WO2010058721A1 - Dispositif de type soupape à commande variable et son procédé de commande - Google Patents

Dispositif de type soupape à commande variable et son procédé de commande Download PDF

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Publication number
WO2010058721A1
WO2010058721A1 PCT/JP2009/069170 JP2009069170W WO2010058721A1 WO 2010058721 A1 WO2010058721 A1 WO 2010058721A1 JP 2009069170 W JP2009069170 W JP 2009069170W WO 2010058721 A1 WO2010058721 A1 WO 2010058721A1
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WO
WIPO (PCT)
Prior art keywords
hydraulic
valve
vva
signal
crank angle
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Application number
PCT/JP2009/069170
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English (en)
Japanese (ja)
Inventor
悦郎 佐藤
英明 橘
陽平 久田
一男 太田
Original Assignee
株式会社小松製作所
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.)
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Application filed by 株式会社小松製作所 filed Critical 株式会社小松製作所
Priority to US13/129,662 priority Critical patent/US20110220045A1/en
Priority to CN2009801465126A priority patent/CN102224325A/zh
Priority to EP09827502A priority patent/EP2357328A1/fr
Publication of WO2010058721A1 publication Critical patent/WO2010058721A1/fr

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    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations

Definitions

  • the present invention relates to a variable valve device and a control method thereof.
  • some engines mounted on a vehicle include a variable valve device that controls the opening / closing timing of an intake valve and an exhaust valve according to the operating state of the engine and adjusts the intake air amount and the exhaust air amount.
  • variable valve devices use an electric motor or hydraulic pressure as a drive source.
  • the hydraulically driven variable valve device driven by hydraulic pressure responds to the hydraulic control depending on the temperature environment such as cold or engine start. In some cases, the control accuracy of the variable valve device is lowered.
  • variable valve device When the control accuracy of the variable valve device is lowered, the opening / closing timing of the intake valve changes, and the compression ratio changes, which may affect combustion.
  • Patent Document 1 the response performance of a valve / actuator whose response performance varies depending on the viscosity of the hydraulic oil is determined based on the measurement result of the viscosity of the hydraulic oil, and the valve / actuator is provided based on the determined response performance.
  • Techniques for a control system and a control method of a variable valve that correct and control the opening / closing timing of the variable valve are disclosed.
  • Patent Document 2 discloses a technology of an engine valve control system and a control method for controlling the operation timing of a variable valve in accordance with the engine temperature environment such as engine temperature, hydraulic oil temperature, fluid temperature, and the like.
  • Patent Document 1 and Patent Document 2 indirectly estimate the operation timing of the variable valve based on the viscosity of the hydraulic oil or the measurement results of the temperature environment such as the engine temperature and the hydraulic oil temperature.
  • the actual opening / closing timing of the intake valve or exhaust valve due to changes in the viscosity of the hydraulic fluid or changes in the temperature environment is not measured. There was a problem that the opening / closing timing of the camera could not be corrected accurately.
  • the present invention has been made in view of the above problems, and actually measures the response performance of a variable valve due to a change in temperature environment, and corrects the opening / closing timing of the variable valve based on the measurement result. And it aims at providing the control method.
  • the first invention has a valve mechanism for moving an intake valve of an engine to open or close an intake port, and a crank angle at which the intake port is fully closed by the valve mechanism.
  • the hydraulic actuator is operated by the movement of the intake valve and discharges the hydraulic oil in the pressurizing chamber provided in the cylinder portion by the closing movement of the intake valve;
  • a hydraulic control valve that controls the supply and discharge of the hydraulic oil to and from the hydraulic actuator, and prevents the intake valve from closing and moving by preventing the hydraulic oil from flowing out of the pressurizing chamber of the hydraulic actuator when closed.
  • a crank angle detection sensor that detects a crank angle that indicates the rotation angle of the crankshaft of the engine, and a TDC detection sensor that detects that each cylinder of the engine has reached top dead center.
  • a hydraulic pressure detecting means for detecting the hydraulic pressure of the pressurizing chamber of the hydraulic actuator, and a predetermined signal based on the detection signal of the TDC detection sensor and the detection signal of the crank angle detection sensor during the closing movement of the intake valve.
  • a controller for outputting a signal and the controller outputs a signal for closing the hydraulic control valve in the current control cycle at the predetermined crank angle, and then adds the signal accompanying the closing operation of the hydraulic control valve.
  • the surge pressure of the hydraulic pressure in the pressure chamber is monitored by the detection signal of the hydraulic pressure detecting means, the operation start crank angle of the hydraulic control valve is obtained based on the surge pressure, and the operation start crank.
  • the output crank angle of the signal for closing the hydraulic control valve and the waveform of the hydraulic control valve are corrected, and the corrected signal is output to the hydraulic control valve in the next control cycle.
  • the controller has the crank angle of the intake port fully closed at which the intake valve is closed after the signal for closing the hydraulic control valve is turned off within a predetermined range. So that at least one of the output crank angle and the waveform of the signal for closing the hydraulic control valve is corrected.
  • the intake valve of the engine is moved by the valve operating mechanism to open or close the intake port, the hydraulic actuator is operated by the movement of the intake valve, and the cylinder provided in the cylinder portion of the hydraulic actuator is provided.
  • the intake valve In the control method of the variable valve device in which the crank angle at which the intake port is fully closed is made variable by preventing the hydraulic oil from flowing out from the pressure chamber, in the current control cycle, the intake valve The hydraulic actuator is actuated by the closed movement to discharge the hydraulic oil in the pressurizing chamber of the hydraulic actuator, and after each cylinder of the engine reaches the respective top dead center, the intake valve is closed during the closed movement.
  • the hydraulic control valve that controls the supply and discharge of the hydraulic oil to and from the hydraulic actuator is closed to prevent the hydraulic oil from flowing out of the pressurizing chamber.
  • the intake valve is prevented from closing movement, the hydraulic control valve is closed for a predetermined time, the intake valve closing movement is stopped, and the intake port is opened at a predetermined opening for a predetermined time.
  • monitoring the surge pressure of the hydraulic pressure in the pressurizing chamber when the hydraulic oil is prevented from flowing out of the pressurizing chamber and determining the actual VVA operation start timing based on the surge pressure, Based on the actual VVA operation start timing, at least one of the output crank angle and the waveform of the signal for closing the hydraulic control valve is corrected, and the corrected signal is supplied to the hydraulic control valve in the next control cycle. It is characterized by output.
