JPH0711294B2 - Launch clutch - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial field of use) The present invention relates to a starting clutch which is incorporated and used in an automatic continuously variable transmission mechanism of a vehicle.

(Prior art and its problems) In the conventional starting clutch, since the friction plate is directly pressed by the force of the governor mechanism, in order to obtain the prescribed transmission torque, the diameter of the governor mechanism becomes large, and normally, In the hydraulic clutch, since the pressing force of the friction plate is directly controlled by controlling the source pressure of the hydraulic pressure, the mechanism becomes complicated and the assemblability is poor.

(Object of the present invention) The present invention has been made in view of the above circumstances, and enables a sufficient pressing force of the friction plate to be obtained while the structure is simple and compact, and the friction during semi-clutching is achieved. An object of the present invention is to provide a starting clutch that can prevent seizure of a part and improve the assemblability.

(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 side rotating bodies. Also, the rotary power of the input side rotary body is interposed between the rotary body and the output side rotary body so that the rotary power of the input side rotary body is transmitted to the output side rotary body when the pressure bonding is performed, and the rotary power of the input side rotary body is separated from the rotary side. Is provided between the pressing body and the output-side rotating body, a friction plate that is not transmitted to the output-side rotating body, a pressing body that presses the friction plate so that both rotating bodies are in a power-transmittable state, In addition, a pressure chamber having a discharge port for discharging the pressure fluid for operating the pressing body and discharging the pressure fluid toward the friction plate side, a pressure control valve for adjusting the pressure in the pressure chamber, and a pressure chamber in the pressure chamber. As the pressure is proportional to the rotation speed of the input shaft A control mechanism for controlling the pressure regulating valve, wherein the control mechanism is incorporated in the input side rotating body to form a part of an input side assembly, and the pressure chamber and the pressure regulating valve are arranged at the output side rotation body. It is incorporated in the body to form a part of the output side assembly, and the input side assembly and the output side assembly are fitted to each other and assembled to generate a pressure fluid having a value proportional to the rotation speed of the input shaft. The pressure fluid supply source is configured to supply the pressure fluid to the pressure chamber.

(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 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 shaft 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 mounted on 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 a cam plate 13 axially slidably fitted in a governor housing 12 fixed to the input side rotating body 5 by a riveting, and a cam surface of the cam plate 13. 13a and a guide surface 12a of the governor housing 12, and a governor ball 14 interposed in the radial direction so as to be slidable in the radial direction. The cam plate 13 includes the cam plate 13 and a spring receiving member 15. A coil-shaped spring 16 interposed between and is urged toward the input side rotating body 5. When the number of rotations of the input shaft 2 is less than a predetermined set value, the governor ball 14 is deviated to 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 number of rotations 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
It is designed to deviate to the output side rotation 6 side against the urging force of 16.

The output side rotating body 6 is spline-fitted to the drive shaft 4 and fixed by a nut 17 to a clutch cylinder 18, and a clutch outer fixed to the outer periphery of the clutch cylinder 18 so as to be immovable both in the circumferential direction and in the axial direction. It consists of 19 and. In the clutch cylinder 18, a clutch piston (pressing body) 20 is fitted so as to be slidable in the axial direction. The clutch piston 20 presses a friction plate 21, which will be described later, and is operated by 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 urged 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 formed along the radial direction at the boss portion of the clutch cylinder 18, and the pressure fluid introduced into the pressure chamber 22 is the clutch piston. It is possible to discharge outward through the pressure regulating valve 10 slidably fitted in a fitting hole (discharge opening of the pressure chamber 22) 25 formed in the boss portion of 20 along the axial direction. It has become. The fitting hole 25 has one end communicating with the supply port 24 and the other end opening to the 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. Therefore, a discharge port 26 is provided.

When the rotation speed of the input shaft 2 is less than a predetermined set value, the pressure regulating valve 10 is displaced toward the input side rotating body 5 side by the action of the pressure fluid introduced from the supply port 24, and the discharge port 26 is opened. However, since the pressure fluid in the pressure chamber 22 is discharged from the discharge port 26, the pressure in the pressure chamber 22 does not rise, and the clutch piston 20 is displaced toward the output side rotating body 6 side by the urging force of the spring 23. is doing. 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 is displaced to the output side rotating body 6 side so that the discharge port 26 is closed and the pressure chamber is closed. The pressure inside 22 is adjusted by the opening ratio between the discharge port 26 and an orifice 48 described later.

