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WO2011033179A2 - Arrangement for operating a gas exchange valve - Google Patents

Arrangement for operating a gas exchange valve Download PDF

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Publication number
WO2011033179A2
WO2011033179A2 PCT/FI2010/050724 FI2010050724W WO2011033179A2 WO 2011033179 A2 WO2011033179 A2 WO 2011033179A2 FI 2010050724 W FI2010050724 W FI 2010050724W WO 2011033179 A2 WO2011033179 A2 WO 2011033179A2
Authority
WO
WIPO (PCT)
Prior art keywords
valve
hydraulic fluid
pressure chamber
gas exchange
valve member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/FI2010/050724
Other languages
French (fr)
Other versions
WO2011033179A3 (en
Inventor
Matti Vilenius
Kalevi Huhtala
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wartsila Finland Oy
Original Assignee
Wartsila Finland Oy
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wartsila Finland Oy filed Critical Wartsila Finland Oy
Publication of WO2011033179A2 publication Critical patent/WO2011033179A2/en
Publication of WO2011033179A3 publication Critical patent/WO2011033179A3/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/04—Sensors
    • F01L2820/045—Valve lift

Definitions

  • the present invention relates to an arrangement for operating a gas exchange valve of an engine.
  • the gas exchange valves i.e. inlet and exhaust valves in the piston engines are moved toward closed position by springs and opened at desired moments by engine driven camshaft.
  • This type of the operating system has a disadvantage that the timing of valve opening and closing, lift and speed of the valve are predetermined and fixed through the operating range of the engine. Therefore, the engine performance is a compromise in most operating conditions and optimal operating conditions cannot be reached.
  • the object of the present invention is to provide an improved arrangement for op- erating the gas exchange valve of the piston engine.
  • the arrangement according to the invention comprises a hydraulic actuator for moving the gas exchange valve toward an open position by hydraulic fluid pressure acting in a pres- sure chamber of the hydraulic actuator, a hydraulic fluid source and a drain line.
  • the arrangement further comprises a proportional control valve having a valve member and an electrical actuator arranged to directly move the valve member.
  • the valve member is movable to a first main position, in which the control valve is arranged to connect the hydraulic fluid source to the pressure chamber, and a main second position, in which the control valve is arranged to connect the pressure chamber to the drain line.
  • the flow hydraulic fluid to and from the actuator can be controlled as desired because the proportional valve has a plurality of intermediate positions between the main positions. As a re- suit, the movement of the gas exchange valve can be controlled precisely. Further, the gas exchange valves can be operated individually in a desired manner over the operating range of the engine.
  • the proportional control valve has a third main position in which the flow of hydraulic fluid through the valve to and from the actuator can be prevented.
  • the movement of the gas exchange valve can be stopped at the desired moment.
  • the drawing shows an arrangement 1 for operating gas exchange valve(s) 2 i.e. inlet or exhaust valve(s) of the piston engine.
  • the engine is a large piston engine which can be used in ships or power plants.
  • the engine can be an otto or a diesel engine.
  • the engine comprises an engine block with a plurality of cylinders (not shown).
  • the engine also comprises a cylinder head, which together with a piston and a cylinder liner defines a combustion chamber of the cylinder.
  • the cylinder head is provided with an inlet port opening into the combustion chamber. Combus- tion air is fed into the cylinder through the inlet port.
  • the flow in the inlet port is controlled by an inlet valve.
  • the cylinder head is provided with an exhaust port opening into the combustion chamber.
  • Exhaust gas is discharged from the cylinder through the exhaust port.
  • the flow in the exhaust port is controlled by the exhaust valve.
  • Each cylinder has at least one inlet valve and one exhaust valve.
  • each cylinder has two inlet valves and two exhaust valves.
