KR20190099646A - Stroke Response type Variable Force Solenoid Valve - Google Patents

Abstract

The present invention relates to a stroke response-type variable force solenoid valve. According to the present invention, the stroke response-type variable force solenoid valve (1) comprises: a spool valve (30) which increases the surface pressure (Feedback A) with the feedback chamber (32) while making a force balance with a magnetic force (Magnetic Force F) by a spring force (Spring F) added to a feedback force (Feedback F), which is the sum of control pressure (Control P) and surface pressure (Feedback A); and a switching valve (50) which controls the control pressure (Control P) which is different from a preset threshold pressure (Threshold P) by a pressure discharge inside the feedback chamber (32). According to the present invention, when the solenoid valve works as a direct-control variable force solenoid valve, the switching of magnetic force direction of the spool valve (30) maintains maximum pressure and responsiveness.

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 directly controlled variable force solenoid valve in which a response increase is achieved by a stroke reaction.

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

In one example, the on / off / PWM solenoid valve is controlled by an on / off signal from the shift control unit. On the other hand, the VFS valve is driven by an amount of current proportional to the output duty in accordance with the duty control signal output for driving the solenoid valve in the shift control unit.

Therefore, the VFS valve is classified into an indirect control VFS valve and a direct control VFS valve. In particular, the direct control VFS valve is applied to an automatic transmission, the pressure balance is determined and controlled by the magnetic force and the corresponding spring force, feedback force. In addition, the direct control VFS valve may have a control pressure increase as the magnetic force has a tendency to increase with the current.

Domestic Patent Publication 10-2007-0076938 (2007.07.25)

However, the direct control VFS valve has the following disadvantages compared to the indirect control VFS valve.

First, in terms of responsiveness, the responsiveness of the system of the direct control VFS valve is slower than that of the indirect control VFS system by lowering the valve actuation force level that actuates the valve to 1/4 of the existing indirect control VFS system. Second, in terms of valve actuation force, the indirect control VFS system is 80N level due to hydraulic pressure amplification, while the direct control VFS system is low at 20N level using magnetic force as a source of valve actuation force.

As a result, when the direct control VFS valve is used in a hybrid engine clutch or the like, there is no choice but to cause fuel efficiency problems due to a decrease in response during operation / power performance and release.

In view of the above, the present invention is composed of a direct control variable force solenoid valve which supplements the control pressure reduced by the switching valve system while increasing the responsiveness by increasing the feedback area. The maximum pressure is maintained by switching the magnetic force direction of the valve by the inflow shutoff and the discharge of the chamber pressure. The purpose is to provide.

Stroke-responsive direct control variable force solenoid valve of the present invention for achieving the above object forms a feedback force by the control pressure and the surface pressure, and forms a force balance with the _magnetic force (F _{magnetic force} ) by the spring force in addition to the feedback force A spool valve having a feedback chamber for increasing the surface pressure; And a switching valve for setting a threshold pressure with respect to the control pressure, and controlling a pressure discharge in the feedback chamber by a difference between the control pressure and the threshold pressure.

In a preferred embodiment, the feedback chamber consists of a feedback area enlargement chamber which is continued from the spring chamber in which the valve spring is received. The feedback area enlargement chamber increases the area under which the control pressure is applied, and is formed by connecting an axial path and a circumferential path perpendicular to the spool valve. 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.

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

In a preferred embodiment, each operation of the shutoff check valve and the discharge check valve is made based on a threshold pressure set for the control pressure. The shutoff check valve opens the control port side at the control pressure that is less than the threshold pressure while blocking the control port side at the control pressure reaching the threshold pressure. The discharge check valve blocks the discharge port side at the control pressure less than the threshold pressure while opening the discharge port side at the control pressure at which the threshold pressure is reached.

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

First, the responsiveness is improved compared to the conventional direct control VFS by expanding the feedback area. Second, the fuel efficiency improvement effect is caused by the reduction of the engagement time of the engine clutch that combines / blocks the power of the engine and the motor, and the additional drag reduction of the motor. Third, there is no restriction on the input torque since the pressure decrease does not occur due to the maintenance of the maximum pressure even in response increase. Fourth, it is suitable for the engine clutch used in the hybrid because of the improvement of power performance, fuel efficiency and maximum pressure.

1 is a block diagram of a stroke-responsive variable force solenoid valve according to the present invention, Figure 2 is an operating state of the variable force solenoid valve during the initial operation according to the present invention, Figure 3 is variable when forming the control pressure according to the present invention 4 is an operating state of the variable solenoid valve when the control pressure is cut 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.

