JPH08193629A - Hydraulic power transmission coupling - Google Patents

Abstract

PURPOSE: To provide the combination of a two-stage torque characteristic for the improvement of maneuvering stability of a vehicle, the torque characteristic of a torque limiter for the compactness and weight reduction of a power train system and each demand torque characteristic, with simple constitution regarding a hydraulic power transmission coupling. CONSTITUTION: A first storage hole 68 is formed at a rotary valve 41 and provided with a first spool valve 75, a first spring 77, a first pin member 78, a first communicating hole 71 and a second communicating hole 80. A small diameter second storage hole 70 communicated with the first storage hole 68 is formed and provided with a second spool valve 81 smaller in diameter than the first spool valve 75, a second spring 83, a second pin member 84, a third communicating hole 82, a fourth communicating hole 72 and an orifice 85.

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 As a conventional hydraulic power transmission joint, there are those shown in FIGS. 19 and 20, for example. 19 and 20, reference numeral 1 denotes a rotary valve of a hydraulic power transmission joint, a high pressure chamber 2 is formed in the rotary valve 1, and the high pressure chamber 2 communicates with a discharge port (not shown). A ball 3 as a valve body is movably accommodated in the high pressure chamber 2, and the ball 3 is normally pressed and held by a pin member 4. The pin member 4 is biased by a spring 6 as an elastic member via a ball 5, and the spring 6 is formed in the rotary valve 1 and is housed in a housing hole 7. The pin member 4 is prevented from moving by the pin member 8 via the ball 5. The high pressure chamber 2 is closed by a plug 9, and an orifice 10 communicating with the low pressure chamber is opened in the high pressure chamber 2.

As shown in FIGS. 19 (A) and 19 (B), in a normal state, that is, in a rotation difference region of a lock torque or less, a spring 6 presses a ball 5 by a force pushing a pin member 4 by a hydraulic pressure of a high pressure chamber 2. Since the force of pushing the pin member 4 by the lever is larger, the pin member 4 pushes the ball 3. Therefore, the orifice 10 as the flow resistance generating means is open, and the oil passes through the orifice 10. Normally, arrow a
As shown by, the force of pushing the pin member 4 by the spring 6 is large. The arrow b indicates the flow of oil through the orifice 10.

Therefore, the torque characteristic at the normal time is shown by c in FIG. In the figure, Tr is the lock torque, and d is the rotation difference region below the lock torque Tr.
On the other hand, as shown in FIG.
Since the force a1 for pushing is larger than the force for pushing the pin member 4 by the spring 6, the pin member 4 moves, the spring 6 is compressed, the ball 3 becomes free, and the orifice 10 is closed. The joint is thus locked.

The torque characteristic at this time is a lock characteristic as shown in FIG. At the time of release, a force for pushing the ball 3 is required, and the force can be freely set by adjusting the contact position between the orifice 10 and the ball 3 and the contact position between the pin member 4 and the ball 3 in FIG. In order to prevent hunting, it is desirable to release the hydraulic pressure in the high pressure chamber 2 after the hydraulic pressure is slightly reduced. That is, at the time of release, the torque T is set to the torque Tk lower than the lock torque Tr.

Next, FIG. 23 is a diagram showing another conventional example. In FIG. 23, reference numeral 11 denotes a rotary valve of a hydraulic power transmission joint, a high pressure chamber 12 is formed on the front surface side of the rotary valve 11, and a communication groove 13 communicating with the high pressure chamber 12 is formed on the rear surface side. . In addition, the rotary valve 1
A storage hole 14 is formed in the housing 1, and a ball 15 as a valve body is swingably stored in the storage hole 14.

The storage hole 14 and the high pressure chamber 12 are provided with an orifice 16
The orifice 16 is connected by a spring 17
The spring 17 is closed by a ball 15 which is pressed by a ball 18 and a plug 18 which closes the storage hole 14.
Is intervened between. Further, a discharge hole 19 for releasing hydraulic pressure is opened in the storage hole 14. When the hydraulic pressure in the high pressure chamber 12 rises above a predetermined value, the ball 15 moves against the spring 17 and releases the orifice 16.

Therefore, the torque characteristic at this time is shown in f of FIG. 24, and the initial torque is increased by the amount indicated by g.

[0009]

The hydraulic power transmission joint is required to have various torque characteristics for the purpose of improving vehicle performance. For example, in order to improve the vehicle controllability on a low μ road, the initial torque is increased as shown in FIG.
A two-stage torque characteristic as shown in is required.

Further, in order to improve the running performance, the torque characteristic of autolock as shown in FIG. 22 is required. Further, in order to reduce the size and weight of the power train system, FIG.
The torque characteristics of the torque limiter as shown in are required. However, in the conventional example shown in FIG. 19 and FIG. 20, the torque characteristic of the autolock as shown in FIG. 22 is obtained, and in the conventional example shown in FIG. 23, the initial torque increase as shown in FIG. However, in these conventional examples, there is a problem that only individual performances can be obtained, and it cannot be realized unless the structure is largely changed for each function. Further, the two-stage torque characteristic as shown in FIG. 25 and the torque characteristic of the torque limiter as shown in FIG. 26 were not obtained. Further, for example, as shown in FIG. 27, the combination of the torque characteristic of the auto lock and the initial torque increase could not be obtained. Further, in the conventional example in which the torque characteristic of the auto lock is obtained, there is a problem that the configuration is complicated and the cost is increased.

