JPH0711295B2 - Launch clutch - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a starting clutch incorporated into an automatic continuously variable transmission mechanism of a vehicle.

(Prior Art and its Problems) In the conventional starting clutch, the friction plate is directly pressed by the force of the governor mechanism, and therefore the diameter of the governor mechanism becomes large and the normal hydraulic pressure is required to obtain the specified transmission torque. The clutch has a problem that the mechanism is complicated because the pressing force of the friction plate is directly controlled by controlling the source pressure of the hydraulic pressure.

(Object of the Invention) The present invention has been made in view of the above circumstances, and has a simple structure and a compact structure, while being able to obtain a sufficient pressing force of a friction plate and a friction portion during half-clutching. It is an object of the present invention to provide a starting clutch capable of preventing the seizure accident of the above.

(Means for Solving Problems) In order to solve the above problems, in the present invention, an input side rotating body that integrally rotates with an input shaft, an output side rotating body that integrally rotates with an output shaft, and these input sides. And the output-side rotating body so as to be contacted and separated from the output-side rotating body so that the rotational power of the input-side rotating body is transmitted to the output-side rotating body when the pressure-bonding is performed, and the rotational power of the input-side rotating body is transmitted when the separation is performed. A friction plate that is not transmitted to the output side rotating body, a pressing body that presses the friction plate so that the two rotating bodies are in a power transferable state, and a friction plate is provided between the pressing body and the output side rotating body. Pressure chamber for accommodating the pressure fluid for operating the pressing body, which is supplied from a pressure fluid supply source that generates a pressure fluid having a value dependent on the rotating body of the input shaft, and a pressure fluid provided in the pressure chamber. To selectively open and close the supply port and discharge port of And a control mechanism for controlling the pressure regulating valve so that the pressure in the pressure chamber depends on the number of revolutions of the input shaft, the pressure regulating valve and the control mechanism. Is arranged radially inward of the friction plate.

(Embodiment) An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a block diagram of an automatic continuously variable transmission for a vehicle equipped with a starting clutch of the present invention. In FIG. 1, 1 is a starting clutch of the present invention, which is connected to an output shaft of an internal combustion engine (not shown). It is interposed between the rotating input shaft 2 and the drive shaft 4 of the automatic continuously variable transmission 3. The starting clutch 1 has an input side rotating body 5 that rotates integrally with the input shaft 2, and an output side rotating body 6 that rotates integrally with the drive shaft 4 that is an output shaft.

The input side rotating body 5 comprises a disc 8 which is spline-fitted to the input shaft 2 and fixed by bolts 7.
A known clutch damper mechanism 9 is attached to the. A control mechanism 11 for controlling a pressure regulating valve 10 described later is incorporated on the surface of the input side rotating body 5 facing the output side rotating body 6. The control mechanism 11 is a centrifugal governor mechanism, and includes an annular cam plate 13 axially slidably fitted in a governor housing 12 riveted to the input side rotating body 5,
The cam surface 13a of the cam plate 13 and the governor housing 1
The cam plate 13 is provided with a governor ball 14 which is located between the second guide surface 12a and slidably in the radial direction.
Is urged toward the input side rotating body 5 by a coiled spring 16 interposed between the cam plate 13 and the annular spring receiving member 15. When the rotation speed of the input shaft 2 is less than or equal to a predetermined set value, the governor ball 14 is in a state of being deviated toward the center side, and the cam plate 13 is urged by the spring 16 so that the input side rotating body is rotated. When the rotation speed of the input shaft 2 exceeds a predetermined set value from this state, the governor ball 14 is displaced to the outer peripheral side by the action of centrifugal force, and the deviation occurs. The cam plate 13 is biased to the output side rotating body 6 side against the biasing force of the spring 16 in accordance with the position.

The output side rotating body 6 is a spline-fitted clutch cylinder 18 fixed to the drive shaft 4 with a nut 17, and a clutch fixed to the outer circumference of the clutch cylinder 18 so as to be immovable in both the circumferential and axial directions. It consists of outerwear 19. A clutch piston (pressing body) 20 is fitted in the clutch silling 18 so as to be slidable in the axial direction. The clutch piston 20 presses an annular or annularly arranged friction plate 21 described later, and a pressure fluid (pressure oil) introduced into a pressure chamber 22 provided between the clutch piston 20 and the clutch cylinder 18. ). The clutch piston
20 is biased toward the output side rotating body 6 by a disc-shaped spring 23.

A pressure fluid is introduced into the pressure chamber 22 from a supply port 24 of the pressure chamber 22 formed in the boss portion of the clutch cylinder 18 along the radial direction, and the pressure introduced into the pressure chamber 22 is also increased. The fluid is a fitting hole (a discharge port of the pressure chamber 22) 25 formed in the boss portion of the clutch piston 20 along the axial direction.
It can be discharged to the outside through the pressure regulating valve 10 that is slidably fitted inside. A central portion of the fitting hole 25 communicates with the supply port 24, and one end of the fitting hole 25 opens at an end surface of the boss portion of the clutch cylinder 18 on the input side rotary body 5 side. The pressure regulating valve 10 slides along the axial direction of the drive shaft 4 for a predetermined stroke, and is composed of a hollow pipe whose one end is open and the other end is closed. A discharge port 10a is formed, and an annular groove 10b having a predetermined width is formed on the outer peripheral surface of the substantially central portion. The closed end side of the pressure chamber 22 and the fitting hole 25 is a passage 22.
connected by a.