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 inside of the end surface of the clutch outer 19 on the input side rotating body 5, and the clutch facing 27 is non-rotatable on the outer periphery of the governor housing 12 in the axial direction. It is fitted to be movable. Then, the friction plate 21 is pressed by the clutch piston 20 against the clutch outer 19 via the clutch facing 27 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. From the discharge port 26 of the pressure regulating valve 10 to the inside of the governor housing 12 and the governor housing 12
The pressure fluid in the pressure chamber 22 discharged between the clutch piston 20 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 during the half-clutching of the single 27. The supply port
Reference numeral 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.

Further, 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 the drive shaft 4 and the output side rotating body 6 are provided.
(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. These assemblies A and B are assembled individually in advance, and then the center of the clutch facing 27 and the governor housing are assembled.
The assembly of the starting clutch 1 is completed by fitting the two assemblies A and B to each other with the center of the assembly 12 aligned, so that the assembling property can be improved accordingly.

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

Next, the structure of the automatic continuously variable transmission 3 provided with the starting clutch 1 of the present invention will be described in detail. The drive shaft 4 is formed of a hollow pipe having openings on both end faces, and both end sides thereof are rotatably supported by ball bearings 31 and 32 on both end side walls of the transmission box 30. The drive shaft 4 is 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 periphery of the drive shaft 4 on the side of the starting clutch 1, and a drive pulley 4 that faces the fixed pulley 33 and slides on the outer periphery of the drive shaft 4 along its axial direction. The movable pulley 34 is movably and non-rotatably fitted through a plurality of balls 35. The movable pulley 34 is integrally provided with a disk-shaped pulley main body 34b on the outer periphery of one end of a cylindrical boss portion 34a, and protrudes in the direction opposite 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 wall thereof fitted into the outer periphery of the drive 4 so as not to be rotatable and axially movable, and the inner peripheral surface of the cylindrical body 36a is the movable pulley. The outer peripheral surface of the flange 36b is loosely fitted to the outer peripheral surface of the boss portion 34a of the rotary shaft 34, and the outer peripheral surface of the flange 36b is a cylindrical peripheral wall 34c of the movable pulley 34.
Is fitted in a liquid-tight manner and slidably on the inner peripheral surface of the. 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 One end of the cylinder 37 has a mounting flange portion 37a on the outer periphery thereof, which is mounted on the inner surface of one side wall of the transmission box 30 with a bolt 38.

The pulley body 34b of the movable 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 along the axial direction by a predetermined stroke; One end is opposed to the first valve body 43 and the other end is connected to 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, the first valve body 43 and the second valve body 45, and a third valve body 46 slidably fitted over the inner peripheral surfaces thereof.

The bearing cylindrical body 42 is in the form of a bottomed short shaft cylinder having an open end, and is positioned by a stop ring 47 to drive the drive shaft 4
Liquid-tightly fitted inside. The bearing cylindrical body 42 has an orifice 48 extending in a radial direction at a predetermined position on a circumferential side wall of the bearing cylindrical body 42. The orifice 48 has a first port 49 and a first port 49 formed in a circumferential side wall of the drive shaft 4 along the radial direction. It communicates with the supply port 24 of the pressure chamber 22 of the starting clutch 1 through an annular groove 50 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.

The first valve element 43 has a short-axis cylindrical shape with both ends open and a large diameter portion on the outer circumference at one end side, and the outer peripheral surface of the large diameter portion is liquid-tight and slidable on the inner peripheral surface of the drive shaft 4. The pressure chamber 43a between the outer peripheral surface of the small diameter portion and the inner peripheral surface of the drive shaft 4.
Are formed. A port 51 opening to the pressure chamber 43a is bored along a radial direction at a predetermined location on the side wall of the small diameter portion of the first valve body 43.

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 deviation of a predetermined axial length. 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 coil-shaped member having a spring receiving portion 45a and a spring receiving member / stopper abutting member 54 fitted to the end face of the first valve body 43 on the second valve body 45 side. The spring 55 urges the first valve element 43 toward the starting clutch 1 side and the second valve element 45 toward the counter starting clutch 1 side. The second valve body
A large-diameter flange portion 45b is integrally formed on the outer periphery of the extension end of the 45 into the governor chamber 44, and a governor weight 56 abuts on the flange portion 45b. The governor weight 56 rotates counterclockwise around the shaft 57 as the engine speed increases, and slides the second valve body 45 to the starting clutch 1 side against the biasing force of the spring 55. To move.