  • the actual VVA operation start timing is compared with a predetermined VVA operation start timing set in advance, and the actual VVA operation start timing is compared with the predetermined VVA operation start timing. If it is later than this time, the correction that makes the output crank angle of the signal for closing the hydraulic control valve in the next control cycle earlier than the current output crank angle, and the hydraulic control valve in the next control cycle are closed.
  • the hydraulic pressure of the next control cycle Correction to make the output crank angle of the signal that closes the control valve slower than the current output crank angle, And characterized by at least one of the hydraulic control valve of the next control cycle correction to smaller than the current output value an output value of the signal to be closing operation.
  • the fifth invention is the third invention, wherein the actual VVA operation start timing is compared with a predetermined VVA operation start timing set in advance, and the actual VVA operation start timing is compared with the predetermined VVA operation start timing.
  • the output time of the signal for closing the hydraulic control valve in the next control cycle is made longer than the current output time and the output crank angle is made earlier than the current output crank angle, Or, while making the output time of the signal for closing the hydraulic control valve in the next control cycle longer than the current output time, either one of the corrections to make the output value larger than the current output value.
  • the oil of the next control cycle is Correct the output time of the signal for closing the control valve to be shorter than the current output time and make the output crank angle slower than the current output crank angle, or the hydraulic control valve for the next control cycle. It is characterized in that either the output time of the closing operation signal is made shorter than the current output time, and the correction is made so that the output value
  • the response performance from when the operation command for the hydraulically driven variable valve is issued until the operation corresponding to the operation command is actually performed by the variable valve is measured, and variable based on the response performance. Since the opening / closing timing of the valve is corrected so as to fall within the predetermined timing, the opening / closing timing of the variable valve can be more accurately controlled to the predetermined timing regardless of the temperature environment of the hydraulic oil.
  • the operation corresponding to the operation command for the variable valve is detected by the variable valve based on the measurement result of the hydraulic pressure of the variable valve hydraulic actuator, the actual operation of the variable valve is more accurately performed.
  • the response performance of the variable valve measured and based on the measurement result can be detected more accurately.
  • variable valve device and a control method thereof according to the present invention will be described in detail with reference to the drawings.
  • FIG. 1 is a conceptual diagram showing a variable valve device 1 according to the present invention.
  • the variable valve device 1 will be described assuming that it is applied to a four-cycle diesel engine.
  • the variable valve device is not limited to this embodiment.
  • controller variable valve device control controller
  • the controller 90 performs control according to the present invention based on the measurement results of various signals from the sensors.
  • the gap sensor 24 is connected to the controller 90, and is disposed on the side of a rod portion 23c of the piston 23 described later.
  • the gap sensor 24 measures a gap between the rod portion 23c and the gap sensor 24, and a valve lift amount as a measurement signal thereof.
  • a signal (see FIG. 10D) is output to the controller 90.
  • the TDC detection sensor 70 is connected to the controller 90, detects that the engine piston 80 in the intake stroke is located at the top dead center for each cylinder of the diesel engine unit, and detects the TDC detection sensor signal (FIG. 10A). To the controller 90.
  • the hydraulic pressure detecting means 71 is connected to the controller 90, measures the hydraulic pressure in the pressurizing chamber of the hydraulic actuator 20 described later, and outputs a hydraulic signal (for example, see FIG. 10E) as a measurement signal to the controller 90.
  • crank angle detection sensor 72 measures a rotation angle (hereinafter referred to as “crank angle”) of the crankshaft 82 of the diesel engine unit, and a rotation number detection signal (a pulse having a number of pulses corresponding to the crank angle) as the measurement signal.
  • the output (see FIG. 10B) is output to the controller 90.
  • a pulse signal is output at every predetermined rotation angle such that the crank angle is 0 degrees, 30 degrees, 60 degrees,... 360 degrees,.
  • the crank angle is detected by measuring the pulse signal.
  • the diesel engine section has a cylinder block and a cylinder head, and a cylinder block (not shown) that allows the engine piston 80 to slide in the vertical direction is provided in the cylinder block. Further, the cylinder head is provided with a pair of intake ports 2 inserted outside the cylinder and a pair of exhaust ports (not shown).
  • the pair of intake ports 2 are each provided with an intake valve 3 that moves so as to close or open the intake port 2 (vertical direction in FIG. 1).
  • the pair of exhaust ports is provided with an exhaust port. Exhaust valves (not shown) that move so as to be closed or opened are respectively provided.
  • Each intake valve 3 and each exhaust valve are umbrella-shaped poppet type valves, each having a valve portion (umbrella-shaped portion) 3a for closing or opening the intake port 2 and the exhaust port, and a stem ( Bar-like part) 3b.
  • Valve springs 4 are mounted on stems 3b of the pair of intake valves 3 inserted through the intake ports 2, respectively, and the valve springs 4 are arranged in a direction in which the valve portions 3a of the intake valves 3 close the intake ports 2. Energized.
  • a side-view T-shaped crosshead 5 that presses the ends of the stems 3b of the pair of intake valves 3 is provided above the cylinder head.
  • the crosshead 5 is guided by a shaft 6 provided in parallel with the movement direction of each intake valve 3, and can be moved up and down in the movement direction (vertical direction in FIG. 1) of each intake valve 3.
  • one arm 5a of the crosshead 5 is provided with an adjusting screw 7 for adjusting the intake valve 3 and the crosshead 5 to be in close contact with each other.
  • the adjustment screw 7 can be screwed with respect to the cross head 5 and can adjust a gap between one of the pair of intake valves 3 and the intake valve 3.
  • the gap is adjusted so that the pair of intake valves 3 open and close the respective intake ports 2 simultaneously.
  • a lock nut 8 is screwed onto the adjustment screw 7, and the adjustment screw 7 can be prevented from loosening by bringing the lock nut 8 into close contact with the crosshead 5 after the adjustment screw 7 is adjusted.
  • a rocker arm 9 is provided above the crosshead 5 (in FIG. 1).
  • the rocker arm 9 is rotatable about the rocker shaft 10, and one end portion (left end portion in FIG. 1) forms a pressing portion 9 a that presses the cross head 5, and the other end portion forms an operating portion 9 b. It is configured as follows.
  • the pressing portion 9a of the rocker arm 9 is disposed so as to be able to press the substantially central portion of the cross head 5.
  • the rocker arm 9 is rotated counterclockwise (in FIG. 1), the pressing portion 9a of the rocker arm 9 is The crosshead 5 is pressed, and the intake valve 3 moves downward to open the intake port 2.