The present invention has been made in view of the above-mentioned conventional problems, and has a two-step torque characteristic for improving vehicle maneuverability, and a torque limiter torque for reducing the size and weight of a power train system. It is an object of the present invention to provide a hydraulic power transmission joint that can obtain characteristics and a combination of required torque characteristics with a simple configuration.

[0012]

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; housed in each of the plurality of plunger chambers so as to be reciprocally movable under the pressure of a return spring, and driven by the cam surface when the two shafts relatively rotate. A plurality of plungers; suction and discharge holes formed in the rotor and communicating with the plunger chamber; rotatably slidably contacting an end surface of the rotor and positioned in a predetermined relationship with the cam housing. , A rotary valve having a plurality of suction ports and discharge ports which act as suction valves and discharge valves depending on the positional relationship with the suction and discharge holes And a flow resistance generating means for generating a flow resistance by the flow of the discharge oil by driving the plunger; in a hydraulic power transmission joint transmitting a torque according to a rotational speed difference between the two shafts, to the rotary valve. , A first storage hole is formed, and a first spool valve and a first spool valve are pressed into the first storage hole.
And a first pin member that moves by the first spool valve, and a first communication hole that communicates with the high pressure chamber side on the first spool valve side, and a low pressure chamber side on the first pin member side. A second communication hole communicating with the first storage hole, a second storage hole communicating with the first storage hole and having a diameter smaller than that of the first storage hole is formed, and a second spool hole is formed in the second storage hole. A second spool valve having a small diameter, a second spring compressed by the movement of the second spool valve, a second pin member for stopping the movement of the second spool valve, and a second spool valve are provided. Side, a third communication hole communicating with the low pressure chamber side, a second pin member side communicating with the high pressure chamber side with a fourth communication hole, and a third communication hole between the third communication hole and the fourth communication hole. The flow resistance generating hand that is closed by the movement of the spool valve 2 An orifice as provided.

Further, according to the present invention, a fifth communication hole communicating with the low pressure chamber side by the movement of the first spool valve is provided between the first communication hole and the second communication hole. .
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. A rotor that is connected and is rotatably housed in the cam housing, and has a plurality of plunger chambers formed in the axial direction; reciprocally movable by receiving a return spring pressure in each of the plurality of plunger chambers. A plurality of plungers that are housed in the housing and are driven by the cam surface when the two shafts rotate relative to each other; suction and discharge holes that are formed in the rotor and communicate with the plunger chamber; Sliding on the
A plurality of suction ports that are positioned in a predetermined relationship with the cam housing and act as suction valves and discharge valves depending on the positional relationship with the suction and discharge holes; a rotary valve having discharge ports formed on the surface; A hydraulic resistance transmission means for generating a flow resistance by the flow of the discharged oil by the driving of the jar; in the hydraulic power transmission joint for transmitting the torque according to the rotational speed difference between the two shafts, the first storage in the rotary valve. A first spool valve having a hole formed therein and having a first large diameter portion and a second large diameter portion inside the first storage hole; a first spring for pressing the first spool valve; A first pin member that is moved by the spool valve, a first communication hole that communicates with the high pressure chamber side on the first spool valve side, and a first communication hole that communicates with the low pressure chamber side on the first pin member side. 6 communicating with the high pressure chamber side and the communicating hole, be between the first large diameter portion and the second large diameter portion of the
And a orifice as a flow resistance generating means, which is closed by the first large diameter portion by the movement of the first spool valve and then closed by the second large diameter portion.
A second communicating with the first storage hole and having a smaller diameter than the first storage hole;
A second spool valve having a smaller diameter than that of the first spool valve, and a second spring compressed by the movement of the second spool valve.
A second pin member that stops the movement of the second spool valve is provided, and a third communication hole that communicates with the low pressure chamber side on the second spool valve side and a high pressure chamber side on the second pin member side. A fourth communication hole communicating with each other was provided.

Further, in the present invention, the second large diameter portion of the first spool valve and the sixth communication hole are eliminated, and the third communication hole and the fourth communication hole are always opened. An orifice as the flow resistance generating means is provided.
Further, according to the present invention, a fifth communication hole communicating with the low pressure chamber side is provided between the first communication hole and the sixth communication hole by the movement of the first spool valve, and the fifth communication hole is provided. The diameter of the large-diameter portion 2 in the axial direction was increased.

[0015]

According to the hydraulic power transmission joint of the present invention having such a structure, the rotary valve has the first accommodation hole, and the first spool valve and the first spool valve are provided in the first accommodation hole. 1
First spring for pressing the spool valve of the
Is provided with a first pin member that is moved by the spool valve, and a first communication hole that communicates with the high pressure chamber side on the first spool valve side and a second communication hole that communicates with the low pressure chamber side on the first pin member side. A communication hole is provided, a second storage hole communicating with the first storage hole and having a smaller diameter than the first storage hole is formed, and a second spool valve having a smaller diameter than the first spool valve is provided in the second storage hole. And a second spring compressed by the movement of the second spool valve and a second pin member for stopping the movement of the second spool valve, and communicating with the second spool valve side to the low pressure chamber side. A third communication hole, and a fourth communication hole that communicates with the second pin member side to the high-pressure chamber side,
Since the orifice as the flow resistance generating means that is closed by the movement of the second spool valve is provided between the third communication hole and the fourth communication hole, the auto-lock characteristic can be obtained with a simple configuration.

