JP2731464B2 - 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 applicant of the present invention has proposed a hydraulic power transmission coupling as described below in Japanese Patent Application No. 2-184735. That is, the hydraulic power transmission coupling is provided between a relatively rotatable input and output shaft, is connected to the one shaft, and has a cam housing having a cam surface having two or more peaks on an inner surface thereof; Connected to the other axis,
A rotor rotatably housed in the cam housing and having a plurality of plunger chambers formed in an axial direction; and a plurality of plunger chambers being housed in each of the plurality of plunger chambers so as to be reciprocally movable 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; a suction / discharge hole formed in the rotor and communicating with the plunger chamber; and rotatably slidingly contacting an end face of the rotor; A valve body having a plurality of suction ports and discharge ports formed on a surface thereof which are positioned in a predetermined relationship with the cam housing and act as a suction valve and a discharge valve according to the positional relationship with the suction and discharge holes; A means for generating a flow resistance by the flow of the discharge oil by driving the jar; a hydraulic pressure transmitting a torque corresponding to a rotational speed difference between the two shafts In power transmission coupling, provided on the rear surface does not form a suction port, a discharge port of the valve body,
A communication groove for communicating with each of the discharge ports, a lid member provided in close contact with the back surface, and a flow resistance generating means provided between the communication groove or the discharge port and the low-pressure chamber. is there.

That is, in this conventional hydraulic power transmission joint, the cam and the housing are integrally formed to form a closed container, and the rotary valve rotates by a predetermined angle with respect to the cam housing, thereby providing a relative rotation direction. Enables torque transmission in either forward or reverse rotation.

[0004]

However, in such a conventional hydraulic power transmission coupling, there is provided a mechanism for controlling the transmission torque characteristic of the coupling by an external signal or a signal from a coupling state sensor. However, there is a problem that it is difficult, complicated and expensive. That is, the high-pressure part of the rotary valve to be controlled is structured to rotate by a predetermined angle with respect to the housing, and there is a thrust block behind the thrust block that controls the high-pressure part. Was difficult to set up.

[0005] In addition, there is a problem that the sealing performance on the back surface of the rotary valve is poor, which causes pulsation. The present invention has been made in view of such a conventional problem, and a mechanism for controlling torque characteristics by internal and external signals can be easily provided at low cost, and sealing performance can be improved. An object is to provide a good hydraulic power transmission coupling.

[0006]

In order to achieve the above object, the present invention is provided between input / output shafts which are rotatable relative to each other,
A housing connected to the one shaft and containing components therein; a cam rotatably supported on an inner surface of the housing by a predetermined angle and having two or more peaks toward the inside of the housing; Connected to the other shaft,
A rotor rotatably housed in the housing and having a plurality of plunger chambers formed in the axial direction; and a rotor reciprocally housed in each of the plurality of plunger chambers, while the two shafts rotate relative to each other. A plurality of plungers driven by the cam surface; a suction / discharge hole which opens at one end face of the rotor that does not accommodate the plunger and communicates with the plunger chamber; A valve having a plurality of suction ports and discharge ports formed on a surface thereof, which are positioned in a housing so as to have a predetermined relationship with the cam, and act as a suction valve and a discharge valve according to the positional relationship with the suction and discharge holes. A high-pressure chamber provided with a discharge port communicating with the inside of the valve; a means for generating flow resistance at an outlet from the high-pressure chamber to the low-pressure chamber in the joint; It is intended to transmit a torque corresponding to the rotational speed difference between the axes.

[0007]

In the present invention, the valve body is fixed to the housing, and the cam is positioned so as to be rotatable by a predetermined angle instead. For this purpose, the cam and the housing were separated from each other, and a sealed container was constituted only by the housing, and the cam could be rotated with respect to the housing.

The cam is used to transmit torque between the housing and the cam through the positioning and torque transmitting projection of the cam. Then, the valve element and the thrust block were formed into an integral structure and positioned and fixed to the housing. As a result, it is possible to easily provide a valve mechanism for controlling the pressure oil in the high pressure chamber (communication passage) having a closed structure provided in the valve body and an actuator for controlling the valve mechanism.