The third valve body 46 has a long-axis cylindrical shape in which the end face on the starting clutch 1 side is open and the end face on the repulsing clutch 1 side 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 manner and slidably. A first port 58 along the radial direction on the side wall of the repulsion clutch 1 side end of the third valve body 46, and a second port 59 along the radial direction on the side wall of the start clutch 1 side end portion. 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 third valve body 46 on the repulsion clutch 1 side.
One end of 60 is rotatably connected by a pin 61, and the rod 60
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 degree is increased, the third valve body 46 is rotated clockwise in the drawing to slide the third valve body 46 toward the repulsive clutch 1. Inside the control fork chamber 44a is the pressure fluid conducting pipe 6
It communicates with the inside of the second valve body 45 via 2. A ring-shaped stopper 66 is provided on the outer surface of the peripheral side wall of the third valve element 46, and the stopper 66 also serves as a spring receiving member and a stopper contact member 54 provided on the first valve element 43 at a predetermined time. By contacting, it is possible to prevent the follow-up delay of the first valve body 43 at the time of sudden closing of the throttle.

The drive shaft 4 has a second side wall extending in the radial direction along the radial direction of the drive shaft 4 toward the repulsion clutch 1 side from a substantially middle portion in the axial direction.
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. Second port 67
Notch groove to secure continuity into 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,
It is located at the end portion on the repulsive clutch 1 side of the boss portion of the movable pulley 34.

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
It communicates with the second pressure chamber 40 between the closing plate 34d and the flange 36b of the fixed piston member 36. The fourth port 69
The fifth port 70 and the fifth port 70 communicate with each other at a predetermined time through 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 and 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 that are slidable and non-rotatable along the axial direction on the outer circumference of the driven shaft 75 so as to face the fixed pulley 78. And a movable pulley 79 fitted together.

In the movable pulley 79, a disk-shaped pulley main body 79b is integrally projectingly provided on an outer periphery of one end side of a cylindrical boss portion 79a, and the main body 79b has a radial direction substantially intermediate portion on a surface opposite to the fixed pulley 78 side in the axial direction. A cylindrical peripheral wall 79c is integrally formed along the above, and an annular closing plate 79d is fitted to the inner peripheral surface of the cylindrical peripheral wall 79c on the projecting end side to form a drum shape.

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 such that it cannot rotate and cannot move in the axial direction, and the outer peripheral surface of the flange 81c is the 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 connected to the pressure chamber 83, and a closing plate for the movable pulley 79.
A second pressure chamber 84 is formed between the facing 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 axially bored 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.
They are communicated with each other through a guide tube 86 in which the inner and outer peripheral surfaces are loosely fitted to the closing plate 79d of 9.

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 circumferential 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 port 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 the 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. A spring 95c for urging the valve 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 opposite side of the communication passage 94. When the supply pressure from the pump 29 is smaller than the biasing force of the spring 95c, the valve 96b causes the port 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 96c.
→ It is discharged to the fluid tank 93 via the communication pipe 97. Also,
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 is changed steplessly by changing the groove widths of the pulleys C and D. You can do it.

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 starting clutch of the present invention and the operation of the automatic continuously variable transmission will be described.

(1) At start-up The input side rotating body 5 and the control mechanism 11 rotate together with the input shaft 2 of the starting clutch 1 as the output shaft of the internal combustion engine rotates.
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 lower than a predetermined set value, the governor ball 14 of the control mechanism 11 has an urging spring of the cam plate 13 attached thereto.
The centrifugal force that overcomes 16 is not generated, so the pressure regulating valve 10
The discharge port 26 is open. In addition, in the illustrated state, the second valve 45 is
Communication with the third port 68 of the drive shaft 4 is cut off, and the first pressure chamber 39 of the drive shaft pulley C has the cutout groove 73 of the movable pulley 34 → the drive shaft 4 Annular groove 72 with the movable pulley 34 → fourth port 69 of the drive shaft 4 → annular groove 52 of the second valve element 45 → fifth port 70 of the drive shaft 4 → notch groove 74 of the fixed piston member 36 → guide It communicates with the second pressure chamber 40 of the drive shaft pulley C via the path of the cylinder 37. Further, the third valve body 46 is also in the illustrated state, and the second port 59 is in a state in which the 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 through the pressure fluid supply passage 91 → inlet 90 → pressure fluid communication pipe 89 → pressure fluid communication passage 87 → communication hole 88, and then the pressure is increased. Fluid supply path 91 → control fork chamber 44a →
Pressure fluid communication pipe 62-> inside second valve body 45-> third valve body 46
First port 58 → in the third valve body 46 → in the bearing cylindrical body 42 → orifice 48 of the bearing cylindrical body 42 → first port 49 of the drive shaft 4 →
The annular groove 50 between the drive shaft 4 and the clutch cylinder 18 → flows into the pressure chamber 22 of the starting clutch 1 via the path of the supply port 24 of the clutch cylinder 18, but the pressure regulating valve 10 is operated by the action of the pressure fluid. Since the discharge port 26 is opened by being pressed by the input side rotator 5, the pressure fluid is discharged from the discharge port 26 to the inside of 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. For this reason,
Since the rotational power of the input shaft 2 of the start clutch 1 is not transmitted to the drive shaft 4, the drive shaft pulley C and the driven shaft pulley D
Is stationary.

