KR100293661B1 - Hydraulic control system of continuously variable transmission for vehicle - Google Patents

Abstract

PURPOSE: A hydraulic control system for a continuously variable transmission of a vehicle is provided to perform shifting conveniently and to prevent damage of frictional members by operating first and second frictional members and primary and secondly pulleys efficiently, and to supply hydraulic pressure stably with simple structure. CONSTITUTION: A hydraulic control system of a continuously variable transmission for a vehicle is composed of a pressure regulating unit having a primary line pressure regulating valve(102), a first solenoid valve(S1), a secondly regulating valve(104) and a solenoid supply valve(106); a transmission control unit having a transmission gear ratio control valve(108) and a second solenoid valve(S2); a forward and backward movement control unit having a pressure control valve(110), a third solenoid valve(S3), a manual valve(112) and first and second frictional factors(C,B); and a torque converter control unit having a torque feed valve(114) receiving hydraulic pressure from the pressure regulating unit, a lockup clutch control valve(116), and a fourth solenoid valve(S4). Hydraulic pressure is supplied stably, and the continuously variable transmission is controlled conveniently with simple structure.

Description

Hydraulic control system of continuously variable transmission for automobile

The present invention relates to a hydraulic control system for more effectively operating a continuously variable transmission for a vehicle to which the belt type continuously variable transmission means is applied.

For example, the transmission of the vehicle has a function of transmitting the driving force of the engine to the driving wheels, which includes a manual transmission in which the driver directly selects a shift stage at the driver's will, and automatically shifts according to the driving conditions of the vehicle. It is divided into the automatic transmission which is made, and the continuously variable transmission in which continuous transmission is continuously performed without a specific speed change area between each transmission stage.

In the transmission as described above, the present invention relates to a continuously variable transmission having a great advantage in terms of fuel economy, power transmission performance, and weight by supplementing the disadvantages of the automatic transmission using hydraulic pressure, the continuously variable transmission thereof has an input shaft and an output shaft The method using the diameter displacement of the pulley mounted on the is mainly used.

Looking at an example of such a belt type continuously variable transmission, as shown in Figure 1, the rotational power generated from the engine 2 is transmitted through the torque shaft 6 is a torque conversion by the torque burner (4).

In addition, the forward and reverse rotation control means 8 disposed on the input shaft 6 is a pinion planetary gear set, whose sun gear 10 is integrally formed with the input shaft 6, and is equally spaced on the outer circumference of the sun gear. Carrier 12 for supporting a plurality of pinions are arranged to be connected to the input shaft 6 and the first power transmission shaft 14 via the first friction member (C), the ring inscribed with the pinion The gear 14 is connected to the transmission housing 18 via the second friction member B as a reaction force element.

In the above, the first friction member (C) is a multi-plate clutch is used as a clutch means, and when the friction member is operated, the planetary gear set is locked and directly connected, and the second friction member (B) is a brake means. When the brake is used and its friction member is operated, the ring gear 140 acts as a reaction force element and the planet carrier 12 reversely rotates, thereby making a reverse shift.

In addition, the continuously variable transmission means 22 disposed on the rear end of the first power transmission shaft 14 and the second power transmission shaft 20 disposed at a predetermined distance therefrom may be the first power transmission shaft ( 14, a primary pulley 24 connected to the rear end, a second pulley 26 disposed on the second power transmission shaft 20, and a belt connecting the both pulleys 24 and 26 ( 28).

In the above, the primary and secondary pulleys 24 and 26 are controlled by the hydraulic pressure generated by the driving force of the engine 2 so that their outer diameters can be changed to perform a shifting operation. The configuration of one embodiment is shown.

That is, the primary pulley 24 is composed of the fixed side pulley 30 and the variable side pulley 32, the fixed side pulley 30 is formed integrally with the first power transmission shaft 14, the variable side The pulley 32 is coupled in a state capable of moving left and right on the first power transmission shaft 14.

A casing member 34 is provided on the side of the variable side pulley 32 to form a hydraulic chamber 36 therebetween.

This hydraulic chamber 36 is such that the pressure fluid generated by the primary force of the engine can be supplied through the flow path 38 formed in the first power transmission shaft 14.

And the second pulley 26 is made of a fixed side pulley 40 and a variable side pulley 42 as described above, the fixed side pulley 44 is formed integrally with the second power transmission shaft (20).

In addition, the variable side pulley 42 is coupled to move left and right on the second power transmission shaft 20, the variable side pulley 42 is provided with a casing member 44 interposed of the engine through the hydraulic chamber 46 The pressure fluid generated by the driving force can be supplied.

And when the rotational power input through the continuously variable transmission means 22 is shifted in accordance with the change in the diameter of the primary pulley 24 and the secondary pulley 26 to form the shift control means 50, this stepless Conditions for changing the rotational speed of the transmission means 22 include the first material, when the outer diameters of the primary pulley 24 and the second pulley 926 are the same, and the outer diameter of the second primary pulley 24 is the second pulley 26. It can be considered to divide into a case larger than the diameter and a case where the diameter of the third primary pulley 24 is smaller than the diameter of the secondary pulley 26.