Further, in the above-mentioned structure, the power of the fifth spool is communicated with the low pressure chamber side by the movement of the first spool valve only by providing the fifth communication hole between the first communication hole and the second communication hole. The characteristics of the torque limiter for reducing the size and weight of the train system can be obtained. Also, a first storage hole is formed in the rotary valve, and the first large diameter portion and the second storage hole are formed in the first storage hole.
A first spool valve having a large-diameter portion, a first spring that presses the first spool valve, and a first pin member that moves by the first spool valve, and the first spool valve side Between the first communication hole communicating with the high pressure chamber side, the second communication hole communicating with the first pin member side with the low pressure chamber side, and between the first large diameter portion and the second large diameter portion. There is a sixth communication hole communicating with the high pressure chamber side, and a flow resistance generating means that is closed by the first large diameter portion by the movement of the first spool valve and then closed by the second large diameter portion. An orifice is provided to communicate with the first storage hole to form a second storage hole having a smaller diameter than the first storage hole, and a second spool valve having a smaller diameter than the first spool valve is formed in the second storage hole. , A second spring compressed by the movement of the second spool valve, Provided with a second pin member stopping the movement of the second spool valve, and a third communicating hole which communicates with the low pressure chamber side to the second spool valve side, the second
By providing the fourth communication hole on the pin member side that communicates with the high pressure chamber side, it is possible to obtain a combination of the auto-lock characteristic and the initial torque increase.

Further, in the above structure, the second large diameter portion of the first spool valve and the sixth communication hole are eliminated, and the flow is always released between the third communication hole and the fourth communication hole. By providing the orifice as the resistance generating means, the two-stage torque characteristic can be obtained. Further, in the above configuration, the movement of the first spool valve allows the fifth valve communicating with the low pressure chamber side.
Since the communication hole of is provided between the first communication hole and the sixth communication hole and the axial diameter of the second large diameter portion is lengthened, a combination of the auto lock characteristic and the torque limiter characteristic can be obtained. You can

That is, by changing the valve structure, it is possible to obtain a two-stage torque characteristic for improving vehicle maneuverability and a torque limiter characteristic for reducing the size and weight of the power train system with a simple structure. It is possible to obtain a combination of various required torque characteristics.

[0019]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 5 are views showing a first embodiment of the present invention. FIG. 2 is a sectional view of a joint according to the first embodiment of the present invention. First, the configuration will be described. In FIG. 2, reference numeral 31 is a cam having an inner surface formed with a cam surface 32 having two or more ridges. The cam 31 is connected to an output shaft (not shown) and rotates integrally with the output shaft. To do. The cam 31 is fixed to the cam housing 34 by the welded portion 33, and the cam 31 rotates integrally with the cam housing 34.

Reference numeral 35 denotes a rotor rotatably housed in the cam housing 34. The rotor 35 is connected to the input shaft 36 and rotates integrally with the input shaft 36. A plurality of plunger chambers 37 are formed in the rotor 35 in the axial direction,
A plurality of plungers 38 are slidably accommodated in the plunger chamber 37 via return springs 39. Further, the rotor 35 is formed with a plurality of suction and discharge holes 40 so as to communicate with the respective plunger chambers 37.

Reference numeral 41 designates a suction port 42 and a suction passage 43 on the surface.
And a discharge port 44 are formed on the back surface of the rotary valve 41.
A communication groove 45 communicating with each of the above is formed. In addition, a lid member 46 is provided in close contact with the back surface to close the communication groove 45. Further, the rotary valve 41 has a positioning protrusion 48 that engages with a notch 47 formed on the inner circumference of the cam housing 34.

The rotary valve 41 constitutes a timing member which determines the opening / closing timing of the intake / discharge hole 40, and the notch 47 and the projection 48 constitute a positioning mechanism which regulates the phase relationship between the cam 31 and the rotary valve 41. . When the plunger 38 is in the intake stroke, there is a positional relationship in which the intake port 42 of the rotary valve 41 and the intake / discharge hole 40 of the rotor 35 communicate with each other, and an orifice, an intake port 42, an intake passage 43, and an intake / discharge hole of the rotor 35, which will be described later. Oil can be sucked into the plunger chamber 37 through 40.

When the plunger 38 is in the discharge stroke, the relationship is the reverse of the suction stroke, and the suction / discharge hole 40 of the rotor 35 communicates with the communication groove 45 via the discharge port 44 of the rotary valve 41. Reference numeral 49 is a bearing retainer that rotates integrally with the cam housing 34, and supports the input shaft 36 via a bearing 50. A thrust needle bearing 51 is interposed between the bearing retainer 49 and the rotary valve 41, and the friction torque on the thrust needle bearing 51 side is set to be smaller than the friction torque between the rotor 35 and the rotary valve 41. There is. Therefore, when the direction of the differential rotation changes, the rotary valve 41 moves to the rotor 3
5, the rotary valve 41 rotates until it comes into contact with the notch 47 of the cam housing 34, and then rotates together with the cam housing 34. As a result, the intake / discharge hole 40 is forcibly opened / closed at a predetermined timing even during normal rotation or reverse rotation.