  • the arrangement for operating the gas exchange valve comprises a hydraulic actuator 3 for moving the gas exchange valve or valves 2 toward an open position.
  • the actuator 3 is arranged to move either both inlet valves or both exhaust valves.
  • the stems 4 of the gas exchange valves to be actuated by a single actuator 3 are mechanically bridged together by means of a yoke 5.
  • the hydraulic actuator 3 comprises a movable piston 6.
  • the hydraulic actuator 3 comprises a pressure chamber 7 for hydraulic fluid, for example hydraulic oil.
  • the pressure chamber 7 is delimited by a piston surface 8 of the piston 6. Additionally, the hydraulic actuator 3 comprises a further pressure chamber 9 for hydraulic fluid.
  • the further pressure chamber is delimited by a further piston 10 surface of the piston 6.
  • the area of the piston surface 8 is larger than that of the further piston surface 10.
  • the pressure of the hydraulic fluid in the pressure chamber 7 acts on the piston surface 8, thus urging the piston 6 downwards and the gas exchange valves 2 toward an open position.
  • the pressure of the hydraulic fluid in the further pressure chamber 9 acts on the further piston surface 10 and urges the piston 3 upwards.
  • the gas exchange valves 2 are urged upwards i.e. toward the closed position by springs 22 arranged around the valve stems 4.
  • the arrangement 1 comprises a hydraulic fluid source, for example a hydraulic accumulator 1 1 for hydraulic fluid.
  • the hydraulic accumulator 1 1 is in continuous flow connection with the further pressure chamber 9 through a feed line 12.
  • the arrangement 1 comprises a pump 13 for feeding hydraulic fluid into the hydraulic accumulator 1 1 and the feed line 12.
  • the feed line 12 is connected through a pressure relief 14 valve to a drain, for example a drain line 15.
  • the pressure relief valve 14 is arranged to open when the pressure in the feed line 12 exceeds a predetermined value.
  • the pressure in the drain 15 is lower than that in the hydraulic fluid source 1 1.
  • a connecting line 16 is in flow connection with the pressure chamber 7. Hydraulic fluid can be fed to and discharged from the pressure chamber 7 through the connecting line 16.
  • the flow of hydraulic fluid into and out of the pressure chamber 7 is controlled by a proportional control valve 17, preferably by an electrically controlled proportional control valve.
  • the control valve 17 is actuated by an electromagnetic actuator 18, for example a solenoid or voice coil.
  • the control valve 17 comprises a valve member 19, for example a spool, which is directly actuated by the actuator 18.
  • the movement of the valve member 19 is proportional to the control signal (current or voltage) driving the actuator 18.
  • the motion of the valve member 19 varies the cross-sectional flow area through the control valve 17, which in turn varies the flow rate of the hydraulic fluid through the control valve 17 proportionally.
  • the valve member 19 has an unlimited number of stable positions.
  • the positions of the valve member 19 are proportional to the control signal fed to the actuator 18.
  • the control valve 17 is of a 3-position, 3-way type.
  • the connecting line 16, feed line 12 and discharge line 15 are connected to the control valve 17.
  • the valve member 19 has three main positions. In the first main position of the valve member 19, the control valve 17 connects the hydraulic fluid source 1 1 to the pressure chamber 7. Thus, hydraulic fluid can flow from the hydraulic fluid source 1 1 through connecting line 16 into the pressure chamber 7. Further, in the first main position, the control valve 17 prevents the flow of hydraulic fluid from the pressure chamber 7 into the drain line 15. In the first main position the cross sectional flow area through the control valve 17 toward pressure chamber 7 is at the maximum.
  • control valve 17 connects the pressure chamber 7 to the drain line 15.
  • hydraulic fluid can flow from the pressure chamber 7 to the drain 15.
  • the control valve 17 prevents the flow of hydraulic fluid from the hydraulic fluid source 11 to the pressure chamber 7.
  • the cross-sectional flow area through the control valve 17 toward drain line 15 is at the maximum.
  • control valve 17 prevents the flow of hydraulic fluid from the hydraulic fluid source 1 1 to the pressure chamber 7 and from the pressure chamber 7 to the drain line 15.