In the first condition, when the outer diameters of the primary and secondary pulleys 24 and 26 are the same, the transmission ratio is 1: 1.

Second, when the outer diameter of the primary pulley 24 is larger than the diameter of the secondary pulley 26, the rotation speed of the secondary pulley 26 becomes larger than the rotation speed of the primary pulley 24, thereby increasing speed.

When the outer diameter of the third primary pulley 24 is smaller than the diameter of the secondary pulley 26, the deceleration is performed because the rotation speed of the primary pulley 24 becomes smaller than the rotation speed of the secondary pulley 26. will be.

In addition, the rotational power that is shifted by the above process is transmitted to the differential 32 through the third power transmission shaft 30 disposed in parallel with the second power transmission shaft 20 and distributed to the corner wheels. Can be driven.

In the continuously variable transmission as described above, the first and second friction members and the primary and secondary pulleys are controlled by hydraulic pressure, and a hydraulic control system for operating the same is required.

In addition, the hydraulic control system must be configured to control the friction member and the pulley more efficiently so that the shift can be easily performed and the burnout of the friction member can be prevented.

Accordingly, an object of the present invention is to provide a hydraulic control system capable of more effectively operating the first and second friction members and primary and secondary pulleys of the continuously variable transmission.

In order to realize this, the present invention primarily controls the hydraulic pressure supplied from the oil pump and supplies it to the continuously variable transmission mechanism, and adjusts the primary regulated hydraulic pressure secondly to distribute the forward and reverse pressures and the multiple solenoid valves. ;

Shift control means for controlling a shift ratio by adjusting a part of the hydraulic pressure supplied from the pressure regulating means to the continuously variable transmission mechanism by the duty control of the solenoid valve;

Forward and backward control means for receiving the same forward and backward pressure from the pressure regulating means and changing the flow path according to the forward and backward selection to supply the friction member to operate during forward and backward movements;

A torque converter operation control means for receiving oil from the pressure regulating means and supplying oil to the operation of the torque converter and to the rate of action;

It provides a hydraulic control system of a continuously variable transmission for a vehicle comprising a.

1 is a block diagram of a continuously variable transmission operated by the present invention.

2 is a block diagram of a belt type continuously variable transmission means applied to the continuously variable transmission of FIG.

3 is a flow chart of hydraulic pressure in the neutral (N) range in the hydraulic control system according to the present invention.

Figure 4 is a block diagram of a pressure regulating means applied to the present invention.

5 is a configuration diagram of a shift control means applied to the present invention.

Figure 6 is a block diagram of the forward, reverse control means applied to the present invention.

7 is a configuration diagram of a torque converter operation control means applied to the present invention.

8 is a flow chart of hydraulic pressure in the advance (D) range.

9 is a hydraulic flow chart in the reverse R range.

Hereinafter, with reference to the accompanying drawings, preferred embodiments of the present invention that can specifically realize the above object will be described in detail.

3 is a configuration diagram of the hydraulic control system according to the present invention, the present invention is largely the primary line pressure control valve 102 for adjusting the hydraulic pressure supplied from the oil pump 100, the first solenoid valve (S1) and A pressure regulating means composed of a secondary control valve 104 and a solenoid supply valve 106;

Shift control means including a speed ratio control valve 108 and a second solenoid valve S2 for controlling the valve 108 thereof;

Pressure control valve 110, the third solenoid valve (S3) for controlling the valve 110, the maneuver valve 112, and the first and second friction elements (C) which is the operating element of the forward and backward (B) forward and backward control means;

Torque converter operation control means consisting of a torque feed valve 114, the lock-up clutch control valve 116, the fourth solenoid valve (S4) for controlling the valve 116 thereof receives hydraulic pressure from the pressure regulating means Is done.

In the above pressure control means, the hydraulic pressure pumped from the oil pump 100 is primarily adjusted in the line pressure through the primary line pressure control valve 102, the secondary pressure control valve 104 to control the hydraulic pressure primarily Secondary control is supplied to the solenoid supply valve 106, the shift control means, and the forward and reverse control means and the torque converter operation control means.

In addition, the hydraulic pressure supplied to the solenoid supply valve 106 is again distributed to each solenoid valve S1, S2, S3, and S4, and is supplied to the speed ratio control valve 108 of the shift control means. The hydraulic pressure is supplied to the primary pulley 120, which is a continuously variable transmission mechanism, under the control of the second solenoid valve S2, so that the variable speed of the pulley can be achieved by varying the diameters of the pulleys.

