KR100279427B1 - Manual valve for forward and reverse control of continuously variable transmissions - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a manual valve of a continuously variable transmission, in which hydraulic control of a continuously variable transmission in which the manual valve 132 is supplied with different hydraulic pressure through the first pressure regulating valve 120 and the second pressure regulating valve 122. In the apparatus, the first port 16 in communication with the first pressure control valve 120 and the hydraulic pressure supplied to the first port 16 in the "R" range to the "NR" pressure regulating valve 134. Hydraulic pressure supplied to the second port 18, the third port 20 in communication with the second pressure control valve 122, and the third port 20 in the "L" and "D" range A valve body 12 formed with a fourth port 22 and two discharge ports 24, 26 for supplying the "ND" pressure regulating valve 136, and the first port 16 in the "R" range. ) And the third port 20 and the first land 28 and the second land 30 that communicate the second port 18 and the second land 30 together with the second land 30 in the "D" range. 4th port (22 The third land (32) communicating with each other is composed of the valve spools 14 formed at regular intervals, so that the valve spools 14 are embedded in the valve body 12. A manual valve for reverse control.

Description

Manual valve for forward and reverse control of continuously variable transmissions

The present invention relates to a manual valve of a continuously variable transmission, and more particularly, to provide a manual valve that can separately adjust the line pressure for controlling the forward clutch and the reverse brake, thereby improving control performance during the forward and reverse switching of the continuously variable transmission. Manual valve for forward and reverse control of a continuously variable transmission.

The continuously variable transmission that can improve the power performance and fuel economy characteristics of the vehicle generally includes a torque converter that receives power from the engine, a forward and reverse control unit that converts input power into forward and reverse, a continuously variable transmission that converts a transmission ratio, It consists of a longitudinal reduction device for decelerating and transmitting the converted power to the drive wheel.

The forward and reverse control device of the continuously variable transmission is a device for changing the direction of power to forward and backward. As a method of controlling it, the forward and reverse control device adopting a double planetary gear is widely known.

The forward and reverse control device of the continuously variable transmission using the double planetary gear has a structure that inputs power to the sun gear and outputs power to the carrier of the double planetary gear, and a forward clutch is provided between the input shaft and the carrier of the double planetary gear. A reverse brake is formed between the double planetary gear, the ring gear inscribed with the double planetary gear, and the transmission housing, thereby selectively converting power to forward and backward by selectively clamping the forward clutch and the reverse brake hydraulically.

The hydraulic control device for controlling the continuously variable transmission automatically connects the oil pump for generating hydraulic pressure to each of the operating elements of the continuously variable transmission with the flow paths and installs various valves on these flow paths to selectively control these valves. This is done.

An example of such a hydraulic control device is shown in FIG. 3.

As shown in FIG. 3, the hydraulic actuation elements in the hydraulic control device are the damper clutch, the drive pulley 112, the driven pulley 114, the reverse brake 116 and the forward clutch 118 in the torque converter 110. The valves used to control the actuation elements are: first pressure regulating valve 120, second pressure regulating valve 122, torque converter supply valve 124, lock-up clutch valve 126, speed ratio control valve 128, solenoid supply Valve 130, manual valve 132, NR pressure regulating valve 134, ND pressure regulating valve 136 and a plurality of solenoid valves S1, S2, S3, S4.

Referring to the hydraulic operation of the continuously variable transmission configured as described above are as follows.

The oil pressure generated by the oil pump 138 is first controlled by the line pressure in the first pressure regulating valve 120, the speed ratio control valve 128, the second pressure regulating valve 122, and the manual valve 132. And the driven pulley 114.

The hydraulic pressure supplied to the speed ratio control valve 128 is supplied back to the driving pulley 112 under the control of the second solenoid valve S2, which will be described later. At this time, the hydraulic pressure is in communication with the driven pulley 114 to complement each other. It is controlled by controlling the diameter of both pulleys to shift.

