KR101649878B1 - Clutch module actuator for automatic transmission - Google Patents

Abstract

The present invention relates to an actuator to drive a clutch module to perform a one-way clutch function and a low & reverse brake function in an automatic transmission of a vehicle. The present invention provides a clutch module actuator for an automatic transmission, which realizes a new type of a hydraulic actuator mixing one pressure line and two check valves so as to control operation of a clutch module to perform a one-way clutch function and a low & reverse brake function in multiple stages, thereby improving control and operation efficiency by accurately performing various positions under various pressure ranges as well as simplifying a structure.

Description

Clutch module actuator for automatic transmission < RTI ID = 0.0 >

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch module actuator of an automatic transmission, and more particularly, to an actuator that drives a clutch module that performs a one-way clutch function and a low & reverse brake function in an automatic transmission of a vehicle.

In general, automatic transmission is an automation system in which a clutch and a transmission are replaced by a machine instead of a man, and the power generated by the engine is automatically changed to change the rotational speed and the rotational force to drive the wheel.

There are two main types of automatic transmissions: a front-wheel drive automatic transmission and a rear-wheel drive automatic transmission.

The automatic transmission includes a torque converter that transmits the rotational force of the engine to the transmission, and a torque converter that is hydraulically operated in accordance with the position of the selector lever of the driver. The automatic transmission transmits the driving force of the input shaft to the planetary gear. The front clutch, rear clutch, , A kick-down brake, a one-way clutch, and a planetary gear that is driven by an operating element in the clutch and brake and transmits rotational force to the wheels in the first and fourth steps and shifts backward, And an electronic control unit for controlling the hydraulic pressure applied to the clutch and brake by driving the solenoid valve by inputting to the TCU.

Each component of the automatic transmission will be described in detail as follows.

The torque converter serves as a fluid coupling role and a torque increasing function, and includes a pump (drive shaft), a turbine (driven shaft), a stator, and the like.

Therefore, when the engine rotates, the converter pump also rotates to extract the oil from the center portion and discharge to the wing, and the oil discharged from the pump strikes the wing of the turbine, so that the force for rotating the turbine is transmitted.

The stator then turns the direction of rotation of the oil to the same direction as the direction of rotation of the pump and the force of the oil to rotate the turbine .

The force of oil flowing out of the turbine into the stator vane tries to rotate the stator counterclockwise, but the one-way clutch prevents this.

The front clutch is composed of a retainer, a disk, a plate, and a piston in a multi-plate type. When the front clutch is operated, the front clutch transmits the driving force from the input shaft to the planetary gearset reverse sun gear and operates at three speeds .

The rear clutch is composed of a retainer, a disk, a plate and a piston in a multi-plate type. When the rear clutch is operated, the rear clutch transmits a driving force from an input shaft to a forward sun gear of a planetary gear set. , And 3 speeds (including L range 1 speed).

The end clutch is composed of a multi-plate type re-denier, a disk, a plate, and a piston. When the end clutch is operated, the end clutch transmits the driving force from the input shaft to the planetary gear set carrier. , And it works in actual 3 and 4 speeds.

The low / reverse brake has a multi-plate type, and is constituted by a center support, a disk, a plate and a piston, and the brake plate is mounted on the transmission housing.

The operation of this low / reverse brake operates at first speed and reverse of the L-rage to transmit the power of the carrier of the planetary gear set, that is, the pinion of the long pinion and the short pinion.

The kick down brake (Kick Down Brake) It is composed of band type, K / D brake bend, drum, servo piston, anchor rod, servo switch and so on.

The operation of the kick-down brakes operates in the second and fourth speeds and, in operation, the kick-down bands lock the reverse sun gear of the planetary gear set with drums connected to the kick-down drum.

The One-Way Clutch is of a sprag type, assembled between the carrier of the planetary gear set and the center support, and the other is assembled to the stator of the torque converter.

When the one-way clutch in the planetary gear set is D or a first range of 2 ranges, since the long pinion rotates in the clockwise direction, the carrier is prevented from rotating in the counterclockwise direction when viewed from the direction of the arrow " To the annular gear of the planetary gear set.

Therefore, the carrier coupled with the out-race of the one-way clutch can rotate only in the clockwise direction, so that the carrier revolves clockwise from the annular gear side in the case of the D or 2 range first speed or engine brake, So that the shift between the first and second gears is smooth.