  • An adjusting screw 11 that adjusts a gap between the pressing portion 9a and the crosshead 5 is screwed into the operating portion 9b of the rocker arm 9.
  • the adjustment screw 11 has a hemispherical shape at one end, and a male screw is formed at the other end.
  • a lock nut 12 is screwed to the other end portion of the adjustment screw 11 screwed to the operating portion 9 b of the rocker arm 9, and the lock nut 12 is brought into close contact with the rocker arm 9. Sag prevention is possible.
  • the hemispherical one end of the adjusting screw 11 is accommodated in one end of the push rod 13.
  • a hemispherical recess 13a is formed at one end of the push rod 13, and the hemispherical end of the adjusting screw 11 can be accommodated.
  • the push rod 13 rotates the rocker arm 9 counterclockwise (in FIG. 1).
  • the other end portion 13 b of the push rod 13 is housed in a push rod housing portion 14 a provided above the arm portion of the tappet arm 14.
  • a return spring 15 is stretched between the operating portion 9b of the rocker arm 9 and the cylinder head.
  • the return spring 15 urges the rocker arm 9 in the clockwise direction (in FIG. 1), and makes it possible to maintain a state where one end of the adjustment screw 11 is accommodated in the recess 13 a of the push rod 13.
  • the return spring 15 only needs to urge the rocker arm 9 clockwise (in FIG. 1), and may be a torsion coil spring wound around the rocker shaft 10.
  • one end of the coil spring is fixed to the rocker arm 9 and the other end is fixed to the cylinder head.
  • the tappet arm 14 is pivotally attached about the tappet shaft 16, and when the tappet arm 14 rotates clockwise (in FIG. 1), the tappet arm 14 pushes up the push rod 13 to counter the rocker arm 9. Rotate clockwise (in FIG. 1).
  • roller follower 17 is rotatably attached below the arm portion of the tappet arm 14, and a cam 18 that is in rolling contact with the roller follower 17 is rotatably provided below the roller follower 17.
  • the cam 18 rotates in conjunction with the crankshaft 82 of the engine and moves the intake valve 3 through the tappet arm 14, push rod 13, rocker arm 9, and crosshead 5 in a direction in which the intake port 2 is opened. Is possible.
  • the opening timing of the intake port 2 and the valve lift amount of the intake valve 3 are controlled by the outer shape (cam profile) of the cam 18.
  • the movement of the intake valve 3 in the direction of opening the intake port 2 is “open movement”
  • the movement of the intake valve 3 in the direction of closing is “closed movement”
  • all of the intake ports 2 are moved.
  • the amount corresponding to the distance from the position of the intake valve 3 when closed to the position of the intake valve 3 when the intake port 2 is opened is called a “valve lift amount”, and the “valve lift amount” corresponds to the amount.
  • the value when the intake port 2 is fully closed is shown as 0 (zero).
  • a hydraulic actuator 20 is provided above the crosshead 5.
  • the hydraulic actuator 20 is disposed so that the tip of the rod portion 23 c of the piston 23 is in contact with the cross head 5 and can be interlocked with the operation of the cross head 5.
  • the tip of the rod portion 23c presses the cross head 5, and the intake valve 3 is connected to the predetermined intake port 2 regardless of the operations of the cam 18, the tappet arm 14, the push rod 13 and the rocker arm 9. It is comprised so that the open state in an opening degree can be maintained.
  • the hydraulic actuator 20 applied to the present embodiment is a single-acting type, in which a cylinder portion 22 is formed integrally with a block 21, and a hydraulic control valve 30 that controls the flow of hydraulic oil is configured to be housed and attachable. .
  • the hydraulic control valve 30 is a two-port electromagnetic on-off valve having an input port 30a and an output port 30b, for example.
  • the block 21 is formed with a supply / discharge conduit 21 d that communicates the cylinder portion 22 and the output port 30 b of the hydraulic control valve 30, and communicates the output port 50 a of the accumulator 50 and the input port 30 a of the hydraulic control valve 30.
  • a first pipeline 21b is formed.
  • the cylinder portion 22 of the hydraulic actuator 20 is formed with a cylindrical pressurizing chamber 22a. One end of the pressurizing chamber 22a is opened so that the piston 23 can be inserted, and is closed by the piston 23. It is configured as follows.
  • the other end of the pressurizing chamber 22a communicates with the output port 30b of the hydraulic control valve 30 through the supply / discharge pipe 21d.
  • the cylinder portion 22 accommodates a piston 23 slidable in the axial direction (vertical direction in FIG. 1).
  • the piston 23 has a rod portion 23 c that advances to the outside of the cylinder portion 22.
  • the rod portion 23c has a tapered shape formed in a manner of gradually becoming narrower from the root toward the tip, and can press the cross head 5.
  • the gap sensor 24 connected to the controller 90 is provided on the side of the rod portion 23c of the piston 23, and the gap between the rod portion 23c and the gap sensor 24 is measured by the gap sensor 24. .
  • the gap sensor 24 can measure the gap with the rod portion 23c, for example, by measuring eddy current. Since the rod portion 23c has a tapered shape, when the rod portion 23c advances from the cylinder portion 22, the decrease in the gap is measured, and when the rod portion 23c is pulled into the cylinder portion 22, the gap increases. Is measured.
  • the controller 90 can monitor the operation of the rod portion 23c by monitoring the gap with the rod portion 23c measured by the gap sensor 24. Therefore, the controller 90 abuts against the crosshead 5 and The operation (movement amount) of the intake valve 3 can be detected from the operation of the interlocking rod portion 23c.
  • the hydraulic control valve 30 is attached to the block 21. As described above, the hydraulic control valve 30 is a two-port electromagnetic opening / closing valve having the input port 30a and the output port 30b.
  • the hydraulic control valve 30 In the normal state (the state where the solenoid 30d is not excited), the hydraulic control valve 30 communicates with the input port 30a and the output port 30b. When the solenoid 30d is excited, the communication state between the input port 30a and the output port 30b is cut off. To do.
  • the hydraulic control valve 30 can be switched between a hydraulic fluid supply / discharge state and a hydraulic fluid cutoff state.
  • the hydraulic fluid that has flowed out gradually flows out of the hydraulic actuator 20 via the output port 30b and the input port 30a of the hydraulic control valve 30 and the first pipe line 21b, and the piston 23 pressurizes the cylinder portion 22 with the pressure.
