DE102013216004A1 - Electrohydraulic control sub-system of torque converter for use in hydraulically actuated automatic transmission, has booster valve assembly that is directly connected between specific port and source of pressurized hydraulic fluid - Google Patents

Abstract

The sub-system (100) has cooler subsystem (108) and regulator valve (110) with six fluid ports (110A-110F). The first and second ports are connected with source of pressurized hydraulic fluid and side connection respectively. The third port is connected with cooler subsystem. The fourth and fifth ports are connected with fluid source and sixth port is connected with release side connector. A booster valve assembly is directly connected between fourth port and fluid source. The hydraulic fluid is transmitted to fourth port, when hydraulic pressure fluid exceeds threshold pressure. The first and fourth ports are disconnected, second port is connected with third port and fifth port is connected to sixth port, when the slide (130) is in first position. The first port is connected with second port, fourth port is connected with third port and fifth port is separated when the spool is in second position.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of US Provisional Application No. 61 / 683,013 filed Aug. 14, 2012. The disclosure of the above application is incorporated herein by reference.

TECHNICAL AREA

The invention relates to a control system of a torque converter for an automatic transmission, and more particularly to an electro-hydraulic control system of a torque converter.

BACKGROUND

A typical automatic transmission includes a hydraulic control system that is used to provide cooling and lubrication to components in the transmission and to actuate a plurality of torque transmitting devices. These torque-transmitting devices may be, for example, friction clutches and brakes arranged with gear sets or in a torque converter. The conventional hydraulic control system typically includes a main pump that supplies a pressurized fluid, such as oil, to a plurality of valves and solenoid valves in a valve body. The main pump is driven by the engine of the motor vehicle. The valves and solenoid valves are operable to direct hydraulic fluid through a hydraulic fluid circuit to various subsystems including lubrication subsystems, radiator subsystems, shift actuator subsystems, actuators that engage torque transmitting devices, and torque converter clutch control subsystems that engage a torque converter clutch , include. The hydraulic pressure fluid delivered to the torque converter clutch control subsystem is used to apply or release the torque converter clutch, and thus toggle between fluid coupling between the engine and the transmission and a mechanical direct drive connection.

While previous hydraulic torque converter control systems are useful for their intended purpose, the need for new and improved hydraulic control system configurations for torque converters in transmissions that exhibit improved performance, failure modes, and return response is substantially constant. Accordingly, there is a need for an improved, low-cost, hydraulic control system of a torque converter for use in a hydraulically-actuated automatic transmission.

SUMMARY

A hydraulic control subsystem of a torque converter for a transmission is provided. The torque converter hydraulic control subsystem includes a source of hydraulic pressure fluid that communicates with a torque converter clutch (DWK) control valve, a DWK control valve, and a lubrication boost valve. The torque converter hydraulic control subsystem is configured to provide coolant and lubrication fluid flow to a torque converter in all modes of operation.

In one example, a system is provided that includes a source of hydraulic pressure fluid, a torque converter actuator operable to engage a torque converter lock-up clutch, the torque converter actuator having a release-side port and a apply-side port, a radiator subsystem, and a control valve assembly , The control valve assembly includes a first port in communication with the source of pressurized hydraulic fluid, a second port in communication with the apply-side port, a third port in communication with the radiator subsystem, a fourth port, a fifth port in communication with the source for Hydraulic pressure fluid, a sixth port in communication with the release-side port and a spool movable between at least a first position and a second position. The first and fourth ports are disconnected, the second port communicates with the third port, and the fifth port communicates with the sixth port when the spool is in the first position. The first port communicates with the second port, the fourth port communicates with the third port, and the fifth port is disconnected when the spool is in the second position. A boost valve assembly is disposed directly between the fourth port and the source of hydraulic pressure fluid, wherein the boost valve assembly communicates hydraulic fluid to the fourth port when the hydraulic pressure fluid exceeds a threshold pressure.

In another example of the present invention, a control solenoid is in direct fluid communication with the spool of the control valve, and the control solenoid selectively communicates a hydraulic pressure fluid signal that is on the slider acts to move the slider between the first and second positions.

In yet another example of the present invention, the control solenoid valve is a normally-off, variable-force solenoid valve.

In yet another example of the present invention, the control valve assembly includes a signal port that communicates with a first end of the spool, and the control solenoid valve is in direct fluid communication with the signal port.