Such an automatic transmission has various structures disclosed in Korean Registered Utility Model No. 20-0372627 and Korean Patent No. 10-1428368.

The present invention eliminates the conventional clutch type in which the vehicle fuel economy is greatly reduced due to the spring resistance occurring during the idling operation of the one-way clutch and the contact resistance between the friction materials during the idling operation of the low & reverse brakes, And an actuator for driving a clutch module that integrates a function and a low & reverse brake function in multiple stages.

SUMMARY OF THE INVENTION Accordingly, the present invention has been made in view of the above circumstances, and it is an object of the present invention to provide a hydraulic control apparatus and a control method for controlling the operation of a clutch module performing a one-way clutch function and a low & The object of the present invention is to provide a clutch module actuator of an automatic transmission capable of improving control and operation efficiency, such as simplifying the structure and accurately performing various positions under various pressure ranges by implementing a new type of hydraulic actuator.

In order to achieve the above object, a clutch module actuator of an automatic transmission provided in the present invention has the following features.

The clutch module actuator of the automatic transmission includes a piston rod and a cylinder which are operated by a hydraulic pressure type. In the cylinder, a first fluid passage and a second fluid passage, which are connected between an inlet and an oil pressure chamber, And a first bypass passage and a second bypass passage are respectively connected between the first fluid passage and the second fluid passage, and one of the first bypass passage and the second bypass passage is supported by a spring A first check ball and a second check ball are provided in the piston rod of the piston rod, and a fluid hole is formed in the piston portion of the piston rod to allow the space in front of the piston portion of the hydraulic chamber and the space in the rear portion of the piston portion to communicate with each other.

Therefore, the clutch module actuator of the automatic transmission has various features such as being able to perform various positions stepwise and accurately under various pressure ranges, and to increase the efficiency of control and operation.

Here, the first fluid passage may communicate with the space in front of the piston portion of the hydraulic chamber, and the second fluid passage may communicate with the space behind the piston portion of the hydraulic chamber.

The first bypass passage and the second bypass passage may be formed in parallel to each other across the first fluid passage and the second fluid passage which are arranged in parallel with each other.

The first check ball may be disposed in a direction that can interrupt the flow of the fluid that is about to flow toward the first fluid passage from the second fluid passage, It can be arranged in a direction in which the flow of the fluid to flow toward the passage can be interrupted.

The first check ball and the second check ball may be set to be opened at different pressures, wherein the first check ball may be set to open at 6.1 to 6.9 bar, preferably 6.5 bar, The check ball may be set to open at 0.1 to 0.9 bar, preferably at 0.1 bar.

As a preferred embodiment, the clutch module actuator of the automatic transmission includes means for directly operating the clutch module side, a rod housing coupled to the front end portion of the cylinder while receiving the piston rod along the axial line, And a return spring which is disposed around the piston rod inside the cylinder and elastically supports the piston rod to the return position. The lever housing rotates while being coupled to the piston rod in a concentric manner and moves the clutch module side using a lever on one side of the outer circumference, .

The rod housing is formed with a spiral slit having a locus inclined along the longitudinal direction of the housing. A linear slit is formed in the lever housing along the longitudinal direction of the housing. The piston rod is passed through the spiral slit and the linear slit It is preferable that the piston rod can be operated forward and backward in parallel with the linear motion and the rotational motion.

The clutch module actuator of the automatic transmission provided by the present invention has the following advantages.

In the automatic transmission of a vehicle, when a clutch module that performs a one-way clutch function and a low & reverse brake function is operated, different hydraulic pressures are provided to precisely control various positions corresponding to respective hydraulic pressures, for example, three positions By implementing a new hydraulic actuator, it is possible to ensure excellent operability and control efficiency by effectively controlling each mode of the clutch module while having a minimal number of components and a simple structure.

