JPH05118350A - Hydraulically-operated power transmitting coupling - Google Patents

Abstract

PURPOSE:To attain torque-up by large setting starting torque, relating to a hydraulically-operated power transmitting coupling used for distributing drive power of a vehicle. CONSTITUTION:A power transmitting coupling is constituted by providing a thrust member 31 stored slidably in an axial direction in a notch of a cam housing 4, elastic member 33 for pressing the thrust member 31 and a friction plate 34, having a protrusion fitted to a groove formed in the periphery of a rotor 5, pressed by the thrust member 31.

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. 2-184735. That is, the hydraulic power transmission joint is provided between the relatively rotatable input / output shafts, is connected to the one shaft, and has a cam housing having a cam surface having two or more ridges on its inner surface; While being connected to the other shaft,
A rotor that is rotatably housed in the cam housing and has a plurality of plunger chambers formed in the axial direction; and a rotor that is 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 and communicating with the plunger chamber; and an end face of the rotor rotatably slidably contacted, A plurality of intake ports that are positioned in a predetermined relationship with the cam housing and act as intake valves and discharge valves according to the positional relationship with the intake and discharge holes; A means for generating a flow resistance by the flow of the discharged oil by the driving of the jar; In a power transmission joint, a communication groove that is provided on a back surface of the valve body that does not form a suction port and a discharge port, and that communicates with each of the discharge ports, a lid member that is closely attached to the back surface, and the communication groove. Alternatively, it is provided with flow resistance generating means provided between the discharge port and the low pressure chamber.

[0003]

However, in such a conventional hydraulic power transmission joint, the starting torque depends on the friction coefficient between the rotor and the valve body, the friction coefficient between the cam and the plunger, and the plan. It was not possible to set a large starting torque because it was determined by the pressing force of the return spring of the jar.

As a result, there is a problem that the torque cannot be increased with the same size. The present invention has been made in view of such conventional problems,
It is an object of the present invention to provide a hydraulic power transmission joint that can increase the starting torque by increasing the starting torque.

[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 connected to the one shaft and having a cam surface having two or more ridges on the inner surface; a cam housing connected to the other shaft and rotatably housed in the cam housing; A rotor having a plunger chamber formed in the axial direction; a plurality of plungers housed in each of the plurality of plunger chambers so as to be capable of reciprocating movement and driven by the cam surface when the two shafts relatively rotate. An inlet / outlet hole formed in the rotor and communicating with the plunger chamber; and an inlet / outlet hole rotatably slidably contacting an end surface of the rotor and positioned in a predetermined relationship with the cam housing. A valve body having a plurality of suction ports and discharge ports that act as suction valves and discharge valves depending on the positional relationship, and the flow of discharge oil by driving the plunger. In a hydraulic power transmission joint that transmits torque according to the rotational speed difference between the two shafts, the thrust housed in the notch of the cam housing so as to be slidable in the axial direction. Members,
An elastic member that presses the thrust member and a friction plate that has a protrusion that fits in a groove formed on the outer periphery of the rotor and that is pressed by the thrust member are provided.

[0006]

In the present invention, when the thrust member is axially pressed by the elastic member, the thrust member presses the friction plate having the projection fitted in the groove formed on the outer periphery of the rotor, and the friction plate applies the brake to the rotor. Call. That is, since the clutch brake mechanism is provided and the rotor is braked by utilizing the notch of the cam housing and the extra portion between the plunger chambers, the starting torque can be applied to the joint.

As described above, since the starting torque can be set to a large value, the starting torque can be added to the conventional torque characteristic, and the torque can be increased. That is, the torque can be increased with the same size without increasing the size of the joint.

[0008]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 4 are views showing an embodiment of the present invention.
First, the configuration will be described. In FIG. 1 and FIG.
Is a cam having a cam surface 2 having two or more ridges on its inner surface, and the cam 1 is connected to the output shaft 3 and rotates integrally with the output shaft 3. Further, the cam 1 is fixed to the cam housing 4, and the cam housing 4 rotates integrally with the cam 1.