In addition, the hydraulic pressure supplied to the pressure regulating valve 110 of the forward and backward control means is supplied to the manual valve 112 under the control of the third solenoid valve S3, and the forward and backward pressure pipelines according to the driver's selector lever operation ( 112 and 124 are supplied to the first friction member (C) that is operated when driving forward, and the second friction member (B) that is operated when driving backward.

The accumulators 126 and 128 are installed and arranged on the front and rear pressure pipelines 112 and 124, respectively, so that the operation of the first and second friction members C and B is stabilized. The pass pipes 130 and 132 were formed so that the check valves 134 and 136 are respectively disposed to open the flow path when the hydraulic pressure is released, so that the release pressure can be quickly discharged.

The hydraulic pressure supplied to the torque converter feed valve 114 of the torque converter operation control means is stably controlled at the valve 114 thereof, and is supplied to the lock-up clutch control valve 116. It is supplied to the torque converter or the lubrication point under the control of the solenoid valve S4.

Looking at each valve configuration applied to the hydraulic system of the present invention to form a flow path as described above, the primary line pressure control valve 102 is in communication with the oil pump 100 in the valve body, as shown in FIG. A large diameter first port 200 and a small diameter second port 202, a third port 204 selectively communicating with the first port 200, and a first solenoid valve S1. It has a fourth port 206 that receives a control pressure from the discharge port, and a discharge port EX for discharging oil introduced into the second port 204 when the oil leaks.

The valve spool embedded in the valve body is touched through one side of the adjuster plug 2080 and the carbon member 210, and receives the control pressure of the first solenoid valve S1 from the plug 208 side. The first land 212, the second land 214 for selectively communicating and blocking the first and third ports 200 and 204, and the third hydraulic pressure flowing into the second port 202 acts. And a land 216 and a fourth land 218 for adjusting the opening amount of the second port 202.

Accordingly, the valve spool is initially moved to the right side in the drawing due to the elastic force of the elastic member 21, but is applied to the hydraulic pressure supplied from the oil pump 100 and the control pressure introduced from the first solenoid valve S1. Accordingly, the hydraulic pressure supplied to the first port 200 while the valve spool moves left and right is discharged to the inlet side of the oil pump 1000 through the third port 204 to adjust the line pressure.

The secondary pressure regulating valve 104 which receives the line pressure from the primary pressure regulating valve 102 has a first port 22 communicating with the primary line pressure regulating valve 102 to a valve body; The hydraulic pressure introduced into the first port 22 is the pressure control valve 110, the second port 224 in communication with the one side hydraulic detection chamber 222, and the hydraulic pressure introduced into the first port 220 A third port 226 for supplying the solenoid supply valve 106 and the torque converter operation control means, a fourth port 228 in communication with the inlet side of the oil pump 110, and a discharge to discharge the oil when the oil leaks. Reserve port EX.

The valve spool embedded in the valve body has a first land 230 for opening and closing the first port 220 while receiving a hydraulic pressure from the hydraulic detection chamber 222 and a bullet member 232 on the rear side. And a second land 234 for opening and closing the four ports 228.

Accordingly, the valve spool is moved to the left side in the drawing due to the repulsive force of the SXKSQKFQNWO 232 when the hydraulic pressure is not supplied, but the communication between the first port 22 and the second port 224 when the hydraulic pressure is supplied. By controlling the opening amount of the first port 220 while moving to the right according to the size of the hydraulic pressure supplied to the hydraulic detection chamber 222 to adjust the hydraulic pressure.

The solenoid supply valve 106 supplied with the hydraulic pressure from the secondary pressure regulating valve 104 supplies the control pressure to the first, second, third and fourth solenoid valves S1, S2, S3 and S4. The first and second ports 240 communicate with the third port 226 of the secondary pressure control valve 104 and the hydraulic pressure introduced into the first port 240 in the valve body. And 3, 4, a second port 242 for supplying the solenoid valves S1, S2, S3, and S4, and a third port for supplying hydraulic pressure to the hydraulic detection chamber while communicating with the second port 242. 224 and the discharge port EX for discharging oil leakage.

The valve spool embedded in the valve body is disposed through the adjuster plug 246 and the elastic member 248 on one side, and is supported by the elastic member 258 to open and close the discharge port Ex. 250, and the inflow of the oil into the hydraulic detection chamber on one surface acts, and the second land 252 opens and closes the first port 240.

Accordingly, when the hydraulic pressure is not supplied, the valve spool is moved to the right side in the drawing by the elastic force of the elastic member 258, and when the hydraulic pressure is supplied, the second port 242 of the first port 24 is supplied. The oil pressure is controlled by controlling the opening amount of the first port 240 while moving to the left side according to the size of the oil pressure supplied to the oil pressure detection chamber through the communication of.