1 and 2 are perspective views illustrating a clutch module actuator according to an embodiment of the present invention.
3 is a cross-sectional view illustrating a clutch module actuator according to an embodiment of the present invention;
FIG. 4 is a perspective view showing the mounting state of the clutch module actuator according to the embodiment of the present invention. FIG.
5 is a cross-sectional view showing a state of operation of a one-way clutch from a lift to a clutch module actuator according to an embodiment of the present invention
6 is a cross-sectional view showing a one-way clutch-lock operation state of the clutch module actuator according to an embodiment of the present invention
FIG. 7 is a cross-sectional view showing a lock-to-one-way clutch operation state of the clutch module actuator according to the embodiment of the present invention;
8 is a cross-sectional view showing the one-way clutch to lift operation state of the clutch actuator of the embodiment of the present invention
9 is a front view showing an operating state of the clutch module in the lift mode operation of the clutch module actuator according to the embodiment of the present invention;
10 is a front view showing an operating state of the clutch module in one-way clutch mode operation of the clutch module actuator according to the embodiment of the present invention;
11 is a front view showing an operating state of the clutch module in the lock mode operation of the clutch module actuator according to the embodiment of the present invention;

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

1 to 3 are a perspective view and a cross-sectional view illustrating a clutch module actuator according to an embodiment of the present invention, and FIG. 4 is a perspective view illustrating an installed state of a clutch module actuator according to an embodiment of the present invention.

1 to 4, the clutch module actuator rotates the cam ring 110 of the clutch module 100 and is fixed to one side of the outer circumferential surface of the hub outer race 120.

That is, a pair of race brackets 130 are formed on one side of the outer peripheral surface of the hub outer race 120, a cylinder bracket 29 is formed on both ends of the cylinder 11 of the clutch module actuator, The cylinder 11 of the clutch module actuator can be installed on the hub outer race 120 in a structure in which the hub 130 and the cylinder bracket 29 are fastened together with bolts.

The cylinder 11 of the clutch module actuator installed in this manner can take an attitude looking forward from the upper side of the hub outer race 120 while having an axis parallel to the axis of the hub outer race 120.

The clutch module actuator includes a rod housing 22 and a cylinder 11 coupled to each other and a piston rod 10 extending from the inside of the cylinder 11 through the rod housing 22 while being extended to the outside, A lever housing 24 coupled to an outer periphery of the housing 22, and the like.

The cylinder 11 and the piston rod 10 are operated by hydraulic pressure such as oil pressure or air pressure and the oil pressure supplied to the cylinder 11 causes the piston rod 10 It is possible to move back and forth while rotating.

A return spring 25 is mounted in the cylinder 10 and the return spring 25 is formed on the inner wall surface of the rod housing 22 and the rod portion 10b of the piston rod 10 And is supported at both ends between the spring support plates 30 to provide a restoring force for backward movement of the piston rod.

For example, when the hydraulic pressure is not supplied to the inside of the cylinder 10, the restoring force of the return spring 25 can maintain the initial position where the piston rod 10 is retracted backward. As a result, 10, the lever housing 24 and the cam ring 110, which will be described later, can also maintain the initial position.

Of course, in the case of the piston rod 10, the piston rod 10 may be of the type that is reciprocated by the hydraulic pressure supplied to the cylinder 11, the advance by the hydraulic pressure supplied to the cylinder 11 and the reverse type by the restoring force of the return spring 25 .

Particularly, the piston rod 10 is not merely moved forward and backward, but has a characteristic of moving back and forth while rotating.

For this, a spiral slit 26 having loci inclined along the longitudinal direction of the case is formed on both side surfaces of the rod housing 22, and a pin 28, which is perpendicular to the rod axis, And both ends of the pin 28 are coupled to the lever housing 24 side which is coupled to the outer circumferential surface of the rod housing 22 through the spiral slit 26 in the rod housing 22. [

That is, on both sides of the lever housing 24, there is formed a linear slit 27, which is formed by cutting off a predetermined length from the front end side to the rear end side, and the linear slit 27 is passed through the spiral slit 26 The end of the pin 28 is caught.

As a result, the piston rod 10 is linearly moved simultaneously with rotation through the pin 28 guided along the helical slit 26, and the rotation and forward / backward movement of the piston rod 10 and the pin 28 The lever housing 24 can be rotated by the operation.

Here, the pin 28 may be integrally formed with the cylinder rod 10, or may be integrally coupled to the cylinder rod 10.

When the piston rod 10 is advanced or retracted, the pin 28 is guided along the helical slit 26 and can be rotated. As a result, the piston rod 10 is rotated So that the lever housing 24 can be rotated.