An oil seal 52 is provided between the bearing retainer 49 and the input shaft 36.
An accumulator piston 53 for absorbing thermal expansion and contraction of oil is slidably housed inside the. 54
Is a lid member that prevents muddy water from entering the accumulator chamber 55. The accumulator chamber 55 communicates with the inside of the joint via oil passages 56 and 57.

The rotary valve 41 includes the discharge port 4
A high pressure chamber 58 communicating with the fuel cell 4 is formed, and the outlet of the high pressure chamber 58 is closed by a plug 59. In addition, 60 is an oiling hole, 61 is a needle bearing, 62 is a screw hole, 6
3, 64 are O-rings, 65 and 66 are snap rings, 6
7 is a mounting hole. Next, FIG. 3 is a front view of the rotary valve.

In FIG. 3, reference numeral 41 denotes the rotary valve. A plurality of suction ports 42 and a plurality of discharge ports 44 are alternately formed on the surface of the rotary valve 41 in the circumferential direction, and the suction ports 42 are sucked. The paths 43 communicate with each other. The rotary valve 41 has a first storage hole 68.
And a second storage hole 70 that communicates with the first storage hole 68 via the communication portion 69. Second
The storage hole 70 has a smaller diameter than the first storage hole 68. The first storage hole 68 communicates with the discharge port 44 through the first communication hole 71, and the second storage hole 70 communicates with the discharge port 44 through the fourth communication hole 72.

Next, FIG. 1 is a sectional view taken along the line AA of FIG. In FIG. 1, the first storage hole 68 is the seal member 73.
The first spool valve 75 is movably accommodated in the first accommodation hole 68 by being closed by the stopper pin 74 via the. First spool valve 75 and seal member 73
A first high pressure chamber 76 is formed between the first high pressure chamber 7 and the first high pressure chamber 7
6 communicates with the discharge port 44 through the first communication hole 71, and high pressure is supplied to the first high pressure chamber 76. A first spring 77 is interposed between the first spool valve 75 and the inner wall of the first housing hole 68, and the first spring 7
7 biases the first spool valve 75 to the left. A first pin member 78 is housed in the first housing hole 68 following the first spool valve 75. One end of the first pin member 78 is pressed by the first spool valve 75 and the other end is in communication. It is slidably supported by the portion 69. The first pin member 78 and the first spring 77 are accommodated in the first
A first low-pressure chamber 79 is formed in the storage hole 68 of the first low-pressure chamber 79, and the first low-pressure chamber 79 communicates with the low-pressure chamber side via the second communication hole 80.

A second spool valve 81 having a diameter smaller than that of the first spool valve 75 is movably accommodated in the second accommodation hole 70, and the second spool valve 81 is pressed by the first pin member 78. Then, it moves to the right in the figure. A third communication hole 82 is opened in the second storage hole 70, and the third communication hole 82 communicates with the low pressure chamber side. Further, the second spring 83 is housed in the second housing hole 70,
The second pin member 84 is housed in the spring 83. The second spring 83 is the second spool valve 8
The second pin member 84 blocks the movement of the second spool valve 81 by being compressed by 1. An orifice 85 as a flow resistance generating means that communicates with the low pressure chamber side is opened in the second storage hole 70, and the orifice 85 is closed by the movement of the second spool valve 81. Second
A second high pressure chamber 86 is formed on the right side of the spool valve 81 in the second storage hole 70 in which the second spring 83 and the second pin member 84 are stored. 86 communicates with the discharge port 44 through the fourth communication hole 72. The high pressure from the discharge port 44 enters the second high pressure chamber 86 through the fourth communication hole 72, passes through the orifice 85, and presses the second spool valve 81 to the left to cause the third communication. The hole 82 is closed. The orifice 85 is formed on the left side of the tip of the second pin member 84, and the second spool valve 81 serves as the second pin member 8.
When it comes into contact with No. 4, it is completely closed. Second storage hole 70
Is closed by a stopper pin 88 via a seal member 87.

Next, the operation will be described. When there is no rotation difference between the cam 31 and the rotor 35, the plunger 3
8 is inactive and no torque is transmitted. At this time, the plunger 38 is pressed against the cam surface 32 by the return spring 39. Next, when a rotation difference occurs between the cam 31 and the rotor 35, the plunger 38 in the discharge stroke is pushed axially by the cam surface 32 of the cam 31.

At this time, the suction / discharge hole 40 is formed in the discharge port 44.
Therefore, the plunger 38 pushes the oil in the plunger chamber 37 from the suction / discharge hole 40 to the discharge port 44 of the rotary valve 41. The oil pushed out to the discharge port 44 is supplied from the suction passage 43 to the suction port 42 through the fourth communication hole 72, the second storage hole 70, and the orifice 85. At this time, the resistance of the orifice 85 increases the hydraulic pressure in the second storage hole 70, the fourth communication hole 72, the discharge port 44, the plunger chamber 37, etc., and the plunger 38
A reaction force is generated. A torque is generated by rotating the cam 31 against the plunger reaction force,
Torque is transmitted between the rotor and the rotor 35. Since the discharge port 44 is communicated with the communication groove 45, the hydraulic pressures of all the plunger chambers 37 in the discharge process are equal.

