WO2010058720A1 - Distribution variable et son procédé de commande - Google Patents

Distribution variable et son procédé de commande Download PDF

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Publication number
WO2010058720A1
WO2010058720A1 PCT/JP2009/069164 JP2009069164W WO2010058720A1 WO 2010058720 A1 WO2010058720 A1 WO 2010058720A1 JP 2009069164 W JP2009069164 W JP 2009069164W WO 2010058720 A1 WO2010058720 A1 WO 2010058720A1
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WO
WIPO (PCT)
Prior art keywords
valve
control
variable
intake
hydraulic
Prior art date
Application number
PCT/JP2009/069164
Other languages
English (en)
Japanese (ja)
Inventor
悦郎 佐藤
橘　英明
陽平 久田
太田　一男
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.)
Filing date
Publication date
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 US13/129,088 priority Critical patent/US20110214631A1/en
Priority to CN2009801465944A priority patent/CN102224326A/zh
Priority to EP09827501A priority patent/EP2357327A4/fr
Publication of WO2010058720A1 publication Critical patent/WO2010058720A1/fr

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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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0223—Variable control of the intake valves only
    • F02D13/0226—Variable control of the intake valves only changing valve lift or valve lift and timing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0269—Controlling the valves to perform a Miller-Atkinson cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • 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
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
    • F01L2001/34443—Cleaning control of 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L2013/0089—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002—Controlling intake air
    • F02D2041/001—Controlling intake air for engines with variable valve actuation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

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.
  • a hydraulically driven variable valve device driven by hydraulic pressure the variable valve is operated by controlling the flow of hydraulic oil. There is something configured.
  • the flow actuator from the fluid actuator that follows the rocker arm is prevented from flowing out by a directional control valve at a predetermined timing, so that the fluid actuator stops and acts on the rocker arm so that the intake valve remains open.
  • a valve device is provided.
  • This hydraulically driven variable valve device supplies low-pressure pressurized oil, which uses a part of the lubrication unit attached to the engine as a fluid source, to the directional control valve.
  • the piston may not be able to follow the high-speed opening / closing operation of the intake valve. For this reason, there has been a problem that the piston of the fluid actuator cannot reach a desired position, and the open state of the intake valve cannot be maintained at a desired opening.
  • Patent Document 1 discloses that an engine valve device that uses a part of a lubrication unit attached to an engine as a hydraulic power source to change the operation can achieve high-speed rotation of the engine. There is disclosed a technology of an engine valve device that can follow and that can accurately open an intake valve at a desired opening.
  • the electromagnetic open / close valve shown in Patent Document 1 is composed of a solenoid, a spool portion including a spool, a spring, and the like.
  • a normal state the solenoid is not excited, hereinafter referred to as an off state
  • the spool moves in the spring pressing direction to open the electromagnetic on-off valve, and when the solenoid is energized (hereinafter referred to as the on state), the spool resists the biasing force of the spring so as to close the electromagnetic on-off valve. And move to move.
  • the intake valve and the engine piston may collide.
  • the present invention has been made in view of the above problems, and operates only the spool of the electromagnetic on-off valve at a timing that does not affect the operation of the intake valve to prevent the oil film from being cut off on the spool portion. It is an object of the present invention to provide a variable valve device that is stabilized and a control method thereof.
  • a variable valve device includes a valve mechanism that moves an intake valve of an engine to open or close an intake port, and a rod portion of a piston that blocks the movement of the intake valve.
  • a hydraulic actuator, and a valve for controlling hydraulic oil supplied to or discharged from the hydraulic actuator, the valve member and a sliding surface on which the valve member slides, and the valve member of the hydraulic actuator A hydraulic control valve that moves between a blocking-side position where the operation of the rod portion of the piston is blocked and an open-side position where the operation of the piston rod portion is not blocked;
  • Valve stabilization control means for performing control valve stabilization control for sliding the valve member of the hydraulic control valve within a period in which the intake port is fully closed, and the valve member during the closing movement of the intake valve
  • the blocking side Variable valve control means for performing variable valve control for making the timing at which the intake port fully closes variable by sliding to stop the closing movement of the intake valve by blocking the operation of the rod portion of the piston. It is characterized by that.