  • valve member 19 As the valve member 19 is moved from the first main position to the third main position, the cross sectional flow area of the control valve 17, through which hydraulic fluid can flow from the hydraulic fluid source 1 1 into the pressure chamber 7, decreases.
  • the valve member 19 has an unlimited number or plurality of stable positions between the first and third main positions. This enables the adjustment of the flow of the hydraulic fluid from the hydraulic fluid source 1 1 to the pressure chamber 7 in a desired manner.
  • valve member 19 As the valve member 19 is moved from the second main position to the third main position, the cross sectional flow area of the control valve 17, through which hydraulic fluid can flow from the pressure chamber 7 to the drain pipe 15, decreases.
  • the valve member 19 has an unlimited number or plurality of stable positions between the second and third main positions. In this way, the flow of the hydraulic fluid from the pressure chamber 7 to the drain line 15 can be adjusted in a desired manner.
  • the arrangement 1 comprises a control unit 20 arranged to control the position of the valve member 19. Additionally, the arrangement 1 comprises a sensor 21 for measuring the position of the piston 6.
  • the sensor 21 is attached to the piston 6.
  • the sensor 6 can be of LVDT (Linear Variable Differential Transformer) type.
  • LVDT is an electromechanical transducer that can convert the rectilinear motion of an object, to which is mechanically coupled, into a corresponding electrical signal.
  • the measuring data of the sensor 21 is transferred to the control unit 20.
  • the valve member 19 is moved to the first main position or a intermediate position between the first and third main positions. Hydraulic fluid from the hydraulic accumulator 1 1 flows through the control valve 17 into the pressure chamber 7.
  • the pressure in the pressure chamber 7 increases as well as the pressure force acting onto the piston surface 18 of the piston 6. As the pressure force acting onto the piston surface 18 exceeds sum of the force of the springs 22 and the pressure force acting onto the further piston surface 10, the piston starts 6 to move downward and urges the gas exchange valves 2 toward an open position.
  • the opening speed of the gas exchange 2 valves can be controlled.
  • the motion of the gas exchange valves 2 can be stopped at a desired position by moving the valve member 19 to the third main position. If desired, the gas exchange valves 2 can be stopped at an intermediate position between fully open and fully closed positions.
  • valve member 19 To close the gas exchange valves 2 the valve member 19 is moved to the second main position or an intermediate position between second and third main positions. Hydraulic fluid from the pressure chamber 7 flows through the control valve 17 into the drain line 15. The pressure in the pressure chamber 7 decreases as well as the pressure force acting onto piston surface 8 of the piston 6. As a result, the force of the springs 22 and the pressure force acting onto the further piston surface 10 start to move piston 6 upward and the gas exchange valves 2 toward the closed position. By adjusting the flow rate of hydraulic fluid into the drain line 15 the closing speed of the gas exchange valves 2 can be controlled. The motion of the gas ex- change valves 2 can be stopped at a desired position by moving the control valve 17 to the third main position.
  • the control unit 20 controls the position of the valve member 19 by outputting control signals to the actuator 18.
  • the control can be performed as a position feedback control of the piston 6.
  • Measuring data from the piston position sensor 21 is transmitted to the control unit 20, which is arranged to control the position of the valve member 19 on the basis of the position measurement data of the piston 6.
  • the control system compares the measured value to a set value. If the measured value differs from the set value, the control unit 20 adjusts the position of the valve member 19 so that the measured value approaches the set value.
  • the set value can be a predetermined value based on the engine load and/or other operating conditions of the engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