When the rotation speed of the input shaft 2 is less than a predetermined set value, the pressure regulating valve 10 is in the state shown in FIG. 2, that is, the pressure fluid in the pressure chamber 22 flowing into the fitting hole 25 through the passage 22a. By action, the discharge port 10a is eccentrically displaced toward the input side rotating body 5 side, and the pressure fluid in the pressure chamber 22 is discharged from the discharge port 10a, so that the pressure in the pressure chamber 22 does not rise and the clutch piston
20 is biased to the output side rotating body 6 side by the biasing force of the spring 23. Further, when the rotation speed of the input shaft 2 is equal to or higher than a predetermined set value, the pressure regulating valve 10 is pressed by the cam plate 13, and as the rotation speed of the input shaft 2 increases, the state shown in FIG. 24 and the discharge port 10a are both closed), that is, the discharge port 10a is closed and the annular groove 10b is displaced to the output rotary body 6 side to the position where the supply port 24 is opened. Then, the pressure fluid flows from the supply port 24 into the pressure chamber 22 to increase the pressure in the pressure chamber 22 (point X in FIG. 5). When the pressure in the pressure chamber 22 overcomes the pressing force of the cam plate 13, the pressure regulating valve 10 is displaced to the state shown in FIG. 2, the supply port 24 is closed and the discharge port 10a is opened. Eventually, the pressure in the pressure chamber 22 is adjusted by the balance between the force of the pressure fluid pressing the pressure regulating valve 10 and the force of the governor ball 14 pushing the pressure regulating valve 10 of the cam plate 13.

The friction plate 21 pressed by the clutch piston 20.
Is located between the input-side and output-side rotating bodies 5 and 6, and is fitted to the inner peripheral surface of the clutch outer 19 such that it cannot rotate but is movable in the axial direction. A clutch facing 27 is interposed between the friction plate 21 and the inner surface of the clutch outer 19 on the input side rotating body 5 side, and the clutch facing 27 is non-rotatable on the outer periphery of the governor housing 12 in the axial direction. It is movably fitted. Then, the friction plate 21 is pressed against the clutch outer 19 via the clutch facing 27 by the clutch piston 20 so that the input side rotating body 5 and the output side rotating body 6 can transmit power, and the pressing is released. The power cannot be transmitted.

Pressure fluid distribution holes 12b and 20a are formed at predetermined locations on the side walls of the governor housing 12 and the clutch piston 20, respectively. And the discharge port 10a of the pressure regulating valve 10
To the inside of the governor housing 12 and the governor housing
The pressure fluid in the pressure chamber 22 discharged between the clutch 12 and the clutch piston 20 is guided to the sliding contact portion of the clutch facing 27 via the pressure fluid distribution holes 12b and 20a. It is possible to prevent a seizure accident at the time of 27 half-clutch. The supply port 24 is connected to a pump 29 which is a pressure fluid supply source via a pressure fluid switching valve mechanism 41 incorporated in the automatic continuously variable transmission 3 described in detail below.

The starting clutch 1 of the present invention includes an input shaft 2, an input side rotating body 5 (disc 8), a bolt 7, a clutch damper mechanism 9,
The control mechanism 11 (the governor housing 12, the cam plate 13, the governor ball 14, the spring receiving member 15, the spring 16) constitutes the input side assembly A, and also the drive shaft 4 and the output side rotating body 6.
(Clutch cylinder 18, clutch outer 19) Pressure regulator 10,
The clutch piston 20, the friction plate 21, the spring 23, and the clutch facing 27 constitute an output side assembly B. After these assemblies A and B are individually assembled in advance, the center of the clutch facing 27 and the governor housing.
The assembly of the starting clutch 1 as a whole is completed by fitting the two assemblies A and B together with the center of 12 together, and therefore, the assemblability can be improved.

The starting clutch 1 of the present invention is configured as described above.

Next, the structure of the automatic continuously variable transmission 3 including the starting clutch 1 of the present invention will be described in detail. The drive shaft 4 is composed of a hollow pipe whose both ends are open, and both ends thereof are rotatably supported by ball bearings 31 and 32 on one end side walls of the transmission box 30. The drive shaft 4 located in the box 30
Is provided with a drive shaft pulley C capable of changing the groove width in the axial direction by fluid pressure control.

The drive shaft pulley C is a disk-shaped fixed pulley 33 integrally formed on the outer circumference of the drive shaft 4 on the side of the starting clutch 1, and a fixed pulley 33 that faces the outer circumference of the drive shaft 4 along the axial direction thereof. And a movable pulley 34 that is movably and non-rotatably fitted through a plurality of balls 35. The movable pulley 34 has a disk-shaped pulley main body 34b integrally formed on the outer periphery of one end of the cylindrical boss portion 34a, and projects in the opposite direction to the fixed pulley 33 along the axial direction on the outer peripheral surface of the main body 34b. A cylindrical peripheral wall 34c is integrally formed to project, and an annular closing plate 34d is fitted to the inner peripheral surface of the cylindrical peripheral wall 34c on the projecting end side to form a drum shape.