The lever housing 24 is a means for substantially actuating the cam ring 110 on the clutch module side and is connected concentrically to the outer circumferential surface of the rod housing 22 and is connected to the pin 28 on the piston rod 10 side And can be rotated around its own axis while being coupled.

A lever 23 protrudes from one side of the outer circumferential surface of the rod housing 22. The lever 23 is positioned inside the lever holder 140 in the cam ring 110. [

Accordingly, when the rod housing 22 rotates, the lever 23 pushes or pulls the lever holder 140 in the cam ring 110, so that the cam ring 110 can be rotated.

At this time, the cam ring 110 can be reciprocally rotated within a range of 0 to 10 degrees. For example, the cam ring 110 is inclined by 3.5 degrees from the vertical line passing through the center line of the cam ring 110, And can be rotated in two steps within the range.

That is, the cam ring 110 is rotated by one step from the position of -3.5 ° to the position of 0 °, and then rotated two steps from the position of 0 ° to the position of 3.5 °, And then rotates in two steps from the 0 ° position to the -3.5 ° position.

When the hydraulic pressure is supplied to the cylinder 11 by the output control of a controller (not shown) that receives a speed change signal as input, the clutch module actuator as described above moves forward and rotates the piston rod 10 → rotates the lever housing 24 The cam ring 110 can be operated in the order of rotation.

At this time, the clutch module actuator can be of a type in which the advance and rotation strokes of the piston rod 10 can be adjusted according to the oil pressure supplied to the cylinder 11, for example, the oil pressure.

For example, an oil pressure of about 4 to 8 bar, preferably 6 bar, is supplied to the cylinder 11 in the first stage, and an oil pressure of about 9 to 11 bar, preferably 10 bar, And a hydraulic pressure of 0 bar is supplied in the second to sixth stages.

Therefore, the forward and reverse strokes of the piston rod 10, the reverse stroke and the rotation stroke of the piston rod 10 are changed according to the intensity of the oil pressure supplied at each gear position, and the rotational angle of the cam ring 110 is also varied. The restoring force of the spring 25 enables the entire cam ring 110 including the piston rod 10 to be returned to the initial position (-3.5 DEG position).

The multi-step operation control for each shift mode of the clutch module actuator will be described in more detail as follows.

A hydraulic chamber 13 in which the piston portion 10 of the piston rod 10 is positioned is formed in the cylinder 11 of the clutch module actuator and the hydraulic chamber 13 at this time is formed with the piston portion 10 as a reference The front space 13a of the piston part and the rear space 13b of the piston part can be distinguished.

The front space 13a of the piston part and the rear space 13b of the piston part can communicate with each other by a plurality of fluid holes 21 formed in the piston part 10. [

An inlet 12 is formed in the bottom surface of the cylinder 11 to allow fluid to flow in and out, for example, and oil supplied from an external hydraulic pressure source (not shown) flows in through the inlet 12, And the oil on the side of the oil pressure chamber 13 can be discharged from the cylinder.

A first fluid passage 14 and a second fluid passage 15 are formed in the cylinder 11 so as to connect between the inlet 12 and the hydraulic chamber 13.

The first fluid passage (14) and the second fluid passage (15) are arranged in parallel to each other and connected to the hydraulic chamber (13) side.

That is, one of the first fluid passages 14 communicates with the space 13a in front of the piston portion of the hydraulic chamber 13, and one of the second fluid passages 15 communicates with the rear portion of the piston 13 of the hydraulic chamber 13 And communicates with the space 13b.

At this time, the other side of the first fluid passage 14 communicates with the side of the entrance 12, and the other side of the second fluid passage 15 communicates with the side of the first bypass passage 16, which will be described later.

Accordingly, the fluid introduced through the entrance 12 can be supplied to the interior of the hydraulic chamber 13 through the first fluid passage 14, and the fluid in the interior of the hydraulic chamber 13 2 fluid passage 15 to the exit 12 side.

Of course, depending on the pressure of the fluid, the fluid introduced through the inlet 12 can be supplied to the hydraulic chamber 13 via the second fluid passage 15, and the fluid in the hydraulic chamber 13 can be supplied to the first fluid passage It is possible to escape to the entrance 12 side via the door 14.

