JPH07248032A - Hydraulic power transmission coupling - Google Patents

Abstract

PURPOSE:To reduce cost, make an operation failure less apt to cause, and prevent a reduction in torque by using a closing valve which facilitates the working of a hydraulic power transmission coupling and dispenses with a driving cam. CONSTITUTION:Two orifices 22, 30 are provided as flow resistance generating means on the projections 19A, 19B of a valve element 11, and a closing valve 25 having a spherical or tapered top end for closing the outlet port part of at least one orifice 22 from the outside is also provided. When the relative rotating direction of input and output shafts is positive, the outlet port part of the one orifice 22 is closed by the closing valve 24, and the one orifice 22 is opened by the closing valve 24 at the reverse rotation.

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 application has proposed in Japanese Patent Application No. 3-248595 a hydraulic power transmission joint in which the torque characteristic is changed depending on whether the differential direction of the joint is forward or reverse. There is. That is, the hydraulic power transmission joint is provided between the input / output shafts that can rotate relative to each other, 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 housed in each of the plurality of plunger chambers so as to be capable of reciprocating movement, and when the two shafts rotate relative to each other. A plurality of plungers driven by the cam surface; an intake / discharge hole that opens to one end surface of the rotor that does not house the plunger and communicates with the plunger chamber; and rotatably slidably contacts the end surface of the rotor. A plurality of suction ports that act as suction valves and discharge valves depending on the positional relationship with the suction and discharge holes, and a valve element that has discharge ports formed on its surface. A high pressure chamber communicating with the discharge port and a means for generating flow resistance at the outlet from the high pressure chamber to the low pressure chamber in the joint; In a hydraulic power transmission joint that transmits the same torque, the valve body is provided with two orifices as the flow resistance generating means, and a spool-shaped one for controlling the conduction state between at least one of the orifices and the high pressure chamber. A switching valve is provided, and the cam housing or a member integrally fixed thereto is provided with a cam surface for controlling the operation of the switching valve according to the positional relationship with the valve body.

[0003]

However, such a conventional hydraulic power transmission joint has such problems. (1) Since the spool valve has a severe machining accuracy and requires a certain length for sealing, the coupling becomes large, which causes a cost increase. (2) In order to open and close the spool valve, a cam for opening and closing is required, which causes a cost increase. (3) Since the clearance between the spool valve and the hole is small, foreign matter or dust is likely to enter the clearance between the valve and the hole, which causes malfunction. (4) Since there is a gap between the spool valve and the hole, the seal cannot be completely sealed, and the torque is reduced due to leakage from the high pressure chamber.

The present invention has been made in view of the above-mentioned conventional problems. By using a stop valve which is easy to process and does not require a driving cam, cost reduction and malfunction occur. An object of the present invention is to provide a hydraulic power transmission joint that is difficult to prevent a decrease in 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 reciprocally movable, and driven by the cam surface when the two shafts relatively rotate; A suction / discharge hole that opens to one end surface of the rotor that does not accommodate the plunger and communicates with the plunger chamber; rotatably slidably contacts the end surface of the rotor and rotatable by a predetermined angle with the cam housing. Positioned in
A plurality of suction ports that act as a suction valve and a discharge valve according to a positional relationship with the suction and discharge holes, a valve body having a discharge port formed on the surface, and a high-pressure chamber that connects the discharge ports.
A means for generating flow resistance at an outlet portion from the high pressure chamber to the low pressure chamber in the joint is provided; in a hydraulic power transmission joint for transmitting torque according to a rotational speed difference between the two shafts, the protrusion of the valve body is provided with Two orifices as flow resistance generating means are provided, and at least one of the orifices is provided with a stop valve having a spherical surface or a tapered surface for closing the outlet of the orifice from the outside. The closing valve closes the outlet of the one orifice, and the reverse valve opens the outlet of the one orifice at the time of reverse rotation.