As a result, it is possible to obtain an inexpensive joint in which the transmission torque characteristic of the joint can be controlled by an external signal. Thereby, it is possible to select a characteristic that is more suitable for the running conditions of the vehicle than a conventional joint whose characteristic cannot be changed. Also, control by internal signals such as the joint temperature and the transmission torque is facilitated. Further, since the high-pressure chamber of the valve element is sealed by the outer diameter surface of the bearing, the sealing performance can be improved.

[0010]

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 configuration will be described. In FIG. 1, reference numeral 1 denotes a housing, and the housing 1 is connected to an output shaft (one shaft) (not shown) and rotates integrally with the output shaft.

Reference numeral 2 denotes a cam. The cam 2 is supported on the inner surface of the housing 1 so as to be rotatable at a predetermined angle. Cam 2
As shown in FIG. 2, a plurality of projections 2D for positioning and torque transmission are provided at a cam surface 2C including a plurality of cam ridges 2A and cam valleys 2B, and on the outer periphery of the cam surface 2C where the cam ridges 2A are located. Having. As shown in FIG. 3, the cam 2 engages with a notch 1A formed in the housing 1 so that the cam 2 rotates integrally with the housing 1 in the rotation direction of the rotor 3 indicated by an arrow A. When the rotation direction A changes, the cam 2 rotates together with the rotor 3, rotates until the projection 2D of the cam 2 hits the notch 1A of the housing 1, and then rotates integrally with the housing 1. B indicates a discharge stroke, C indicates a suction stroke, and the discharge stroke B starts at the cam valley 2
B, end of cam 2A, start of suction stroke C is cam 2
A, the end is Kam Valley 2B.

The rotor 3 is rotatably housed in the housing 1, is coupled to the input shaft 4, and rotates integrally with the input shaft 4. As shown in FIG. 4, a plurality of plunger chambers 5 are formed in the rotor 3 in the axial direction, and a plurality of plungers 6 are slidably housed in the plunger chamber 5 via a return spring 7. I have. A plurality of suction / discharge holes 8 are formed in the rotor 3 so as to communicate with each plunger chamber 5.

Reference numeral 9 denotes a valve (valve element) in which a suction port 10, a suction path 11, and a discharge port 12 are formed. As shown in FIG.
The positioning is fixed to the housing 1 by engaging the projections 13 with. In FIG. 5, D indicates the seal margin, and E indicates the advance angle. A bearing 14 is mounted between the input shaft 4 and the inner diameter of the valve 9, and a ring-shaped groove formed in the inner diameter of the valve 9 is sealed by an outer diameter surface of the bearing 14 to form a high-pressure chamber 15. . Reference numeral 16 denotes a communication passage formed in the valve 9. The storage passage 18 for storing a torque characteristic control mechanism defined by the nonmagnetic cover 17 communicates with the suction passage 11 via the communication passage 16. I have.

The discharge port 12 communicates with the high-pressure chamber 15 through a passage (not shown), and an orifice 19 as a flow resistance generating means is formed at an outlet from the high-pressure chamber 15 to the suction path 11. When the plunger 6 is in the suction stroke, there is a positional relationship between the suction port 10 of the valve 9 and the suction / discharge hole 8 of the rotor 3, and the orifice 19 and the suction passage 1
1, the oil can be sucked into the plunger chamber 5 through the suction port 10 and the suction / discharge hole 8 of the rotor 3.

When the plunger 6 is in the discharge stroke, the relationship is opposite to that of the suction stroke, and the suction and discharge holes 8 of the rotor 3 communicate with the high-pressure chamber 15 through the discharge port 12 of the valve 9. Reference numeral 20 denotes an accumulator piston that rotates integrally with the housing 1.
Is provided to absorb the thermal expansion of the sealed oil.

Reference numeral 20A denotes a retainer fixed to the housing 1. The retainer 20A and the accumulator piston 2
Between 0, a return spring 21 is interposed.
Reference numeral 22 denotes a magnetic frame fixed to an external member and held in non-contact with the joint.
3 are stored. Reference numeral 24 denotes a movable magnetic body slidably accommodated in a storage chamber 18 defined by a nonmagnetic cover 17 fixed to the housing 1 by excitation of a solenoid coil 23. The movable magnetic body 24 includes a control valve 25. , 26 are fixed.

