JP2989468B2 - 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, in Japanese Patent Application No. 3-248595, a hydraulic power transmission coupling in which the torque characteristics are changed when the differential direction of the coupling is forward rotation and reverse rotation. I have. 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 the axial direction; and a rotor housed in each of the plurality of plunger chambers so as to be reciprocally movable, and when the two shafts rotate relative to each other. A plurality of plungers driven by the cam surface; a suction / discharge hole opened at one end face of the rotor not containing the plunger and communicating with the plunger chamber; and a rotatable sliding contact with the end face of the rotor. A plurality of suction ports, which are positioned so as to be rotatable at a predetermined angle between the cam housing and a suction port and a discharge valve depending on a positional relationship with the suction and discharge holes, and a valve body having discharge ports formed on a surface thereof; A high-pressure chamber communicating with the discharge port, and means for generating flow resistance at an outlet from the high-pressure chamber to the low-pressure chamber in the joint; In the hydraulic power transmission coupling for transmitting the same torque, two orifices as the flow resistance generating means are provided on the valve body, and a spool-shaped orifice for controlling a conduction state between at least one orifice and the high-pressure chamber. A switching valve is provided, and the cam housing or a member fixed integrally with the cam housing is provided with a cam surface for controlling the operation of the switching valve according to a positional relationship with the valve body.

[0003]

However, such a conventional hydraulic power transmission coupling has such a problem. (1) The spool valve has a strict machining accuracy and requires a certain length for sealing, so that the coupling becomes large and causes an increase in cost. (2) Opening and closing the spool valve requires an opening / closing cam, which causes an increase in cost. (3) Since the clearance between the spool valve and the hole is small, foreign matter and dust easily enter the clearance between the valve and the hole, and an operation failure is likely to occur. (4) Since there is a gap between the spool valve and the hole, the seal cannot be completely sealed, and the torque decreases due to leakage from the high-pressure chamber.

SUMMARY OF THE INVENTION 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, the cost can be reduced and an operation failure occurs. It is an object of the present invention to provide a hydraulic power transmission coupling that is difficult to reduce a torque.

[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 forming a cam surface having two or more peaks on an inner surface and having a plurality of notches ; and a cam housing connected to the other shaft; A rotor rotatably housed in the cam housing and having a plurality of plunger chambers formed in an axial direction; and a rotor housed in each of the plurality of plunger chambers so as to be reciprocally movable, and when the two shafts rotate relative to each other. A plurality of plungers driven by the cam surface; an inlet / outlet port which is open at one end face of the rotor that does not accommodate the plunger and communicates with the plunger chamber; And said
A pair of positioning engaging the notch of the cam housing
The has a projection of use are given pivotably positioned between the cam housing, a plurality of suction ports to the action of the suction valve and the discharge valve by the positional relationship between the suction and discharge hole, the discharge port surface A high pressure chamber communicating with the formed valve element and the discharge port; and a means for generating a flow resistance at an outlet from the high pressure chamber to the low pressure chamber in the joint; a torque corresponding to a rotational speed difference between the two shafts is provided. in the hydraulic power transmission joint for transmitting, to one of the projections of the valve body, provided with a first orifice as the flow resistance generating means, set the second orifice on the opposite side of the other projection
Only, the outlet of the first orifice, the provided closing valve of a spherical end surface or tapered surface which closes from the outside, the relative rotation direction of the input and output shaft by said closure valve during normal rotation of the first orifice outlet And shutting off the outlet of the first orifice by the shut-off valve at the time of reverse rotation.

Further, the present invention, the of the shutoff valve, for the positioning of the valve body provided in said cam housing
The closing valve, which is provided between the one projection and the outlet of the first orifice of the valve body and is operated by receiving a frictional rotating force acting between the valve body and the one projection. The outlet of the first orifice is closed. Further, the present invention is characterized in that a stopper member is provided around the one protrusion to prevent the closing valve from coming off.

Further, the present invention is characterized in that a second orifice of the two orifices is always opened. Further, the present invention is first of said two orifices
The outlet of the second orifice is opened by another stop valve during normal rotation and closed by another stop valve during reverse rotation.