A fixed piston member 36 is fitted in the movable pulley 34. The fixed piston member 36 is formed by integrally projecting an annular flange 36b in the radial direction on the outer circumference of the other end of a cylindrical body 36a having a fitting hole in the center of the wall on one end face and having the other end face open. The fixed piston member 36 has a fitting hole at the center of one end surface wall thereof fitted into the outer circumference of the drive shaft 4 so as not to rotate and move in the axial direction, and the inner peripheral surface of the cylindrical body 36a is movable. The outer peripheral surface of the flange 36b is loosely fitted to the outer peripheral surface of the boss portion 34a of the pulley 34, and the outer peripheral surface of the flange 36b is a cylindrical peripheral wall 34c of the movable pulley 34.
Is fitted to the inner peripheral surface of the so as to be liquid-tight and slidable. Also,
A cylindrical guide cylinder 37 having both end surface openings is fitted to the outer peripheral side of the cylindrical body 36a of the fixed piston member 36 located on the inner peripheral side of the central hole of the closing plate 34d of the movable pulley 34, and The cylinder 37 has a mounting flange portion 37a on the outer periphery at one end attached to the inner surface of one side wall of the transmission box 30 with a bolt 38.

The pulley body 34b of the possible pulley 34 and the fixed piston member 3
A first pressure chamber 39 is formed between the flange 36b of 6 and
Further, the closing plate 34d of the movable pulley 34 and the fixed piston member 3
A second pressure chamber 40 is formed between the six flanges 36b. These first and second pressure chambers 39 and 40 are connected to the pump 29 via a pressure fluid switching valve mechanism 41.

The pressure fluid switching valve mechanism 41 includes a bearing cylindrical body 42 fitted and fixed inside the end of the drive shaft 4 on the side of the starting clutch 1.
A first valve body 43 which is adjacent to the opposite side of the starting clutch 1 of the bearing cylindrical body 42 and is slidably fitted to the inner peripheral surface of the drive shaft 4 for a predetermined stroke along the axial direction thereof; One end is opposed to the first valve body 43 and the other end is the transmission box 30.
A second valve body 45 that extends into a governor chamber 44 provided on the outer side of one side wall and is slidably fitted to the inner peripheral surface of the drive shaft 4 along the axial direction by a predetermined stroke. The bearing cylindrical body 4
2. It has a third valve body 46 slidably fitted over the inner peripheral surfaces of the first valve body 43 and the second valve body 45.

The bearing cylindrical body 42 is a bottomed short shaft cylindrical body having an opening at one end surface, and is positioned by a stop ring 47 to drive the drive shaft 4.
Liquid-tightly fitted inside. The bearing cylindrical body 42 has a port 48 along the radial direction at a predetermined position on the peripheral side wall thereof.
Reference numeral 48 denotes a first port 49 formed in the peripheral side wall of the drive shaft 4 along the radial direction, and an annular shape between the outer peripheral surface of the drive shaft 4 and the inner peripheral surface of the boss portion of the clutch cylinder 18 of the starting clutch 1. groove
Supply port of the pressure chamber 22 of the starting clutch 1 via 50
It communicates with 24.

The first valve body 43 has a short-axis cylindrical shape with both ends open and a large diameter portion on the outer circumference on one end side, and the outer peripheral surface of the large diameter portion slides liquid-tightly on the inner peripheral surface of the drive shaft 4. The pressure chamber 43 is freely fitted in between the outer peripheral surface of the small diameter portion and the inner peripheral surface of the drive shaft 4.
a is formed. The first valve body 43 has a port 51 opening in the pressure chamber 43a at a predetermined position on the side wall of the small diameter portion thereof along the radial direction.

The second valve body 45 has a long-axis cylindrical shape with both end surfaces open, and has an annular groove 52 extending over a predetermined axial length on the outer peripheral surface of the axially substantially intermediate portion, and is located closer to the first valve body 43 than the annular groove 52. Ports 53 are formed along the radial direction with a predetermined axial length offset. A small diameter spring receiving portion 45 is provided at an end portion of the second valve element 45 on the first valve element 43 side.
a spring receiving member / stopper member 54 which has a spring receiving portion 45a and is fitted to the end face of the first valve body 43 on the second valve body 45 side.
The coil-shaped spring 55 interposed between the first valve body 43 and
Is biased toward the starting clutch 1 and the second valve element 45 is biased toward the counter starting clutch 1. A large-diameter collar portion 45b is integrally formed on the outer circumference of the extension end of the second valve body 45 into the governor chamber 44, and a governor weight 56 is abutted against the collar portion 45b. As the engine speed increases, the governor wheel 56 rotates counterclockwise around the shaft 57 to slide the second valve body 45 toward the starting clutch 1 side against the biasing force of the spring 55. .

The third valve body 46 has a long-axis cylindrical shape in which the end surface on the side of the starting clutch 1 is open and the end surface on the side of the counter starting clutch 1 is closed, and the bearing cylindrical body 42, the first valve body 43, and the second valve body It is fitted to the inner peripheral surface of 45 in a liquid-tight and slidable manner. The third valve element 46 has a first port 58 along the radial direction on the side wall of the start clutch 1 side end, and a second port 59 along the radial direction on the side wall of the start clutch 1 side end. Annular groove 59 along the direction
a is provided for each.

The second port 59 and the annular groove 59a selectively communicate with the port 51 of the first valve body 43 at a predetermined time.