The control valves 25 and 26 are provided in the insertion holes 2 of the valve 9.
7 and 28 are slidably inserted into the high pressure chamber 15 to control the pressure oil. A stopper 29 is urged by a pair of springs 30 and 31 so that the movable magnetic body 24 contacts the stopper 29. 32 is a stopper ring, 33, 3
4 is a needle bearing, 35 is an oil seal, and 36 is a spline that meshes with the output shaft.

Next, the operation will be described. Cam 2 and rotor 3
When there is no difference in rotation between the two, the plunger 6 does not operate, and no torque is transmitted. At this time, the plunger 6 is pressed against the cam surface 2C by the return spring 7. Next, when a rotation difference occurs between the cam 2 and the rotor 3, the plunger 6 in the discharge stroke is pushed in the axial direction by the cam surface 2C of the cam 2 (FIG. 3, FIG.
(See FIG. 5).

At this time, since the suction / discharge port 8 communicates with the discharge port 12, the plunger 6 pushes oil in the plunger chamber 5 from the suction / discharge port 8 to the discharge port 12 of the valve 9. The oil pushed out to the discharge port 12 is supplied to the suction passage 11 through the high-pressure chamber 15 and the orifice 19. At this time, the resistance of the orifice 19 causes the high pressure chamber 1
5, the hydraulic pressure in the discharge port 12 and the plunger chamber 5 increases, and a reaction force is generated in the plunger 6. By rotating the cam 2 against the plunger reaction force, a torque is generated, and the torque is transmitted between the cam 2 and the rotor 3.

Further, when the cam 2 rotates, a suction stroke occurs and the suction / discharge port 8 communicates with the suction port 10, so that the oil in the suction path 11 flows into the plunger chamber 5 through the suction port 10 and the suction / discharge hole 8. After being sucked, the plunger 6 returns along the cam surface 2C of the cam 2 (see FIGS. 3 and 5). When the rotation direction of the rotor 3 is reversed, the cam 2 rotates together with the rotor 3 and rotates integrally with the housing 1 after rotating until the projection 2D of the cam 2 hits the notch 1A of the housing 1. Accordingly, the differential rotation speed ΔN as shown by F in FIG.
It is possible to obtain a torque characteristic that rises with the power.

In this embodiment, since the valve 9 is fixed to the housing 1 and the cam 2 is positioned so as to be rotatable by a predetermined angle, a valve mechanism for controlling the pressure oil in the high-pressure chamber 15 is easily provided on the valve 9. be able to. Therefore, as shown in FIG. 1, when the solenoid coil 23 is not energized, the movable magnetic body 24 does not move, and the high-pressure chamber 15 is closed by the control valve 25 and opened by the control valve 26. 19 communicates with the high-pressure chamber 15, and the normal torque characteristics as shown in FIG.

When the solenoid 23 is energized and the movable magnetic body 24 moves rightward in FIG. 1 against the spring 30, the high-pressure chamber 15 is opened to the control valve 25, and the pressure oil in the high-pressure chamber 15 is stored in the storage chamber. 18, and enters the suction passage 11 through the communication passage 16. Thus, a free state as shown in FIG. 6G can be obtained. Further, the movable magnetic body 24 is connected to the spring 30,
When further moved to the right in FIG. 1 in opposition to 31, the high-pressure chamber 15 is closed by the control valve 25, and the orifice 1
9 is closed by the control valve 26. Thus, H in FIG.
The lock state shown in FIG.

As described above, the torque characteristics of the joint can be easily and inexpensively controlled by an external signal or an internal signal. Further, since the high-pressure chamber 15 of the valve 9 is sealed by the outer diameter surface of the bearing 14, the sealing performance can be improved and pulsation can be prevented. Next, FIG. 7 is a view showing another embodiment of the present invention.

Also in this embodiment, the valve 41 is fixed to the housing 1, and the cam 2 is positioned so as to be rotatable at a predetermined angle with respect to the housing 1. In FIG. 7, 42
Is an accumulator piston that is fixed to the inner periphery of the housing 1 and absorbs thermal expansion of the sealed oil. The accumulator piston 42 is provided outside the valve 41.

A control valve 45 inserted into the insertion holes 43 and 44 of the valve 41 and a support member 46 are fixed to the accumulator piston 42, respectively. As shown in FIG. 7, when the accumulator piston 42 does not move,
The orifice 49 provided between the high-pressure chamber 47 and the suction passage 48 conducts, and a normal torque characteristic as shown in FIG.