DETAILED DESCRIPTION Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings. Since the exemplary embodiments of the present invention may be implemented in various different forms, one of ordinary skill in the art to which the present invention pertains may be described herein. Not limited to the embodiment.

Referring to FIG. 1, a variable force solenoid valve 1 (hereinafter referred to as a VFS valve) may include an electric component 10, a flange 20, and a spool valve 30 to control a clutch control pressure of a clutch 100. ), A valve spring 40 and a switching valve 50. In particular, the VFS valve (1) is a general component of the electric field portion 10, the supply port 21, the control port 22 and the valve spring 40, the feedback area expansion chamber 32b and the discharge port ( 23, the shut-off check valve 50-1 and the discharge check valve 50-2 are special components, and the switching valve 50 is increased while the responsiveness is increased by increasing the feedback area of the spool valve 30 with these components. It is operated as direct control variable force solenoid valve by supplementing control pressure reduction with).

In one example, the electric part 10 forms a _magnetic force (F _{magnetic force} ) to push or pull the spool valve 30. To this end, the electric part 10 is the same as the electric part of the conventional VFS valve by moving the spool valve 30 by the rod movement while forming a _magnetic force (F _{magnetic force} ) by applying power to the yoke, coil and bobbin.

In one example, the flange 20 receives 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 VFS valve 1. The control port 22 receives a pressure from the supply port 21 and forms a control pressure in which a force equilibrium relationship is formed between the _magnetic force (F _{magnetic force} ) and the force of the spring force (F _spring ) and the feedback force (F _feedback ). It plays a role. The discharge port 23 serves to discharge the pressure of the VFS valve 1 in the pressure control. The drain port 24 acts as a residual pressure discharge of the VFS valve (1).

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

The land part is divided into a chamber land 31 and a moving land 37 which are positioned before and after the connection land 35, respectively. The chamber land 31 is elastically supported by the valve spring 40 to form a spring force (F _spring ) while forming a feedback force (F _feedback ) with a control pressure (P _control ) and a surface pressure (A _feedback ), and the movement The land 37 receives a rod movement moving by the _magnetic force (F _magnetic force) of the electric field unit 10.

The feedback chamber 32 includes a spring chamber 32a and a feedback area enlargement chamber 32b formed using the chamber land 31. The spring chamber 32a has a valve spring 40 inserted therein to receive a spring force (F _spring ), and the feedback area enlargement chamber 32b forms a control pressure (P _control ) at the supplied pressure, thereby providing a surface pressure (A). _{The area} under which the control pressure P _control is applied to form _feedback ). In particular, the feedback area enlargement chamber 32b forms a circumferential path of the chamber land 31 which is switched at right angles to the axial path of the chamber land 31 connected to the spring chamber 32a to be controlled toward the discharge port 23. Allow pressure to be released. In addition, the feedback chamber 32 may communicate internally and externally using a chamber hole. In this case, the chamber hole is drilled in the circumferential direction of the chamber land 31 so as to communicate with the feedback area enlargement chamber 32b.

In one example, provides a restoring force of the valve spring 40 has a magnetic force (F _{magnetic force)} against the spring force to form a _(spring F), and the magnetic force (F _{magnetic force)} off when the spool valve 30 in the.

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

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

Therefore, the VFS valve 1 is generally implemented by opening of the shutoff check valve 50-1 and closing of the discharge check valve 50-2, as shown in the current-pressure control diagram of FIG. 1. The control mode (① → ②), operation of the maximum pressure switching mode (② → ③) realized by the closing of the shutoff check valve 50-1 and the opening of the discharge check valve 50-2. Is implemented.

 As a result, the VFS valve 1 is increased in the feedback area to increase the responsiveness to the feedback area enlargement chamber 32b, and is reduced by the switching valve operation of the shutoff / discharge check valves 50-1 and 50-2. The control pressure is supplemented, and the maximum pressure is maintained by switching the spool valve 30 in the magnetic force direction by discharging the chamber pressure by the inlet blocking of the feedback area enlargement chamber 32b of the control pressure above a certain control pressure.

2 to 4 illustrate the operation of the VFS valve 1 according to the current-pressure control diagram.

Referring to the initial operation of Fig. 2, the VFS valve 1 _controls P at the initial operation. = 0, F _feedback With 0, neither the control pressure P _control nor the feedback force F _feedback is formed, so that the VFS valve 1 is moved to the position ① by the _magnetic force (F _{magnetic force} ). This condition includes supply port 21 = CLOSE, shutoff check valve 50-1 = CLOSE, discharge check valve 50-2 = CLOSE, outlet port 23 = shutoff ( CLOSE).