According to the present invention, the shut-off valve is provided between a projection for positioning the valve body provided on the cam housing and an outlet portion of the one orifice of the valve body, and It is characterized in that the outlet of the one orifice is closed by the closing valve which operates by receiving a frictional rotational force acting between the valve body and the protrusion. Further, the invention is characterized in that a stopper member is provided around the projection to prevent the stop valve from coming off.

Further, the present invention is characterized in that the other of the two orifices is always opened. Further, the present invention is characterized in that the outlet portion of the other of the two orifices is opened by another closing valve at the time of forward rotation and closed by another closing valve at the time of reverse rotation.

Further, the present invention is characterized in that one of the two orifices has a diameter larger than that of the other orifice. The present invention also provides a cam housing which is provided between relatively rotatable input / output shafts, is connected to the one shaft, and has a cam surface having two or more ridges on its inner side surface; and the other shaft. With being connected,
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 housed in each of the plurality of plunger chambers so as to be capable of reciprocating movement, and when the two shafts rotate relative to each other. A plurality of plungers driven by the cam surface; an intake / discharge hole that opens to one end surface of the rotor that does not house the plunger and communicates with the plunger chamber; and rotatably slidably contacts the end surface of the rotor. A plurality of suction ports that act as suction valves and discharge valves depending on the positional relationship with the suction and discharge holes, and a valve element that has discharge ports formed on its surface. , A means for generating flow resistance at the outlet part from the high pressure chamber to the low pressure chamber in the joint, the high pressure chamber communicating with the discharge port; In the hydraulic power transmission joint that transmits the generated torque, one protrusion of the valve element is formed with one orifice that is always opened, and the other protrusion is formed with the orifice formed in the cam housing during forward rotation. It is characterized in that the other orifice is formed which is closed by the projection and is opened at the time of reverse rotation.

Further, the present invention is characterized in that the diameter of the other orifice is larger than the diameter of the one orifice.

[0010]

According to the hydraulic power transmission joint of the present invention having such a structure, the valve body is provided with two orifices as flow resistance generating means, and at least one of the orifices is opened / closed in accordance with forward / reverse rotation. Since a stop valve for controlling the above is provided and the cross-sectional area of the orifice is changed between forward rotation and reverse rotation, the torque characteristics can be changed by forward and reverse rotation.

This makes it possible to prevent the malfunction of the ABS during braking. In the present invention, the spool valve that controls the conduction state between the orifice and the high-pressure chamber is replaced with a valve structure that directly closes the outlet of the orifice from the outside by the frictional rotational force that acts on the valve body. In addition to the need for high-precision machining required by, the need for a cam for opening and closing the spool is eliminated, and costs can be reduced.

Further, in principle, the problem that the spool does not move due to the foreign matter being caught in the gap between the spool and the spool hole does not occur. Furthermore, since there is no gap like the spool valve, it is possible to prevent leakage from the high pressure chamber, and the torque does not decrease.

[0013]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 8 are views showing a first embodiment of the present invention. FIG. 3 is a sectional view of a joint according to the first embodiment of the present invention. First, the configuration will be described. In FIG. 3, reference numeral 1 is a cam having a cam surface 2 having two or more ridges on its inner surface. The cam 1 is connected to an output shaft (not shown) and rotates integrally with the output shaft. To do. The cam 1 is fixed to the cam housing 4 by the welded portion 3, and the cam housing 4 rotates integrally with the cam 1.

Reference numeral 5 denotes a rotor 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 / 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. Here, the positional relationship between the cam housing 4 and the rotary valve 11 is shown in FIGS.

1 and 2, a plurality of protrusions 17A, 17B are formed in the circumferential direction on the inner circumference of the cam housing 4, and notches 18A, 1 are provided between the protrusions 17A, 17B.
8B is formed. The rotary valve 11 has positioning projections 19A and 19B that engage with the notches 18A and 18B of the cam housing 4.

