FIG. 5, this torque characteristic becomes a torque T proportional to the square of the differential rotation speed ΔN.
Further, when the rotor 11 is rotated, the suction stroke begins,
Since the suction / discharge hole 15 and the suction passage 21 communicate with each other, the suction passage 21
Oil from the plunger chamber 12 through the suction / discharge hole 15
And the plunger 13 returns along the cam surface 8A of the cam housing 8.

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

In this embodiment, since the rotary valve 16 having the suction passage 21 and the discharge port 17 is used, the one-way valve which is required for each plunger chamber as in the conventional case is not necessary. You can
As a result, the structure is simple. Since an actuator for controlling the operation of the rotary valve 16 can be provided on the outer periphery of the input shaft 1, the limitation on mounting on a vehicle is reduced. Furthermore, since the solenoid coil 28 only directly operates the rotary valve 16, the actuator can be downsized.

[0024]

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

[Brief description of drawings]

FIG. 1 is a diagram showing an 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 perspective view of a rotary valve.

FIG. 5 is a graph showing torque characteristics

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

[Explanation of symbols]

 1: Input shaft 2: Oil passage 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: Protrusion 16C: Notch 17: Discharge port 18: Orifice (flow resistance generating means) 19: Oil groove 20: Notch 21: Intake passage 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 passage 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

Claims (3)

[Claims] 1. A cam housing provided between relatively rotatable input / output shafts, connected to said one shaft, and having an inner surface having a cam surface having two or more ridges, and connected to said other shaft. And a rotor that is rotatably housed in the cam housing and forms a plurality of plunger chambers, and a plurality of plunger chambers that are reciprocally housed in each of the plurality of plunger chambers under the pressure of a return spring. A plurality of plungers driven by the cam surface when the two shafts rotate relative to each other, an intake / discharge hole formed in the rotor, which communicates with the plunger chamber, and a relative rotation direction of the two shafts, It is positioned rotatably by a predetermined angle with respect to the cam housing, and acts as a suction valve or a discharge valve depending on the positional relationship with the suction / discharge hole of the rotor. Along with the above, there is provided a flow resistance generating means, and a valve body that is movable in the axial direction, and an actuator that is provided on the other shaft and that controls the movement of the valve body in the axial direction. Power transmission joint. 2. The valve body is made of a movable magnetic material, has a notch on the outer periphery, and a plurality of notches are formed in a cylindrical portion protruding from the valve body, and a discharge port is formed on the surface of the cylindrical portion. To
2. The hydraulic power transmission joint according to claim 1, wherein an oil groove is formed on the back surface, and an orifice is formed as a flow resistance generating means for communicating the discharge port with the oil groove. 3. The hydraulic power transmission joint according to claim 1, wherein the actuator comprises a solenoid coil that attracts the valve body and a magnetic frame that houses the solenoid coil.