In yet another example of the present invention, a control valve assembly includes a signal port in direct communication with the control solenoid, an inlet in communication with the source of hydraulic pressure fluid, an outlet in direct communication with the first port of the control valve assembly, a return port, and a port A control slide movable between a plurality of positions, and the signal port and the return port communicate with opposite ends of the control spool, and the position of the control spool controls the amount of hydraulic pressure fluid communicated from the inlet to the outlet.

In yet another example of the present invention, the boost valve assembly includes a first inlet in communication with the source of hydraulic pressure fluid, a second inlet in communication with the source of hydraulic pressure fluid through a first orifice, an outlet in direct communication with the fourth port, and a second port A reinforcement slide movable between at least first and second positions, wherein the reinforcement slider prevents fluid communication between the first inlet and the outlet when in the first position, and the reinforcement slider allows fluid communication between the first inlet and the outlet when he is in the second position.

In yet another example of the present invention, the reinforcement slider includes a first end, a second end in communication with the second inlet, and a biasing member in contact with the first end, wherein the reinforcement slider is moved to the second position when a force is applied a second end acts by the hydraulic pressure fluid exceeding a force acting on the first end by the biasing member.

In yet another example of the present invention, a second orifice is disposed directly between the outlet of the boost valve assembly and the fourth port of the control valve assembly.

In yet another example of the present invention, the outlet communicates directly with the source of hydraulic pressure fluid through a third orifice.

In yet another example of the present invention, the threshold pressure is defined as the pressure from the source of hydraulic pressure fluid associated with normal operating conditions of the motor vehicle.

In yet another example of the present invention, hydraulic fluid communicated to the apply-side port engages the torque converter lock-up clutch, and hydraulic fluid communicated to the release-side port disengages the torque converter lock-up clutch.

Other features, aspects, and advantages of the present invention will become apparent by reference to the following description and the accompanying drawings, in which like reference characters refer to the same component, component, or feature.

BRIEF DESCRIPTION OF THE DRAWINGS

The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way.

1 FIG. 12 is a diagram of a hydraulic control subsystem in a first operating state in accordance with the principles of the present invention; FIG.

2 FIG. 12 is a diagram of the hydraulic control subsystem in a second operating state in accordance with the principles of the present invention; FIG.

3 FIG. 12 is a diagram of the hydraulic control subsystem in a third mode of operation in accordance with the principles of the present invention; FIG. and

4 FIG. 12 is a diagram of the hydraulic control subsystem in a fourth operating condition in accordance with the principles of the present invention. FIG.

DESCRIPTION

With reference to 1 FIG. 13 is a control subsystem of a torque converter (DWK) of a hydraulic control system for a transmission according to the principles of the present invention, generally designated by reference numerals 100 specified. The DWK subsystem 100 is operable to control the operating state of a torque converter clutch 102 working in a torque converter 104 is arranged to control. The DWK subsystem 100 stands with a pressure regulator subsystem 106 and a cooling subsystem 108 in hydraulic connection. It should be noted that the DWK subsystem 100 may be associated with various other hydraulic control subsystems, such as ETRS or manual shift valve subsystems, lubrication subsystems, and / or clutch actuation subsystems, without departing from the scope of the present invention.

The pressure regulator subsystem 106 is operable to supply hydraulic pressure fluid, such as transmission oil, to the DWK subsystem 100 to deliver and to regulate. The pressure regulator subsystem 106 may have various configurations, but generally draws hydraulic fluid from a sump (not shown). The hydraulic fluid is forced out of the sump via a pump (not shown) and through the DWK subsystem 100 and various other connected subsystems. The pump is preferably driven by an engine (not shown) and may be, for example, a gear pump, a vane pump, an internal gear pump or any other positive displacement pump. The pressure regulator subsystem 106 may also include an alternative source of hydraulic fluid, including an auxiliary pump (not shown), which is preferably powered by an electric engine, battery, or other power plant (not shown). The pressure and flow rates of the hydraulic fluid in the pressure regulator subsystem 106 can also be controlled by various connecting valves and solenoid valves, such as line pressure regulator valves, one-way valves and so on. The cooling subsystem 108 is used to dissipate heat stored in the hydraulic fluid. The cooling subsystem 108 may include various connected components (not shown), for example an oil cooler, valves and filters.

The DWK subsystem 100 includes a DWK regulator valve assembly 110 , a DWK control valve assembly 112 and a lubrication boost valve assembly 114 , The DWK regulator valve 110 includes fluid connections 110A -F. fluid port 110A communicates with a boarding line 120 and aperture 121 , fluid port 110B is a drain port that communicates with the sump (not shown) or a drain backfill circuit. fluid port 110C communicates with the boarding line 120 , fluid port 110D communicates with a main supply line 122 , The main supply line 122 conducts hydraulic pressure fluid at line pressure (ie, pump pressure) from the pressure regulator subsystem 106 to. fluid port 110E communicates with a signal line 124 , The signal line communicates with a solenoid valve 126 , The solenoid valve 126 is preferably a normally-in-position solenoid valve with variable force. fluid line 110F communicates with a signal line 127 that with a solenoid valve 128 communicated.