A rod is provided at the end of the repulsion clutch 1 side of the third valve body 46.
One end of 60 is rotatably connected by a pin 61,
The other end is inserted into the pressure fluid conducting pipe 62 having openings at both end faces in a loosely fitted state, extends outwardly, and is rotatably connected to an accelerator control fork 63 by a pin 64.
One end of the pressure fluid communication pipe 62 is fixed to the outer wall of the governor chamber 44, and the other end is fluid-tightly and slidably fitted to the inner peripheral surface of the second valve body 45. The accelerator control fork 63 is provided in a control fork chamber 44a provided outside the governor chamber 44, and rotates about a shaft 65 in conjunction with a throttle (not shown). As the opening is increased, it rotates clockwise in the drawing
The valve body 46 of No. 1 is slid to the repulsion clutch 1 side. Inside the control fork chamber 44a, the pressure fluid conducting pipe 62
Through the inside of the second valve body 45. A ring-shaped stopper 66 is projectingly provided on the outer surface of the peripheral side wall of the third valve body 46, and the stopper 66 serves as a spring receiving member / stopper contact member 54 provided on the first valve body 43 at a predetermined time. By making contact with each other, it is possible to prevent the following delay of the first valve body 43 when the throttle is rapidly closed.

The peripheral side wall of the drive shaft 4 is arranged along the radial direction and sequentially from the substantially intermediate portion in the axial direction toward the repulsion clutch 1 side, the second,
The third, fourth and fifth ports 67, 68, 69 and 70 are bored at predetermined intervals. In the second port 67, when the groove width of the drive shaft pulley C is maximum, that is, when the fixed pulley 33 and the movable pulley 34 are in the most separated state, both pulleys 33, 34 are provided.
They are located approximately in the center of each other and open in the transmission box 30. When the groove width of the drive shaft pulley C is minimum, that is, when the fixed pulley 33 and the movable pulley 34 are closest to each other, the boss portion of the movable pulley 34 covers the opening end of the second port 67. The second port 67
Notch groove for ensuring continuity of the inside of the transmission box 30
71 is formed on the outer periphery of the drive shaft 4. The third port
When the groove width of the drive shaft pulley C is the maximum, 68 is located in the axially substantially intermediate portion of the boss portion of the movable pulley 34, and the third port 68 has the groove width of the drive shaft pulley C that is the minimum. Time,
The movable pulley 34 is located at the end portion of the boss portion of the movable pulley 34 on the repulsion clutch 1 side.

The outer peripheral side opening ends of the third and fourth ports 68 and 69 are the annular groove 72 between the outer peripheral surface of the drive shaft 4 and the inner peripheral surface of the boss portion of the movable pulley 34, and the end surface of the boss portion 34a of the movable pulley 34. And a first pressure chamber 39 between the pulley body 34b of the movable pulley 34 and the flange 36b of the fixed piston member 36 via a gap between the fixed piston member 36 and the inner end surface of the cylindrical body 36a of the fixed piston member 36. When the groove width of the drive shaft pulley C is maximum, that is, when the end surface of the boss portion 34a of the movable pulley 34 contacts the inner end surface of the cylindrical body 36a of the fixed piston member 36, the annular groove 72 and the first pressure chamber 39 are formed. A cutout groove 73 is provided on the end surface of the boss portion 34a to ensure communication between the two. The third port 68 is a port of the second valve body 45.
Communicate with 53 at a specified time. The fifth port 70 is located between the outer end surface of the cylindrical body 36a of the fixed piston member 36 and the bearing 32, and includes the cutout groove 74 in the central boss portion of the outer end surface of the cylindrical body 36a and the guide tube 37. Through the movable pulley 34
Closing plate 34d and the flange 36b of the fixed piston member 36
And communicates with the second pressure chamber 40 between. The fourth port
The 69 and the fifth port 70 communicate with each other at a predetermined time via an annular groove 52 provided on the outer surface of the peripheral side wall of the second valve body 45.

Both ends of a driven shaft 75 are rotatably supported by ball bearings 76, 77 on both side walls of the transmission box 30 on the other end side. The driven shaft 75 located in the box 30
Driven shaft pulley D that can change groove width by fluid pressure control
Is provided. The driven shaft pulley D is the driven shaft.
A fixed pulley 78 integrally formed on the outer circumference of 75 and a plurality of balls 80 facing the fixed pulley 78 and slidably and non-rotatably on the outer circumference of the driven shaft 75 along the axial direction thereof. And a movable pulley 79 fitted together.

In the movable pulley 79, a disk-shaped pulley main body 79b is integrally projectingly provided on the outer periphery of one end side of a cylindrical boss portion 79a. A cylindrical peripheral wall 79c is integrally provided along the inner peripheral surface of the cylindrical peripheral wall 79c, and an annular closing plate 79d is fitted to the inner peripheral surface of the cylindrical peripheral wall 79c on the projecting end side.