  • the series of actions of the hydraulic actuator 20 is completed by being accommodated in the chamber 22a.
  • the solenoid 30d of the hydraulic control valve 30 is connected to the controller 90, and the excitation timing and excitation time of the hydraulic control valve 30 are controlled by the controller 90.
  • the controller 90 can arbitrarily control the hydraulic control valve 30 in units of millisec (1/1000 second).
  • the pressurizing chamber 22a of the hydraulic actuator 20 is provided with the aforementioned oil pressure detecting means 71 connected to the controller 90, and the oil pressure detecting means 71 measures the oil pressure in the pressurizing chamber 22a.
  • the controller 90 can detect the surge pressure when the hydraulic oil is sealed in the pressurizing chamber 22a by monitoring the hydraulic pressure of the pressurizing chamber 22a measured by the hydraulic pressure detecting means 71.
  • the output port 50a of the accumulator 50 is connected to the first pipeline 21b of the block 21.
  • the accumulator 50 constitutes a pressure accumulating means for accumulating hydraulic pressure, and the accumulator 50 in this embodiment is a mechanical accumulator.
  • the accumulator 50 includes the above-described output port 50a, an input line 50c communicating with the output port 50a, and an input port 50d communicating with the input line 50c.
  • the input line 50c includes a pressure accumulator. 52 is provided.
  • the pressure accumulating part 52 has a cylinder 55 formed in the accumulator 50 main body.
  • the cylinder 55 communicates with the input pipe line 50c, and hydraulic oil supplied from the input port 50d and hydraulic oil supplied from the output port 50a can flow in.
  • a plunger 56 that slides in the axial direction of the cylinder 55, and a compression spring 57 that biases the plunger 56 toward the bottom wall of the cylinder 55 (downward in FIG. 1). ing.
  • the hydraulic actuator 20, the hydraulic control valve 30, and the accumulator 50 form a hydraulic circuit 60 (a hydraulic circuit surrounded by a broken line) as shown in FIG.
  • the hydraulic circuit 60 can be supplied with low-pressure hydraulic oil from a lubrication unit 61 attached to the engine and supplying lubricating oil to the engine via the input port 50d of the accumulator 50.
  • a check valve 62 is disposed between the lubrication unit 61 and the hydraulic circuit 60, and only when the hydraulic pressure of the hydraulic circuit 60 is smaller than the hydraulic pressure of the lubrication unit 61 by the check valve 62, The hydraulic oil is supplied from the lubrication unit 61 to the hydraulic circuit 60 so that the hydraulic oil does not flow into the lubrication unit 61 from the hydraulic circuit 60 side.
  • a relief valve 63 is provided between the check valve 62 and the hydraulic circuit 60.
  • the relief valve 63 discharges the hydraulic oil of the hydraulic circuit 60 to the engine oil pan 64 when the hydraulic pressure of the hydraulic circuit 60 becomes higher than a preset pressure.
  • the intake port 2 is opened and closed by opening or closing movement of the intake valve 3, and the intake port 2 is closed by closing movement of the intake valve 3 in the compression stroke, explosion stroke, and exhaust stroke of the engine.
  • variable valve device 1 configured as described above will be described with reference to FIGS.
  • FIG. 3 to 8 are schematic diagrams showing the operation of the variable valve device 1
  • FIG. 9 is a diagram showing the relationship between the cam rotation angle and the valve lift amount in the intake stroke of the engine.
  • the intake valve 3 fully closes the intake port 2 by the urging force of the valve spring 4.
  • the relationship between the rotation angle of the cam 18 and the valve lift amount at this time is as shown in the closed region of FIG. 9, and the value of the valve lift amount of the intake valve 3 is not related to the rotation angle of the cam 18. 0.
  • the hydraulic oil from the lubrication unit 61 is supplied in the order of the hydraulic control valve 30 and the hydraulic actuator 20, and the rod portion 23 c of the piston 23 gradually advances downward while contacting the cross head 5, and enters the accumulator 50.
  • the stored hydraulic oil is gradually supplied to the pressurizing chamber 22 a of the cylinder portion 22 of the hydraulic actuator 20.
  • the relationship between the rotation angle of the cam 18 and the valve lift amount at this time is as shown in the opening action region of FIG. 9, and the valve lift of the intake valve 3 is increased as the rotation angle of the cam 18 increases. The amount increases gradually.
  • the force that the rod portion 23c advances downward does not have a force that pushes down the intake valve 3 against the urging force of the valve spring 4 of the intake valve 3, and therefore the rod portion 23c is crossed.
  • the intake valve 3 is not pushed down without regard to the operation of the rocker arm 9.
  • the hydraulic oil is not stored in the accumulator 50, the hydraulic oil is gradually supplied from the lubrication unit 61 attached to the engine to the hydraulic circuit 60 via the check valve 62.
  • the relationship between the rotation angle of the cam 18 and the valve lift at this time is the relationship shown in the closing action region A (curve extending from the point P to the point R via the point Q) in FIG.
  • the valve lift gradually decreases.
  • the rod portion 23 c of the piston 23 is gradually accommodated in the cylinder portion 22, so that the hydraulic oil in the pressurizing chamber 22 a of the cylinder portion 22 is stored in the accumulator 50.
  • the hydraulic actuator 20 has a function of a piston pump, and hydraulic oil is stored in the accumulator 50 via the hydraulic actuator 20 and the hydraulic control valve 30.
  • the intake valve 3 maintains the open state of the intake port 2 at a predetermined opening, and in the intake stroke of the engine.
  • the closing timing of the intake port 2 is delayed.
  • the relationship between the rotation angle of the cam 18 and the valve lift at this time is the relationship shown in the closing delay region of FIG. 9, and the rotation angle of the cam 18 is maintained for a predetermined time during which the hydraulic control valve 30 is excited. Even if increases, the valve lift amount of the intake valve 3 becomes constant.
  • the rocker arm 9 has a biasing force of the return spring 15 even when the rod 23c of the stopped piston 23 presses the cross head 5 and the intake valve 3 keeps the intake port 2 open.
  • the push rod 13 does not fall off from the rocker arm 9, and the rocker arm 9 operates so that a gap is generated between the cross head 5 and the rocker arm 9.
  • the hydraulic control valve 30 When the hydraulic control valve 30 is demagnetized after a predetermined time has elapsed, the hydraulic control valve 30 is switched to a state in which the input port 30a and the output port 30b communicate with each other, and the hydraulic fluid supply / discharge state is switched from the hydraulic fluid cutoff state. Transition to the state.