On the protrusion 19A of the rotary valve 11,
A collecting chamber 20 as a high-pressure chamber is formed, and the collecting chamber 20 communicates with each discharge port 14. At the outlet of the collecting chamber 20, a first orifice 22 is formed laterally as a flow resistance generating means. The projection 19A on the outlet side of the first orifice 22 is formed with a discharge oil passage 23 through which the oil that has passed through the first orifice 22 is discharged to the in-joint low pressure chamber.

Further, a closing valve 24 is provided on the projection 19A concentrically with the first orifice 22 so as to be movable in the axial direction, and the closing valve 24 is made of a rod-shaped member having a spherical surface or a tapered surface. When the shut-off valve 24 is pushed from the outside, its tip closes the first orifice 22. That is, the shutoff valve 24 includes the rotary valve 11 and the cam housing 4.
The first orifice 22 is closed by receiving the frictional rotational force (friction torque) acting between the first orifice 22 and the protrusion 17A.

When the friction torque does not act between the rotary valve 11 and the protrusion 17A, the shutoff valve 24 opens the first orifice 22 by the hydraulic pressure from the collecting chamber 20. The friction torque acting between the rotary valve 11 and the protrusion 17A is basically proportional to the transmission torque of the joint. A stopper member 25 for preventing the stop valve 24 from coming off from the outside is shown in FIG.

In FIG. 4, reference numeral 26 is a plate portion for preventing the stop valve 24 from coming off and pressing the stop valve 24 by the action of friction torque, and 27 is a stopper portion for positioning the plate portion 26 in the returning direction. . The plate portion 26 and the stopper portion 27 are connected by a connecting portion 28. The projection 19A is housed with a predetermined gap between the plate portion 26 and the stopper portion 27.

In FIGS. 1 and 2, a collecting chamber 20 as a high pressure chamber is formed on the protrusion 19B of the rotary valve 11 on the side opposite to the protrusion 19A provided with the shutoff valve 24.
A second orifice 30 is formed at the outlet of the collecting chamber 20. When the rotary valve 11 rotates in the direction shown by the arrow A in FIG. 1 and the plate portion 26 contacts the protrusion 17A of the cam housing 4, the stop valve 24 is pressed by the friction torque, and the stop valve 24 is rotated. Causes the first orifice 22 to be closed, while the second orifice 30 is always open, which results in normal torque characteristics.

On the other hand, when the rotary valve 11 rotates in the direction shown by the arrow B in FIG. 2, it does not act on the friction torque during reverse rotation, the plate portion 26 does not push the closing valve 24, and the second orifice 30 is always provided. Since it is open, the torque characteristic is lower than that during normal rotation. Referring again to FIG. 3, the rotary valve 11 constitutes a timing member that determines the opening / closing timing of the intake / discharge hole 10, and the notch 1
8A, 18B and the protrusions 19A, 19B 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 second orifice 30, the discharge oil passage 23, the intake passage 13, the intake port 12,
Through the suction / discharge hole 10 of the rotor 5, the plunger chamber 7
Can inhale oil. Further, 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 collecting chamber 20 via the discharge port 14 of the rotary valve 11.

Reference numeral 32 denotes a retainer that rotates integrally with the cam housing 4, and the retainer 32 supports the input shaft 6 via a bearing 33. A thrust needle bearing 35 is interposed between the retainer 32 and the rotary valve 11 via the lid member 16 and the quenching plate 34, and the friction torque on the thrust needle bearing 35 side is the friction between the rotor 5 and the rotary valve 11. It is set to be smaller than the torque. Therefore, when the direction of the differential rotation is changed, the rotary valve 11 turns around together with the rotor 5, rotates until the positioning projection 19B of the rotary valve 11 hits the projection 17B of the cam housing 4, and then becomes integral with the cam housing 4. Rotate. As a result, the intake / discharge hole 10 is forcibly opened / closed at a predetermined timing even during normal rotation or reverse rotation.