Further, the present invention is characterized in that the diameter of the first orifice of the two orifices is larger than the diameter of the second orifice. Further, the present invention is provided between relatively rotatable input and output shafts, coupled to said one axis, forming Then a cam surface having two or more peaks on the inside surface
A cam housing formed with a plurality of notches ; a rotor connected to the other shaft and rotatably housed in the cam housing, and having a plurality of plunger chambers formed in an axial direction; A plurality of plungers housed in each of the plunger chambers so as to be reciprocally movable, and driven by the cam surface when the two shafts rotate relative to each other; a suction and discharge hole communicating with said plunger chamber; together rotatably sliding contact with an end surface of said rotor, said
A pair of positioning engaging the notch of the cam housing
The has a projection of use are given pivotably positioned between the cam housing, a plurality of suction ports to the action of the suction valve and the discharge valve by the positional relationship between the suction and discharge hole, the discharge port surface A high pressure chamber communicating with the formed valve element and the discharge port; and a means for generating a flow resistance at an outlet from the high pressure chamber to the low pressure chamber in the joint; a torque corresponding to a rotational speed difference between the two shafts is provided. In the hydraulic power transmission joint that transmits power, it is formed on one protrusion and
Closed by a projection formed on the cam housing.
To form a first orifice that is opened at the time of reverse rotation,
A second orifice always open to the other projection of the valve body
Is formed .

Further, the present invention is characterized in that the diameter of the first orifice is larger than the diameter of the second orifice.

[0010]

According to the hydraulic power transmission joint of the present invention having such a configuration, 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. Is provided, and the cross-sectional area of the orifice is changed between forward rotation and reverse rotation, so that the torque characteristics can be changed by forward / reverse rotation.

As a result, malfunction of the ABS during braking can be prevented. In the present invention, instead of the spool valve for controlling the state of conduction between the orifice and the high-pressure chamber, a valve structure for directly closing the outlet of the orifice from the outside by a frictional rotating force acting on the valve body is used. This eliminates the need for high-precision machining required in the above, and eliminates the need for a cam for opening and closing the spool, thereby reducing costs.

Further, in principle, a problem that the spool does not move due to the foreign matter getting into the gap between the spool and the spool hole does not occur. Furthermore, since there is no gap like a spool valve, leakage from the high-pressure chamber can be prevented, and torque does not decrease.

[0013]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 8 show a first embodiment of the present invention. FIG. 3 is a sectional view of the joint according to the first embodiment of the present invention. First, the configuration will be described. In FIG. 3, reference numeral 1 denotes a cam having a cam surface 2 having two or more peaks on an inner surface thereof. The cam 1 is connected to an output shaft (not shown) and rotates integrally with the output shaft. I do. Further, the cam 1 is fixed to the cam housing 4 by the welding 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. The rotor 5 is connected to an input shaft 6,
It rotates integrally with the input shaft 6. A plurality of plunger chambers 7 are formed in the rotor 5 in the axial direction.
Inside, a plurality of plungers 8 are slidably accommodated via return springs 9. Further, a plurality of suction / discharge holes 10 are formed in the rotor 5 so as to communicate with each plunger chamber 7.

Reference numeral 11 denotes a suction port 12 and a suction passage 13 on the surface.
And a rotary valve (valve element) formed with a discharge port 14, 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 on the back surface so as to be in close contact therewith. Here, FIGS. 1 and 2 show the positional relationship between the cam housing 4 and the rotary valve 11.

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

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

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

When no friction torque acts between the rotary valve 11 and the projection 17A, the closing 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 projection 17A is basically proportional to the transmission torque of the joint. FIG. 4 shows a stopper member 25 for preventing the closing valve 24 from coming off from the outside.

In FIG. 4, reference numeral 26 denotes a plate portion for preventing the closing valve 24 from coming off and pressing the closing valve 24 by the action of friction torque, and 27 a stopper portion for positioning the plate portion 26 in the return direction. . The plate part 26 and the stopper part 27 are connected by a connecting part 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, an assembly chamber 20 as a high-pressure chamber is formed on the projection 19B of the rotary valve 11 opposite to the projection 19A provided with the closing valve 24.
A second orifice 30 is formed at an outlet of the collecting chamber 20. When the rotary valve 11 rotates in the direction indicated by the arrow A in FIG. 1 and the plate portion 26 hits the projection 17A of the cam housing 4, the closing valve 24 is pressed by friction torque. Closes the first orifice 22, while the second orifice 30 is always open, so that normal torque characteristics are obtained.