Further, when the cam 31 rotates, a suction stroke is established, and the suction / discharge hole 40 communicates with the suction port 42. Therefore, the oil in the suction passage 43 is sucked into the suction port 42 and the suction / discharge hole 4.
It is sucked into the plunger chamber 37 via 0, and the plunger 38 returns along the cam surface 32 of the cam 31. In the initial state, as shown in FIG. 4 (A), the differential rotation speed ΔN
Is small and the hydraulic pressure is not high, the hydraulic pressure is supplied to the first high-pressure chamber 76 via the first communication hole 71, but the first spool valve 75 and the first pin member 78 are The spring 77 and the second spool valve 81 prevent the rightward movement. On the other hand, the hydraulic pressure that has entered the second high-pressure chamber 86 via the fourth communication hole 72 presses the second spool valve 81 to the left and causes the orifice 8 to move.
It passes through 5 and is supplied to the low-pressure chamber side.

Therefore, the torque characteristic is as shown by h in FIG. The differential rotation speed ΔN reaches a predetermined value, the hydraulic pressure reaches a predetermined value, and the difference between the force exerted on the first spool valve 75 by the hydraulic pressure and the force exerted on the second spool valve 81 is the first spring 77. 4B, the hydraulic pressure supplied to the first high pressure chamber 76 through the first communication hole 71 causes the first spool valve 75 to move the first spring valve 77 to the first spring 77, as shown in FIG. 4B. To the right, the first pin member 78 is also pressed by the first spool valve 75 and moves to the right,
The second spool valve 81 is pressed and moved until it hits the second spring 83. When the hydraulic pressure becomes higher and the difference between the force applied to the first spool valve 75 and the force applied to the second spool valve 81 becomes larger than the sum of the spring forces of the first spring 77 and the second spring 83, The second spool valve 81 begins to close the orifice 85. Thus, the lock is started. The torque characteristic at this time is as shown by i in FIG.

When the hydraulic pressure is further increased, the second spool valve 81 moves further to the right to completely close the orifice 85, as shown in FIG. 4 (C). This completes the lock. In addition, the second spool valve 81
When is moved further to the right, it comes into contact with the second pin member 84 to prevent the movement, as shown in FIG. 4 (D). This is the bottomed state. The torque characteristic after the lock is started and the lock is completed is shown by j in FIG. 5 (C).

In this way, it is possible to obtain the characteristics of auto-lock for improving the running performance with a simple structure. Next, FIG. 6 is a cross-sectional view of an essential part showing a second embodiment of the present invention. The present embodiment is intended to obtain the characteristics of a torque limiter in order to reduce the size and weight of a power train system.

In FIG. 6, reference numeral 89 is a fifth communication hole that opens into the first storage hole 68, and the fifth communication hole 89 is located between the first communication hole 71 and the second communication hole 80. It is formed.
The fifth communication hole 89 communicates with the low pressure chamber side and allows the hydraulic pressure of the first high pressure chamber 76 to escape to the low pressure chamber side. That is, the fifth communication hole 89 has the first spool valve 75 in the initial state.
It is closed by and when the hydraulic pressure reaches a certain value,
It is opened by the first spool valve 75 and communicates with the first high pressure chamber 76. The rest of the configuration is the same as that of the first embodiment, and the description is omitted.

In the initial state in which the differential rotation speed ΔN is small and the hydraulic pressure reaches a predetermined value, as shown in FIG. 7A, the first high pressure chamber 76 is passed through the first communication hole 71.
Is supplied to the first spool valve 7 by the first spring 77 and the second spool valve 81.
5 and the first pin member 78 do not move to the right. On the other hand, when the hydraulic pressure is supplied to the second high pressure chamber 86 via the fourth communication hole 72, the hydraulic pressure moves the second spool valve 81 to the left and also passes through the orifice 85 to cause the low pressure chamber to flow. Supplied to the side. In this initial state,
The fifth communication hole 89 is closed by the first spool valve 75.

Therefore, the torque characteristic is as shown by h in FIG. 8 (A). Next, the differential rotation speed ΔN increases, the hydraulic pressure reaches a certain value, and the difference between the force exerted on the first spool valve 75 and the second spool valve 81 by the hydraulic pressure is the first spring. When it becomes larger than the spring force of 77, the first spool valve 75 moves to the right against the first spring 77, and the first pin member 78 moves to the second pin, as shown in FIG. 7B. The spool valve 81 is pressed rightward.

When the first spool valve 75 moves to the right, the fifth communication hole 89 begins to open and the hydraulic pressure is released to the low pressure chamber side. As a result, when the hydraulic pressure in the first high pressure chamber 76 decreases, the first spool valve 75 moves leftward and closes the fifth communication hole 89. Further, when the second spool valve 81 closes the orifice 85, the hydraulic pressure of the second high pressure chamber 86 rises, the second spool valve 81 moves leftward, and the orifice 85 is opened again. In such a pressure regulated state, the torque characteristic of the torque limiter is obtained as indicated by k in FIG. 8 (B).