  • the intake valve 3 gradually closes the intake port 2, and at this time, the cross head 5 rises and pushes the rod portion 23c of the piston 23 upward, 23 is gradually accommodated again in the cylinder part 22, and the hydraulic oil in the pressurizing chamber 22 a of the cylinder part 22 is stored in the accumulator 50 via the hydraulic control valve 30.
  • the relationship between the rotation angle of the cam 18 and the valve lift amount at this time is the relationship shown in the blockage region B of FIG. 9, and the valve lift amount gradually decreases as the rotation angle of the cam 18 increases.
  • variable valve device 1 excites the hydraulic control valve 30 at a predetermined timing in the intake stroke, thereby stopping the upward movement of the rod portion 23c of the piston 23 and the closing movement of the intake valve 3, and the intake valve 3
  • intake blocking delay control The control of delaying the closing timing of the intake port 2 by the control (referred to as “intake blocking delay control” for convenience of explanation) is possible, and this control is performed in accordance with the operating state of the engine, so that the operating state of the engine It is possible to adjust the intake air amount suitable for the vehicle.
  • this variation in the closed end timing may change the compression ratio as a result and may affect the combustion.
  • the intake blockage delay control of the variable valve device 1 closes the intake valve 3 even if the response performance indicating the operating speed of the hydraulic control valve 30 changes depending on the temperature environment. It is configured to suppress variations in end timing.
  • FIG. 10 is an explanatory diagram showing an example of measurement signals measured by the sensors accompanying the operation of the variable valve device 1 described above.
  • FIG. 10A shows an example of the TDC detection sensor signal 100 measured by the TDC detection sensor 70
  • FIG. 10B shows the rotation speed detection signal (pulse) measured by the crank angle detection sensor 72
  • FIG. 10C is a diagram illustrating an example of an intake blockage delay control signal (hereinafter referred to as a VVA start signal) 120 generated and output by the controller 90
  • FIG. ) Is a diagram illustrating an example of a valve lift amount signal 130 measured by the gap sensor 24
  • FIG. 10E is a diagram illustrating an example of a hydraulic pressure signal 140 measured by the hydraulic pressure detection means 71.
  • the variable valve device 1 is controlled by the controller 90.
  • the controller 90 performs the closing delay control in the intake stroke when the engine piston 80 in the intake stroke is positioned at the top dead center for each cylinder of the engine.
  • the lift amount signal 130 and the hydraulic pressure signal 140 output from the hydraulic pressure detection means 71 are monitored, and when the TDC detection sensor signal 100 is detected for each cylinder, the number of pulses of the rotation speed detection signal 110 starts to be counted,
  • the engine speed is calculated based on the engine speed detection signal 110.
  • the operation of the intake valve 3 during this period is measured by the gap sensor 24 as the closed region and the open action region of the valve lift amount signal 130, and the hydraulic pressure in the pressurizing chamber 22 a is detected as the hydraulic oil supply / discharge region A of the hydraulic signal 140. It is measured by means 71.
  • VVA activation setting pulse a preset number of pulses
  • the controller 90 excites the hydraulic control valve 30. It is determined that the output timing of the VVA activation signal to be performed (for convenience of explanation, “excitation instruction timing (Pcom)”) is reached, and the VVA activation signal 120 (see FIG. 10C) is generated to generate the hydraulic control valve. 30 to excite the hydraulic control valve 30.
  • VVA activation setting pulse 111 is set so that the counted number of pulses of the rotation speed detection signal 110 reaches the VVA activation setting pulse 111 during the closing movement of the intake valve 3.
  • VVA holding time TW set in advance from the excitation instruction timing (Pcom).
  • the hydraulic control valve 30 When the hydraulic control valve 30 is excited, as described above, the hydraulic control valve 30 shifts from the hydraulic oil supply / discharge state to the hydraulic oil cutoff state, and the hydraulic oil in the pressurizing chamber 22a of the cylinder portion 22 is sealed. Since the rod portion 23c of the piston 23 is stopped, the rod portion 23c is stopped during the VVA holding time TW, and the closing movement of the intake valve 3 is also stopped, and the open state of the intake port 2 at a predetermined opening is maintained. Thus, the closing timing of the intake port 2 is delayed.
  • the operation of the intake valve during this period is measured as a closing delay region of the valve lift amount signal 130 (see FIG. 10D), and the hydraulic pressure in the pressurizing chamber 22a is measured as a hydraulic oil cutoff region of the hydraulic signal 140 ( (Refer FIG.10 (e)).
  • VVA start signal 120 After the VVA start signal 120 is set to ON (ON), when the VVA hold time TW elapses and the VVA start signal 120 is set to OFF (OFF), the output of the excitation current to the hydraulic control valve 30 is stopped.
  • the hydraulic control valve 30 is demagnetized.
  • the hydraulic control valve 30 When the hydraulic control valve 30 is demagnetized, the hydraulic control valve 30 shifts from the hydraulic oil cut-off state to the hydraulic oil supply / discharge state as described above, and the intake valve 3 is energized by the biasing force of the valve spring 4 of the intake valve 3. 3 is closed and moved, and the intake port 2 is gradually closed, and then the intake port 2 is fully closed.
  • the operation of the intake valve 3 during this period is measured as the closing action region B of the valve lift amount signal 130 (see FIG. 10D), and the hydraulic pressure in the pressurizing chamber 22a is set as the hydraulic oil supply / discharge region B of the hydraulic signal 140. It is measured (see FIG. 10 (e)).
  • the response performance of the hydraulic control valve 30 may vary depending on the temperature of the hydraulic oil.
  • FIG. 11 is an explanatory diagram showing a change in response performance of the hydraulic control valve 30 due to a change in the temperature of hydraulic oil and a variation in the closing end timing of the intake valve.
  • FIG. 11A shows an example of the VVA start signal 120
  • FIG. 11B shows an example of the valve lift amount signal 131 when the VVA start signal 120 is output in a temperature environment with hydraulic oil
  • FIG. 11C is a diagram illustrating an example of the valve lift amount signal 132 when the VVA activation signal 120 is output in another temperature environment of the hydraulic oil.
  • VVA response performance ( ⁇ P) As shown in FIGS. 11 (b) and 11 (c), after the VVA activation signal 120 is set to ON, the closing movement of the intake valve 3 is stopped and the intake port 2 is opened at a predetermined opening degree.
