KR102575141B1 - Stroke Response type Variable Force Solenoid Valve - Google Patents

Abstract

The direct control variable force solenoid valve 1 of the present invention balances the magnetic force (F magnetic force) and force with the spring force (F _{spring )} added to the feedback force (F _feedback ), which is the sum of the control pressure (P control ) and surface _pressure (A _feedback ) The spool valve 30 that increases the surface pressure (A _feedback ) to the feedback chamber 32 while forming a control pressure (P _control ) that is different from the set threshold pressure (P _threshold ) to control the pressure discharge in the feedback chamber 32 The inclusion of the switching valve 50 has the characteristics of maintaining the maximum pressure and improving responsiveness by switching the direction of magnetic force of the spool valve 30 when operating as a direct control variable force solenoid valve.

Description

Stroke response type variable force solenoid valve {Stroke Response type Variable Force Solenoid Valve}

The present invention relates to a solenoid valve, and more particularly, to a direct control variable force solenoid valve in which a response is increased by a stroke response.

In general, a solenoid valve is applied to an automatic transmission or continuously variable transmission of a vehicle. The solenoid valve is divided into an on-off/pulse width modulation (PWM) solenoid valve and a variable force solenoid valve.

For example, the on/off/PWM solenoid valve is controlled by an on/off signal from a shift control unit. On the other hand, the variable force solenoid valve is also driven by an amount of current proportional to the output duty according to the output of the duty control signal for driving the solenoid valve in the shift control unit.

Therefore, the variable force solenoid valve is divided into an indirect control variable force solenoid valve and a direct control variable force solenoid valve. In particular, the direct control variable force solenoid valve is applied to an automatic transmission, and has a characteristic in that pressure balance is determined and controlled by a magnetic force, a spring force corresponding thereto, and a feedback force. In addition, as the direct control variable force solenoid valve has a tendency for magnetic force to increase according to current, control pressure may be increased.

Domestic Patent Publication 10-2007-0076938 (2007.07.25)

However, the direct control variable force solenoid valve has the following disadvantages compared to the indirect control variable force solenoid valve.

First, in terms of responsiveness, the response of the system of the direct control variable force solenoid valve is slower than that of the indirect control variable force solenoid valve system because the level of valve actuation force that operates the valve is as low as 1/4 of the existing indirect control variable force solenoid valve. have responsiveness. Second, in terms of valve actuation force, the indirect control variable force solenoid valve system has a valve actuation force of 80N due to amplification by hydraulic power, while the direct control variable force solenoid valve system uses magnetic force as the source of valve actuation force, and is as low as 20N. do.

As a result, when the direct control variable force solenoid valve is used in a hybrid engine clutch or the like, fuel consumption problems are inevitably caused due to deterioration in driving/power performance and response when released.

Therefore, in consideration of the above points, the present invention is composed of a direct control variable force solenoid valve in which the reduced control pressure is compensated for by a switching valve system while increasing the responsiveness by increasing the feedback area, and in particular, the control pressure chamber at a certain control pressure or higher. Stroke responsive variable force solenoid valve used in the engine clutch of a hybrid vehicle without driving/power performance and fuel economy problems due to response deterioration during release by maintaining the maximum pressure through the magnetic force direction switching of the valve by blocking the inflow and discharging the chamber pressure. purpose is to provide

The stroke-responsive direct control variable force solenoid valve of the present invention for achieving the above object forms a feedback force with a control pressure and a surface pressure, and balances the magnetic force (F _{magnetic force} ) with a spring force added to the feedback force. , a spool valve forming a feedback chamber for increasing the surface pressure; and a switching valve that sets a threshold pressure for the control pressure and controls pressure discharge in the feedback chamber with a difference between the control pressure and the threshold pressure.

As a preferred embodiment, the feedback chamber is composed of a feedback area expansion chamber connected to a spring chamber in which a valve spring is accommodated. The feedback area expansion chamber increases an area to which the control pressure is applied, and is formed by connecting an axial path and a circumferential path perpendicular to the axial path to the spool valve. The axial path introduces the control pressure to the inside of the spool valve, and the circumferential path discharges the control pressure to the outside of the spool valve.

As a preferred embodiment, the switching valve is composed of a shut-off check valve provided in a control port for transmitting the supply pressure of the supply port where the control pressure is formed, and a discharge check valve for discharging the control pressure to a discharge port.