The first solenoid valve S1 controlling the primary line pressure regulating valve 102 converts a flow path while the valve spool embedded in the valve body moves left and right by a solenoid, and the valve body S is the solenoid supply valve ( The first port 260 communicated with the second port 242 of the 106 and the fourth port of the primary line pressure control valve 102 to selectively supply the hydraulic pressure supplied thereto while communicating with the first port 260. And a second port 262 communicating with 206 and a third port 266 for supplying hydraulic pressure to one end of the valve body through the bypass pipe 264.

In addition, the valve spool has a hydraulic pressure supplied from the third port 266 acting on one side, and the first land 268 and the first port 268 for selectively opening and closing the first port 260 by the operation of the solenoid. The second land 170 for opening and closing the discharge port EX for discharging residual hydraulic pressure in the valve body when the 160 is closed is retained.

Accordingly, by controlling the infant supplied from the solenoid feed valve 106 to supply to the primary line pressure control valve 102, the artificial line pressure is adjusted.

In addition, the speed ratio control valve 108 forming the shift control means includes a first port 280 communicating with the primary line pressure regulating valve 102 and a first port 180 as shown in FIG. 5. And the second port 282, which is selectively in communication with and supplies hydraulic pressure to the primary pulley 120, the third port 284, which is in communication with the second solenoid valve S2, and the solenoid supply valve 106. The fourth port 286 communicates with each other.

The valve spool embedded in the valve body has a first elastic member 290 interposed between the plug 288 and a first land for selectively opening and closing the discharge port EX while being supported by the elastic member 190. The second land 294 for selectively opening and closing the first port 280 and the hydraulic pressure flowing into the fourth port 285 are actuated and supported by the second elastic member 290. It will have three lands 296.

Accordingly, the opening and closing amount of the first port 280 is adjusted while the valve spool moves left and right by the hydraulic pressure supplied from the second solenoid valve S2 to supply the hydraulic pressure to the primary pulley 12.

In addition, like the first solenoid valve 9S1, the second solenoid valve S2 that controls the speed ratio control valve 108 converts the small flow path when the valve spool embedded in the valve body moves left and right by the solenoid.

To this end, the valve body is configured to communicate with the first port 298 communicating with the second port 242 of the solenoid feed valve 108 and the hydraulic pressure supplied thereto while selectively communicating with the first port 298. And a second port 300 in communication with the third port 284 of the valve 108, and a third port 304 for supplying hydraulic pressure to one end of the valve body through the bypass conduit 302. .

In addition, the valve spool has a hydraulic pressure supplied from the third port 304 acting on one side, and the first land 306 and the first port for selectively opening and closing the first port 298 by the operation of the solenoid. The second land 308 opens and closes the discharge port EX for discharging residual hydraulic pressure in the valve body when the 298 is closed.

Accordingly, by controlling the hydraulic pressure supplied from the solenoid supply valve 106 to supply to the speed ratio control valve 108, by varying the diameter of the primary pulley 120 and the secondary pulley 118 to make a stepless shift.

The pressure regulating valve 110 forming the forward and reverse control means is a first port 310 in communication with the second port 224 of the solenoid pressure regulating valve 108 in the valve body, as shown in Figure 6, And a second port 312 for supplying the hydraulic pressure introduced into the first port 310 to the manual valve 112, and a third port 316 for receiving control pressure from the third solenoid valve S3. do.

In addition, the balance spool embedded in the valve body has a first land 320 in which the carbon member 318 is held on one side, and the first and second ports 310 and 312 communicate with the first land 3200. The second land 322 and the third land 324 to which the control pressure flowing into the third port 316 acts.

Similar to the first solenoid valve S1, the third solenoid valve S3 supplying the control pressure to the pressure regulating valve 1100 converts a flow path while the valve spool embedded in the valve body moves left and right by the solenoid. .

To this end, the valve body may be configured to communicate with the first port 330 communicating with the second port 242 of the solenoid supply valve 106 and the hydraulic pressure supplied thereto while selectively communicating with the first port 330. The second port 332, which supplies the third port 316 of the 110, and the third port 336, which supplies hydraulic pressure to one side of the valve body through the bypass pipe 334, are provided.

In addition, the valve spool has a hydraulic pressure supplied from the third port 336 on one side, the first land 338 for selectively opening and closing the first port 330 by the operation of the solenoid, and the first The second land 340 opens and closes the discharge port EX for discharging residual hydraulic pressure in the valve body when the port 330 is closed.

Accordingly, the hydraulic pressure supplied from the solenoid supply valve 106 is controlled to supply the manual valve 112.

In addition, the manual valve 112 which receives hydraulic pressure from the valve 110 and converts the flow path according to the selected range has a first port communicating with the second port 312 of the pressure regulating valve 110. And 3500, and second and third ports 352 and 354 in communication with the forward and backward pressure pipelines 122 (! 24), respectively.