As described above, in this embodiment, the torque characteristic of the torque limiter can be obtained only by adding the fifth communication hole 89 to the first embodiment. Next, FIG. 9 is a cross-sectional view of essential parts showing a third embodiment of the present invention. The present embodiment is intended to obtain a combination of the torque characteristic of the auto lock and the initial torque increase.

In FIG. 9, 90 is a first spool valve housed in the first housing hole 68. The first spool valve 90 has a first large diameter portion 91 and a second large diameter portion. It has a portion 92 and a small diameter portion 93 that connects the first large diameter portion 91 and the second large diameter portion 92. A third high pressure chamber 94 is formed between the first large diameter portion 91 and the second large diameter portion 92, and a sixth communication hole 95 is opened in the third high pressure chamber 94. As shown in FIG. 10, the sixth communication hole 95 communicates with the discharge port 44, and hydraulic pressure is supplied to the third high pressure chamber 94.

An orifice 96 as a flow resistance generating means is formed substantially on the opposite side of the sixth communicating hole 95. The other structure is the same as that of the first embodiment. The axial length of the first large diameter portion 91 is formed to be larger than the diameter of the orifice 96, and the orifice 96 is closed by the first large diameter portion 91 in the initial state until reaching a predetermined hydraulic pressure.

When the first spool valve 90 moves to the right, the orifice 96 communicates with the third high pressure chamber 94,
Further, when the first spool valve 90 moves to the right, the orifice 96 is closed by the second large diameter portion 92. That is, as shown in FIG. 11 (A), in the initial state until the hydraulic pressure reaches a predetermined value,
The first spool valve 90 does not move and the orifice 96
Is closed by the first large diameter portion 91. Therefore, the initial torque increase can be obtained as shown by l in FIG.

The hydraulic pressure rises, and by the hydraulic pressure supplied to the first high pressure chamber 76 through the first communication hole 71 and the hydraulic pressure supplied to the third high pressure chamber 94 through the sixth communication hole 95. , When the first spool valve 90 moves to the right,
As shown in FIG. 11B, the orifice 96 is opened. That is, the orifice 96 communicates with the third high pressure chamber 94, and the hydraulic pressure of the third high pressure chamber 94 is supplied to the orifice 96.

When the opening of the orifice 96 is completed, the torque characteristic becomes as shown by m in FIG. 12 (B).
When the hydraulic pressure further rises, the first spool valve 90
Moves to the right, and the second large diameter portion 92 begins to close the orifice 96 as shown in FIG. 11 (C). This starts the lock. The torque characteristic at this time is as shown by n in FIG.

When the hydraulic pressure further rises, FIG. 11 (D)
The orifice 96 is closed by the second large diameter portion 92, as shown in FIG. When the hydraulic pressure further rises, as shown in FIG. 11 (E), the second spool valve 81 comes into contact with the second pin member 84 to be in a bottomed state. In this case, the orifice 96 remains closed by the second large diameter portion 92. In the locked state and bottomed state, the torque characteristic is as shown by o in FIG.

In this embodiment, it is only necessary to change the shape of the first spool valve 90 and the position of the orifice 96.
It is possible to obtain a combination of the torque characteristic of the auto lock and the initial torque increase. Next, FIG. 13 shows a fourth embodiment of the present invention.
It is an important section sectional view showing an example. The present embodiment is intended to obtain a two-stage torque characteristic.

In FIG. 13, 97 is the first storage hole 68.
The first spool valve 97 is a first spool valve housed therein, and the first spool valve 97 includes a large diameter portion 98 and a pin member 99 integrally connected to the large diameter portion 98. The second orifice 100 as a flow resistance generating means is formed between the first communication hole 71 and the second communication hole 80, is closed by the large diameter portion 98 in the initial state, and the hydraulic pressure is not less than a predetermined value. Will be released.

Further, the third communication hole 82 and the fourth communication hole 7
Between the two, and on the right side of the tip of the second pin member 84, a first orifice 101 as a flow resistance generating means is formed. Even if the second spool valve 81 moves to the right, the first orifice 101 does not close by the second spool valve 81 because it abuts on the second pin member 84 and stops. It is open. As compared with the third embodiment, the second large diameter portion 92, the sixth
The communication hole 95 and the third high pressure chamber 94 are not provided, but the first orifice 101 is added.

In the initial state, as shown in FIG. 14A, the first spool valve 97 does not move, the second orifice 100 is closed by the large diameter portion 98, and the first orifice 101 is open. Has been done. Therefore, the torque characteristic in this case is as shown by h in FIG.

When the hydraulic pressure rises above a certain value,
As shown in FIG. 14B, the first spool valve 97
Moves to the right to open the second orifice 100. In this case, the first orifice 101 remains open. In this way, the first orifice 101 and the second orifice 101
Since the hydraulic pressure is supplied to the orifice 100 of FIG.
The torque characteristic is as shown by p in (B).