On the other hand, when the rotary valve 11 rotates in the reverse direction in the direction indicated by the arrow B in FIG. 2, no friction torque is applied, the plate portion 26 does not press the closing valve 24, and the second orifice 30 is always Since it is open, the torque characteristics are lower than those at the time of normal rotation. Referring again to FIG. 3, the rotary valve 11 constitutes a timing member for determining the opening / closing timing of the suction / discharge port 10,
8A, 18B and the projections 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,
There is a positional relationship between the suction port 12 of the rotary valve 11 and the suction / discharge hole 10 of the rotor 5, and the second orifice 30, the discharge oil passage 23, the suction passage 13, the suction port 12,
Through the suction and discharge holes 10 of the rotor 5, the plunger chamber 7
Oil can be inhaled. When the plunger 8 is in the discharge stroke, the relationship is opposite to that of the suction stroke, and the suction and discharge holes 10 of the rotor 5 communicate with the collecting chamber 20 through the discharge port 14 of the rotary valve 11.

A retainer 32 rotates integrally with the cam housing 4. 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 through 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 changes, the rotary valve 11 rotates together with the rotor 5, rotates until the positioning projection 19 </ b> B of the rotary valve 11 hits the projection 17 </ b> B of the cam housing 4, and then rotates integrally with the cam housing 4. Rotate. Thus, the suction / discharge port 10 is forcibly opened / closed at a predetermined timing even in the normal rotation or the reverse rotation.

A cover 3 is provided between the retainer 32 and the input shaft 6.
6 provided inside the cover 36 and the retainer 3
An oil seal 37 is interposed between the input shaft 6 and the input shaft 6. Oil seal 37 prevents oil from leaking out of the joint. Numerals 38 and 39 are communication paths formed in the input shaft 6, and the inside of the joint and the accumulator chamber 40 communicate with each other through the communication paths 38 and 39. Accumulator room 4
Inside 0, the accumulator piston 41 is movably housed, 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 sealed in the joint.

Reference numeral 42 denotes a lid provided on the input shaft 6. The lid 42 also has a function as a stopper for the accumulator piston 41. Air 43 is sealed 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 rotation difference between the plunger 8 and the plunger 8, the plunger 8 does not operate and no torque is 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 in the axial direction by the cam surface 2 of the cam 1.

At this time, the suction / discharge port 10 is connected to the discharge port 1
Because of the communication with the plunger 4, the plunger 8 pushes the oil in the plunger chamber 7 from the suction / discharge port 10 to the discharge port 14 of the rotary valve 11. The oil pushed out to the discharge port 14 is supplied to the communication groove 15, the collecting chamber 20, the second orifice 3.
0, the oil is supplied from the discharge oil passage 23 to the suction passage 13.
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 increases, and a reaction force is generated in the plunger 8.
By rotating the cam 1 against this plunger reaction force, a torque is generated, and the torque is transmitted between the cam 1 and the rotor 5. Note that each discharge port 14 is
, The hydraulic pressures of all the plunger chambers 7 in the discharge stroke become equal.

Further, when the cam 1 rotates, a suction stroke occurs, and the suction / discharge port 10 communicates with the suction port 12.
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. FIG. 5 shows the flow of oil when the joint rotates forward.

In FIG. 5, an arrow C indicates the rotation direction (forward rotation) of the rotor 5. The oil in the plunger chamber 7 of the plunger 8 during the discharge stroke is supplied to the suction / discharge port 10 and the discharge port 1.
4. Pass the second orifice 30 through the collecting chamber 20. 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 the arrow A, and the projection 19A of the rotary valve 11 becomes the projection 17A of the cam housing 4.
Hit.

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

FIG. 6 shows the flow of oil when the joint is reversed. In FIG. 6, an arrow C indicates that the rotation direction of the rotor 5 has been reversed. At the time of this reverse rotation, the closing 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 port 10, the discharge port 14, and the collecting chamber 20. 1 orifice 2
Pass 2 Also, on the other hand, the second orifice 30 remains open.

That is, as shown in FIG. 2, at the time of reverse rotation, the rotary valve 11 rotates in the direction shown by the arrow B, and the projection 19A becomes the notch 18A of the cam housing 4.
Move in the direction indicated by the arrow B, but separate from the projection 17A of the cam housing 4. For this reason, since no friction torque acts, the closing valve 24 does not operate, and the first
The orifice 22 is opened. The second orifice 30 remains open. Therefore, a low torque characteristic as shown by E in FIG. 7 is exhibited.