Referring to the control pressure formation of FIG. 3, in the VFS valve 1, the supply port starts to open so that the control pressure P is balanced by a spring force F _spring and a feedback force F _feedback with respect to the _magnetic force F _{magnetic force} . _Control ) is formed. As a result, the VFS valve 1 is moved to the position ② at the control pressure (P _control ). This condition includes supply port (21) = open (OPEN), shutoff check valve (50-1) = open (OPEN), discharge check valve (50-2) = CLOSE, discharge port (23) = shutoff ( CLOSE).

Referring to the control pressure blocking of FIG. 4, in the VFS valve 1, the shutoff check valve 50-1 is closed by the control pressure (P _control ) which is increased above the operating condition (that is, the P _threshold ). The inflow is interrupted by switching, and the discharge check valve 50-2 is switched to OPEN by the pressure in the feedback area enlargement chamber 32b at which the operating condition reaches or exceeds the operating condition, and the discharge port 23 is connected to the feedback area. The pressure in the expansion chamber 32b is discharged. As a result, the VFS valve 1 is moved to the position of ③ by the control pressure (P _control ). This condition includes supply port (21) = open (OPEN), shutoff check valve (50-1) = shut off (CLOSE), discharge check valve (50-2) = open (OPEN), outlet port (23) = open ( OPEN).

FIG. 5 is an example of the responsiveness diagram of the VFS valve 1. As illustrated, the VFS valve 1 is a conventional direct control VFS valve under the effect of the feedback chamber 32 forming the feedback area enlargement chamber 32a. It improves responsiveness compared to

Therefore, the VFS valve 1 is applied to the clutch 100 for the engine of the hybrid and contributes to the improvement of fuel efficiency and power performance by the response increase effect. This is because the engine clutch combines / blocks the power of the engine and the motor, so the reduction of the coupling time has the effect of improving the power performance, and the reduction of the release time has the fuel efficiency improvement effect by the additional drag reduction of the motor.

In addition, since the VFS valve 1 is applied to the hybrid clutch 100 for the engine, the maximum torque is not reduced even when the response is increased, thereby eliminating the input torque limit.

As described above, the direct control variable force solenoid valve 1 according to the present embodiment has a magnetic force as a spring force (F _spring ) in addition to the feedback force (F _feedback ) that is the sum of the control pressure (P _control ) and the surface pressure (A _feedback ). The spool valve 30 increases the surface pressure (A _feedback ) to the feedback chamber 32 while forming a force balance with the (F _{magnetic force} ), and the control pressure (P _control ) different from the set threshold pressure (P _threshold ) is supplied to the feedback chamber 32. By including the switching valve 50 to control the pressure discharge in) the maximum pressure maintenance and response is achieved by the magnetic force direction switching of the spool valve 30 when operating as a direct control variable force solenoid valve.

1: Variable Force Solenoid Valve
10: total length 20: flange
21: supply port 22: control port
23: drain port 24: drain port
30: spool valve 31: chamber land
32: feedback chamber 32a: spring chamber
32b: feedback area enlargement 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 which forms a feedback force with a control pressure and a surface pressure, and balances a magnetic force with a spring force in addition to the feedback force;
A feedback chamber formed in the spool valve to increase the surface pressure;
Variable force solenoid valve, characterized in that it is included.
The variable force solenoid valve of claim 1, wherein the feedback chamber comprises a feedback area enlargement chamber connected to a spring chamber in which the valve spring is accommodated.
3. The variable force solenoid valve according to claim 2, wherein the feedback area enlargement chamber increases the area under which the control pressure is applied.
The variable force solenoid valve according to claim 2, wherein the feedback area enlargement chamber is formed by connecting an axial path and a circumferential path to the spool valve.
5. The variable force solenoid valve of claim 4, wherein the axial path and the circumferential path are at right angles.
The variable force solenoid valve according to 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.
The apparatus of claim 1, further comprising: a switching valve configured to control inflow and outflow of the control pressure to the feedback chamber;
Variable force solenoid valve, characterized in that it is included.
The method of claim 7, wherein the switching valve is characterized in that the shutoff check valve provided in the control port for transmitting the supply pressure of the supply port in which the control pressure is formed, the discharge check valve for discharging the control pressure to the discharge port Variable solenoid valve.
The variable force solenoid valve according to claim 7, 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 control valve of claim 9, wherein the shutoff check valve opens the control port side at the control pressure that is less than the threshold pressure while blocking the control port side at the control pressure reaching the threshold pressure. Variable force solenoid valve.
The discharge check valve of claim 9, wherein the discharge check valve blocks the discharge port side at the control pressure less than the threshold pressure while opening the discharge port side at the control pressure at which the threshold pressure is reached. Variable force solenoid valve.

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