  • VVA response performance ( ⁇ P) the closed end of the intake valve 3
  • the VVA response performance ( ⁇ P) is ⁇ P1
  • the intake valve 3 at that time (fully closed) timing referred to as “closed end timing (S)” for convenience of explanation.
  • closed end timing (S) When the hydraulic oil is in another temperature environment, the VVA response performance ( ⁇ P) is ⁇ P2, and the closing end timing (S) of the intake valve 3 at that time is S2. .
  • the closing end timing (S) of the intake valve 3 may change due to the temperature change of the hydraulic oil.
  • the change in the closing timing (S) of the intake valve 3 may affect the combustion by changing the compression ratio as described above.
  • the controller 90 of the variable valve device 1 maintains the open state of the intake port 2 after the VVA start signal 120 is set to ON in order to suppress the variation in the closing end timing (S) of the intake valve 3. Is actually detected based on the measurement result of the hydraulic pressure signal detected by the hydraulic pressure detection means 71 of the pressurizing chamber 22a, and the detected timing is controlled to fall within the predetermined range C1.
  • VVA activation signal 120 is set to ON (ON)
  • the crank angle at the time when the hydraulic pressure in the pressurizing chamber 22a exceeds a predetermined value (threshold value) D1 is detected, and the detected crank angle is detected.
  • Is corrected and intake blockage delay control is performed so as to suppress the variation in the closing end timing (S) of the intake valve 3.
  • FIGS. 12 and 13 are flowcharts showing the control procedure of the intake blockage delay control
  • FIGS. 14 to 16 are explanatory diagrams showing examples of measurement signals measured by the sensors in the control procedure of the intake blockage delay control. is there.
  • the controller 90 is a TDC detection sensor for determining a VVA activation signal for exciting the hydraulic control valve 30 of the variable valve device 1 and its output timing (excitation instruction timing (Pcom)).
  • 70 a TDC detection sensor signal 100 (see FIG. 14A), a rotation speed detection signal 110 (see FIG. 10B) output from the crank angle detection sensor 72, and a valve output from the gap sensor 24.
  • the lift amount signal 133 (see the valve lift amount signal indicated by point O, point P, point Q1, and point S1 in FIG. 14D) and the hydraulic pressure signal 143 output from the hydraulic pressure detection means 71 (see FIG. 14E).
  • the TDC detection sensor signal 100 is detected (S100)
  • the engine speed is determined based on the engine speed detection signal.
  • to start the number of pulses counted up the rotational speed detection signal 110 (S101, S102).
  • the information on the excitation instruction timing is, for example, the time (or the number of revolutions) from when the TDC detection sensor signal 100 is detected until the VVA activation signal 123 is set from OFF (OFF) to ON (ON). (It may be a crank angle based on the number of pulses of the detection signal 110).
  • the hydraulic control valve 30 When the VVA activation signal 123 is output to the hydraulic control valve 30, the hydraulic control valve 30 is excited based on the VVA activation signal 123 for the VVA holding time TW from the time of the excitation instruction timing (Pcom). In S103, if the counted number of pulses does not reach the VVA activation setting pulse 111 (NO in S103), the process waits until the number of pulses of the rotation speed detection signal 110 reaches the VVA activation setting pulse 111.
  • the surge pressure signal M1 is measured by the hydraulic pressure detection means 71 as a surge pressure signal M1.
  • the process waits until the VVA holding time Tw elapses.
  • the VVA holding time Tw elapses YES
  • the VVA activation signal is turned off in S107.
  • VVA response performance ( ⁇ P) in the current control cycle is determined. Is calculated as VVA response performance ( ⁇ P1) by the following equation (1) (S108).
  • VVA response performance ( ⁇ P) VVA operation start timing (Pac) ⁇ reference VVA operation start timing (Pacs) Equation (1).
  • the VVA response performance uses the reference VVA operation start timing (Pacs) as a reference for determining the response, and thus is a positive or negative value depending on the magnitude of the actual VVA operation start timing (Pac). Take. Further, here, for one cylinder, the control period from the TDC detection time point to the next TDC detection time point is referred to as a “control cycle”.
  • VVA response performance ( ⁇ P1) When the VVA response performance ( ⁇ P1) is calculated, whether the VVA response performance ( ⁇ P1) is within a predetermined range C1 (C1: 0 ⁇
  • the closing end timing (S) of the intake valve 3 associated with the VVA response performance ( ⁇ P1) is within an allowable range of variations in the closing end timing. Therefore, it is not necessary to correct the excitation instruction timing (Pcom) and the waveform of the VVA start signal for the next control cycle.
  • the predetermined range C1 is a value indicating a range in which the magnitude of the VVA response performance ( ⁇ P) is allowed. If the variation in the closed end timing included in this range is affected, the engine combustion is affected. It is a value indicating a range not giving.
  • the process proceeds to S111.
  • the magnitude of the crank angle corresponding to the absolute value of the VVA response performance ( ⁇ P1) is the control range of the intake stroke (the crank angle at which the variable valve device can be controlled in the intake stroke). The range is less than 30%, or more than 30% and less than 60%, or more than 60%.
  • the output timing of the VVA start signal 123 in the current control cycle ( At the same timing as the excitation instruction timing (Pcom)), the waveform of the VVA activation signal 123 is corrected to the waveform of the VVA activation signal 124 (see FIG. 14C) and output to the hydraulic control valve 30 in the next control cycle.
  • the output timing and waveform of the VVA activation signal 124 for each cylinder in the next control cycle are set (S113).
  • the output timing of the VVA activation signal 124 output to the hydraulic control valve 30 in the next control cycle is the same as the excitation instruction timing (Pcom) of the VVA activation signal 123 in the current control cycle, and the VVA activation signal
  • the voltage obtained by adding a predetermined adjustment voltage ⁇ V to the output voltage Vc of 123 is used as the output voltage of the VVA activation signal 124 to improve the response performance of the hydraulic control valve 30, and the closing end timing of the intake valve 3 is set to a timing within a predetermined range. Correct to fit.
  • , and when the VVA response performance ( ⁇ P, ⁇ P1) is negative, the output voltage of the VVA start signal 124 Vc ⁇
  • the magnitude of the output voltage of the VVA start signals 123 and 124 is set within a predetermined range in which the hydraulic control valve 30 can operate normally against the oil pressure within the allowable operating temperature range.
  • the closing end timing (S) of the intake valve 3 changes from S1 to St (see FIG. 14 (d)), and a constant closing end timing according to the engine operating state such as the engine speed and engine load. (Crank angle) is adjusted to St.