A cover 3 is provided between the retainer 32 and the input shaft 6.
6 is provided inside the cover 36, and the retainer 3
An oil seal 37 is interposed between 2 and the input shaft 6. The oil seal 37 prevents oil from leaking outside the joint. Reference numerals 38 and 39 denote communication passages formed in the input shaft 6, and the inside of the joint and the accumulator chamber 40 communicate with each other through the communication passages 38 and 39. Accumulator room 4
In 0, the accumulator piston 41 is movably accommodated, and the accumulator piston 41 moves according to the internal pressure of the joint. That is, the accumulator piston 41 absorbs the thermal expansion of the oil filled in the joint.

Reference numeral 42 denotes a lid provided on the input shaft 6, and the lid 42 also has a function as a stopper for the accumulator piston 41. Air 43 is enclosed in the accumulator piston 41. In addition, 44 is an oiling hole, 45 is a screw hole, 46 is a needle bearing, 47 and 48 are stopper rings, and 49 and 50 are O-rings.

Next, the operation will be described. Cam 1 and rotor 5
When there is no difference in rotation between and, 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, the suction / discharge hole 10 is the discharge port 1
4, 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 connected to the communication groove 15, the collecting chamber 20, and the second orifice 3.
It is supplied from the discharge oil passage 23 to the suction passage 13 through 0.
At this time, due to the resistance of the second orifice 30, the communication groove 1
5, the hydraulic pressure in the collecting chamber 20, the discharge port 14 and the plunger chamber 7 rises, 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. In addition, each discharge port 14 has a
The hydraulic pressures of all the plunger chambers 7 in the discharge stroke are equal because they are communicated with each other.

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 sucked into the plunger chamber 7 through the suction port 12 and the suction / discharge hole 10, and the plunger 8 returns along the cam surface 2 of the cam 1. The flow of oil during forward rotation of such a joint is shown in FIG.

In FIG. 5, an arrow C indicates the rotation direction (normal rotation) of the rotor 5. The oil in the plunger chamber 7 of the plunger 8 due to the discharge stroke is sucked and discharged through the suction hole 10 and the discharge port 1.
4. Pass through the collecting chamber 20 and the second orifice 30. The first orifice 22 is closed by a stop valve 24. As shown in FIG. 1, during normal rotation, the rotary valve 11 rotates in the direction indicated by arrow A, and the protrusion 19A of the rotary valve 11 becomes the protrusion 17A of the cam housing 4.
Hit

Therefore, the stop valve 24 is pressed by the plate portion 26 by the friction torque acting between the protrusion 17A and the protrusion 19A to close the first orifice 22,
The second orifice 30 is always open. Therefore,
A normal torque characteristic as shown in D of FIG. 7 is shown. That is, during normal rotation, the torque characteristic is proportional to the square of the rotation speed difference ΔN.

Next, FIG. 6 shows the flow of oil when the joint is rotated in the reverse direction. In FIG. 6, the arrow C indicates that the rotation direction of the rotor 5 has been reversed. At the time of this reverse rotation, the shutoff valve 24 opens the first orifice 22, and the oil in the plunger chamber 7 of the plunger 8 due to the discharge stroke passes through the suction / discharge hole 10, the discharge port 14, and the collecting chamber 20. Orifice 2 of 1
Pass 2. On the other hand, the second orifice 30 remains open.

That is, as shown in FIG. 2, during reverse rotation, the rotary valve 11 rotates in the direction indicated by the arrow B, and the projection 19A is provided with the notch 18A of the cam housing 4.
Along the direction of arrow B, but separates from the protrusion 17A of the cam housing 4. Therefore, since the friction torque does not act, the stop valve 24 does not operate and the first valve
Open the orifice 22 of. The second orifice 30 remains open. Therefore, it exhibits a low torque characteristic as shown by E in FIG.