In addition, the hydraulic pressure supplied to the second pressure regulating valve 122 is secondarily adjusted to line pressure and is supplied to the solenoid supply valve 130, the manual valve 132, and the fourth solenoid valve S4, and the torque converter supply. The damper clutch in the torque converter 110 is controlled via the valve 124 and the lockup clutch valve 126.

Here, the line pressure supplied to the solenoid supply valve 130 is controlled once more uniformly, and then the first solenoid valve S1 for controlling the first pressure regulating valve 120 and the speed ratio control valve 128. ) Is supplied to the second solenoid valve S2 for controlling) and the third solenoid valve S3 for controlling the lockup clutch valve 126.

The hydraulic pressure supplied to these solenoid valves S1, S2, and S3 has a lower line pressure than the solenoid supply valve 130 and controls the valves 120, 128, and 126 connected thereto by controlling the solenoid valves on / off.

Meanwhile, the manual valve 132 supplied with hydraulic pressure through the first pressure regulating valve 120 and the second pressure regulating valve 122 has a range of "R", "N" and "P", and "D" and ". The flow path is switched according to the L "range, and the line pressure is sent to or discharged from the NR pressure regulating valve 134 and the ND pressure regulating valve 136.

When the driver selects the select lever (not shown) in the "R" range, the manual valve 132 transfers the hydraulic pressure supplied from the first pressure regulating valve 120 via the NR pressure regulating valve 134 to the reverse brake 116. ), The hydraulic pressure is discharged when the "N" and "P" ranges are selected, and the forward clutch (118) via the ND pressure control valve 136 when the "D" and "L" ranges are selected. Will be sent).

In this case, the fourth solenoid valve S4 controls the N-R pressure regulating valve 134 and the N-D pressure regulating valve 136.

As can be seen from the above description, the manual valve is supplied with different hydraulic pressure through two hydraulic lines, that is, the first pressure regulating valve 120 and the second pressure regulating valve 122.

The hydraulic control device of the continuously variable transmission is not widely known and is one of the hydraulic control methods that have been recently studied. The hydraulic control proposed to appropriately control torques acting differently on the reverse brake 116 or the forward clutch 118 is proposed. Device.

The present invention has been proposed to effectively control the hydraulic pressure supplied to the manual valve at different pressures as described above, and provides a manual valve that can switch the line pressure for the forward clutch and the reverse brake control separately to transfer the continuously variable transmission. It aims to provide a manual valve for forward and reverse control of a continuously variable transmission that can improve control performance during reverse switching.

In order to achieve the above object, the present invention primarily controls the hydraulic pressure generated in the oil pump in the first pressure regulating valve, and then supplies the speed ratio control valve, the manual valve and the driven pulley, and a part of the second pressure regulating valve. The hydraulic pressure supplied to the second gear solenoid valve is supplied back to the driving pulley under the control of the second solenoid valve, and the hydraulic pressure supplied to the second pressure regulating valve is secondly regulated. To the solenoid supply valve, the manual valve and the fourth solenoid valve, and the line pressure supplied to the solenoid supply valve is controlled once more uniformly, and then the first solenoid valve, the second solenoid valve and the third solenoid Supplied to the valve, wherein the manual valve is provided through the first pressure regulating valve and the second pressure regulating valve. In the hydraulic control device of a continuously variable transmission that is to receive a different hydraulic pressure, the first port in communication with the first pressure control valve, and the hydraulic pressure supplied to the first port in the "R" range to the "NR" pressure control valve A second port for supplying, a third port in communication with the second pressure control valve, and a fourth port for supplying hydraulic pressure supplied to the third port in the "L" and "D" ranges to the "ND" pressure regulating valve. And a valve body having two discharge ports, a first land and a second land communicating with the first port and the second port in the "R" range, and the second land in the "D" range. The third land connecting the third port and the fourth port is composed of valve spools formed at regular intervals, so that the valve spool is built in the valve body for forward and reverse control. Manual valve Not getting.