  • the valve stabilization control means sets the time for holding the valve member on the blocking side longer as the engine becomes a lower engine speed according to the engine speed. It is characterized by doing.
  • valve stabilization control means sequentially performs the control valve stabilization control for each cylinder corresponding to the order in which combustion is started in each cylinder of the engine. It is characterized by doing.
  • control means according to any one of the first to third aspects, wherein the variable valve control and the control valve stabilization control are implemented in combination.
  • the control valve stabilization control is performed by the valve stabilization control means within a period in which the valve control is not performed.
  • the fifth invention further comprises control means for performing the variable valve control and the control valve stabilization control in combination in any one of the first to third inventions, and the control means comprises the variable When performing the valve control, the variable valve control is performed by the variable valve control unit after the control valve stabilization control is performed by the valve stabilization control unit.
  • the variable valve device control method moves the intake valve of the engine by the valve operating mechanism to open or close the intake port, and prevents the movement of the intake valve by the rod portion of the piston of the hydraulic actuator.
  • the valve member of the hydraulic control valve that controls the supply or discharge of the hydraulic oil of the hydraulic actuator, the blocking side position where the operation of the rod portion of the piston of the hydraulic actuator is blocked, and the operation of the rod portion of the piston.
  • the control method of the variable valve device which makes the timing of full closing of the intake port variable by moving between the open side position where the air flow is not blocked and controlling the operation of the rod portion of the piston of the hydraulic actuator And the valve member of the hydraulic control valve slides between the open side and the blocking side during a period in which the intake valve fully closes the intake port.
  • the control valve stabilization control is performed, and while the intake valve is closed, the valve member of the hydraulic control valve is slid to the blocking side to block the operation of the rod portion of the piston, thereby A variable valve control is implemented in which the closing movement is stopped and the timing at which the intake port is fully closed is made variable.
  • control valve stabilization control is configured such that the time during which the valve member is held on the blocking side is longer as the engine becomes lower in accordance with the engine speed. It is characterized by doing.
  • control valve stabilization control is sequentially performed for each cylinder corresponding to an order in which combustion is started in each cylinder of the engine. .
  • a ninth aspect of the present invention is the method according to any one of the sixth to eighth aspects, wherein the variable valve control and the control valve stabilization control are implemented in combination, and the control valve stabilization control is performed by the variable valve control. Is carried out within a period in which is not carried out.
  • a tenth aspect of the invention is any one of the sixth aspect to the eighth aspect of the invention, wherein the variable valve control and the control valve stabilization control are performed in combination, and when the variable valve control is performed, The variable valve control is performed after the control valve stabilization control is performed.
  • the control valve stabilization control for sliding the valve member of the hydraulic control valve is performed during the period in which the intake valve fully closes the intake port. Since variable valve control is performed after the valve member is in a state in which the sliding surface can smoothly slide, the delay of the sliding operation of the valve member when the variable valve control is performed can be prevented. Variations in the closing timing of the intake valve can be suppressed.
  • the control valve stabilization control holds the valve member on the blocking side to such an extent that an oil film is formed on the sliding surface of the hydraulic control valve according to the engine speed. Therefore, the valve member of the hydraulic control valve can smoothly slide on the sliding surface regardless of the engine speed, and the delay of the sliding operation of the valve member of the variable valve control performed thereafter is delayed. And the variation in the closing timing of the intake valve due to the operation delay of the valve member can be suppressed.
  • control valve stabilization control is sequentially performed for each cylinder corresponding to the order in which the combustion is started in each cylinder of the engine, so that the variable valve control is performed for each cylinder.
  • the delay of the sliding operation of the valve member at the time can be prevented, and the variation in the closing timing of the intake valve due to the delay of the operation of the valve member can be suppressed.
  • variable valve control and the control valve stabilization control are combined, and the valve stabilization control is performed within the period when the variable valve control is not performed.
  • Valve stabilization control can be performed at a timing that does not affect the operation of the intake valve by the control.