As described above, by changing the shape of the first spool valve, eliminating the sixth communicating hole 95 and adding the first orifice 101 to the third embodiment, the two-stage torque characteristic is obtained. Can be obtained. Next, in FIG.
[FIG. 8] is a sectional view of a key portion showing a fifth embodiment of the present invention. The present embodiment is intended to obtain a combination of the initial torque increase and the torque characteristic of the torque limiter.

In FIG. 16, 102 is the first storage hole 6
8 is a first spool valve housed in the first spool valve 102, and the first spool valve 102 includes a first large diameter portion 91, a second large diameter portion 103, a first large diameter portion 91 and a second large diameter portion 91. Large diameter part 103
The second large diameter portion 103 has a smaller axial dimension than the first large diameter portion 91. A fifth communication hole 89 is formed between the first communication hole 71 and the sixth communication hole 95, and the fifth communication hole 89 communicates with the low pressure chamber side.

The fifth communication hole 89 is closed by the second large diameter portion 103 in the initial state and when the orifice 96 is opened, and when the first spool valve 102 is further moved,
It is opened to release the hydraulic pressure to the low pressure chamber side.
As shown in FIG. 17A, in the initial state, the first
The spool valve 102 of does not move to the right, the fifth communication hole 89 is closed by the second large diameter portion 103, and
The orifice 96 is closed by the first large diameter portion 91.

Therefore, the initial torque increase as shown by l in FIG. 18 (A) is obtained. When the hydraulic pressure rises above a certain value, the orifice 96 is opened by the first large diameter portion 91, as shown in FIG. 17 (B). With this hydraulic pressure, the fifth communication hole 89 remains closed by the second large diameter portion 103. When the opening of the orifice 96 is completed, the torque characteristic shown by m in FIG. When the hydraulic pressure further rises, the first spool valve 1
02 moves further to the right, the second large diameter portion 103 opens the fifth communication hole 89, and pressure regulation is started. In the bottomed state in which the second spool valve 81 abuts the second pin member 84, the orifice 96 is the second large diameter portion 10.
The state immediately before being closed by 3 is obtained, and the torque characteristic as shown by Q in FIG. 18 (C) is obtained.

As described above, by changing the shape of the first spool valve 102 and forming the fourth communication hole 89 with respect to the third embodiment, the torque characteristic of the auto lock and the torque characteristic of the torque limiter are formed. Can be obtained.

[0056]

As described above, according to the present invention, by changing the valve structure, a simple structure can be obtained.
It is possible to obtain a combination of a two-stage torque characteristic for improving vehicle steerability, a torque limiter characteristic for reducing the size and weight of a power train system, and various required torque characteristics.

[Brief description of drawings]

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

FIG. 2 is a sectional view of the joint.

FIG. 3 is a front view of a rotary valve.

FIG. 4 is an operation explanatory diagram of the first embodiment.

FIG. 5 is a diagram showing torque characteristics of the first embodiment.

FIG. 6 is a cross-sectional view of an essential part showing a second embodiment of the present invention.

FIG. 7 is an operation explanatory diagram of the second embodiment.

FIG. 8 is a diagram showing torque characteristics of the second embodiment.

FIG. 9 is a cross-sectional view of an essential part showing a third embodiment of the present invention.

FIG. 10 is a front view of a rotary valve according to a third embodiment.

FIG. 11 is an operation explanatory diagram of the third embodiment.

FIG. 12 is a diagram showing torque characteristics of the third embodiment.

FIG. 13 is a cross-sectional view of an essential part showing a fourth embodiment of the present invention.

FIG. 14 is an operation explanatory diagram of the fourth embodiment.

FIG. 15 is a diagram showing torque characteristics of the fourth embodiment.

FIG. 16 is a cross-sectional view of essential parts showing a fifth embodiment of the present invention.

FIG. 17 is an operation explanatory diagram of the fifth embodiment.

FIG. 18 is a diagram showing torque characteristics of the fifth embodiment.

FIG. 19 is a view showing a conventional example (normal time).

FIG. 20 is a view showing a conventional example (when locked).

FIG. 21 is a diagram showing torque characteristics during normal operation.

FIG. 22 is a diagram showing torque characteristics when locked.

FIG. 23 is a diagram showing another conventional example.

FIG. 24 is a diagram showing torque characteristics of initial torque increase.

FIG. 25 is a diagram showing a two-step torque characteristic.

FIG. 26 is a diagram showing torque characteristics of a torque limiter.

FIG. 27 is a diagram showing a combination of initial torque-up and torque characteristics of auto lock.

[Explanation of symbols]