A fixed piston member 81 is fitted in the movable pulley 79. The fixed piston member 81 is integrally provided with a taper cylinder portion 81b having a gradually larger diameter on the outer circumference on one end side of the boss portion 81a, and an annular flange 81c is integrated with the large diameter end portion of the taper cylinder portion 81b in the radial direction. It will be projected. The fixed piston member 81 has its boss portion 81a fitted onto the outer periphery of the driven shaft 75 in a non-rotatable and axially immovable manner, and the outer peripheral surface of the flange 81c has a cylindrical shape of the movable pulley 79. It is fitted to the inner peripheral surface of the peripheral wall 79c so as to be liquid-tight and slidable.
The pulley body 79b of the movable pulley 79 and the fixed piston member 8
A coiled spring 82 is interposed between the facing surfaces of the flange 81c of the first flange 81c, and the movable pulley 79 is fixed by the spring 82.
It is urged to the 78 side (the side where the groove width becomes smaller). The spring 82 is for applying an appropriate tension to the belt when the engine is stopped and for setting the movable pulley 79 to the low speed side which is the initial position.

The pulley body 79b of the movable pulley 79 and the fixed piston member 8
1 between the facing surfaces of the tapered cylindrical portion 81b and the flange 81c of the first
It is a pressure chamber 83 and also a closing plate for the movable pulley 79.
A second pressure chamber 84 is formed between the opposed surfaces of 79d and the tapered cylindrical portion 81b of the fixed piston member 81 and the flange 81c. Between the first and second pressure chambers 83 and 84, an orifice 85 bored axially in the boss 81a of the fixed piston member 81, the outer peripheral surface of the boss 81a and the movable pulley 7 are provided.
The nine closing plates 79d communicate with each other through a guide tube 86 whose inner and outer circumferences are loosely fitted.

The guide cylinder 86 is integrally rotatably fitted on the driven shaft 75. The first pressure chamber 83 communicates with a pressure fluid communication path 87 provided along the inside of the shaft center of the driven shaft 75 through a communication hole 88 formed in the peripheral wall of the driven shaft 75 along the radial direction. ing. The pressure fluid passage 87 communicates with the pressure fluid inlet 90 via a pressure fluid passage pipe 89 having both open ends. The pressure fluid conducting pipe 89 has an outer peripheral surface on one end side which is fitted in a liquid tight manner with an inner peripheral surface of the pressure fluid conducting passage 87 of the driven shaft 75. An outer peripheral surface of the pressure fluid conducting pipe 89 on the other end side is fluid-tightly fitted to a wall surface between the bearing 77 and the pressure fluid inlet 90 of the transmission box 30.
The pressure fluid inlet 90 communicates with a pressure fluid supply passage 91 that connects the discharge outlet 29a of the pump 29 and the control fork chamber 44a. The suction port 29b of the pump 29 communicates with a fluid tank 93 via a filter 92.

The upstream side of the pressure fluid inlet 90 of the pressure fluid supply passage 91 is connected to a valve chamber 95a of a regulator valve 95 via a communication passage 94.
It communicates with the inside. The regulator valve 95 keeps the line pressure of the pressure fluid supplied from the pump 29 at a constant value, and a valve body 95b for opening and closing the port 96 is slidably fitted in the valve chamber 95a and A spring 95c for urging the body 95b in the valve closing direction is provided, and the port 96 communicates with the fluid tank 93 via a communication pipe 97. Further, the valve chamber 95a of the regulator valve 95 communicates with the inside of the transmission box 30 via an orifice 98 formed on the side opposite to the communication passage 94. When the supply pressure from the pump 29 is smaller than the biasing force of the spring 95c, the valve body 95b
When 96 is closed and the supply pressure overcomes the biasing force of the spring 95c, the valve body 95b opens the port 96, and a part of the pressure fluid flows to the port 9
6 → It is discharged to the fluid tank 93 through the communication pipe 97. A return pipe 99 for returning the fluid accumulated in the transmission box 30 to the fluid tank 93 is provided between the communication hole 100 on one side wall of the transmission box 30 and the fluid tank 93.

An endless metal (steel) belt 101 is wound between the drive shaft pulley C and the driven shaft pulley D.
The rotational power of the drive shaft pulley C is transmitted to the driven shaft pulley D via 01, and the gear ratio of the belt 101 can be changed steplessly by changing the groove widths of the pulleys C and D. It is like this.

The inner diameter D ₁ of the cylindrical peripheral wall 34c that is the cylinder diameter of the movable pulley 34 of the drive shaft pulley C is the inner diameter D ₁ of the cylindrical peripheral wall 79c that is the cylinder diameter of the movable pulley 79 of the driven shaft pulley D.
It is set to be larger than ₂ , that is, D ₁ > D ₂ .

(Operation) Next, the operation of the automatic clutch and the operation of the starting clutch of the present invention will be described.