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 outermost side of the driven shaft pulley D.

(2) Start-up After the engine is started, the accelerator pedal (not shown) is gradually depressed to start, and the throttle opening is gradually increased to gradually increase the rotational speed of the internal combustion engine and reach 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
The pressure regulating valve 10 is pushed and moved by the cam plate 13 toward the non-input side rotating body 5 side, and the discharge port 26 thereof is pushed.
Is blocked. Therefore, the pressure in the pressure chamber 22 of the starting clutch 1 rises, the clutch piston 20 is pushed and moved by the pressure toward the input side rotating body 5, and the clutch piston 20 causes the friction plate 21 to move the clutch facing 27. It is pressed against the inner end surface of the clutch outer 19 via this, the rotational power of the input shaft 2 is transmitted to the drive shaft 4, the drive shaft pulley C rotates together with the drive shaft 4, and the rotational power of the drive shaft pulley C becomes the belt. The pulley D is transmitted to the driven shaft pulley D via 101.
The driven shaft 75 rotates integrally with the driven shaft 75, and the rotation of the driven shaft 75 causes the drive wheels (not shown) of the vehicle to rotate at the lowest speed.

(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 turns counterclockwise in the figure. Move and take the governor weight 56 second
Valve body 45 of the second valve body 45 is pushed and moved toward the starting clutch 1 side against the biasing force of the spring 55 so that the port 53 of the second valve body 45 and the third port 68 of the drive shaft 4 communicate with each other, and 4 port of the drive shaft 4 through the annular groove 52 between the No. 4 and the second valve body 45
The communication between 69 and the fifth port 70 is cut off. Then, the pressure fluid that has flowed into the second valve body 45 via the pressure fluid conducting pipe 62 is transferred from the port 53 of the second valve body 45 to the third portion of the drive shaft 4.
Port 68 → Between the movable pulley 34 and the fixed piston member 36 via the path of the annular groove 72 between the drive shaft 4 and the boss portion 34a of the movable pulley 34 → the cutout groove 73 of the boss portion 34a of the movable pulley 34. Flowing into the first pressure chamber 39, the pressure in the first pressure chamber 39 rises, the movable pulley 34 is moved from the state shown in the figure to the fixed pulley 33 side by the pressure, and the groove width decreases, With the decrease, the belt 101 is forcibly moved toward the outer peripheral side of the drive shaft 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 that on the driven shaft pulley D side. It is larger than the surface pressure of the belt 101. Therefore, as the belt 101 on the side of the drive shaft pulley C moves toward the outer peripheral side, the movable pulley 79 of the driven shaft pulley D receives the surface pressure of the belt 101 and moves from the inlet 90 to the pressure. Fluid communication pipe 89 → pressure fluid communication path 87 and communication hole of movable pulley 79
To the side opposite to the fixed pulley 78 side against the pressure of the pressure fluid flowing into the first pressure chamber 83 between the movable pulley 79 and the fixed piston member 81 via the path of 88 and the biasing force of the spring 82. The belt 101 on the driven shaft pulley D side is moved to the center side, and the rotation of the driven shaft pulley D continuously changes from a low speed state to a medium / high speed state. 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 (maximum groove width) and the belt 101 on the driven shaft pulley D side is located on the most center side (minimum groove width). It is in a state.

(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 on the side of the driven shaft pulley D is moved toward the outer peripheral side to be decelerated.