A rotor 5 is rotatably housed in the cam housing 4, and the rotor 5 is connected to the input shaft 6.
It rotates integrally with the input shaft 6. Plural plunger chambers 7 are formed in the rotor 5 in the axial direction.
A plurality of plungers 8 are slidably housed inside via return springs 9. Further, the rotor 5 is formed with a plurality of suction and discharge holes 10 so as to communicate with the respective plunger chambers 7.

Reference numeral 11 indicates a suction port 12 and a suction passage 13 on the surface.
And a discharge port 14 are formed in the rotary valve (valve body), and a communication groove 15 communicating with each of the discharge ports 14 is formed on the back surface of the rotary valve 11. Further, a lid member 16 is provided in close contact with the back surface. Then, the communication groove 15 and one suction port 12
An orifice (flow resistance generating means) 17 is formed between and.

The rotary valve 11 also has a positioning projection 19 which engages with a notch 18 formed in the inner circumference of the cam housing 4. The rotary valve 11 constitutes a timing member that determines the opening / closing timing of the intake / discharge hole 10, and the notch 18 and the protrusion 19 constitute a positioning mechanism that regulates the phase relationship between the cam 1 and the rotary valve 11.

When the plunger 8 is in the suction stroke,
The intake port 12 of the rotary valve 11 and the intake / discharge hole 10 of the rotor 5 communicate with each other, and the orifice 17,
Suction port 12, suction passage 13, suction / discharge hole 1 of rotor 5
Through 0, oil can be sucked into the plunger chamber 7. 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 communication groove 15 via the discharge port 14 of the rotary valve 11.

Reference numeral 20 is a thrust block that rotates integrally with the cam housing 4, and supports the input shaft 6 via a bearing 21. A needle bearing 22 is interposed between the thrust block 20 and the rotary valve 11, and the friction torque on the needle bearing 22 side is set to be smaller than the friction torque between the rotor 5 and the rotary valve 11. Therefore, when the direction of the differential rotation changes, the rotary valve 11 circulates together with the rotor 5, rotates until the positioning projection 19 of the rotary valve 11 hits the notch 18 of the cam housing 4, and then becomes integral with the cam housing 4. To rotate. As a result, the intake / discharge hole 10 is forcibly opened / closed at a predetermined timing even during normal rotation or reverse rotation.

Reference numeral 23 is an accumulator piston that rotates integrally with the cam housing 4, and the accumulator piston 23 moves according to the internal pressure. A return spring 25 is interposed between the accumulator piston 23 and the retainer 24. In addition, 26 is an oil seal, 2
7 is a stopper ring, 28 is a bolt, 29 is a lubricating hole, 3
0 is a needle bearing.

Reference numeral 31 is a thrust member, which is the outer periphery of the rotor 5 and is housed in the notch 18 of the cam housing 4 so as to be slidable in the axial direction. The rotation of the thrust member 31 in the circumferential direction is prevented by a valve positioning projection 32 formed on the cam housing 4. One end surface of the thrust member 31 is formed as a friction surface 31A, and the other end surface is formed as a slide surface 31B that slides with respect to the protrusion 32 (see FIG. 3).

Reference numeral 33 denotes a disc spring as an elastic member. The disc spring 33 is located outside the needle bearing 22 and is interposed between the thrust block 20 and the thrust member 31 to press the thrust member 31 in the axial direction. (See Figure 3). As shown in FIG. 3, the rotor 5 has a plurality of grooves 5A in the circumferential direction in the outer periphery thereof where there is no plunger chamber 7.
Are formed.

Reference numeral 34 is a friction plate, and a plurality of projections 34A are formed on the inner circumference of the friction plate 34 in the circumferential direction, and the projections 34A are fitted in the grooves 5A, respectively. The projection 32 of the cam housing 4 is scraped off in order to fit the friction plate 34 into the groove of the rotor 5 and to incorporate it into the cam housing 4 (see A and B parts).

Reference numeral 35 is a retainer, and the retainer 35 is fixed to the inner circumference of the cam housing 4 so as to contact the friction plate 34. The surface of the retainer 35 that contacts the friction plate 34 is formed as a friction surface 35A. Next, the operation will be described. When there is no rotation difference between the cam 1 and the rotor 5, the plunger 8 does not operate and torque is not transmitted. At this time, the plunger 8 is pressed against the cam surface 2 by the return spring 9.