The valve spool embedded in the valve body includes first and second lands 356 and 358 for communicating the first and second ports 350 and 352 in the "D" range, and the second land in the "R" range. (358) guides the hydraulic discharge which flowed into the reverse pressure pipeline (124) together with the third land (360) for communicating the first and third ports (359, 354) and the third land (360) when neutral. A fourth land 362 and a connector 364 protruding outward from the valve body and connected to a select lever and a cable or a link are not shown.

In addition, the torque converter feed valve 114 forming the torque converter operation control means is a first port 370 in communication with the third port 226 of the secondary pressure control valve 104 in the valve body as shown in FIG. And a second port 374 that communicates the hydraulic pressure introduced into the first port 370 with the one side hydraulic detection chamber 372, and locks up the hydraulic pressure introduced into the first port 370. The third port 276 to be supplied to the 116, the fourth port 278 in communication with the inlet side of the oil pump 100, and the discharge port EX for discharging oil leakage.

The valve spool embedded in the valve body has a first land 380 that opens and closes the first port 270 while receiving a hydraulic pressure from the hydraulic detection chamber 272, and a bullet member 382 is supported by the rear side. And a second land 384 for opening and closing the four ports 378.

Accordingly, when the hydraulic pressure is not supplied, the valve spool is moved to the left side in the drawing by the elastic force of the elastic member 382, but when the hydraulic pressure is supplied, the second port 374 of the first port 370 communicates with the valve spool. By controlling the opening of the first port 3700 while controlling the opening of the first port 3700 to the right according to the size of the hydraulic pressure supplied to the hydraulic detection chamber 372 to supply to the lock-up clutch control valve 116 .

The lock-up clutch control valve 116 connects the first port 390 to the third body 276 of the torque converter feed valve 114 and the first port 390 to the valve body. Second and third ports 396 and 398 communicating with the lock-up clutch operating pressure pipeline 392 and the release pressure pipeline 394 of the torque converter, and the hydraulic pressure flowing into the first port 390 to one end The fourth and fifth ports 400 and 4020 to bypass and the sixth port 404 supplied with the control pressure from the fourth solenoid valve S4 are provided.

The valve spool embedded in the valve body includes a first land 406 through which hydraulic pressure supplied to the sixth port 404 acts, and a release pressure pipe 394 when the fourth solenoid valve S4 is controlled on. The second and third lands 408 and 210 for guiding the hydraulic discharge of the oil, and the working pressure pipe 392 together with the three lands 410, are connected to the fourth land 412 in communication with the first port 390. The fourth land 412 is held by the bullet member 414.

The fourth solenoid valve S4 controlling the lock-up clutch control valve 116 converts a flow path while the valve spool embedded in the valve body moves left and right by the solenoid similarly to the first solenoid valve S1. Let's go.

To this end, the valve body locks up the first port 416 communicating with the second port 242 of the solenoid supply valve 106, and the hydraulic pressure supplied thereto while selectively communicating with the first port 416. And a second port 418 for supplying the sixth port 404 of the clutch control valve 116 and a third port 422 for supplying hydraulic pressure to one end of the valve body through the bypass conduit 420. Done.

In addition, the valve spool has a hydraulic pressure supplied from the third port 422 on one side, and the first land 424 and the first port for selectively opening and closing the first port 416 by the operation of the solenoid. The second land 426 for opening and closing the discharge port EX for discharging residual hydraulic pressure in the valve body when the 416 is closed is retained.

Accordingly, the hydraulic pressure supplied from the solenoid supply valve 106 is controlled to control the lock-up clutch control valve 116.

According to the hydraulic control system of the present invention as described above, in the neutral (N) and parking (P) range, as shown in Figure 3, the first, second, fourth solenoid valves (S1), S2 (S4) is controlled off The third solenoid valve S3 is controlled on.

Then, the hydraulic pressure supplied from the oil pump is supplied to each part in the state adjusted in the secondary pressure control valve 104 after the line pressure is adjusted by the primary line pressure control valve 102, the first and second , The hydraulic pressure supplied to the friction member (C) (B) is made neutral and parking in the state blocked in the manual valve (11).

In this state, when the driver changes the select lever to the "D" range position for driving, the first and second ports 350 and 352 communicate with each other in the manual valve 104 as shown in FIG. The hydraulic pressure supplied from the 104 through the pressure regulating valve 110 is supplied to the first friction member C through the forward pressure pipeline 122, so that forward travel is possible.

At this time, the first pulley 120 and the second pulley 118 is operated by the first friction member (C) in a state in which the operating pressure is supplied, it is possible to travel forward, these pulleys (120) The operating pressure is controlled by the duty control of the first and second solenoid valves S1 and S2 under the control of the transmission control unit TCU that is different from the driving conditions. ) Is variable while the primary pulley 120 and the secondary pulley 118 is supplied with the hydraulic pressure is a relative diameter variable is made without endless shift.