As shown in FIG. 8, on the front wheel 51 side,
In a vehicle in which the main joint 53 is mounted near the front-wheel differential device 52, the joint transmission torque at the time of 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,
Reference numeral 8 denotes a rear wheel side differential device, 59 denotes a rear wheel side propeller shaft, and 60 denotes a front wheel side propeller shaft.

As described above, in the present embodiment, since the first orifice 22 is closed by the closing valve 24, the processing is easier and the cost can be reduced as compared with the spool valve. In addition, since the friction torque of the rotary valve 11 is used to close the first orifice 22, an opening / closing cam is not required, which leads to cost reduction. Further, by eliminating the spool valve and replacing it with the closing valve 24, 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 the sealing can be sufficiently performed by the closing valve 24, there is no leakage from the collecting chamber 20, and a decrease in torque can be prevented. Next, FIG.
FIG. 10 is a diagram showing a second embodiment of the present invention. 9 and 10, a collective chamber 20 as a high-pressure chamber is formed on a protrusion 19B of the rotary valve 11 opposite to the protrusion 19A, and the collective 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, and
On the outlet side of the orifice 61, there is formed a discharge oil passage 62 through which oil passing through the second orifice 61 is discharged.

A stop valve 63 is provided concentrically with the second orifice 61 on the projection 19B so as to be movable in the axial direction, and the end of the stop valve 63 is formed of a rod-shaped member having a spherical surface or a tapered surface. The closing 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. At the time of normal rotation in which the rotary valve 11 rotates in the direction indicated by the arrow A in FIG.
Since the plate portion 26 comes into contact with the projection 17A of the cam housing 4, the plate portion 26 is pressed by the friction torque acting between the projection 17A and the projection 19A,
The shut-off valve 24 closes the first orifice 22.

On the other hand, since the projection 19B on the side opposite to the projection 19A does not contact the projection 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, a 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 shown by the arrow B, and the projection 19B is
Move along the notch 18A of the cam housing 4 and hit the projection 17B of the cam housing 4. The closing valve 63 closes the second orifice 61 by the friction torque acting between the projection 17B and the projection 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, but
Opens the first orifice 22. The torque characteristic at the time of 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 forward rotation.

In this embodiment, the same effects as in the above embodiment can be obtained because the shutoff valves 24 and 63 are used. Next, FIGS. 11 and 12 show a third embodiment of the present invention. 11 and 12, a collecting chamber 66 as a high-pressure chamber is formed on the projection 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 an outlet of the collecting chamber 66.

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

The outlet of the second orifice 68 is formed on a projection 19B on the side of the cam housing 4 which does not come into contact with the projection 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
The orifice 67 is closed by the projection 17A. On the other hand, the second orifice 68 is always open.

Therefore, a 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 projection 19B moves along the notch 18A of the cam housing 4, and the projection 19B moves to the projection 17B of the cam housing 4. However, the second orifice 68 is open.

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

[0045]

As described above, according to the present invention, since the orifice is closed by the closing valve, the processing is easier and the cost can be reduced as compared with the spool valve. Further, since the friction torque of the rotary valve is used to close the orifice, an opening / closing cam is not required, 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.

Further, since the sealing can be sufficiently performed, it is possible to prevent the leak from the collecting chamber and prevent the torque from decreasing.

[Brief description of the drawings]

FIG. 1 is a diagram 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 a joint.

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

FIG. 5 is a diagram showing the flow of oil 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 view showing a position of a joint.

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

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

FIG. 11 is a diagram showing a state at the time of forward rotation showing a 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: welding portion 4: cam housing 5: rotor 6: input shaft 7: plunger chamber 8: plunger 9: return spring 10: suction and discharge hole 11: rotary valve (valve element) 12: Suction port 13: Suction path 14: Discharge port 15: Communication groove 16: Lid member 17A, 17B, 19A, 19B: Projection 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 portion 27: Stopper portion 28: Connecting portion 30: Second orifice 32: Retainer 33: Bearing 34: Hardened plate 35: Thrust needle bearing 36: Cover 37: Oil seals 38, 39: communication passage 40: accumulator chamber 41: accumulator piston 42 Lid 43: Air 44: Lubrication 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: Coupling 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: shut-off valve 64: plate portion 65: stopper portion 66: collective chamber 67: first orifice 68: second orifice