Next, when a rotation difference occurs between the cam 1 and the rotor 5, the plunger 8 in the discharge stroke is pushed axially by the cam surface 2 of the cam 1. At this time, since the suction / discharge hole 10 communicates with the discharge port 14, the plunger 8 pushes the oil in the plunger chamber 7 from the suction / discharge hole 10 to the discharge port 14 of the rotary valve 11.

The oil pushed out to the discharge port 14 is
It is supplied to the suction port 12 through the communication groove 15 and the orifice 17. At this time, the hydraulic pressure in the communication groove 15, the discharge port 14, and the plunger chamber 7 increases due to the resistance of the orifice 17, and a reaction force is generated in the plunger 8. A torque is generated by rotating the cam 1 against the plunger reaction force, and the torque is transmitted between the cam 1 and the rotor 5. Since the discharge ports 14 are communicated with each other through the communication groove 15, the hydraulic pressures of all the plunger chambers 7 in the discharge process are equal.

Further, when the cam 1 rotates, the suction stroke is started, and the suction / discharge hole 10 communicates with the suction port 12, so that
The oil in the suction passage 13 is supplied to the suction port 12 and the suction / discharge hole 1.
It is sucked into the plunger chamber 7 via 0, and the plunger 8 returns along the cam surface 2 of the cam 1. Here, the notch 18 of the cam housing 4 is diverted to provide the thrust member 31 slidably in the axial direction, and the disc spring 33 presses the thrust member 31 in the axial direction. Friction surface 3 of thrust member 31
1A presses the friction plate 34, and the friction plate 34 makes frictional contact with the friction surface 35A of the retainer 35. As a result, the rotor 5 can be braked and the joint can be given a starting torque.

As described above, since the starting torque can be set to a large value, the starting torque can be rubbed with respect to the conventional torque characteristic C as shown in FIG.
It is possible to obtain torque characteristics as shown in. As a result, the torque can be increased without increasing the size of the joint.

[0023]

As described above, according to the present invention, since the thrust member is pressed by the disc spring to bring the thrust member into frictional contact with the friction plate fitted in the groove of the rotor, the starting torque is increased. It can be set large. As a result, the torque can be increased with the same size without increasing the size of the joint.

[Brief description of drawings]

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

FIG. 2 is another sectional view showing an embodiment of the present invention.

FIG. 3 is an exploded perspective view of essential members.

FIG. 4 is a graph showing torque characteristics

[Explanation of symbols]

 1: Cam 2: Cam surface 3: Output shaft 4: Cam housing 5: Rotor 5A: Groove 6: Input shaft 7: Plunger chamber 8: Plunger 9: Return spring 10: Suction / discharge hole 11: Rotary valve 12: Suction Port 13: Suction path 14: Discharge port 15: Communication groove 16: Lid member 17: Orifice 18: Notch 19: Protrusion 20: Thrust block 21: Bearing 22: Needle bearing 23: Accumulator piston 24: Retainer 25: Return spring 26 : Oil seal 27: Stopper ring 28: Bolt 29: Oiling hole 30: Needle bearing 31: Thrust member 31A: Friction surface 31B: Sliding surface 32: Protrusion 33: Disc spring (elastic member) 34: Friction plate 34A: Protrusion 35: Retainer 35A: Friction surface

Claims (1)

[Claims] 1. A cam housing provided between relatively rotatable input / output shafts, connected to said one shaft, and having a cam surface having two or more ridges on its inner side surface; connected to said other shaft. And a rotor having a plurality of plunger chambers axially formed therein and rotatably housed in the cam housing; reciprocally housed in each of the plurality of plunger chambers; Plural plungers driven by the cam surface when the shaft rotates relative to each other; suction and discharge holes formed in the rotor, which communicate with the plunger chamber; A valve having a plurality of suction ports and a discharge port, which are positioned in a predetermined relationship between the suction port and And a means for generating a flow resistance by the flow of the discharge oil by the driving of the plunger; a hydraulic power transmission joint for transmitting a torque according to a rotational speed difference between the both shafts, wherein a notch of the cam housing A friction plate that is axially slidably housed, has an elastic member that presses the thrust member, and has a protrusion that fits into a groove formed on the outer periphery of the rotor and that is pressed by the thrust member. A hydraulic power transmission joint characterized by having.