(5) When the vehicle suddenly starts (during down), 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 conjunction with the accelerator pedal. As a result, the third valve element 46 slightly moves from the state shown in the figure to the repulsive clutch 1 side (lower side in the figure) through the rod 60, and the second port 59 of the third valve element 46 and the first port Valve body
The pressure fluid in the third valve body 46 is in slight communication with the port 51 of the drive valve 43 of the drive valve 4 via the second port 59 of the third valve body 46 and the port 51 of the first valve body 43. And the first valve body 43
A small amount is supplied into the pressure chamber 43a between 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 51 of the first valve body 43 and the second port 59 of the third valve body 46. The communication with the first valve body 43 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, and the action of the governor is exerted via the governor weight 56. Is a little limited.

When the accelerator pedal is released and the throttle opening is reduced, the accelerator control fork 63 is returned to its original position in conjunction 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 (the 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 depressed rapidly to increase the throttle opening rapidly, the third valve body 46 causes the repulsion clutch 1 to move.
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 into the 43a, and the first valve body 43 is moved to the repulsion clutch 1 side by that much, and the balance of the pressure in the pressure chamber 43a and the spring 55 is greatly disturbed. The governor weight 56 is rotated back in the clockwise direction in the figure, and the deceleration state is brought about. 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 is accumulated in 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 via 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 81 is made uniform.

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, that is, the input side assembly A and the output side assembly B, and both assemblies A and B are assembled in advance, and then they are assembled by aligning their 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 input side only rotates when starting, and the output shaft 4 side does not start to rotate unless the rotation speed of the input shaft 2 reaches a predetermined set value, but when the clutch 1 is turned off. 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 the pressed state.
The clutch 1 is not cut off until the rotation speed of the clutch 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 driving to control the pressing force of the clutch piston 20 on the friction plate 21.

Further, in the above embodiment, the case where the starting clutch 1 of the present invention is incorporated in the automatic continuously variable transmission has been described.
The present invention is not limited to this, and can be implemented by being incorporated in another device.

(Effects of the Invention) As described in detail above, the starting clutch of the present invention is simple and compact in structure, yet can sufficiently obtain the pressing force of the friction plate, and prevents seizure of the friction portion during the half-clutch. It can be prevented in advance, and further, the assembling property can be improved.

[Brief description of drawings]

1 is a sectional view of an automatic continuously variable transmission equipped with a starting clutch of the present invention, and FIG. 2 is a His characteristic diagram of the starting clutch of the present invention. A: Input side assembly, B: Output side assembly, 1 ... Start clutch, 2 ... Input shaft, 5 ... Input side rotating body, 6 ... Output side rotating body, 10 ... Pressure regulating valve, 11 ... … Control mechanism, 20 …… Pressing body (clutch piston), 21 …… Friction plate, 22 …… Pressure chamber, 25 …… Pressure chamber discharge port (fitting hole), 29 …… Pressure fluid supply source (pump)

Claims (1)

[Claims] 1. An input-side rotating body that rotates integrally with an input shaft, an output-side rotating body that integrally rotates with an output shaft, and a contact-separable interposed member between the input-side rotating body and the output-side rotating body. And a friction plate in which the rotational power of the input side rotating body is transmitted to the output side rotating body during the pressure contact and the rotational power of the input side rotating body is not transmitted to the output side rotating body during the separation. A pressing body that presses the two rotating bodies so that power can be transmitted to both of the rotating bodies, and the pressure fluid for operating the pressing bodies that flows between the pressing body and the output side rotating body flows in and out. A pressure chamber having a discharge port for discharging the pressure fluid toward the friction plate side, a pressure regulating valve for regulating the pressure in the pressure chamber, and the pressure regulating valve so that the pressure in the pressure chamber is proportional to the rotation speed of the input shaft. And a control mechanism for controlling
The control mechanism is incorporated into the input side rotating body so as to be rotatable integrally with the input side rotating body and movable in the axial direction of the input side rotating body, and constitutes a part of the input side assembly together with the input shaft. The pressure regulating valve is incorporated in the output side rotating body so as to be able to rotate integrally with the output side rotating body, and the opening degree can be changed by moving in the axial direction of the output side rotating body. A part of the output side assembly together with the friction plate, and the input side assembly and the output side assembly are fitted and assembled with each other, and a pressure fluid having a value proportional to the rotation speed of the input shaft is generated. A starting clutch, characterized in that the pressure fluid can be supplied to the pressure chamber by a pressure fluid supply source.