As a preferred embodiment, each operation of the shutoff check valve and the discharge check valve is performed based on a threshold pressure set for the control pressure. The shut-off check valve opens the control port side at the control pressure less than the critical pressure, while blocking the control port side at the control pressure reaching the critical pressure. The discharge check valve blocks the discharge port side at the control pressure less than the critical pressure, while opening the discharge port side at the control pressure reaching the critical pressure.

The direct control variable force solenoid valve of the present invention implements the following actions and effects by operating in a stroke response type.

First, responsiveness is improved compared to conventional direct control variable force solenoid valves by expanding the feedback area. Second, the coupling time of the engine clutch that connects/disconnects the power of the engine and the motor is shortened, resulting in improved power performance and reduced disengagement time, resulting in additional drag reduction of the motor, resulting in improved fuel efficiency. Third, there is no limit on the input torque because the pressure reduction does not occur due to the maintenance of the maximum pressure despite the increase in responsiveness. Fourth, it is suitable for engine clutches used in hybrids due to the effect of improving power performance and fuel economy and maintaining maximum pressure.

1 is a configuration diagram of a stroke-responsive variable force solenoid valve according to the present invention, FIG. 2 is an operating state of the variable force solenoid valve at the initial stage of operation according to the present invention, and FIG. 3 is a variable force control pressure formation according to the present invention 4 is an operating state of the variable force solenoid valve when the control pressure is cut off according to the present invention, and FIG. 5 is a response diagram of the stroke-responsive variable force solenoid valve according to the present invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying exemplary drawings, and since these embodiments can be implemented in various different forms by those skilled in the art as an example, the description herein It is not limited to the example of

Referring to FIG. 1 , a variable force solenoid valve 1 includes an electrical part 10, a flange 20, a spool valve 30, and a valve spring to control the clutch control pressure of the clutch 100. (40) and a switching valve (50). In particular, the variable force solenoid valve 1 has the electric part 10, the supply port 21, the control port 22, and the valve spring 40 as general components, and the feedback area expansion chamber 32b and the discharge port 32b. The port 23, the blocking check valve 50-1 and the discharge check valve 50-2 are special components, and these components increase the feedback area of the spool valve 30 to increase the responsiveness of the switching valve The operation of (50) supplements the control pressure reduction and operates as a direct control variable force solenoid valve.

For example, the electrical part 10 forms a magnetic force (F _{magnetic force} ) to push or pull the spool valve 30 to move it. To this end, the electric part 10 is the same as the electric part of a conventional variable force solenoid valve by moving the spool valve 30 by moving the rod while forming magnetic force (F _{magnetic force} ) by applying power to the yoke, coil, and bobbin.

For example, the flange 20 accommodates the spool valve 30 and includes a supply port 21 , a control port 22 , a discharge port 23 and a drain port 24 . The supply port 21 supplies pressure to the variable force solenoid valve 1 . The control port 22 receives pressure from the supply port 21 and forms a control pressure in which a force balance relationship is formed with the magnetic force (F magnetic _force ) as a result of the spring force (F _spring ) and the feedback force (F _feedback ). plays a role in The discharge port 23 functions to discharge the pressure of the variable force solenoid valve 1 during pressure control. The drain port 24 discharges the residual pressure of the variable force solenoid valve 1.

For example, the spool valve 30 is accommodated in the spool valve 30 and moved with the magnetic force (F _{magnetic force} ) of the electronic part 10, and against the magnetic force (F _{magnetic force} ), the spring force (F _spring ) and the feedback force (F _feedback ). The feedback force (F _feedback ) is divided into control pressure (P _control ) and surface pressure (A _feedback ). To this end, the spool valve 30 includes a land portion and a feedback chamber 32 .

The land portion is divided into chamber lands 31 and moving lands 37 located before and after the connection lands 35, respectively. The chamber land 31 is elastically supported by the valve spring 40 to form a spring force (F _spring ) and a control pressure (P _control ) and surface pressure (A _feedback ) to form a feedback force (F _feedback ), and the movement The land 37 receives the movement of the rod moving by the magnetic force (F _{magnetic force} ) of the electrical part 10 .