When the driver changes the reverse shift to the “R” range, the hydraulic pressure supplied from the secondary pressure regulating valve 104 to the pressure regulating valve 110 is transferred to the third solenoid valve S3 as shown in FIG. 9. When controlled by the duty control of the supplied to the manual valve 112, the first and third ports 350, 354 are communicated with the manual valve 112 through the second friction member (B) through the reverse pressure pipeline (124) It is possible to reverse by supplying the working pressure.

As described above, according to the present invention, the hydraulic control system applied to the continuously variable transmission in which the continuously variable transmission is made by the variable diameter of the primary pulley and the secondary pulley is formed in a simpler configuration to provide stable hydraulic pressure and at the same time the continuously variable transmission It is an invention that can be controlled to operate.

Claims (17)

Pressure regulating means for firstly adjusting the oil pressure supplied from the oil pump to supply the continuously variable transmission mechanism, and for controlling the first adjusted oil pressure secondly to distribute the forward and backward pressures and the plurality of solenoid valves; Shift control means for controlling a shift ratio by adjusting a part of the hydraulic pressure supplied from the pressure regulating means to the continuously variable transmission mechanism by the duty control of the solenoid valve; Forward and backward control means for receiving the same forward and backward pressure from the pressure regulating means and changing the flow path according to the forward and backward selection to supply the friction member to operate during forward and backward movements; Torque converter operation control means for receiving oil pressure from the pressure regulating means and supplying oil to the operation of the torque converter and the lubrication point; In the hydraulic control system of a continuously variable transmission for a vehicle comprising: The pressure adjusting means primarily controls the hydraulic pressure pumped from the oil pump to supply the secondary pulley of the continuously variable transmission mechanism, the speed ratio control valve of the speed change control means, and the primary line pressure control to supply pressure control valves of the low and reverse control means. A valve; A secondary pressure regulating valve for controlling the hydraulic pressure supplied from the primary line pressure regulating valve in a second manner and supplying the pressure regulating valve of the forward and backward control means and the torque converter feed valve of the torque converter operation control means; A solenoid feed valve configured to receive hydraulic pressure from the secondary pressure regulating valve and control the hydraulic pressure to supply a plurality of solenoid valves; A first solenoid valve disposed to control the primary pulley F by controlling the hydraulic pressure supplied from the solenoid feed valve; Hydraulic control system of a continuously variable transmission for a vehicle comprising a. The primary line pressure control valve of claim 1, wherein the primary line pressure regulating valve comprises: a first port having a large diameter and a second port having a small diameter communicating with the oil pump; a third port selectively communicating with the first port; A valve body having a fourth port 206 supplied with a control pressure from the solenoid valve and a discharge port for discharging oil leaked into the second port; A first land which is carried through one side of the adjuster plug and the elastic member, and receives a control pressure of the first solenoid valve from the plug side, and a second land for selectively communicating and blocking the first and third ports; A valve spool having a third land on which the hydraulic pressure flowing into the second port acts, and a fourth land adjusting the opening amount of the second port; Hydraulic system of a continuously variable transmission for a vehicle comprising a. The secondary pressure control valve of claim 1, wherein the secondary pressure control valve comprises: a first port communicating with the primary line pressure control valve; a hydraulic pressure introduced into the first port; and a second port communicating with one side hydraulic detection chamber; And a third port for supplying the hydraulic pressure introduced to the first port to the solenoid supply valve and the torque converter operation control means, a fourth port communicating with the inlet side of the oil pump, and a discharge port for discharging oil leakage. A valve body; A valve bush including one end receiving a hydraulic pressure of the hydraulic detection chamber and a first land opening and closing the first port, and a second land opening and closing the fourth port, wherein the barrel member is held at the rear side; Hydraulic control system of continuously variable transmission for cars, including The solenoid supply valve of claim 1, wherein the solenoid supply valve comprises: a first port communicating with a third port of the secondary pressure control valve; a second port for supplying hydraulic pressure introduced to the first port to a plurality of solenoid valves; A valve body having a third port communicating with the port and supplying hydraulic pressure to the hydraulic detection chamber, and a discharge port for discharging oil when the oil is leaked; The first land for opening and closing the discharge port and the inlet flows into one side of the adjuster plug and the elastic member are interposed between the adjuster plug and the elastic member of one side, and the inflow of one surface is introduced into the hydraulic detection chamber. A valve spool holding the land; Hydraulic control system of a continuously variable transmission for a vehicle comprising a. The method according to claim 1, wherein the first solenoid valve is configured to convert the flow path while the valve spool embedded in the valve body to move left and right by the solenoid, the valve body is a first port in communication with the second port of the solenoid supply valve And a second port for selectively communicating with the first port and supplying hydraulic pressure to the first port, and a second port for communicating with a fourth port of the primary line pressure control valve, and supplying hydraulic pressure to one end of the valve body through a bypass pipe. 3 ports In the valve spool, the hydraulic pressure supplied from the third port is acted on one side, and the first land selectively