  • the output timing of the VVA activation signal 126 is set to be higher than the excitation instruction timing (Pcom) of the VVA activation signal 123 (see FIG. 15B) of the current control cycle.
  • the next control is performed so that the waveform is corrected to the timing (Pcom1) advanced by ⁇ P2 and the waveform of the VVA activation signal 123 is corrected to the waveform of the VVA activation signal 126 (see FIG. 15C) and output to the hydraulic control valve 30.
  • the output timing and waveform of the VVA activation signal 126 for each cylinder in the cycle are set (S115).
  • ⁇ P2 is obtained by multiplying the VVA response performance ⁇ P1 obtained in the current control cycle by a predetermined coefficient K1 (0 ⁇ K1 ⁇ 1), and the magnitude of the coefficient K1 is an empirical value. Therefore, ⁇ P2 has the same sign as ⁇ P1.
  • the output timing of the VVA activation signal 126 output to the hydraulic control valve 30 in the next control cycle is advanced by P2 from the excitation instruction timing (Pcom) of the VVA activation signal 123 of the current control cycle (Pcom1).
  • the output voltage of the VVA start signal 126 is a voltage obtained by adding a predetermined adjustment voltage ⁇ V to the output voltage Vc of the VVA start signal 123, so that the response performance of the hydraulic control valve 30 is improved and the closed end of the intake valve 3 is closed. Correction is made so that the timing falls within a predetermined range.
  • timing advanced by ⁇ P2 is a timing advanced by ⁇ P2 when ⁇ P2 is positive and delayed by
  • the output timing of the VVA activation signal 126 determined above is set within a predetermined controllable range so that the control of the variable valve device can be normally performed.
  • the sign of the adjustment voltage ⁇ V is determined according to the sign of the VVA response performance ( ⁇ P, ⁇ P1), and the method of calculating the output voltage of the VVA activation signal 126 is the same as described above.
  • the closing end timing (S) of the intake valve 3 changes from S2 to St (see FIG. 15 (d)), and a constant closing end timing according to the engine operating state such as the engine speed and engine load. (Crank angle) is adjusted to St.
  • VVA is shown in FIG.
  • the output timing of the VVA start signal 128 is corrected to a timing earlier by ⁇ P3 than the excitation instruction timing (Pcom) of the VVA start signal 123 (see FIG. 16B) of the current control cycle.
  • the output timing of the VVA activation signal 128 for each cylinder in the next control cycle so that the VVA activation signal 128 (see FIG. 16C) having the same waveform as the VVA activation signal 123 is output to the hydraulic control valve 30.
  • a waveform is set (S116).
  • ⁇ P3 is obtained by multiplying the VVA response performance ⁇ P1 obtained in this control cycle by a predetermined coefficient K2 (0 ⁇ K2 ⁇ 1), and the magnitude of the coefficient K2 is an empirical value. > K1. Therefore, ⁇ P3 has the same sign as ⁇ P1 and
  • the timing (Pcom2) that the output timing of the VVA activation signal 128 output to the hydraulic control valve 30 in the next control cycle is advanced by ⁇ P3 from the excitation instruction timing (Pcom) of the VVA activation signal 123 in the current control cycle.
  • the output voltage of the VVA activation signal 128 is set to a voltage value similar to the output voltage Vc of the VVA activation signal 123, and the closing end timing of the intake valve 3 is corrected to fall within a predetermined range.
  • timing advanced by ⁇ P3 is a timing advanced by ⁇ P3 when ⁇ P3 is positive and delayed by
  • the output timing of the VVA activation signal 128 obtained above is set within a predetermined controllable range so that the variable valve device can be normally controlled.
  • the closing end timing (S) of the intake valve 3 changes from S3 to St (see FIG. 16D), and a constant closing end timing according to the engine operating state such as the engine speed and engine load. (Crank angle) is adjusted to St.
  • the waveform of the VVA start signal to be corrected for the next control cycle is the magnitude of the voltage with respect to the VVA start signal of the current control cycle.
  • the VVA holding signal 129a may be corrected by the waveform of the VVA activation signal 129a that is the same and has the VVA holding time TW increased by ⁇ T (the VVA holding time TW is increased or decreased by
  • ⁇ T is an adjustment amount set according to ⁇ P, and its sign is the same as ⁇ P. Therefore, when ⁇ P> 0, the VVA holding time TW is set longer by ⁇ T, and when ⁇ P ⁇ 0, the VVA holding time TW is set shorter by
  • the intake port 2 is originally opened with a large opening. Since the control for maintaining the state is controlled so that the open state of the intake port 2 is maintained in a state where the opening degree is small, the change in the intake air amount is increased by the ⁇ VA holding time TW. And the output timing of the VVA activation signal 129a (excitation instruction timing (Pcom)) is changed so as to be output earlier so that the closing end timing of the intake valve 3 falls within a predetermined range.
  • the waveform of the VVA start signal to be corrected for the next control cycle is increased or decreased with respect to the VVA start signal of the current control cycle
  • the VVA holding time TW may be corrected by the waveform of the VVA activation signal 129b in which the VVA holding time TW is increased by ⁇ T (the VVA holding time TW is increased or decreased by
  • ⁇ T is an adjustment amount set in the same manner as described above, and the method of setting the VVA holding time TW by increasing / decreasing by
  • the intake port 2 is originally opened with a large opening. Since the control to maintain the state is controlled so that the open state of the intake port 2 is maintained in a state where the opening is small, the output voltage of the VVA start signal 129b of the next control cycle is set to the current control cycle.
  • the response performance of the hydraulic control valve 30 is improved, and control is performed so that the closing end timing of the intake valve 3 falls within a predetermined range.
  • the change in the intake air amount is corrected so as to be compensated by increasing the VVA holding time TW by ⁇ T.
  • variable valve device As described above, the variable valve device according to the present invention is useful for an engine valve device that varies the operation of an engine valve, and is particularly applicable to the engine valve technology of a diesel engine.
  • FIG. 1 is a conceptual diagram showing a variable valve device 1 according to the present invention.
  • FIG. 2 is a diagram illustrating an example of the hydraulic circuit 60.
  • FIG. 3 is a schematic diagram showing the operation of the variable valve device 1.
  • FIG. 4 is a schematic diagram illustrating the operation of the variable valve device 1.
  • FIG. 5 is a schematic diagram showing the operation of the variable valve device 1.