The feedback chamber 32 includes a spring chamber 32a formed by using a chamber land 31 and a feedback area expansion chamber 32b. The spring chamber 32a receives the spring force (F _spring ) through which the valve spring 40 is inserted, and the feedback area expansion chamber 32b forms the control pressure (P _control ) with the supplied pressure while the surface pressure (A Forms the area on which the control pressure (P _control ) is forced to form _feedback ). In particular, the feedback area expansion chamber 32b is controlled toward the discharge port 23 by forming a circumferential path of the chamber land 31 converted at right angles to the axial path of the chamber land 31 connected from the spring chamber 32a. Let the pressure escape. In addition, the feedback chamber 32 may communicate with the inside and outside using the chamber hole. In this case, the chamber hole is drilled in the circumferential direction of the chamber land 31 to communicate with the feedback area expansion chamber 32b.

For example, the valve spring 40 forms a spring force (F _spring ) against the magnetic force (F _{magnetic force} ), and provides a restoring force of the spool valve 30 when the magnetic force (F _{magnetic force} ) is released.

For example, the switching valve 50 is divided into a shutoff check valve 50-1 and a discharge check valve 50-2. The shut-off check valve 50-1 allows the control pressure to flow into the feedback chamber 32 in a range below the set pressure, while blocking the inflow into the feedback chamber 32 above the set pressure. The discharge check valve 50-2 blocks the discharge of pressure in the feedback chamber 32 in a region below the set pressure, whereas discharges the pressure in the feedback chamber 32 above the set pressure.

For example, the clutch 100 is applied to a hybrid vehicle as an engine clutch.

Therefore, the variable force solenoid valve 1 is realized by opening (OPEN) of the cut-off check valve 50-1 and closing (CLOSE) of the discharge check valve 50-2, as shown in the current-pressure control diagram of FIG. general control mode (①→②), maximum pressure switching mode (②→③) realized by blocking (CLOSE) of the shut-off check valve (50-1) and opening (OPEN) of the discharge check valve (50-2). action is implemented.

As a result, the feedback area of the variable force solenoid valve 1 is increased by the feedback area expansion chamber 32b for increasing responsiveness, and the switching valve operation of the cut-off/discharge check valves 50-1 and 50-2 The reduced control pressure is supplemented, and the maximum pressure is maintained by switching the spool valve 30 in the direction of magnetic force by discharging the chamber pressure by blocking the inflow of the control pressure toward the feedback area expansion chamber 32b above a certain control pressure.

Meanwhile, FIGS. 2 to 4 illustrate the operation of the variable force solenoid valve 1 according to the current-pressure control diagram.

Referring to the initial operation of FIG. 2, in the initial operation of the variable force solenoid valve 1, P _control = 0 and F _feedback = 0, and neither control pressure (P _control ) nor feedback force (F _feedback ) is formed. As a result, the variable force solenoid valve (1) is moved to the position ① by magnetic force (F _{magnetic force} ). In this state, supply port (21) = blocked (CLOSE), shutoff check valve (50-1) = closed (CLOSE), discharge check valve (50-2) = closed (CLOSE), discharge port (23) = closed ( CLOSE).

Referring to the control pressure formation of FIG. 3, in the variable force solenoid valve 1, as the supply port starts to open, the control pressure is balanced between the spring force (F _{spring ) and the feedback force (F feedback )} with respect to the magnetic force (F _{magnetic force} ). (P _control ) is formed. As a result, the variable force solenoid valve 1 is moved to the position of ② with the control pressure (P _control ). In this state, supply port (21) = open (OPEN), shutoff check valve (50-1) = open (OPEN), discharge check valve (50-2) = closed (CLOSE), discharge port (23) = closed ( CLOSE).

Referring to the control pressure cutoff of FIG. 4, in the variable force solenoid valve 1, the shutoff check valve 50-1 is blocked (CLOSE) by the control pressure (P _control ) increased above the operating condition (ie, P _threshold ). ), the inflow is stopped, the discharge check valve 50-2 is switched to OPEN by the pressure in the feedback area expansion chamber 32b reaching the operating condition or higher, and the discharge port 23 The pressure in the feedback area expansion chamber 32b is discharged. As a result, the variable force solenoid valve 1 is moved to the position ③ with the control pressure (P _control ). In this state, supply port (21) = open (OPEN), shutoff check valve (50-1) = shut off (CLOSE), discharge check valve (50-2) = open (OPEN), discharge port (23) = open ( OPEN) form.