opens and closes the first port by the operation of the solenoid, and discharge of residual hydraulic pressure in the valve body when the first port is closed. Hydraulic control system of a continuously variable transmission for a vehicle, characterized in that it has a second land for opening and closing the discharge port for. Pressure regulating means for firstly adjusting the oil pressure supplied from the oil pump to supply the continuously variable transmission mechanism, and for controlling the first adjusted oil pressure secondly to distribute the forward and backward pressures and the plurality of solenoid valves; Shift control means for controlling a shift ratio by adjusting a part of the hydraulic pressure supplied from the pressure regulating means to the continuously variable transmission mechanism by the duty control of the solenoid valve; Forward and backward control means for receiving the same forward and backward pressure from the pressure regulating means and changing the flow path according to the forward and backward selection to supply the friction member to operate during forward and backward movements; Torque converter operation control means for receiving oil pressure from the pressure regulating means and supplying oil to the operation of the torque converter and the lubrication point; In the hydraulic control system of a continuously variable transmission for a vehicle comprising a, The shift control means includes a shift ratio control valve for controlling the hydraulic pressure supplied from the pressure regulating means to supply the primary pulley which is a continuously variable transmission mechanism; A second solenoid valve for controlling the speed ratio by controlling the hydraulic pressure supplied from a second pressure control valve to control the speed ratio control valve; Hydraulic control system of a continuously variable transmission for a vehicle comprising a. The speed ratio control valve of claim 6, wherein the speed ratio control valve comprises: a first port communicating with the primary line pressure regulating valve, a second port selectively communicating with the first port to supply hydraulic pressure to the primary pulley, and a second solenoid valve; A valve body having a third port in communication with the fourth port in communication with the solenoid supply valve; A first elastic member is interposed between the one side plug, a first land for selectively opening and closing the discharge port while being supported by the elastic member, a second land for selectively opening and closing the first port, and the fourth port. A valve spool having hydraulic pressure introduced into the valve and having a third land other than the tanji by the second elastic member; Hydraulic control system of a continuously variable transmission for a vehicle comprising a. According to claim 6, The second solenoid valve has a structure in which the valve spool embedded in the valve body to move the left and right while moving by the solenoid to convert the flow path, the valve body is in communication with the second port of the solenoid feed valve first port And a second port communicating selectively with the first port while communicating with the first port, and a third port communicating with a third port of the speed ratio control valve, and a third port supplying hydraulic pressure to one end of the valve body through a bypass pipe. Holds, In the valve spool, the hydraulic pressure supplied from the third port is acted on one side, and the first land selectively opens and closes the first port by the operation of the solenoid, and discharge of residual hydraulic pressure in the valve body when the first port is closed. A hydraulic control system for a continuously variable transmission for a vehicle, characterized by a second land retainer for opening and closing a discharge port for the vehicle. Pressure regulating means for firstly adjusting the oil pressure supplied from the oil pump and supplying it to the continuously variable transmission mechanism, and secondly adjusting the oil pressure adjusted firstly and distributing it to the forward and backward pressures and the plurality of solenoid valves; Shift control means for controlling a shift ratio by adjusting a part of the hydraulic pressure supplied from the pressure regulating means to the continuously variable transmission mechanism by the duty control of the solenoid valve; Forward and backward control means for receiving the same forward and backward pressure from the pressure regulating means and changing the flow path according to the forward and backward selection to supply the friction member to operate during forward and backward movements; A torque converter operation control water supply for receiving oil pressure from the pressure regulating means and supplying oil to the operation of the torque converter and the lubrication point; In the hydraulic control system of a continuously variable transmission for a vehicle comprising: The forward and backward control means includes a pressure control valve for controlling the hydraulic pressure supplied from the secondary pressure control valve of the pressure regulating means with a third solenoid valve; A manual valve for supplying hydraulic pressure to the second and third friction members by receiving the hydraulic pressure from the pressure control valve and changing the flow path to the forward and backward pressure pipelines according to the range change of the driver's select lever; A third solenoid valve controlling the pressure regulating valve by hydraulic pressure supplied from the solenoid feed valve; Hydraulic control system of a continuously variable transmission for a vehicle comprising a. The pressure regulating valve of claim 9, wherein the pressure regulating valve comprises: a first port communicating with a second port of the solenoid pressure regulating valve, a second port for supplying hydraulic pressure introduced into the first port to a manual valve, and a third solenoid valve. A valve body having a third port supplied with a control pressure; A first land on which one side of the shot member is held, a second land allowing the first and second ports to communicate with the first land, and a third land having a control pressure flowing into the third port. Valve spool; Hydraulic control system of a continuously variable transmission for a vehicle comprising a. The method of claim 9, wherein the third solenoid valve is configured to convert the flow path while the valve spool embedded in the valve body is moved left and right by the solenoid, the valve body is a first port in communication with the second port of the solenoid supply