  • FIG. 6 is a schematic diagram illustrating the operation of the variable valve device 1.
  • FIG. 7 is a schematic diagram illustrating the operation of the variable valve device 1.
  • FIG. 8 is a schematic diagram illustrating the operation of the variable valve device 1.
  • FIG. 9 is a diagram showing the relationship between the cam rotation angle and the valve lift amount in the intake stroke.
  • FIG. 9 is a diagram showing the relationship between the cam rotation angle and the valve lift amount in the intake stroke.
  • FIG. 10 is an explanatory diagram illustrating an example of a measurement signal measured by each sensor accompanying the operation of the variable valve device 1.
  • FIG. 11 is an explanatory diagram showing a change in response performance of the hydraulic control valve 30 due to a change in temperature of hydraulic oil and a variation in the closing end timing of the intake valve.
  • FIG. 12 is a flowchart showing a control procedure of intake blockage delay control.
  • FIG. 13 is a flowchart showing a control procedure of intake blockage delay control.
  • FIG. 14 is an explanatory diagram illustrating an example of a measurement signal measured by each sensor in the control procedure of the intake blockage delay control.
  • FIG. 15 is an explanatory diagram of a control method of closed end variation suppression control.
  • FIG. 16 is an explanatory diagram of a control method of closed end variation suppression control.
  • FIG. 17 is a diagram illustrating an example of the corrected VVA activation signal.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

La présente invention concerne un dispositif de type soupape à commande variable et son procédé de commande permettant en fait de mesurer la performance de réaction d'une soupape à commande variable aux changements de l'environnement de température et de corriger précisément le calage de l'ouverture/la fermeture de la soupape sur la base des résultats mesurés. Le dispositif est équipé d'un actionneur hydraulique qui décharge l'huile hydraulique dans la chambre de pression d'un cylindre en utilisant le mouvement de fermeture d'une soupape d'admission et il comprend une soupape de commande hydraulique qui commande l'alimentation de l'huile hydraulique à un actionneur hydraulique et l'évacuation de l'huile de celui-ci en s'ouvrant et en se fermant et qui s'oppose à l'écoulement de l'huile hydraulique de la chambre de pression quand il est fermé de manière à bloquer le mouvement de fermeture de la soupape d'admission. Après qu'un signal commandant la fermeture de la soupape de commande hydraulique est émis à un angle de vilebrequin prescrit dans le cycle actuel de commande moteur, l'angle de vilebrequin auquel la pression de pointe dans la chambre de pression accompagnant la fermeture de la soupape de commande hydraulique dépassera une valeur limite prescrite qui sera trouvé est en fait l'angle de vilebrequin au commencement du fonctionnement de la soupape de commande hydraulique, au moins l'angle de vilebrequin émis ou la forme d'onde du signal commandant la fermeture de la soupape de commande hydraulique est corrigé sur la base de l'angle de vilebrequin au commencement du fonctionnement de la soupape et le signal corrigé est adressé à la soupape de commande hydraulique dans le cycle de commande suivant.
PCT/JP2009/069170 2008-11-20 2009-11-11 Dispositif de type soupape à commande variable et son procédé de commande WO2010058721A1 (fr)

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US13/129,662 US20110220045A1 (en) 2008-11-20 2009-11-11 Variable valve device and control method thereof
CN2009801465126A CN102224325A (zh) 2008-11-20 2009-11-11 可变阀装置及其控制方法
EP09827502A EP2357328A1 (fr) 2008-11-20 2009-11-11 Dispositif de type soupape à commande variable et son procédé de commande

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JP2008-297230 2008-11-20
JP2008297230A JP2010121571A (ja) 2008-11-20 2008-11-20 可変弁装置およびその制御方法

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DK177695B1 (en) * 2012-11-16 2014-03-17 Man Diesel & Turbo Deutschland A large slow running turbocharged two-stoke uniflow internal combustion engine with crosshead and a cam driven exhaust valve actuation system
DE102016218835A1 (de) * 2016-09-29 2018-03-29 Ford Global Technologies, Llc Ölversorgungseinheit und Kraftfahrzeug
CN112960723B (zh) * 2021-02-22 2023-01-10 西安热工研究院有限公司 一种基于时间的动态投入除氧器加热系统的控制系统

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JP2004521275A (ja) * 2001-07-17 2004-07-15 ローベルト　ボツシユ　ゲゼルシヤフト　ミツト　ベシユレンクテル　ハフツング 電気液圧式の弁制御装置
US7059282B2 (en) 1997-12-11 2006-06-13 Jacobs Vehicle Systems, Inc. Variable lost motion valve actuator and method
JP3785464B2 (ja) * 2003-03-24 2006-06-14 よこはまティーエルオー株式会社 内燃機関の可変動弁装置とその制御方法および油圧アクチュエータ
US7178491B2 (en) 2003-06-05 2007-02-20 Caterpillar Inc Control system and method for engine valve actuator
WO2007074072A1 (fr) * 2005-12-27 2007-07-05 Robert Bosch Gmbh Procede de commande electronique d'une soupape de renouvellement des gaz d'un moteur a combustion interne
WO2008001699A1 (fr) * 2006-06-30 2008-01-03 Komatsu Ltd. Dispositif de vanne de moteur

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JP4802394B2 (ja) * 2000-08-03 2011-10-26 アイシン精機株式会社 弁開閉時期制御装置

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US7059282B2 (en) 1997-12-11 2006-06-13 Jacobs Vehicle Systems, Inc. Variable lost motion valve actuator and method
JP2004521275A (ja) * 2001-07-17 2004-07-15 ローベルト　ボツシユ　ゲゼルシヤフト　ミツト　ベシユレンクテル　ハフツング 電気液圧式の弁制御装置
JP3785464B2 (ja) * 2003-03-24 2006-06-14 よこはまティーエルオー株式会社 内燃機関の可変動弁装置とその制御方法および油圧アクチュエータ
US7178491B2 (en) 2003-06-05 2007-02-20 Caterpillar Inc Control system and method for engine valve actuator
WO2007074072A1 (fr) * 2005-12-27 2007-07-05 Robert Bosch Gmbh Procede de commande electronique d'une soupape de renouvellement des gaz d'un moteur a combustion interne
WO2008001699A1 (fr) * 2006-06-30 2008-01-03 Komatsu Ltd. Dispositif de vanne de moteur

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US20110220045A1 (en) 2011-09-15
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CN102224325A (zh) 2011-10-19

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