1 (a) is a plan view showing that the manual valve according to the present invention is in the "R" range state,

(B) is a plan view showing that the manual valve according to the present invention is in the "N" and "P" range state,

(C) is a plan view showing that the manual valve according to the present invention is located in the "L" and "D" range state,

2A is a front view showing a coupling relationship between a manual valve and a detent lever;

(B) is a plan view showing the coupling relationship between the manual valve and the detent lever,

3 is a hydraulic circuit diagram showing an "R" range operating state of a continuously variable transmission equipped with a manual valve according to the present invention;

4 is a hydraulic circuit diagram showing a "P" and "N" range operating state of a continuously variable transmission equipped with a manual valve according to the present invention;

Fig. 5 is a hydraulic circuit diagram showing the “D” and “L” range operating states of a continuously variable transmission equipped with a manual valve according to the present invention.

Hereinafter, specific embodiments for realizing the above object will be described with reference to FIG. 1.

1 is a plan view showing a manual valve according to the present invention, (a) is in the "R" range, (b) is in the "N" and "P" range and (c) is in the "L" and "D" range The position of the manual valve is shown.

Manual valve 132 according to the present invention is composed of a valve body 12, the flow path is formed and the valve spool 14 for switching the flow path.

The valve body 12 of the manual valve has a first port 16 in communication with the first pressure control valve 120 and a hydraulic pressure supplied to the first port 16 in the "R" range to "NR" pressure control. The second port 18 to be supplied to the valve 134, the third port 20 in communication with the second pressure control valve 122, and the third port 20 in the "L" and "D" range Fourth port 22 for supplying the hydraulic pressure supplied to the "ND" pressure regulating valve 136 and two discharge ports 24 and 26 are formed.

The valve spool 14 of the manual valve is the first and second lands 28 and 30 which communicate the first port 16 and the second port 18 in the " R " range and the first and second lands 28 and 30 in the " D " range. In addition to the two lands 30, the third lands communicating the third port 20 and the fourth port 22 are formed at regular intervals.

The valve spool 14, in which three lands are formed, has one end protruding outward from the valve body 12, and is connected by a selection lever (not shown) and the detent lever 34. It is built in).

2 shows a process in which a manual gear 132 according to the present invention selects a gear stage by a selection lever.

2 (a) and 2 (b) show a coupling relationship between a manual valve and a detent lever in a front view and a plan view.

A pin 36 is coupled to one end of the manual valve 132 valve spool 14, and the pin 36 is movably inserted into a curved groove 38 formed in the detent lever 34. It is done.

The groove 38 formed in the detent lever 34 has the "R" range position having the largest radius around the shift 40, the "P" and "N" range positions have the same radius, and the "D" and " The L ″ range positions have the same radius but the smallest shape.

At one end of the shift 40, a selection lever is mounted so that when the selection lever is moved back and forth, the detent 34 rotates up and down, and thus the position of the pin 36 located in the detent groove 38 is increased. Accordingly, the valve spool 14 is moved left and right.

That is, the valve spool 14 is moved left and right (A, B in FIG. 1) according to the radial difference (A, B in FIG. 2) of each range formed on the groove 38, so that the gear stage is selected.

Referring to the operation of the hydraulic control device equipped with a manual valve 132 according to the present invention formed as described above are as follows.

First, when the "R" range is selected by operating the selector lever, the manual valve 132 is in a state as shown in FIG. 1A, and the operating state of the hydraulic control device is shown in FIG.

As shown in FIG. 3, the hydraulic pressure generated by the oil pump 138 is adjusted by the line pressure at the first pressure regulating valve 120, and then the first port 16 and the second port 18 of the manual valve 132 are provided. After passing through, it is supplied to the "NR" pressure regulating valve 134 via the reverse pressure pipeline L1.

The hydraulic pressure reaching the "NR" pressure regulating valve 134 is pushed to the reverse brake 116 by pushing the valve spool of the "NR" pressure regulating valve 134 to the left in the drawing while the fourth solenoid valve S4 is duty controlled. Supply can be reversed.

A relief valve 142 and an accumulator 146 are disposed on the reverse flow path, and the first pressure regulating valve 120 protects the reverse brake 116 by preventing excessive hydraulic pressure from being supplied by a stick or the like. .