The invention relates to an arrangement (1) for operating a gas exchange valve (2) of a piston engine. The arrangement comprises a hydraulic actuator (3) for moving the gas exchange valve (2) toward an open position by pressure of hydraulic fluid acting in a pressure chamber (7) of the hydraulic actuator (3), a hydraulic fluid source, (11) and a drain line(15). The arrangement (1) further comprises a proportional control valve (17) having a valve member (19) and an electrical actuator (18) arranged to directly move the valve member(19). The valve member(19) is movable to a first main position, in which the control valve (17) is arranged to connect the hydraulic fluid source (11) to the pressure chamber (7), and a second main position, in which the control valve (17) is arranged to connect the pressure chamber (7) to the drain line (15).

Description

ARRANGEMENT FOR OPERATING A GAS EXCHANGE VALVE
The present invention relates to an arrangement for operating a gas exchange valve of an engine.
Typically the gas exchange valves i.e. inlet and exhaust valves in the piston engines are moved toward closed position by springs and opened at desired moments by engine driven camshaft. This type of the operating system has a disadvantage that the timing of valve opening and closing, lift and speed of the valve are predetermined and fixed through the operating range of the engine. Therefore, the engine performance is a compromise in most operating conditions and optimal operating conditions cannot be reached.
Recently, camless valve operating systems for piston engines have been devel- oped. Usually, the gas exchange valves of the engine are operated by hydraulic actuators which enable more flexible control of the gas exchange valves over the entire operating range of the engine.
The object of the present invention is to provide an improved arrangement for op- erating the gas exchange valve of the piston engine.
The object of the invention is achieved as disclosed in claim 1. The arrangement according to the invention comprises a hydraulic actuator for moving the gas exchange valve toward an open position by hydraulic fluid pressure acting in a pres- sure chamber of the hydraulic actuator, a hydraulic fluid source and a drain line. The arrangement further comprises a proportional control valve having a valve member and an electrical actuator arranged to directly move the valve member. The valve member is movable to a first main position, in which the control valve is arranged to connect the hydraulic fluid source to the pressure chamber, and a main second position, in which the control valve is arranged to connect the pressure chamber to the drain line. Significant benefits can be achieved by means of the invention. The flow hydraulic fluid to and from the actuator can be controlled as desired because the proportional valve has a plurality of intermediate positions between the main positions. As a re- suit, the movement of the gas exchange valve can be controlled precisely. Further, the gas exchange valves can be operated individually in a desired manner over the operating range of the engine.
According to one embodiment of the invention, the proportional control valve has a third main position in which the flow of hydraulic fluid through the valve to and from the actuator can be prevented. Thus, the movement of the gas exchange valve can be stopped at the desired moment.
In the following, the invention will be explained in more detail, by way of example, with reference to the appended drawing, which illustrates schematically one arrangement according to the invention.
The drawing shows an arrangement 1 for operating gas exchange valve(s) 2 i.e. inlet or exhaust valve(s) of the piston engine. The engine is a large piston engine which can be used in ships or power plants. The engine can be an otto or a diesel engine. The engine comprises an engine block with a plurality of cylinders (not shown). The engine also comprises a cylinder head, which together with a piston and a cylinder liner defines a combustion chamber of the cylinder. The cylinder head is provided with an inlet port opening into the combustion chamber. Combus- tion air is fed into the cylinder through the inlet port. The flow in the inlet port is controlled by an inlet valve. Correspondingly, the cylinder head is provided with an exhaust port opening into the combustion chamber. Exhaust gas is discharged from the cylinder through the exhaust port. The flow in the exhaust port is controlled by the exhaust valve. Each cylinder has at least one inlet valve and one exhaust valve. In the embodiment shown in the drawing, each cylinder has two inlet valves and two exhaust valves. The arrangement for operating the gas exchange valve comprises a hydraulic actuator 3 for moving the gas exchange valve or valves 2 toward an open position. In the embodiment shown the actuator 3 is arranged to move either both inlet valves or both exhaust valves. The stems 4 of the gas exchange valves to be actuated by a single actuator 3 are mechanically bridged together by means of a yoke 5. The hydraulic actuator 3 comprises a movable piston 6. The hydraulic actuator 3 comprises a pressure chamber 7 for hydraulic fluid, for example hydraulic oil. The pressure chamber 7 is delimited by a piston surface 8 of the piston 6. Additionally, the hydraulic actuator 3 comprises a further pressure chamber 9 for hydraulic fluid. The further pressure chamber is delimited by a further piston 10 surface of the piston 6. The area of the piston surface 8 is larger than that of the further piston surface 10. The pressure of the hydraulic fluid in the pressure chamber 7 acts on the piston surface 8, thus urging the piston 6 downwards and the gas exchange valves 2 toward an open position. The pressure of the hydraulic fluid in the further pressure chamber 9 acts on the further piston surface 10 and urges the piston 3 upwards. The gas exchange valves 2 are urged upwards i.e. toward the closed position by springs 22 arranged around the valve stems 4.
The arrangement 1 comprises a hydraulic fluid source, for example a hydraulic accumulator 1 1 for hydraulic fluid. The hydraulic accumulator 1 1 is in continuous flow connection with the further pressure chamber 9 through a feed line 12. Further, the arrangement 1 comprises a pump 13 for feeding hydraulic fluid into the hydraulic accumulator 1 1 and the feed line 12. The feed line 12 is connected through a pressure relief 14 valve to a drain, for example a drain line 15. The pressure relief valve 14 is arranged to open when the pressure in the feed line 12 exceeds a predetermined value. The pressure in the drain 15 is lower than that in the hydraulic fluid source 1 1. A connecting line 16 is in flow connection with the pressure chamber 7. Hydraulic fluid can be fed to and discharged from the pressure chamber 7 through the connecting line 16.