When the accumulator piston 42 moves leftward in FIG. 7 due to the thermal expansion of the sealed oil, the orifice 49 is gradually squeezed by the control valve 45. Further, when the accumulator piston 42 moves leftward, the orifice 49 is moved. It is closed by the control valve 45. The torque characteristic at this time is in the locked state shown in H of FIG. In addition, 5
0 is a suction port and 51 is a discharge port.

In this embodiment, the same effects as in the above embodiment can be obtained.

[0028]

As described above, according to the present invention, since the valve is fixed to the housing and the cam is positioned so as to be rotatable by a predetermined angle on the housing, the valve mechanism for controlling the torque characteristic is provided on the valve. It can be easily provided, and the torque characteristics can be easily and inexpensively controlled by a signal from outside or inside. Further, the sealing performance of the valve can be improved.

[Brief description of the drawings]

FIG. 1 shows an embodiment of the present invention.

FIG. 2 is a perspective view of a cam.

FIG. 3 is a diagram showing a positional relationship between a cam and a housing.

FIG. 4 is a diagram showing a housing and a rotor.

FIG. 5 is a diagram showing a positional relationship between a housing and a valve.

FIG. 6 is a graph showing torque characteristics.

FIG. 7 is a diagram showing another embodiment of the present invention.

[Explanation of symbols]

 1: Housing 1A: Notch 2: Cam 2A: Cam ridge 2B: Cam valley 2C: Cam surface 2D: Projection for positioning and torque transmission 3: Rotor 4: Input shaft 5: Plunger chamber 6: Plunger 7: Return Spring 8: Suction / discharge port 9: Valve (valve element) 10: Suction port 11: Suction path 12: Discharge port 13: Projection 14: Bearing 15: High pressure chamber 16: Communication path 17: Non-magnetic cover 18: Storage chamber 19: Orifice (flow resistance generating means) 20: accumulator piston 20A: retainer 21: return spring 22: magnetic frame 23: solenoid coil 24: movable magnetic body 25, 26: control valve 27, 28: insertion hole 29: stopper 30, 31: Spring 32: Stopper ring 33, 34: Needle bearing 35: Oil seal 36: Spline 1: Valve 42: accumulator piston 43, 44: insertion hole 45: control valve 46: supporting member 47: the high-pressure chamber 48: suction passage 49: Orifice 50: suction port 51: discharge port

Claims (4)

(57) [Claims] 1. A housing provided between input and output shafts rotatable relative to each other, connected to said one shaft and housing components therein, and rotatably supported by an inner surface of said housing so as to be rotatable by a predetermined angle. A cam having two or more peaks toward the inside of the housing; a rotor connected to the other shaft and rotatably housed in the housing, and having a plurality of plunger chambers formed in an axial direction; A plurality of plungers housed in each of the plurality of plunger chambers so as to be reciprocally movable and driven by the cam surface when the two shafts rotate relative to each other; An inlet and outlet opening to the end face and communicating with the plunger chamber; rotatably slidably contacting the end face of the rotor and forming a predetermined relationship between the housing and the cam. A plurality of suction ports, which act as suction and discharge valves depending on the positional relationship with the suction and discharge holes, and a valve body having a discharge port formed on a surface thereof, and a discharge port provided in communication with the inside of the valve body. A high-pressure chamber; means for generating flow resistance at an outlet from the high-pressure chamber to the low-pressure chamber in the joint; and transmitting a torque corresponding to a rotational speed difference between the two shafts. Fittings. 2. The valve according to claim 1, wherein a control valve for controlling pressure oil in the high-pressure chamber is provided on the valve body, and an actuator for operating the control valve is arranged on a side of the valve body that does not slide on the rotor. Item 1. A hydraulic power transmission coupling according to Item 1. 3. A bearing for supporting the other shaft is mounted on an inner diameter portion of the valve body, and a ring-shaped groove provided on an inner diameter surface of the bearing insertion is formed in an outer diameter surface of the bearing. 2. The hydraulic power transmission coupling according to claim 1, wherein the coupling is sealed. 4. The hydraulic power transmission coupling according to claim 1, wherein a projection for positioning and transmitting torque is formed on said cam.