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-5-87163 (JP, A) JP-A-5-65926 (JP, A) JP-A-3-239824 (JP, A) 54868 (JP, A) JP-A-7-248031 (JP, A) JP-A-5-64539 (JP, U) JP-A-6-8827 (JP, U) (58) Fields investigated (Int. Cl. ⁶ , DB name) F16D 31/02 B60K 17/348

Claims (8)

(57) [Claims] A cam provided between input and output shafts which are relatively rotatable, connected to said one shaft and having a cam surface having two or more peaks on an inner surface and a plurality of notches formed therein. a rotor connected to the other shaft and rotatably housed in the cam housing and having a plurality of plunger chambers formed in an axial direction; A plurality of plungers housed respectively in a reciprocally movable manner and driven by the cam surface when the two shafts rotate relative to each other; an opening at one end face of the rotor that does not house a plunger; and suction and discharge hole communicating with; with rotatably sliding contact with an end surface of said rotor, said
A pair of positioning engaging the notch of the cam housing
The has a projection of use are given pivotably positioned between the cam housing, a plurality of suction ports to the action of the suction valve and the discharge valve by the positional relationship between the suction and discharge hole, the discharge port surface A high-pressure chamber formed by communicating the formed valve element and the discharge port; and a means for generating flow resistance at an outlet from the high-pressure chamber to the low-pressure chamber in the joint; a torque corresponding to a rotational speed difference between the two shafts is provided. In the hydraulic power transmission joint for transmitting, a first orifice as the flow resistance generating means is provided on one projection of the valve body, and the other orifice on the opposite side is provided .
The projection is provided with a second orifice, and the outlet of the first orifice is provided with a closing valve having a spherical or tapered surface that closes the outlet from the outside. The closing valve is used when the relative rotation direction of the input / output shaft is normal rotation.
A hydraulic power transmission coupling, wherein the outlet of the first orifice is closed, and the outlet of the first orifice is opened by the shut-off valve at the time of reverse rotation. 2. The valve according to claim 1, wherein the closing valve is provided between the one projection provided on the cam housing for positioning the valve body and an outlet of the first orifice of the valve body. The first valve is actuated by receiving a frictional rotating force acting between the valve body and the one protrusion .
2. The hydraulic power transmission coupling according to claim 1, wherein the outlet of the orifice is closed. 3. The hydraulic power transmission coupling according to claim 2, wherein a stopper member is provided around said one protrusion to prevent the closing valve from coming off. Wherein said two second hydraulic power transmission joint according to claim 1, characterized in that the orifice is open constantly out of the orifice. 5. An outlet portion of a second orifice of the two orifices is opened by another shut-off valve during normal rotation,
2. The hydraulic power transmission coupling according to claim 1, wherein the hydraulic power transmission coupling is closed by another stop valve during reverse rotation. 6. The hydraulic power transmission coupling according to claim 5, wherein the diameter of the first orifice of the two orifices is larger than the diameter of the second orifice. 7. A cam which is provided between input / output shafts which are relatively rotatable, is connected to said one shaft, has a cam surface having two or more peaks on an inner surface, and has a plurality of notches. a rotor connected to the other shaft and rotatably housed in the cam housing and having a plurality of plunger chambers formed in an axial direction; A plurality of plungers housed respectively in a reciprocally movable manner and driven by the cam surface when the two shafts rotate relative to each other; an opening at one end face of the rotor that does not house a plunger; and suction and discharge hole communicating with; with rotatably sliding contact with an end surface of said rotor, said
A pair of positioning engaging the notch of the cam housing
The has a projection of use are given pivotably positioned between the cam housing, a plurality of suction ports to the action of the suction valve and the discharge valve by the positional relationship between the suction and discharge hole, the discharge port surface A high-pressure chamber formed by communicating the formed valve element and the discharge port; and a means for generating flow resistance at an outlet from the high-pressure chamber to the low-pressure chamber in the joint; a torque corresponding to a rotational speed difference between the two shafts is provided. In the hydraulic power transmission coupling for transmission, the projection is formed on one of the projections, and is connected to the cam housing during normal rotation.
Closed by the formed projection and opened at the time of reverse rotation
One orifice is formed, and the other projection of the valve body is always
A hydraulic power transmission coupling, wherein a second orifice that is opened is formed . 8. The first orifice is larger than the diameter of the second orifice .
8. The hydraulic power transmission coupling according to claim 7, wherein the diameter of the orifice is large.