 31: cam 32: cam surface 33: welded part 34: cam housing 35: rotor 36: input shaft 37: plunger chamber 38: plunger 39: return spring 40: intake / discharge hole 41: rotary valve 42: intake port 43: Suction path 44: Discharge port 45: Communication groove 46: Lid member 47: Notch 48: Protrusion 49: Bearing retainer 50: Bearing 51: Thrust needle bearing 52: Oil seal 53: Accumulator piston 54: Lid member 55: Accumulator chamber 56 , 57: Oil passage 58: High pressure chamber 59: Plug 60: Oiling hole 61: Needle bearing 62: Screw hole 63, 64: O-ring 65, 66: Snap ring 67: Mounting hole 68: First storage hole 69: Communication Part 70: Second storage hole 71: First communication hole 72: Fourth Communication hole 73: Seal member 74: Stopper pin 75: First spool valve 76: First high pressure chamber 77: First spring 78: First pin member 79: First low pressure chamber 80: Second communication Hole 81: Second spool valve 82: Third communication hole 83: Second spring 84: Second pin member 85: Orifice (flow resistance generating means) 86: Second high pressure chamber 87: Seal member 88: Stopper pin 89: Fifth communication hole 90: First spool valve 91: First large diameter portion 92: Second large diameter portion 93: Small diameter portion 94: Third high pressure chamber 95: Sixth communication hole 96: Orifice (flow resistance generating means) 97: First spool valve 98: Large diameter part 99: Pin member 100: Second orifice (flow resistance generating means) 101: First orifice (flow resistance generating means) 102 : First spool valve 103: Second large diameter portion

Claims (5)

[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. A rotor having a plurality of plunger chambers axially formed therein and rotatably housed in the cam housing; and a plurality of plunger chambers each of which is reciprocally movable by being pressed by a return spring. Plural plungers that are housed and driven by the cam surface when the two shafts rotate relative to each other; suction and discharge holes formed in the rotor and communicating with the plunger chamber; rotatably on the end surface of the rotor A plurality of suction valves, which are in sliding contact with each other, are positioned in a predetermined relationship with the cam housing, and act as suction valves and discharge valves depending on the positional relationship with the suction / discharge holes. A rotary valve having a port and a discharge port formed on its surface; and a flow resistance generating means for generating a flow resistance by the flow of the discharge oil by driving the plunger; transmitting a torque according to a difference in rotational speed between the two shafts. In the hydraulic power transmission joint, a first storage hole is formed in the rotary valve, a first spool valve in the first storage hole, a first spring for pressing the first spool valve, and A first pin member that is moved by the first spool valve is provided, and a first communication hole that communicates with the first spool valve side to the high pressure chamber side and a second communication hole that communicates with the first pin member side to the low pressure chamber side. And a second hole having a diameter smaller than that of the first storage hole and communicating with the first storage hole.
A second spool valve having a smaller diameter than that of the first spool valve, and a second spring compressed by the movement of the second spool valve.
A second pin member for stopping the movement of the second spool valve is provided, a third communication hole communicating with the low pressure chamber side is provided on the second spool valve side, and a high pressure chamber side is provided on the second pin member side. It is characterized in that a fourth communication hole communicating with each other and an orifice as the flow resistance generating means closed by the movement of the second spool valve are provided between the third communication hole and the fourth communication hole. Hydraulic power transmission joint. 2. By the movement of the first spool valve,
The hydraulic power transmission joint according to claim 1, wherein a fifth communication hole communicating with the low pressure chamber side is provided between the first communication hole and the second communication hole. 3. 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. A rotor having a plurality of plunger chambers axially formed therein and rotatably housed in the cam housing; and a plurality of plunger chambers each of which is reciprocally movable by being pressed by a return spring. Plural plungers that are housed and driven by the cam surface when the two shafts rotate relative to each other; suction and discharge holes formed in the rotor and communicating with the plunger chamber; rotatably on the end surface of the rotor A plurality of suction valves, which are in sliding contact with each other, are positioned in a predetermined relationship with the cam housing, and act as suction valves and discharge valves depending on the positional relationship with the suction / discharge holes. A rotary valve having a port and a discharge port formed on its surface; and a flow resistance generating means for generating a flow resistance by the flow of the discharge oil by driving the plunger; transmitting a torque according to a difference in rotational speed between the two shafts. In the hydraulic power transmission joint, a first accommodation hole is formed in the rotary valve, and a first spool valve having a first large diameter portion and a second large diameter portion in the first accommodation hole; 1st pressing spool valve 1
And a first pin member that moves by the first spool valve, a first communication hole that communicates with the high pressure chamber side on the first spool valve side, and a low pressure chamber on the first pin member side. The second communication hole communicating with the first side, and the first communication hole
Between the large diameter portion of the second large diameter portion and the second large diameter portion and communicating with the high pressure chamber side, and the first large diameter portion is closed by the movement of the first spool valve. An orifice serving as the flow resistance generating means that is closed by the second large diameter portion is provided, communicates with the first storage hole, and has a second diameter smaller than that of the first storage hole.
A second spool valve having a smaller diameter than that of the first spool valve, and a second spring compressed by the movement of the second spool valve.
A second pin member for stopping the movement of the second spool valve is provided, a third communication hole communicating with the low pressure chamber side is provided on the second spool valve side, and a high pressure chamber side is provided on the second pin member side. A hydraulic power transmission joint characterized by having a fourth communication hole communicating therewith. 4. The second large-diameter portion of the first spool valve and the sixth communication hole are eliminated, and the second communication hole is always open between the third communication hole and the fourth communication hole. The hydraulic power transmission joint according to claim 3, wherein an orifice is provided as a flow resistance generating means. 5. By the movement of the first spool valve,
A fifth communication hole communicating with the low pressure chamber side is provided between the first communication hole and the sixth communication hole, and the second communication hole is provided.
4. The hydraulic power transmission joint according to claim 3, wherein the large diameter portion of the shaft has a longer diameter in the axial direction.