The DWK regulator valve 110 further comprises a slide valve 130 and a shuttle valve 131 that within a bore 132 are arranged displaceably. The slider 130 automatically changes the position to the flow from the main supply line 122 to the launch line 120 to control. The position of the slider 130 is from the solenoid valve 126 modulated. If, for example, the solenoid valve 126 is opened, pressurized fluid through the signal line 124 supplied, and fluid pressure acts on the slide valve 130 through the fluid connection 110E and moves the slide valve 130 against a spring 134 in an extended position. The slide valve 130 is by the spring 134 operated in a retracted position when the solenoid valve 126 closed is. When the slide valve 130 is retracted, is fluid connection 110D disconnected while fluid connection 110C by emptying connection 110B emptied. When the slide valve 130 is extended, in 2 shown is the discharge port 110B separated and fluid connection 110D feeds hydraulic pressure fluid into fluid port 1100 one. Return pressure is the valve spool 130 via fluid connection 110A fed. Return pressure acts on the opposite side of the slider 130 and there will be a force balance between the commanded pressure from the solenoid valve 126 and the return pressure on the slider 130 reached.

The DWK control valve 112 includes connections 112A -H. fluid port 112A communicates with the signal line 124 and therefore the solenoid valve 126 , fluid port 112B communicates with the boarding line 120 , fluid port 112C communicates with a DWK management line 136 , The DWK landing line 136 communicates with the torque converter clutch 102 , fluid port 112D communicates with a radiator line 138 , The radiator line 138 communicates with the cooler subsystem 108 , fluid port 112E communicates with a radiator boost line 140 , fluid port 112F communicates with a converter feed line 142 and a panel 143 , The converter feed line 142 provides hydraulic pressure fluid at a regulated pressure (ie, pressure delivered by a regulator valve is regulated) of the pressure regulator subsystem 106 , The converter feed line 142 also communicates with the radiator boost line 140 through a panel 144 , The fluid connection 112G communicates with a DWK release line 146 , The DWK release line 146 communicates with the torque converter clutch 102 and a pressure relief valve 148 , When the pressure of the hydraulic fluid in the DWK release line 146 exceeds a pressure threshold, the pressure relief valve opens 148 immediately to the pressure of the hydraulic fluid within the DWK release line 146 to relax and reduce. fluid port 112H is a drain port that communicates with the sump (not shown) or a drain backfill circuit.

The DWK control valve 112 further comprises a slide valve 150 that in a hole 152 slidably arranged. For example, when pressurized fluid through the signal line 124 by opening the solenoid valve 126 is supplied, fluid pressure acts on the slide valve 150 through the fluid connection 112A and moves the slide valve 150 against a spring 154 in an extended position. The slide valve 150 is by the spring 154 operated in a retracted position when the solenoid valve 126 closed is. When the slide valve 150 is retracted, in 1 shown is fluid connection 112B separated, fluid connection 112D communicates with fluid connection 112C , Fluid connection 112E is disconnected and fluid connection 112F communicates with fluid connection 112G , When the slide valve 150 is extended, in 2 shown communicates fluid connection 112B with fluid connection 112C , Fluid connection 112E communicates with fluid connection 112D , Fluid connection 112F is disconnected and fluid connection 112G communicates with fluid connection 112H ,

The lubrication boost valve 114 includes fluid connections 114A -C. fluid port 114A communicates with the converter supply line 142 , the hydraulic pressure fluid at a regulated pressure (ie, pressure regulated by a regulator valve) from the pressure regulator subsystem 106 supplies. fluid port 114B communicates with the radiator boost line 140 over a panel 156 , fluid port 114C communicates with the converter supply line 142 over a panel 158 ,

The lubrication boost valve 114 further comprises a slide valve 160 that in a hole 162 slidably arranged. The slide valve 160 has a first end 160A and a second end 160B on. For example, when pressurized fluid passes through the transducer feed line 142 is supplied, fluid pressure acts on the second end 160B of the slide valve 160 through the fluid connection 114C and moves the slide valve 160 against a spring 164 that's on the first end 160A acts in an extended position. The slide valve 160 is by the spring 164 operated in a retracted position when the pressure acting on the slide valve 160 acts, drops, for example, when fluid connection 112F by movement of the slide valve 150 of the DWK control valve 112 is opened. When the slide valve 160 is retracted, in 1 shown are fluid connections 114A and 114B separated. When the slide valve 160 is extended, in 2 shown communicates fluid connection 114A with fluid connection 114B ,