A first bypass passage 16 and a second bypass passage 17 are connected between the first fluid passage 14 and the second fluid passage 15, respectively.

That is, the first bypass passage 16 and the second bypass passage 17 intersect at right angles between the first fluid passage 14 and the second fluid passage 15, At this time, the first bypass passage 16 and the second bypass passage 17 are arranged side by side.

This allows the fluid to flow from the first fluid passage 14 side to the second fluid passage 15 through the first bypass passage 16 and through the second bypass passage 17 The flow of the fluid from the second fluid passage (15) side to the first fluid passage (14) can be made.

The first bypass passage (16) and the second bypass passage (17) are each provided with a check valve device as a means for interrupting the flow of fluid in one direction.

For example, a first check ball 19 is provided at one end of the first bypass passage 16, that is, at an end communicating with the first fluid passage 14, and a first check ball 19 The first check ball 19 is urged by the resilient force of the spring 18a so that the first check ball 19 is urged toward the first fluid passage 14 side communication portion 16b of the first bypass passage 16, As shown in Fig.

The first check ball 19 is disposed in the direction of interrupting the flow of the fluid which is going to flow from the side of the second fluid passage 15 toward the side of the first fluid passage 14, The fluid movement to the fluid passage 15 is enabled but the fluid movement to the contrary becomes possible.

A second check ball 20 is installed at one end of the second bypass passage 17, that is, at an end communicating with the second fluid passage 15, and the first check ball 20 The second check ball 20 is supported by the spring 18b so that the second bypass passage 17 communicates with the second fluid passage 15 through the opening 18a, .

Since the second check ball 20 is disposed in the direction for interrupting the flow of the fluid flowing from the first fluid passage 14 toward the second fluid passage 15 in this way, Fluid movement to the fluid passage 14 is enabled but fluid movement to the contrary becomes possible.

The first check ball 19 and the second check ball 20 can be set to be opened and opened at different pressures.

For example, the first check ball 19 installed in the first bypass passage 16 may be set to open at 6.1 to 6.9 bar, preferably 6.5 bar, and the second bypass passage 17 ) Can be set to be opened at 0.1 to 0.9 bar, preferably 0.1 bar.

As a result, it is possible to set the diameter of the spring supporting the first check ball to be larger than the diameter of the spring supporting the second check ball, And the like.

Therefore, the operating state of the clutch module actuator having the above structure will be described below.

5 is a cross-sectional view showing a state of operation of a one-way clutch from a lift to a clutch module actuator according to an embodiment of the present invention.

As shown in Fig. 5, here, the operating state of the clutch module actuator for switching from the lift mode (second-stage to sixth-speed shift mode) to the one-way clutch mode (first-stage shift mode) of the clutch module is shown.

The hydraulic pressure of about 6 bar entered through the entrance 12 of the cylinder 11 passes through the first fluid passage 14 and the front space 13a of the piston portion of the hydraulic chamber 13 and the rear space 13b , And the second fluid passage 15 is filled with the oil pressure at this time, the piston rod 10 is advanced by the hydraulic pressure at this time, so that the clutch module is switched to the one-way clutch mode (one-stage shift mode).

At this time, the piston portion 10a of the piston rod 10 is advanced to a position where it blocks the first fluid passage 14 communicating with the space 13a in front of the piston portion.

FIG. 6 is a cross-sectional view showing a one-way clutch-lock operation state of a clutch actuator of a clutch according to an embodiment of the present invention.

As shown in Fig. 6, the operating state of the clutch module actuator for switching from the one-way clutch mode (one-stage shift mode) to the lock mode (reverse shift mode) of the clutch module is shown here.

For example, the hydraulic pressure of about 10 bar entered through the entrance 12 of the cylinder 11 pushes the first check ball 19 set at a pressure of about 6.5 bar, and then the first bypass passage 16, The piston rod 10 is advanced by the hydraulic pressure at this time, and the clutch module is eventually switched to the lock mode (reverse shift mode).

FIG. 7 is a cross-sectional view illustrating a locked-to-one-way clutch operating state of a clutch module actuator according to an embodiment of the present invention.

7, the operating state of the clutch module actuator for switching from the lock mode (reverse shift mode) of the clutch module to the one-way clutch mode (one-stage shift mode) is shown here.