(1) At the time of starting As the output shaft of the internal combustion engine rotates, the input side rotating body 5 and the control mechanism 11 rotate together with the input shaft 2 of the starting clutch 1. However, since the pressure of the pressure fluid from the pump 29 does not rise and the number of revolutions of the input shaft 2 is equal to or less than a predetermined set value, the governor ball 14 of the control mechanism 11 has a biasing spring 16 of the cam plate 13 on it.
No centrifugal force is generated to overcome this, and therefore the discharge port 10a of the pressure regulating valve 10 is in an open state (Fig. 2). In addition, the second valve 45 is in the state shown in the figure, and the port 53 of the second valve 45 is in a state in which communication with the third port 68 of the drive shaft 4 is blocked, and the drive shaft pulley is The first pressure chamber 39 of C includes the notch groove 73 of the movable pulley 34 → the annular groove 72 between the drive shaft 4 and the movable pulley 34 → the fourth groove of the drive shaft 4.
Port 69 → annular groove 52 of second valve body 45 → fifth of drive shaft 4
Port 70 → Notch groove 74 of fixed piston member 36 → Guide tube 37
And communicates with the second pressure chamber 40 of the drive shaft pulley C via the path. Further, the third valve body 46 is also in the state shown in the drawing, and its second port 59 is in a state in which communication with the port 51 of the first valve body 43 is blocked. With the passage of time, the pressure fluid from the pump 29 fills the first pressure chamber 83 along the path of the pressure fluid supply passage 91 → the inflow port 90 → the pressure fluid communication pipe 89 → the pressure fluid communication passage 87 → the communication hole 88, and then the pressure is increased. Fluid supply path 91 → control fork chamber 44a → pressure fluid communication pipe 62 → second valve body 45
Inside → First port 58 of third valve body 46 → Inside third valve body 46 → Inside bearing cylinder 42 → Port 48 of bearing cylinder 42 → First port 49 of drive shaft 4 → Drive shaft 4 Although it flows into the pressure chamber 22 of the starting clutch 1 via the annular groove 50 between the clutch cylinder 18 and the supply port 24 of the clutch cylinder 18, the pressure control valve causes the pressure regulating valve to move by the action of the pressure fluid. Since the discharge port 10a is pressed to the side and opened, the pressure fluid is discharged from the discharge port 10a into the governor housing 12. Therefore, the pressure in the pressure chamber 22 of the starting clutch 1 does not rise, and the clutch piston 20 does not press the friction plate 21. Therefore, the rotational power of the input shaft 2 of the starting clutch 1 is not transmitted to the drive shaft 4, so that the driven shaft pulley D as well as the drive shaft pulley C is in a stationary state.

In addition, in the drive shaft pulley C, as described above, the second
Since the port 53 of the valve body 45 is isolated from the third port 68 of the drive shaft 4, the pressure fluid is not supplied into the first pressure chamber 39, and the movable pulley 34 is separated from the fixed pulley 33 to the maximum extent, The groove width of the drive shaft pulley C is maximized as shown.

On the other hand, in the driven shaft pulley D, the pressure fluid supplied from the pump 29 is the pressure fluid supply passage 91 → the pressure fluid inlet 90.
→ Pressure fluid passage pipe 89 → Pressure fluid passage of driven shaft 75
The movable pulley 79 comes closest to the fixed pulley 78 by the pressure fluid and the urging force of the spring 82, and flows into the first pressure chamber 83 via the path of the 87 and the communication hole 88, and the groove of the driven shaft pulley D is moved. The width is the smallest as shown.

Therefore, the belt 101 is in the lowest speed state in which the belt 101 slides on the most center side of the drive shaft pulley C and the most outer peripheral side of the driven shaft pulley D.

(2) At start-up After the engine has been started, the accelerator pedal (not shown) is gradually depressed to start, and the throttle opening is gradually increased, whereby the rotational speed of the internal combustion engine gradually increases and reaches a predetermined rotational speed. The centrifugal force acts on the governor ball 14 so that the cam plate 13 resists the urging force of the spring 16 and the anti-input side rotating body 5
Side, the pressure regulating valve 10 is pushed and moved by the cam plate 13 toward the non-input side rotating body 5 side, and its discharge port 10
A is closed and the supply port 24 is opened by the annular groove 10b (FIG. 4). Therefore, the pressure in the pressure chamber 22 of the starting clutch 1 increases, and the clutch piston 20
Is pushed toward the input side rotating body 5 side, and the friction plate 21 is pushed against the inner end surface of the clutch outer 19 by the clutch piston 20 via the clutch facing 27, whereby the rotational power of the input shaft 2 is driven. 4, the drive shaft pulley C rotates together with the drive shaft 4, and the rotational power of the drive shaft pulley C is transmitted to the driven shaft pulley D via the belt 101 and the driven shaft 75 is integrated with the pulley D. Rotates, the driven shaft 75
The drive wheels (not shown) of the vehicle are rotated at the lowest speed by the rotation of.

(3) Acceleration After starting, when the engine speed rises above a specified value by gradually depressing the accelerator pedal to further increase the speed and gradually increasing the throttle opening, the governor weight 56 moves counterclockwise in the figure. The second valve body 45 is rotated and pushed by the governor weight 56 toward the starting clutch 1 against the biasing force of the spring 55, and the port 53 of the second valve body 45 is moved to the drive shaft 4 side. A fourth port 69 of the drive shaft 4 that is in communicative communication with the third port 68 and that has an annular groove 52 between the drive shaft 4 and the second valve body 45.
And the communication with the fifth port 70 is cut off. Then, the pressure fluid that has flowed into the second valve body 45 through the pressure fluid conducting pipe 62 is transferred to the port 53 of the second valve body 45 → the third port 68 of the drive shaft 4 → the drive shaft 4 and the movable pulley. Inflow into the first pressure chamber 39 between the movable pulley 34 and the fixed piston member 36 via the path of the annular groove 72 between the movable pulley 34 and the boss portion 34a → the cutout groove 73 of the boss portion 34a of the movable pulley 34. Then, the pressure in the first pressure chamber 39 rises, the movable pulley 34 is moved from the state shown in the drawing to the fixed pulley 33 side by the pressure, and the groove width is reduced. It is forcibly moved toward the outer peripheral side of the pulley C. On the other hand, since the cylinder diameter D ₁ of the drive shaft pulley C is set to be larger than the cylinder diameter D ₂ of the driven shaft pulley D,
The surface pressure of the belt 101 on the drive shaft pulley C side is larger than the surface pressure of the belt 101 on the driven shaft pulley D side. Therefore, as the belt 101 on the drive shaft pulley C side moves toward the outer peripheral side, the movable pulley 79 of the driven pulley D receives the surface pressure of the belt 101, and the movable pulley 79 of the driven pulley D is introduced into the inflow port 90 →→ pressure fluid conduction. pipe
89 → Pressure and spring of the pressure fluid flowing into the first pressure chamber 83 between the movable pulley 79 and the fixed piston member 81 via the passage of the pressure fluid communication path 87 of the movable pulley 79 and the communication hole 88.
The belt 101 on the driven shaft pulley D side is moved to the center side against the biasing force of 82, to the fixed pulley 78 side, and the rotation of the driven shaft pulley D changes from a low speed state to a medium / high speed state. Change steplessly. That is, the state in which the belt 101 is positioned at a substantially radial intermediate position between the drive shaft pulley C and the driven shaft pulley D (the groove width is an intermediate state for both the pulleys C and D) is the medium speed state. The highest speed is when the belt 101 on the C side is located on the outermost side (the groove width is the smallest) and the belt 101 of the driven shaft pulley D is located on the center side (the groove width is the largest). Is.