To the torque converter clutch 102 to solve, in 1 shown, the solenoid valve 126 closed, reducing both the DWK regulator valve 110 as well as the DWK control valve 112 be placed in the retracted positions. This prevents the regulator feed line 120 with the main supply line 122 and the DWK-Leadship 136 communicates while the DWK release line 146 with hydraulic fluid at regulated pressure from the transducer supply line 142 is fed. The DWK landing line 136 gets into the cooler subsystem 108 over the radiator line 138 emptied.

2 facing the torque converter clutch 102 to apply, the solenoid valve 126 opened, causing both the DWK regulator valve 110 as well as the DWK control valve 112 is moved to the extended position. In addition, the lubrication boost valve becomes 114 due to an increase in the pressure at the fluid port 114C Exceeding a threshold pressure, extended. The threshold pressure is considered pressure from the pressure regulator subsystem 106 defined associated with normal vehicle operating conditions. This provides an increase in the amount of fluid to the cooling subsystem 108 , In extended conditions, the main supply line feeds 122 Hydraulic pressure fluid in the Anlegeleitung 120 in turn, the hydraulic fluid of the DWK-Anlegeleitung 136 supplies. Hydraulic fluid, that of the DWK-Anlegeleitung 136 is fed, the torque converter clutch moves 102 on or press this. In addition, the DWK release line 146 through connection 112H drained and hydraulic fluid becomes the cooler subsystem 108 through the radiator pipes 138 and 140 from the converter feed line 142 cleverly.

In the unlikely event that the DWK regulator valve 110 stuck in the extended condition is the DWK control valve 112 designed so as to always hydraulic fluid to the DWK-Anlegeleitung 136 to transmit and therefore cooling and lubrication to the torque converter 104 to deliver.

3 and 4 facing, is a means of detecting whether the DWK control valve 112 stuck in the extended position, illustrated. In addition to that, the solenoid valve 126 is capable of the DWK regulator valve 130 To operate, the DWK regulator valve 130 from the solenoid valve 128 be operated. For example, the solenoid valve 128 a hydraulic fluid signal to the DWK regulator valve 130 via wire 127 deliver with connection 110F connected is. This hydraulic fluid signal acts on the DWK regulator shuttle valve 131 that with the slider 130 is in contact with the DWK governor slide valve 130 to move to the extended position without the position of the DWK control valve 112 to influence.

3 shows the condition under which the solenoid valve 126 is closed and the DWK control valve 112 is arranged in the normal or retracted position. When the solenoid valve 128 operated under these conditions to provide increased hydraulic fluid pressure, this increased pressure by conduction 127 to connection 110F to be led. The increased oil pressure in connection 110F in turn acts on the DWK regulator shuttle valve 131 to the DWK regulator valve 130 to move to the extended position. Pressure from the pressure regulator subsystem 106 is by wire 122 to connection 110D guided. With the DWK regulator valve in the extended position 130 communicates connection 110D with connection 110C , and pressure from the pressure regulator subsystem 106 is by wire 120 to connection 112B at the DWK control valve 112 guided. When in the retracted position arranged DWK control valve 112 is connection 112B disconnected, so there is no change in the oil feed configuration to the torque converter clutch 102 as a result of which there is the solenoid valve 128 is actuated to an increased pressure. Without changing the oil feed configuration to the torque converter clutch 102 There will be no change in the operating state of the torque converter clutch 102 give.

By monitoring the engine speed and the transmission input speed during this time, it can be verified that the operating state of the torque converter clutch 102 remains unchanged and the release mode is maintained. If no change in the operating state of the torque converter clutch 102 is detected while the solenoid valve 128 is pressed to an elevated pressure, then it verifies that the DWK control valve 112 is arranged in the retracted position.