For example, when the hydraulic pressure supplied at a pressure of about 10 bar is lowered to a pressure of about 6 bar, the restoring force of the return spring 25 causes the piston rod 10 to move backward and, at the same time, After passing through the second bypass passage 17 and the first fluid passage 14 after pushing out the second check ball 20 set at about 0.1 bar through the second fluid passage 15, (12), and eventually the clutch module is switched to the one-way clutch mode (1-speed shift mode).

At this time, the piston portion 10a of the backward piston rod 10 is advanced to the position where it closes the first fluid passage 14 communicating with the space 13a in front of the piston portion, Is maintained at a pressure of about 6 bar.

8 is a cross-sectional view showing a one-way clutch to a lift operation state of the clutch module actuator according to an embodiment of the present invention.

8 shows the operating state of the clutch module actuator for switching from the one-way clutch mode (one-stage shift mode) of the clutch module to the lift mode (second-stage to six-shift mode).

For example, when the hydraulic pressure supplied to the hydraulic chamber 13 is lowered to a pressure of 0 bar, the restoring force of the return spring 25 causes the piston rod 10 to move further backward. The second check valve 20 is pushed by the second fluid passage 15 through the second bypass passage 17 and the first fluid passage 14 while pushing the second check ball 20 set at about 0.1 bar, Passes through the first front space 13a through the first fluid passage 14 and then through the inlet 12 so that the clutch module is switched to the lift mode (second-stage to sixth-speed mode).

At this time, the hydraulic chamber 13 and each passage of the cylinder 11 are maintained at a pressure of 0 bar.

The operation state of the clutch module operating in conjunction with the operation of the clutch module actuator will be described below.

9 is a front view showing an operating state of the clutch module in the lift mode operation of the clutch module actuator according to the embodiment of the present invention;

As shown in Fig. 9, here, the hub inner race 170 can be rotated in both directions in the 2- to 6-speed shifting state (idling).

That is, the piston rod 10, the lever housing 24, and the cam ring 110 are connected to each other by the force of the return spring 25 without being supplied with oil pressure on the cylinder side of the clutch module actuator, The ring 110 adheres to the initial position of -3.5 degrees.

At this time, the first protrusion 160a and the second protrusion 160b in the cam ring 110 are positioned while pressing the upper surface of the head part 150a of the pair of pawls 150, 150 maintains the horizontal posture and does not interfere with the hub inner race 170 side.

Here, the pair of pawls 150 can be supported by the pawl spring 200 while supporting the bottom of the head part 150a.

Thus, the hub inner race 170 can be freely rotated in both directions, so that the planetary gear (not shown) connected to the hub inner race 170 can also be freely rotated.

Here, the coupling relationship between the hub inner race and the planetary gear is the same as that of the conventional art, and a detailed description thereof will be omitted.

10 is a front view showing an operating state of the clutch module in one-way clutch mode operation of the clutch module actuator according to the embodiment of the present invention;

10, a state in which the hub inner race 170 can rotate only in one direction in the one-speed shifting state and the stopping state (neutral state) is shown here (one-way clutch function).

That is, the hydraulic pressure of about 6 bar is provided to the cylinder side of the clutch module actuator, and the forward and rotational operation of the piston rod and the rotation operation of the lever housing cause the cam ring 110 to move from the initial position of -3.5 degrees to the 0 position .

At this time, since the first projection 160a on the cam ring 110 is positioned in a state where the upper surface of the head 150a of one of the pawls 150 belonging to the first pawl 150 is pressed, Such a pole 150 changes only slightly in posture, and the top portion is caught by the first protrusion 160a, so that the top portion 150b is not struck down.

That is, the tail portion 150b of the pawl 150 is positioned outward beyond the notch rotation locus line and is not caught by the notch 180 side of the hub inner race 170.

However, the second protrusion 160b deviates from the position of the remaining one of the pawls 150, and the stem 150b of the pawl 150 at this time is struck down (due to its own weight) (150) is caught by the notch (180) of the hub inner race (170).

Accordingly, the hub inner race 170 can freely rotate in the clockwise direction of the figure, and in the counterclockwise direction, the rotation is restricted by the engagement with the pawl 150. As a result, the planetary gear also rotates only in one direction .