The flow of hydraulic fluid into and out of the pressure chamber 7 is controlled by a proportional control valve 17, preferably by an electrically controlled proportional control valve. The control valve 17 is actuated by an electromagnetic actuator 18, for example a solenoid or voice coil. The control valve 17 comprises a valve member 19, for example a spool, which is directly actuated by the actuator 18. The movement of the valve member 19 is proportional to the control signal (current or voltage) driving the actuator 18. The motion of the valve member 19 varies the cross-sectional flow area through the control valve 17, which in turn varies the flow rate of the hydraulic fluid through the control valve 17 proportionally. The valve member 19 has an unlimited number of stable positions. The positions of the valve member 19 are proportional to the control signal fed to the actuator 18. The control valve 17 is of a 3-position, 3-way type. The connecting line 16, feed line 12 and discharge line 15 are connected to the control valve 17.
The valve member 19 has three main positions. In the first main position of the valve member 19, the control valve 17 connects the hydraulic fluid source 1 1 to the pressure chamber 7. Thus, hydraulic fluid can flow from the hydraulic fluid source 1 1 through connecting line 16 into the pressure chamber 7. Further, in the first main position, the control valve 17 prevents the flow of hydraulic fluid from the pressure chamber 7 into the drain line 15. In the first main position the cross sectional flow area through the control valve 17 toward pressure chamber 7 is at the maximum.
In the second main position of the valve member 19, the control valve 17 connects the pressure chamber 7 to the drain line 15. Thus, hydraulic fluid can flow from the pressure chamber 7 to the drain 15. In the second main position, the control valve 17 prevents the flow of hydraulic fluid from the hydraulic fluid source 11 to the pressure chamber 7. In the second main position the cross-sectional flow area through the control valve 17 toward drain line 15 is at the maximum.
In the third main position of the valve member 19, the control valve 17 prevents the flow of hydraulic fluid from the hydraulic fluid source 1 1 to the pressure chamber 7 and from the pressure chamber 7 to the drain line 15.
As the valve member 19 is moved from the first main position to the third main position, the cross sectional flow area of the control valve 17, through which hydraulic fluid can flow from the hydraulic fluid source 1 1 into the pressure chamber 7, decreases. The valve member 19 has an unlimited number or plurality of stable positions between the first and third main positions. This enables the adjustment of the flow of the hydraulic fluid from the hydraulic fluid source 1 1 to the pressure chamber 7 in a desired manner.
Correspondingly, as the valve member 19 is moved from the second main position to the third main position, the cross sectional flow area of the control valve 17, through which hydraulic fluid can flow from the pressure chamber 7 to the drain pipe 15, decreases. The valve member 19 has an unlimited number or plurality of stable positions between the second and third main positions. In this way, the flow of the hydraulic fluid from the pressure chamber 7 to the drain line 15 can be adjusted in a desired manner.
The arrangement 1 comprises a control unit 20 arranged to control the position of the valve member 19. Additionally, the arrangement 1 comprises a sensor 21 for measuring the position of the piston 6. The sensor 21 is attached to the piston 6. The sensor 6 can be of LVDT (Linear Variable Differential Transformer) type. LVDT is an electromechanical transducer that can convert the rectilinear motion of an object, to which is mechanically coupled, into a corresponding electrical signal. The measuring data of the sensor 21 is transferred to the control unit 20. To open the gas exchange valve(s) 2, the valve member 19 is moved to the first main position or a intermediate position between the first and third main positions. Hydraulic fluid from the hydraulic accumulator 1 1 flows through the control valve 17 into the pressure chamber 7. The pressure in the pressure chamber 7 increases as well as the pressure force acting onto the piston surface 18 of the piston 6. As the pressure force acting onto the piston surface 18 exceeds sum of the force of the springs 22 and the pressure force acting onto the further piston surface 10, the piston starts 6 to move downward and urges the gas exchange valves 2 toward an open position. By adjusting the flow rate of hydraulic fluid through the control valve 17 into the pressure chamber 7, the opening speed of the gas exchange 2 valves can be controlled. The motion of the gas exchange valves 2 can be stopped at a desired position by moving the valve member 19 to the third main position. If desired, the gas exchange valves 2 can be stopped at an intermediate position between fully open and fully closed positions.
To close the gas exchange valves 2 the valve member 19 is moved to the second main position or an intermediate position between second and third main positions. Hydraulic fluid from the pressure chamber 7 flows through the control valve 17 into the drain line 15. The pressure in the pressure chamber 7 decreases as well as the pressure force acting onto piston surface 8 of the piston 6. As a result, the force of the springs 22 and the pressure force acting onto the further piston surface 10 start to move piston 6 upward and the gas exchange valves 2 toward the closed position. By adjusting the flow rate of hydraulic fluid into the drain line 15 the closing speed of the gas exchange valves 2 can be controlled. The motion of the gas ex- change valves 2 can be stopped at a desired position by moving the control valve 17 to the third main position.
The control unit 20 controls the position of the valve member 19 by outputting control signals to the actuator 18. The control can be performed as a position feedback control of the piston 6. Measuring data from the piston position sensor 21 is transmitted to the control unit 20, which is arranged to control the position of the valve member 19 on the basis of the position measurement data of the piston 6. The control system compares the measured value to a set value. If the measured value differs from the set value, the control unit 20 adjusts the position of the valve member 19 so that the measured value approaches the set value. The set value can be a predetermined value based on the engine load and/or other operating conditions of the engine.