4 shows the condition under which the solenoid valve 126 is closed and the DWK control valve 112 is arranged in the fixed or extended position. When the solenoid valve 128 is operated under these conditions to an elevated pressure, this pressure is by line 127 to connection 110F guided. The increased oil pressure in connection 110F in turn acts on the DWK regulator shuttle valve 131 to the DWK regulator valve 130 to move to the extended position. Hydraulic fluid from the pressure regulator subsystem 106 is by wire 122 to connection 110D guided. With the DWK regulator valve in the extended position 130 communicates connection 110D with connection 110C , and hydraulic fluid from the pressure regulator subsystem 106 is by wire 120 to connection 112B at the DWK control valve 112 guided. With the DWK control valve stuck in the extended position 112 communicates connection 112B with connection 112C , The hydraulic fluid pressure of port 112C is by wire 136 to the torque converter clutch 102 guided. Hydraulic fluid pressure from the other side of the torque converter clutch 102 is by wire 146 to connection 112G guided. When the DWK control valve is stuck in the extended position, the port communicates 112G with connection 112H which is connected to the drain. Under this condition, the torque converter clutch becomes 102 from the released state to the applied state.

By monitoring the engine speed and the transmission input speed during this time, it can be verified that there is a change in the operating state of the torque converter clutch 102 from solved to created there. If this change in the operating state of the torque converter clutch 102 is detected while the solenoid valve 128 is pressed to an elevated pressure, then it verifies that the DWK control valve 112 stuck in the extended position and a suitable reaction can be commanded.

The description of the invention is merely exemplary in nature, and modifications which do not depart from the gist of the invention are intended to be within the scope of the invention. Such modifications are not to be regarded as a departure from the spirit and scope of the invention.

Claims (10)

A system for a motor vehicle, comprising: a source of hydraulic pressure fluid; a torque converter actuator operable to engage a torque converter lock-up clutch, the torque converter actuator having a release-side port and a apply-side port; a cooler subsystem; a control valve assembly having a first port in communication with the source of hydraulic pressure fluid, a second port in communication with the apply-side port, a third port in communication with the radiator subsystem, a fourth port, a fifth port in communication with the source of hydraulic pressure fluid, a sixth port in communication with the release port and a spool movable between at least a first position and a second position, the first and fourth ports being separate The second terminal communicates with the third terminal and the fifth terminal communicates with the sixth terminal when the slider is in the first position, and wherein the first terminal communicates with the second terminal, the fourth terminal communicates with the third terminal, and the second terminal fifth terminal is disconnected when the slider is in the second position; and a boost valve assembly disposed directly between the fourth port and the source of hydraulic pressure fluid, wherein the boost valve assembly communicates hydraulic fluid to the fourth port when the hydraulic pressure fluid exceeds a threshold pressure. The system of claim 1, further comprising a control solenoid valve in direct fluid communication with the spool of the control valve, wherein the control solenoid selectively communicates a hydraulic pressure fluid signal acting on the spool to move the spool between the first and second positions. The system of claim 2, wherein the control solenoid valve is a normally-off solenoid variable force solenoid. The system of claim 2, wherein the control valve assembly includes a signal port that communicates with a first end of the spool, and wherein the control solenoid valve is in direct fluid communication with the signal port. The system of claim 2, further comprising a regulator valve assembly having a signal port in direct communication with the control solenoid valve, an inlet in communication with the source of hydraulic pressure fluid, an outlet in direct communication with the first port of the control valve assembly, a return port and a control spool movable between a plurality of positions, the signal port and the return port communicating with opposite ends of the control spool and the position of the spool controlling the amount of hydraulic pressure fluid communicated from the inlet to the outlet. The system of claim 1, wherein the boost valve assembly includes a first inlet in communication with the source of hydraulic pressure fluid, a second inlet in communication with the source of hydraulic pressure fluid through a first orifice, an outlet in direct communication with the fourth port, and a boost valve; which is movable between at least first and second positions, wherein the reinforcement slide prevents fluid communication between the first inlet and the outlet when in the first position, and the reinforcement slide allows fluid communication between the first inlet and the outlet when it does located in the second position. The system of claim 6, wherein the reinforcement slider includes a first end, a second end in communication with the second inlet, and a biasing member in contact with the first end, wherein the reinforcement slider is moved to the second position when a force responsive to a second End acts by the hydraulic pressure fluid, exceeds a force acting on the first end by the biasing member. System according to claim 7, further comprising a second orifice disposed directly between the outlet of the boost valve assembly and the fourth port of the control valve assembly, the outlet communicating directly with the source of hydraulic pressure fluid through a third orifice. The system of claim 1, wherein the threshold pressure is defined as the pressure from the source of hydraulic pressure fluid associated with normal operating conditions of the motor vehicle. The system of claim 1, wherein hydraulic fluid communicated to the apply-side port engages the torque converter lock-up clutch and hydraulic fluid communicated to the release-side port disengages the torque converter lock-up clutch.

Images