  • variable valve control when the variable valve control is combined with the variable valve control and the variable valve control is performed, the variable valve control is performed after the control valve stabilization control is performed. Therefore, the delay of the sliding operation of the valve member when the variable valve control is performed can be prevented more reliably, and the variation in the closing timing of the intake valve due to the operation delay of the valve member can be suppressed.
  • the operation of the valve member is controlled with high accuracy, and incomplete combustion and collision between the intake valve and the engine piston due to variation in the closing timing of the intake valve can be avoided.
  • 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.
  • a 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. 4D) is output to the controller 90.
  • the TDC detection sensor 70 is connected to the controller 90 and 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. 4A). To the controller 90.
  • crank angle detection sensor 72 measures the rotation angle (hereinafter referred to as “crank angle”) of the crankshaft 82 of the diesel engine unit, and uses the rotation number detection signal (see FIG. 4B) as a measurement signal as a controller. Output to 90.
  • the rotation speed detection signal is a pulse signal that is output every time the crank angle reaches a predetermined rotation angle such as 0 degrees, 30 degrees, 60 degrees,... 360 degrees,.
  • 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 T-shaped crosshead 5 in side view that presses the ends of the stem 3b of the pair of intake valves 3, and the crosshead 5 is parallel to the movement direction of each intake valve 3. It is guided by the provided shaft 6 and can be moved up and down in the direction of movement of each intake valve 3.
  • one arm 5 a of the crosshead 5 is provided with an adjustment screw 7 that adjusts the intake valve 3 and the crosshead 5 to be in close contact with each other. It is possible to adjust the gap with one of the intake valves 3.
  • a rocker arm 9 is provided above the crosshead 5 (in FIG. 1).
  • the rocker arm 9 is rotatable about a rocker shaft 10 and has one end (left end in FIG. 1).
  • a pressing portion 9a for pressing the cross head 5 is formed, and the other end portion (the right end portion in FIG. 1) is configured to form an operating portion 9b.
  • the pressing portion 9a of the rocker arm 9 is disposed so as to be able to press the right side of the substantially central portion of the cross head 5.
  • the rocker arm 9 rotates counterclockwise (in FIG. 1)
  • the pressing portion of the rocker arm 9 9 a presses the cross head 5, and the intake valve 3 moves in a direction to open the intake port 2 to open the intake port 2.
  • An adjusting screw 11 that adjusts the gap between the pressing portion 9 a and the cross head 5 is screwed to the operating portion 9 b of the rocker arm 9, and one end of the adjusting screw 11 that has a hemispherical shape is one end of the push rod 13. Is housed in the department.
  • 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), and the other end portion 13b of the push rod 13 is a push rod housing portion 14a provided above the arm portion of the tappet arm 14. Is housed in.
  • 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).
  • the one end of 11 is accommodated in the recess 13a of the push rod 13 to be sustainable.
  • 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, moves the intake valve 3 in the direction in which the intake port 2 is opened via the tappet arm 14, the push rod 13, the rocker arm 9 and the crosshead 5, The intake port 2 can be opened.
  • 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 referred to as “valve lift amount”, and is indicated by a positive value corresponding to the amount.
  • the value when the intake port 2 is fully closed is indicated as 0.
  • 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 intake valve 3 is configured to be able to maintain the open state of the intake port 2 at a predetermined opening.
  • the hydraulic actuator 20 applied to the present embodiment is a single-acting type, and the cylinder portion 22 of the hydraulic actuator 20 is integrally formed with the block 21, and the block 21 on the opposite side of the cylinder portion 22 flows the hydraulic oil.
  • the hydraulic control valve 30 to be controlled is configured to be housed and mountable.
  • 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.
  • a supply / discharge pipe 21d communicating with the output port 30b of the hydraulic control valve 30 is formed, and a first pipe 21b communicating with the output port 50a of the accumulator 50 is formed.
  • the first pipeline 21b communicates with the input port 30a and the outflow pipeline 21e of the hydraulic control valve 30 through the second pipeline 21c.
  • 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 via the supply / discharge line 21d.