Claims

1. An arrangement (1 ) for operating a gas exchange valve (2) of a piston engine, the arrangement comprising:
- a hydraulic actuator (3) for moving the gas exchange valve (2) toward an open position by pressure of hydraulic fluid acting in a pressure chamber (7) of the hydraulic actuator (3),
- a hydraulic fluid source (1 1 ), and
- a drain line (15),
characterized in that
the arrangement (1 ) comprises a proportional control valve (17) having a valve member (19) and an electrical actuator (18) arranged to directly move the valve member (19), which valve member (19) is movable to:
- a first main position, in which the control valve (17) is arranged to connect the hy- draulic fluid source (1 1 ) to the pressure chamber (7), and
- a second main position, in which the control valve (17) is arranged to connect the pressure chamber (7) to the drain line (15).
2. An arrangement according to claim 1 , characterized in that the valve member (19) is movable to a third main position, in which the control valve (17) prevents the flow of hydraulic fluid from the hydraulic fluid source (1 1 ) to the pressure chamber (7) and from the pressure chamber (7) to the drain line (15).
3. An arrangement according to claim 1 , characterized in that valve member (19) is movable to a plurality of intermediate positions between the first main position and the second main position to adjust the flow rate of hydraulic fluid through the control valve (17).
4. An arrangement according to any preceding claim, characterized in that the proportional control valve (17) is a three-position, three-way valve.
5. An arrangement according to any preceding claim, characterized in that the electrical actuator (18) is a voice coil or a solenoid.
6. An arrangement according to any preceding claim, characterized in that the hy- draulic actuator (3) comprises a piston (6) for moving the gas exchange valve (2) and a sensor (21 ) for measuring the position of the piston (6).
7. An arrangement according to any preceding claim, characterized by a control system (20) arranged to control the position of the valve member (19).
8. An arrangement according to claim 6 and 7, characterized in that the control system (20) is arranged to control the position of the valve member (19) on the basis of the position measurement of the piston (6).
PCT/FI2010/050724 2009-09-21 2010-09-17 Arrangement for operating a gas exchange valve Ceased WO2011033179A2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20095970A FI20095970A7 (en) 2009-09-21 2009-09-21 Arrangement for operating a gas exchange valve
FI20095970 2009-09-21

Publications (2)

Publication Number Publication Date
WO2011033179A2 true WO2011033179A2 (en) 2011-03-24
WO2011033179A3 WO2011033179A3 (en) 2011-06-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/FI2010/050724 Ceased WO2011033179A2 (en) 2009-09-21 2010-09-17 Arrangement for operating a gas exchange valve

Country Status (2)

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FI (1) FI20095970A7 (en)
WO (1) WO2011033179A2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013132149A1 (en) * 2012-03-09 2013-09-12 Wärtsilä Finland Oy Hydraulic actuator and gas exchange valve arrangement
CN105782143A (en) * 2016-03-24 2016-07-20 中国北方发动机研究所(天津) Anti-vibration device of rapid hydraulic adjusting system

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2002225937A1 (en) * 2000-12-04 2002-06-18 Sturman Industries, Inc. Hydraulic valve actuation systems and methods
WO2006081829A1 (en) * 2005-02-02 2006-08-10 Man Diesel A/S A large two-stroke diesel engine with hydraulically actuated exhaust gas valves
US7040266B1 (en) * 2005-05-10 2006-05-09 Gm Global Technology Operations, Inc. Electro-hydraulic engine valve actuation

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013132149A1 (en) * 2012-03-09 2013-09-12 Wärtsilä Finland Oy Hydraulic actuator and gas exchange valve arrangement
CN104160119A (en) * 2012-03-09 2014-11-19 瓦锡兰芬兰有限公司 Hydraulic actuator and gas exchange valve arrangement
CN105782143A (en) * 2016-03-24 2016-07-20 中国北方发动机研究所(天津) Anti-vibration device of rapid hydraulic adjusting system

Also Published As

Publication number Publication date
FI20095970L (en) 2011-03-30
WO2011033179A3 (en) 2011-06-03
FI20095970A7 (en) 2011-03-30

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