(4) During deceleration The operation opposite to that during acceleration described above is performed, and the drive shaft pulley C
The belt 101 on the side is moved toward the center side and the belt 101 of the driven shaft pulley D is moved toward the outer peripheral side to be decelerated.

(5) During sudden start (during kickdown) In a normal state, that is, when the accelerator pedal is gradually depressed to gradually increase the throttle opening, the accelerator control fork 63 rotates in the clockwise direction in the figure in communication with the accelerator pedal. As a result, the third valve body 46 slightly moves from the state shown in the figure to the repulsion clutch 1 side (lower side in the figure) via the rod 60, and the second port 59 of the third valve body 46 and the second port 59 1 valve body
The port 43 of the 43 valve is slightly communicated with the pressure fluid in the third valve element 46 so that the pressure fluid in the third valve element 46 passes through the second port 59 of the third valve element 46 and the port 51 of the first valve element 43. 4 and the first valve body
A small amount is supplied into the pressure chamber 43a between the pressure chamber 43 and the pressure chamber 43a. When the pressure fluid is supplied to the pressure chamber 43a, the first valve body 43 moves to the repulsion clutch 1 side, and the port of the first valve body 43
The communication between 51 and the second port 59 of the third valve body 46 is cut off,
The first valve body 43 is stationary and fixed at the moved position, and the spring pressure of the spring 55 is increased by the moved amount, so that the action of the governor is slightly limited via the governor weight 56.

Further, when the accelerator pedal is released and the throttle opening is decreased, the accelerator control fork 63 is returned to its original position by communicating with the accelerator pedal, and the port 51 of the first valve body 43 and the third valve Of the valve body 46 is slightly communicated with the annular groove 59a, and the pressure fluid in the pressure chamber 43a passes through the port 51 and the annular groove 59a into the gap between the third valve body 46 and the drive shaft 4. , Is discharged from the second port 67 of the drive shaft 4 into the box 30. When the pressure fluid in the pressure chamber 43a is discharged in this way, the first valve body 43 moves to the starting clutch 1 side (upper side in the drawing), and the communication between the port 51 and the annular groove 59a is cut off.

The movement so far has little effect on the movement of the governor.

However, when the accelerator pedal is rapidly depressed to rapidly increase the throttle opening, the third valve body 46 causes the rebound clutch 1
The second port 59 of the third valve body 46 and the port 51 of the first valve body 43 are in large communication with each other, and thus the pressure chamber
A large amount of pressure fluid is supplied to 43a, and the first valve body 43 is moved to the repulsion clutch 1 side by that much, and the balance between the pressure in the pressure chamber 43a and the spring 55 is greatly disturbed, which greatly affects the movement of the governor. As a result, the governor weight 56 is returned and rotated in the clockwise direction in the figure, and eventually shifts to the deceleration state. The relationship between the degree of communication between the ports 51 and 59, the balance of the governor, and the spring pressure of the spring 55 allows the above-mentioned operation by setting at the design level.

Note that the pressure fluid is discharged into the second pressure chamber 40 of the drive shaft pulley C during deceleration action, but the fluid accumulates on the outer peripheral side of the second pressure chamber 40 due to centrifugal force, and the accumulated oil , The first pressure chamber
A reaction force is applied to the force acting on the flange 36b of the fixed piston member 36 from the 39 side to equalize the load due to the centrifugal force acting on both sides of the flange 36b. Further, also in the driven shaft pulley D, the pressure fluid flows from the first pressure chamber 83 into the second pressure chamber 84 through the orifice 85 and accumulates on the outer peripheral side. The load due to the centrifugal force acting on both sides of the flange 81c of the is equalized.

Furthermore, since the pressure fluid in the first pressure chamber 39 is discharged into the second pressure chamber 40 as described above, the first valve body 43 and the second valve body 45 are again provided with the spring 55 and the governor weight 56. It is said that the pressure fluid in the first pressure chamber 39 is stopped from being discharged into the second pressure chamber 40 by being returned to the original position by the resultant force, and the deceleration operation is stopped, whereby the speed is decelerated too much. It will be prevented.