Meanwhile, FIG. 5 is an example of a responsiveness diagram of the variable force solenoid valve 1. As shown, the variable force solenoid valve 1 has an effect of the feedback chamber 32 in which the feedback area expansion chamber 32a is formed. Improves response compared to direct control variable force solenoid valves.

Therefore, the variable force solenoid valve 1 is applied to the clutch 100 for a hybrid engine and contributes to improvement in fuel efficiency and power performance through an effect of increasing responsiveness. This is because the engine clutch plays a role of coupling/disconnecting the power of the engine and the motor, so a reduction in coupling time brings about an effect of improving power performance, and a reduction in release time brings about an effect of improving fuel efficiency by reducing additional drag of the motor.

In addition, since the variable force solenoid valve 1 is applied to the clutch 100 for a hybrid engine and the maximum pressure is not reduced even when the responsiveness is increased, the input torque limit is also resolved.

As described above, the direct control variable force solenoid valve 1 according to the present embodiment uses a spring force (F spring ) added to a feedback force (F _feedback ), which is the sum of a control pressure (P _control ) and a surface pressure (A _feedback ), as a magnetic _force . The spool valve 30, which increases the surface pressure (A _feedback ) to the feedback chamber 32 while achieving force balance with (F _{magnetic force} ), and the control pressure (P _{control ) that is different from the set critical pressure (P critical )} in the feedback chamber 32 ) By including the switching valve 50 that controls the pressure discharge in the inside, the maximum pressure is maintained and the response is improved by switching the magnetic force direction of the spool valve 30 when operated as a direct control variable force solenoid valve.

1: Variable Force Solenoid Valve
10: electrical part 20: flange
21: supply port 22: control port
23: discharge port 24: drain port
30: spool valve 31: chamber land
32: feedback chamber 32a: spring chamber
32b: feedback area expansion chamber
35: connection land
37: moving land 40: valve spring
50: switching valve 50-1: shutoff check valve
50-2: discharge check valve 100: clutch

Claims (11)

A spool valve that forms a feedback force with a control pressure and a surface pressure, and balances the force with the magnetic force with a spring force added to the feedback force;
A feedback chamber formed in the spool valve to increase the surface pressure; is included;
In the flange accommodating the spool valve, a control port receiving pressure from a supply port forms the control pressure in a force equilibrium relationship with the magnetic force by the resultant force of the spring force and the feedback force, and the control pressure is moves the clutch control pressure of the variable force solenoid valve to the position of the P _threshold ;
The switching valve controlling the inflow and outflow of the control pressure to the feedback chamber includes a shut-off check valve provided in the control port that transmits the supply pressure of the supply port where the control pressure is formed, and the control pressure to the discharge port. It is composed of a discharge check valve that discharges to;
The movement to the P _critical position is a point at which the pressure value applied to the general control mode of the cut-off check valve and the discharge check valve and the pressure value applied to the maximum pressure switching mode are distinguished in the current-pressure control diagram. Variable force solenoid valve.
The variable force solenoid valve according to claim 1, wherein the feedback chamber comprises a feedback area expansion chamber connected to a spring chamber accommodating a valve spring.
The variable force solenoid valve of claim 2 , wherein the feedback area expansion chamber increases an area to which the control pressure is applied.
The variable force solenoid valve according to claim 2, wherein the feedback area expansion chamber is formed by connecting an axial path and a circumferential path to the spool valve.
5. The variable force solenoid valve according to claim 4, wherein the axial path and the circumferential path form a right angle.
6. The variable force solenoid valve of claim 5, wherein the axial path introduces the control pressure into the spool valve, and the circumferential path discharges the control pressure to the outside of the spool valve.
delete delete The variable force solenoid valve according to claim 1, wherein each operation of the shutoff check valve and the discharge check valve is performed based on a threshold pressure set for the control pressure.
The method according to claim 9, wherein the shut-off check valve opens the control port side by setting the control pressure less than the critical pressure as the normal control mode, and converting the control pressure reaching the critical pressure into the maximum pressure switching mode. A variable force solenoid valve, characterized in that for blocking the control port side.
The method according to claim 9, wherein the discharge check valve blocks the discharge port side by setting the control pressure less than the critical pressure as the normal control mode, and converting the control pressure reaching the critical pressure into the maximum pressure switching mode A variable force solenoid valve, characterized in that for opening the discharge port side.

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