valve And a second port for selectively communicating with the first port and supplying the hydraulic pressure supplied thereto to the third port of the pressure control valve, and a third port for supplying hydraulic pressure to one end of the valve body through a bypass pipe. Holds, In the valve spool, the hydraulic pressure supplied from the third port is acted on one side, and the first land selectively opens and closes the first port by the operation of the solenoid, and discharge of residual hydraulic pressure in the valve body when the first port is closed. Hydraulic control system of a continuously variable transmission for a vehicle, characterized in that it has a second land for opening and closing the discharge port for. The valve according to claim 9, wherein the manual valve includes: a valve body having a first port communicating with a second port of the pressure regulating valve, and second and third ports respectively communicating with a forward pressure and a reverse pressure pipeline; The first and second lands for communicating the first and second ports in the "D" range, the third land for communicating the first and third ports with the second land in the "R" range, and the third land for the neutral A valve spool having a fourth land for guiding hydraulic discharge which has been introduced into the reverse pressure pipe and protruding outwardly of the valve body, and having a connector connected to the select lever and a cable or a link; Hydraulic control system of a continuously variable transmission for a vehicle comprising a. The valve according to claim 9, wherein an accumulator is installed and disposed on the front and rear pressure pipelines so as to stabilize the operation of the first and second friction members, and a bypass channel is formed to open the flow path when the hydraulic pressure is released thereto. The hydraulic control system of a continuously variable transmission for a vehicle, characterized in that to release each of the release pressure to be discharged quickly. Pressure regulating means for firstly adjusting the oil pressure supplied from the oil pump to supply the continuously variable transmission mechanism, and for controlling the first adjusted oil pressure secondly to distribute the forward and backward pressures and the plurality of solenoid valves; Shift control means for controlling a shift ratio by adjusting a part of the hydraulic pressure supplied from the pressure regulating means to the continuously variable transmission mechanism by the duty control of the solenoid valve; Forward and backward control means for receiving the same forward and backward pressure from the pressure regulating means and changing the flow path according to the forward and backward selection to supply the friction member to operate during forward and backward movements; Torque converter operation control means for receiving oil pressure from the pressure regulating means and supplying oil to the operation of the torque converter and the lubrication point; In the hydraulic control system of a continuously variable transmission for a vehicle comprising a, The torque converter operation control means includes a torque converter feed valve for stabilizing the hydraulic pressure supplied from the secondary pressure regulating valve of the pressure regulating means; A lock-up clutch control for supplying the hydraulic pressure supplied from the torque converter feed valve to the torque converter and the lubrication point under the control of the fourth solenoid valve; Hydraulic control system of a continuously variable transmission for a vehicle comprising a. 15. The torque converter feed valve of claim 14, wherein the torque converter feed valve includes a first port communicating with a third port of the secondary pressure regulating valve, a second port communicating hydraulic pressure introduced into the first port with one side hydraulic detection chamber, and the first port. A valve body having a third port for supplying the hydraulic pressure introduced to the lock-up clutch control valve, a fourth port communicating with the oil pump inlet side, and a discharge port for discharging oil leakage; A valve spool having one side end receiving the hydraulic pressure in the hydraulic detection chamber and having a first land for opening and closing the first port, and a second member for holding the bullet member on the rear side and opening and closing the fourth port; Hydraulic control system of a continuously variable transmission for a vehicle comprising a. 15. The lock-up clutch control valve of claim 14, wherein the lock-up clutch control valve communicates with a first port in communication with a third port of the torque converter feed valve, and the first port communicates with the lock-up clutch operating pressure and release pressure lines of the torque converter. A valve body having second and third ports for discharging, fourth and fifth ports for bypassing the hydraulic pressure introduced into the first port to one end, and a sixth port for receiving control pressure from the fourth solenoid valve; The first land to which the hydraulic pressure supplied to the sixth port acts, the second and third lands for guiding the hydraulic discharge of the release pressure pipe during the on-control of the fourth solenoid valve, and the operating pressure pipe together with the three lands A fourth land communicating with the first port, wherein the fourth land includes: a valve spool supported by the ball member; Hydraulic control system of a continuously variable transmission for a vehicle comprising a. The method according to claim 14, wherein the fourth solenoid valve is configured to convert the flow path while the valve spool embedded in the valve body to move left and right by the solenoid, the valve body is in communication with the second port of the solenoid supply valve first port And a second port for selectively communicating with the first port and supplying the hydraulic pressure supplied thereto to the sixth port of the lock-up clutch control valve, and a second hydraulic pressure supply to one side of the valve body through a bypass pipe. It has 3 ports In the valve spool, the hydraulic pressure supplied from the third port is acted on one side, and the first land selectively opens and closes the first port by the operation of the solenoid, and discharge of residual hydraulic pressure in the valve body when the first port is closed. Hydraulic control system of a continuously variable transmission for a vehicle, characterized in that it has a second land for opening and closing the discharge port for.

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