11 is a front view showing an operating state of the clutch module in the lock mode operation of the clutch module actuator according to the embodiment of the present invention;

As shown in Fig. 11, here, the two-way rotation of the hub inner race 170 is restricted in the reverse shift state (low & reverse braking function).

That is, the oil pressure of about 10 bar is provided to the cylinder side of the clutch module actuator, and the cam ring 110 rotates from the 0 ° position to the 3.5 ° position by advancing and rotating the piston rod and rotating the lever housing do.

At this time, the first protrusion 160a and the second protrusion 160b in the cam ring 110 are all deviated from the position of the pair of pawls 150, (Due to its own weight) and eventually the pawl 150 is caught by the notch 180 of the hub inner race 170.

Accordingly, the hub inner race 170 is restricted from rotating in both directions by engagement with the pawl 150, and consequently, the rotation of the planetary gear can also be limited.

As described above, according to the present invention, by implementing a new hydraulic actuator as a means for controlling the operation of the clutch module integrated with the one-way clutch function and the low & reverse brake function in a multistage manner, it is possible to simplify the structure, accurately position various positions And the efficiency of control and operation can be increased.

10: Piston rod
11: Cylinder
12: Entrance and exit
13: Hydraulic chamber
14: first fluid passage
15: second fluid passage
16: first bypass passage
17: second bypass passage
18a, 18b: spring
19: 1st check ball
20: second check ball
21: Fluid hole
22: Load housing
23: Lever
24: Lever housing
25: return spring
26: Spiral slit
27: Straight slit
28:
29: Cylinder bracket
30: spring support plate

Claims (9)

And includes a piston rod (10) and a cylinder (11) which are operated by a hydraulic pressure,
A first fluid passage 14 and a second fluid passage 15 which are connected between the inlet 12 and the hydraulic chamber 13 are formed in the cylinder 11 and the first fluid passage 14 and the second fluid passage 15, The first bypass passage 16 and the second bypass passage 17 are connected to each other between the first fluid passage 15 and the second fluid passage 15 and the first bypass passage 16 and the second bypass passage 17 are connected to each other. A first check ball 19 and a second check ball 20 which are supported by springs 18a and 18b are provided on one side and a piston portion 10a of the piston rod 10 is provided with a hydraulic cylinder And a fluid hole (21) for communicating the front space (13a) of the piston part and the rear space (13b) of the piston part are formed.
The method according to claim 1,
The first fluid passage 14 communicates with the space 13a in front of the piston portion of the hydraulic chamber 13 and the second fluid passage 15 communicates with the space 13b behind the piston portion 13b of the hydraulic chamber 13. [ And the clutch module actuator of the automatic transmission.
The method according to claim 1,
The first bypass passage 16 and the second bypass passage 17 are connected to each other across the first fluid passage 14 and the second fluid passage 15, And the clutch module actuator of the automatic transmission.
The method according to claim 1,
The first check ball 19 is disposed in a direction for interrupting the flow of the fluid flowing from the second fluid passage 15 toward the first fluid passage 14, Is arranged in a direction for interrupting a flow of fluid flowing from the side of the fluid passage (14) toward the side of the second fluid passage (15).
The method according to claim 1 or 4,
Wherein the first check ball (19) and the second check ball (20) are set to open at different pressures.
The method of claim 5,
And the first check ball (19) is set to be opened at 6.1 to 6.9 bar.
The method of claim 5,
And the second check ball (20) is set to be opened at 0.1 to 0.9 bar.
The method according to claim 1,
A rod housing 22 for receiving the piston rod 10 along the axial line and being coupled to a front end portion of the cylinder 11; And a lever housing (24) which is rotatable while being coupled in a concentric circle and which moves the clutch module side using a lever (23) on one side of the outer circumferential surface.
The method of claim 8,
The rod housing 22 is formed with a spiral slit 26 having a locus inclined along the longitudinal direction of the housing. The lever housing 24 is formed with a linear slit 27 parallel to the longitudinal direction of the housing, The rod 10 is formed with a pin 28 which is engaged with the spiral slit 26 and the linear slit 27 while being engaged therewith so that the piston rod 10 is operated forward and backward in parallel with the linear movement and the rotational movement A clutch module actuator of an automatic transmission.

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