In the above embodiment, the starting clutch 1 as a whole is divided into two parts, the input side assembly A and the output side assembly B, and the both assemblies A and B are preassembled and then assembled by aligning the centers with each other. As a result, the assemblability can be improved. Furthermore, the control mechanism 11
On the input shaft 2 side, the clutch piston (pressing body) 20 on the output shaft 4 side, and the pressure regulating valve 10 on the clutch cylinder.
Since it is provided near the center boss of 18, the output shaft 4 side does not start rotating unless the rotation speed of the input shaft 2 reaches a predetermined set value when starting, but the clutch 1 is disengaged. Even if the rotation speed of the input shaft 2 reaches a predetermined set value, centrifugal force acts on the clutch piston 20 to maintain the internal pressure and keep the friction plate 21 in a pressed state, The clutch 1 is disengaged only when the rotation speed is reduced. Therefore, the required hiss characteristics can be obtained as shown in FIG.

In the above embodiment, the pump 29 is linked to the output shaft of the engine to generate the fluid pressure having a value proportional to the number of revolutions of the engine. However, the present invention is not limited to this. The pump 29 may be controlled independently of the driving to control the pressing force of the friction plate 21 by the clutch piston 20.

Further, in the above-mentioned actual embodiment, the starting clutch 1 of the present invention is used.
However, the invention is not limited to this, and the invention can be implemented in other devices.

(Effects of the Invention) As described in detail above, the starting clutch of the present invention includes an input side rotating body that rotates integrally with the input shaft, an output side rotating body that rotates integrally with the output shaft, and these input side and output side rotating bodies. The rotary power of the input side rotary body is transmitted to the output side rotary body when it is crimped, and the rotary power of the input side rotary body is transmitted to the output side rotary body when separated. A friction plate that does not transmit, a pressing body that presses the friction plates so that the two rotating bodies can transmit power, and a rotation of the input shaft that is provided between the pressing body and the output side rotating body. A pressure chamber for accommodating the pressure fluid for operating the pressing body, which is supplied from a pressure fluid supply source that generates a pressure fluid having a body-dependent value, and a pressure fluid supply port and a discharge port provided in the pressure chamber. By selectively opening and closing, the pressure in the pressure chamber A pressure regulating valve for adjusting the force; and a control mechanism for controlling the pressure regulating valve so that the pressure in the pressure chamber depends on the rotation speed of the input shaft, and the friction regulating plate and the control mechanism. It is characterized in that it is arranged radially inward.

Therefore, while the structure is simple and compact, it is possible to obtain a sufficient pressing force of the friction plate and prevent seizure of the friction portion during half-clutching. Since there is no need to provide an orifice upstream of the supply port due to the structure of the pressure regulating valve, there is no restriction on the flow rate by the orifice, and therefore, the unit of time per unit time when the pressure regulating valve opens the supply port by the control mechanism. The amount of the pressure fluid flowing into the pressure chamber is large, and as a result, the responsiveness of the pressing body is high, and the friction plate is pressed in a short time so that the input rotating body and the output rotating body can transmit power. There is an advantage that can be done.

BRIEF DESCRIPTION OF THE DRAWINGS The drawings show one embodiment of the present invention, and FIG. 1 is a sectional view of an automatic continuously variable transmission equipped with a starting clutch of the present invention, and FIGS.
FIG. 4 is an enlarged sectional view of an essential part showing the operating state of the starting clutch, FIG. 5 is a diagram showing the relationship between the engine speed and the fluid pressure of the starting clutch of the present invention, and FIG. 6 is the drawing of the present invention. It is a His characteristic diagram of a starting clutch. 1 ... Starting clutch, 2 ... Input shaft, 4 ... Drive shaft (output shaft), 5 ... Input side rotating body, 6 ... Output side rotating body, 10
...... Pressure regulator, 10a …… Discharge port, 10b …… Annular groove, 11…
… Control mechanism, 20 …… Pressing body (clutch piston), 21…
… Friction plate, 22 …… Pressure chamber, 24 …… Pressure chamber supply port,
25: Pressure chamber discharge port (fitting hole), 29: Pressure fluid supply source (pump).

Claims (1)

[Claims] 1. An input side rotating body which rotates integrally with an input shaft, an output side rotating body which rotates integrally with an output shaft, and an input side and an output side rotating body which are interposed between the input side and the output side rotating body so as to be freely separated from each other. A friction plate that transmits the rotational power of the input-side rotary body to the output-side rotary body during crimping and that does not transmit the rotational power of the input-side rotary body to the output-side rotary body during the separation, and the friction plate. A pressing body that presses the rotating body so that the power can be transmitted, and a pressure that is provided between the pressing body and the output side rotating body and that generates a pressure fluid of a value that depends on the rotating body of the input shaft. Pressure inside the pressure chamber by selectively opening and closing the pressure chamber containing the pressure fluid for pressure operation supplied from the fluid supply source and the pressure fluid supply port and discharge port provided in the pressure chamber. The pressure regulator for adjustment and the pressure in the pressure chamber are A control mechanism for controlling the pressure regulating valve so as to depend on the rotational speed of the input shaft, wherein the pressure regulating valve and the control mechanism are arranged radially inward of the friction plate. Starting clutch.