As shown in FIG. 8, on the front wheel 51 side,
In a vehicle in which the main joint 53 is mounted in the vicinity of the front wheel side differential device 52, the joint transmission torque during braking has a low characteristic indicated by E, so that malfunction of the ABS can be prevented. In FIG. 8, 54 is an engine, 55 is a transmission, 56 is a transfer, 57 is a rear wheel, 5
8 is a rear wheel side differential device, 59 is a rear wheel side propeller shaft, and 60 is a front wheel side propeller shaft.

As described above, in this embodiment, since the first valve 22 is closed by the shutoff valve 24, the machining is easier and the cost can be reduced as compared with the spool valve. Further, since the friction torque of the rotary valve 11 is used to close the first orifice 22, the opening / closing cam is unnecessary, which leads to cost reduction. Further, by removing the spool valve and replacing it with the shutoff valve 24, it is possible to roughen the processing accuracy, and it becomes difficult for foreign matter and dust to enter, and malfunctions are less likely to occur.

Further, since the shutoff valve 24 can sufficiently perform the sealing, there is no leak from the collecting chamber 20 and it is possible to prevent the torque from decreasing. Next, FIG.
FIG. 10 is a diagram showing a second embodiment of the present invention. 9 and 10, a collecting chamber 20 as a high-pressure chamber is formed on the protrusion 19B of the rotary valve 11 opposite to the protrusion 19A, and the collecting chamber 20 communicates with each discharge port 14. A second orifice 61 as a flow resistance generating means is formed laterally at the outlet of the collecting chamber 20.
A discharge oil passage 62 is formed on the outlet side of the orifice 61 for discharging the oil that has passed through the second orifice 61.

A constriction valve 63 is provided on the projection 19B concentrically with the second orifice 61 so as to be movable in the axial direction, and the closure valve 63 is made of a rod-shaped member having a spherical surface or a tapered surface. The stop valve 63 is prevented from coming off by the stopper member 25 as shown in FIG. 64 is a plate part and 65 is a stopper part. When the rotary valve 11 rotates in the direction shown by the arrow A in FIG.
Since the plate portion 26 hits the protrusion 17A of the cam housing 4, the plate portion 26 is pressed by the friction torque acting between the protrusion 17A and the protrusion 19A,
The stop valve 24 closes the first orifice 22.

On the other hand, since the protrusion 19B on the side opposite to the protrusion 19A does not hit the protrusion 17B of the cam housing 4, the friction torque does not act on the closing valve 63, and the closing valve 63 opens the second orifice 61. Therefore, the normal torque characteristic as shown by D in FIG. 7 is exhibited. Next, as shown in FIG. 10, at the time of reverse rotation, the rotary valve 11 rotates in the direction indicated by the arrow B, and the projection 19B is attached to the cam housing 4
It moves along the notch 18A and hits the projection 17B of the cam housing 4. The stop valve 63 closes the second orifice 61 by the friction torque acting between the protrusion 17B and the protrusion 19B.

On the other hand, since the projection 19A moves in the direction shown by the arrow B and separates from the projection 17A of the cam housing 4, the friction torque does not act on the closing valve 24 and the closing valve 24 does not act.
Opens the first orifice 22. The torque characteristic during reverse rotation depends on the diameter of the first orifice 22. First
When the diameter of the orifice 22 is larger than the diameter of the second orifice 61, the torque during reverse rotation is lower than the torque during normal rotation.

Also in this embodiment, since the shutoff valves 24 and 63 are used, the same effect as that of the above embodiment can be obtained. Next, FIGS. 11 and 12 are views showing a third embodiment of the present invention. 11 and 12, a collecting chamber 66 as a high-pressure chamber is formed on the protrusion 19A of the rotary valve 11, and the collecting chamber 66 communicates with each discharge port 14. A first orifice 67 as a flow resistance generating means is formed laterally at the outlet of the collecting chamber 66.