As shown in FIG. 3, when the reverse brake 116 is operating, hydraulic pressure is also supplied to the torque converter 110, the drive pulley 112, and the driven pulley 114, so that the reverse travel is possible. The operating pressure supplied to the element is controlled by the first, second and third solenoid valves S1, S2 and S3.

And in the "N" and "P" range, the manual valve 10 is positioned as shown in Figure 1 (b), the operation state at this time will be described with reference to Figure 4 as follows.

As the second land 30 of the manual valve 132 is positioned between the second port 18 and the fourth port 22, the hydraulic pressure and the second hydraulic pressure supplied from the first pressure regulating valve 120 are increased. The hydraulic pressure supplied from the pressure regulating valve 122 is blocked at the first port 16 and the third port 20, respectively, and the oil on the reverse pressure line L1 and the forward pressure line L2 is discharged. Through 24, 26, respectively.

Finally, in the L " and " D " ranges, the manual valve 10 is positioned as shown in Fig. 1C, and the operating state at this time is shown in Fig. 5.

After the hydraulic pressure reduced in two stages in the first pressure regulating valve 120 and the second pressure regulating valve 122 passes through the third port 20 and the fourth port 22 of the manual valve 132, It is supplied to the "ND" pressure regulating valve 136 via the suppression pipeline L2.

The hydraulic pressure reaching the "ND" pressure regulating valve 136 is moved to the forward clutch 118 by pushing the valve spool of the "ND" pressure regulating valve 136 to the left in the drawing while the fourth solenoid valve S4 is duty controlled. By supplying, forward driving is possible.

The relief valve 140 and the accumulator 144 are arranged on the flow path for the forward movement as in the reverse direction.

As can be seen from the above description, the manual valve for the forward and reverse control of the continuously variable transmission according to the present invention provides a manual valve capable of differently switching the flow path for the forward clutch and the reverse brake control, thereby providing the forward and reverse of the continuously variable transmission. To improve the control performance during switching.

Claims (2)

The oil pressure generated from the oil pump is primarily regulated by the first pressure regulating valve and then supplied to the speed ratio control valve, the manual valve and the driven pulley, and a part thereof is supplied to the second pressure regulating valve to regulate the hydraulic pressure secondly. The hydraulic pressure supplied to the speed ratio control valve is supplied back to the driving pulley under the control of the second solenoid valve. The hydraulic pressure supplied to the second pressure regulating valve is secondarily regulated to supply pressure to the solenoid supply valve, the manual valve, and the fourth solenoid valve. The line pressure supplied to the solenoid supply valve is controlled once more uniformly and then supplied to the first solenoid valve, the second solenoid valve and the third solenoid valve. In the hydraulic control apparatus of the continuously variable transmission wherein the manual valve is to be supplied with different hydraulic pressure through the first pressure control valve and the second pressure control valve, A first port in communication with the first pressure control valve, a second port for supplying hydraulic pressure supplied to the first port in the "R" range to the "NR" pressure control valve, and a second port in communication with the second pressure control valve. A valve body having three ports, a fourth port for supplying hydraulic pressure supplied to the third port in the "L" and "D" ranges to the "ND" pressure regulating valve, and two discharge ports; A first land and a second land communicating the first port and the second port in the "R" range and a third port and the fourth port communicating with the second land in the "D" range. The third land consists of valve spools formed at regular intervals Manual valve for forward and reverse control of the continuously variable transmission, characterized in that the valve spool is embedded in the valve body. The method of claim 1 wherein the manual valve, A pin coupled to one end of the valve spool, On one side, a shift is formed, on the other side, the radius of the "R" range position is the largest, the "P" and "N" range positions have the same radius, and the "D" and "L" range positions have the same radius. It consists of a detent lever in which the smallest groove is formed, The pin is movably inserted in the groove of the detent lever, and the selection lever is fixed to the shift so that the valve spool moves left and right in accordance with the movement of the selection lever. , Manual valve for reverse control.

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