The outlet portion of the first orifice 67 is formed on the side of the projection 17A of the cam housing 4, and when the projection 19A and the projection 17A come into contact with each other, the first orifice 67 becomes the projection 1
It is designed to be closed by 7A. A collecting chamber 66 as a high-pressure chamber is formed on the protrusion 19B of the rotary valve 11 on the opposite side of the protrusion 19A, and the collecting chamber 66 communicates with each discharge port 14. A second orifice 68 as a flow resistance generating means is formed laterally at the outlet of the collecting chamber 66.

The outlet of the second orifice 68 is formed on the protrusion 19B of the cam housing 4 which is not in contact with the protrusion 17B. Therefore, the second orifice 68 is always open. At the time of normal rotation in which the rotary valve 11 rotates in the direction indicated by the arrow A in FIG. 11, the protrusion 1A of the rotary valve 11 is attached to the protrusion 17A of the cam housing 4.
9A comes into contact, and the orifice 67 is closed by the protrusion 17A. On the other hand, the second orifice 68 is always open.

Therefore, the normal torque characteristic as shown by D in FIG. 7 is exhibited. Next, as shown in FIG. 12, at the time of reverse rotation, the rotary valve 11 rotates in the direction indicated by the arrow B, and the protrusion 19B moves along the notch 18A of the cam housing 4 to reach the protrusion 17B of the cam housing 4. Again, the second orifice 68 is open.

On the other hand, since the protrusion 19A moves in the direction shown by the arrow B and separates from the protrusion 17A of the cam housing 4,
The first orifice 67 opens. During this reverse rotation, both the first orifice 67 and the second orifice 68 open, so the torque during reverse rotation becomes lower than the torque during normal rotation.
In this embodiment, since it is not necessary to use the shutoff valves 24 and 63, the cost can be further reduced. In this embodiment, the same effect as that of the above embodiment can be obtained.

[0045]

As described above, according to the present invention, since the closing valve closes the orifice, it is easier to process than the spool valve, and the cost can be reduced. Further, since the friction torque of the rotary valve is used to close the orifice, a cam for opening and closing is unnecessary, which leads to cost reduction. Further, since the spool valve is abolished and replaced with a closing valve, the processing accuracy can be made rough, and foreign matter and dust are less likely to enter and malfunctions are less likely to occur.

Furthermore, since sufficient sealing can be achieved, it is possible to prevent leakage from the collecting chamber and prevent a decrease in torque.

[Brief description of drawings]

FIG. 1 is a view showing a state at the time of forward rotation showing a first embodiment of the present invention.

FIG. 2 is a diagram showing a state at the time of reverse rotation.

FIG. 3 is a sectional view of the joint.

FIG. 4 is a perspective view of a stopper member.

FIG. 5 is a diagram showing an oil flow during normal rotation.

FIG. 6 is a diagram showing the flow of oil during reverse rotation.

FIG. 7 is a graph showing torque characteristics.

FIG. 8 is a diagram showing positions of joints.

FIG. 9 is a view showing a state at the time of forward rotation showing the second embodiment of the present invention.

FIG. 10 is a diagram showing a state at the time of reverse rotation.

FIG. 11 is a view showing a state at the time of forward rotation showing the third embodiment of the present invention.

FIG. 12 is a diagram showing a state at the time of reverse rotation.

[Explanation of symbols]

 1: Cam 2: Cam surface 3: Welded part 4: Cam housing 5: Rotor 6: Input shaft 7: Plunger chamber 8: Plunger 9: Return spring 10: Suction / discharge hole 11: Rotary valve (valve body) 12: Suction port 13: Suction path 14: Discharge port 15: Communication groove 16: Lid member 17A, 17B, 19A, 19B: Protrusion 18A, 18B: Notch 20: Collecting chamber 22: First orifice (flow resistance generating means) 23 : Discharge oil passage 24: Stop valve 25: Stopper member 26: Plate part 27: Stopper part 28: Connection part 30: Second orifice 32: Retainer 33: Bearing 34: Quenching plate 35: Thrust needle bearing 36: Cover 37: Oil seal 38, 39: communication passage 40: accumulator chamber 41: accumulator piston 42 Lid 43: Air 44: Oiling hole 45: Screw hole 46: Needle bearing 47, 48: Stopper ring 49, 50: O-ring 51: Front wheel 52: Front wheel side differential device 53: Joint 54: Engine 55: Transmission 56: Transfer 57 : Rear wheel 58: Rear wheel side differential device 59: Rear wheel side propeller shaft 60: Front wheel side propeller shaft 61: Second orifice 62: Discharge oil passage 63: Stop valve 64: Plate portion 65: Stopper portion 66: Collecting chamber 67: First Orifice 68: Second Orifice

Claims (8)

[Claims] 1. A cam housing provided between relatively rotatable input / output shafts, which is connected to said one shaft and which has a cam surface having two or more ridges on its inner side surface; and is 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 that are driven by the cam surface during relative rotation of the rotor; suction and discharge holes that open to one end surface of the rotor that does not house the plunger and communicate with the plunger chamber; rotatable to the end surface of the rotor Is slidably contacted with and is positioned so as to be rotatable by a predetermined angle with the cam housing,
A plurality of suction ports that act as suction valves and discharge valves depending on the positional relationship with the suction and discharge holes, a valve body having discharge ports formed on the surface, a high-pressure chamber that connects the discharge ports, and a high-pressure chamber A means for generating flow resistance at the outlet to the low-pressure chamber is provided; in a hydraulic power transmission joint for transmitting torque according to a rotational speed difference between the both shafts, the flow resistance generating means is provided on the protrusion of the valve body. In addition to providing two orifices of the above, at least one of the orifices is provided with a stop valve that has a spherical surface or a tapered surface for closing the outlet from the outside, and when the relative rotation direction of the input / output shaft is forward rotation,
A hydraulic power transmission joint, characterized in that the outlet of one of the orifices is closed, and the outlet of the one of the orifices is opened by the closing valve when rotating in the reverse direction. 2. The shutoff valve is provided between a projection provided on the cam housing for positioning the valve body and an outlet portion of the one orifice of the valve body,
2. The hydraulic power transmission coupling according to claim 1, wherein the outlet of the one of the orifices is closed by the closing valve that operates by receiving a frictional rotational force acting between the valve body and the protrusion. 3. The hydraulic power transmission joint according to claim 1, further comprising a stopper member provided around the protrusion to prevent the stop valve from coming off. 4. The hydraulic power transmission joint according to claim 1, wherein the other of the two orifices is always open. 5. The outlet of the other of the two orifices is opened by another stop valve during normal rotation,
2. The hydraulic power transmission joint according to claim 1, wherein the hydraulic power transmission joint is closed by another closing valve when rotating in the reverse direction. 6. The hydraulic power transmission joint according to claim 5, wherein the diameter of one of said two orifices is larger than the diameter of the other orifice. 7. 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 during relative rotation of the rotor; Suction and discharge holes that open to one end surface of the rotor that does not house the plunger and communicate with the plunger chamber; Rotatable to the end surface of the rotor Is slidably contacted with and is positioned so as to be rotatable by a predetermined angle with the cam housing,
A plurality of suction ports that act as suction valves and discharge valves depending on the positional relationship with the suction and discharge holes, a valve body having discharge ports formed on the surface, a high-pressure chamber that connects the discharge ports, and a high-pressure chamber A means for generating flow resistance is provided at an outlet portion to the low pressure chamber; in a hydraulic power transmission joint that transmits torque according to a rotational speed difference between the two shafts, one of which is always open to one protrusion of the valve body. And the other orifice formed on the other protrusion, which is closed by the protrusion formed on the cam housing at the time of forward rotation and is opened at the time of reverse rotation. . 8. The hydraulic power transmission joint according to claim 7, wherein the diameter of the other orifice is larger than the diameter of the one orifice.