  • An oil groove 22b1 is formed in a predetermined part of the cylinder portion 22, and an outflow pipe 21e communicating with the second pipe 21c is formed in the oil groove 22b1.
  • the piston 23 has a piston part 23a and a rod part 23c.
  • the piston part 23 a is a part that slides in the pressurizing chamber 22 a of the cylinder part 22.
  • the rod portion 23c is a portion that advances to the outside of the cylinder portion 22, and has a tapered shape that is formed so as to gradually narrow from the root toward the tip.
  • 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.
  • the rod part 23c advances from the cylinder part 22, the decrease in the gap is measured, and when the rod part 23c retracts into the cylinder part 22, the increase in the gap is measured.
  • the controller 90 can monitor the operation of the rod portion 23 c by monitoring the gap with the rod portion 23 c measured by the gap sensor 24, abuts against the cross head 5, and the operation of the cross head 5.
  • the operation of the intake valve 3 (valve lift amount) can be monitored from the operation of the interlocking rod portion 23c.
  • the hydraulic control valve 30 is accommodated in the recess 21a of the block 21, and the hydraulic control valve 30 is a two-port electromagnetic opening / closing valve having the input port 30a and the output port 30b as described above.
  • the input port 30 a of the hydraulic control valve 30 communicates with the second pipeline 21 c of the block 21, and the output port 30 b communicates with the supply / discharge pipeline 21 d of the block 21.
  • spool portion 34 having a spool 31 that is a valve member and a sliding surface (not shown) on which the spool 31 slides (in the direction of the arrow in the figure).
  • a spring 33 and a solenoid 32 are provided.
  • the hydraulic control valve 30 presses the spool 31 and the spool 31 is input to the input port 30a.
  • the solenoid 32 When the solenoid 32 is energized (for convenience of explanation, for example), it is slid along the sliding surface to the side that communicates with the output port 30b (downward arrow side in the drawing, referred to as “open side” for convenience of explanation).
  • the spool 31 blocks the communication state between the input port 30a and the output port 30b against the urging force of the spring 33 (upward arrow side in the figure, for convenience of explanation, “blocking side”) Slid along the sliding surface.
  • a state in which the spool 31 of the hydraulic control valve 30 is on the blocking side is referred to as a hydraulic oil cutoff state, and the other state is referred to as a hydraulic oil supply / discharge state.
  • the hydraulic oil is supplied to the block 21 via the first and second pipelines 21b and 21c formed in the block 21 and the hydraulic control valve 30. It is supplied to the exhaust pipe 21d and further supplied to the pressurizing chamber 22a.
  • the hydraulic oil supplied to the pressurizing chamber 22a acts on the piston portion 23a of the piston 23 to push the piston 23 out of the cylinder portion 22 and the rod portion 23c is lowered.
  • the hydraulic control valve 30 is connected to the controller 90, and the controller 90 controls the excitation timing and excitation time of the hydraulic control valve 30.
  • the controller 90 can arbitrarily control the hydraulic control valve 30 in units of millisec (1/1000 second).
  • 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 output port 50a described above, an output line 50b extending from the output port 50a, an input line 50c intersecting the output line 50b, and an input port 50d communicating with the input line 50c.
  • the pressure accumulation part 52 is provided in the input pipe line 50c.
  • 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. 2, and are attached to the engine and supply lubricating oil to the engine. Low pressure hydraulic oil can be supplied from the unit 61.
  • 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 FIG.
  • FIG. 3 is a graph showing the relationship between the cam rotation angle and the valve lift amount in the intake stroke of the engine.
  • the intake valve 3 In the compression stroke, the explosion stroke, and the exhaust stroke of the engine, the intake valve 3 is fully closed by the urging force of the valve spring 4, and the relationship between the rotation angle of the cam 18 and the valve lift amount at this time Is in the relationship shown in the closed region of FIG. 3, and the value of the valve lift amount of the intake valve 3 becomes 0 regardless of the rotation angle of the cam 18.
  • the intake port 2 is gradually opened (opening movement), whereby the intake port 2 is gradually opened.
  • 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. 3, 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 relationship between the rotation angle of the cam 18 and the valve lift amount at this time is the relationship shown in the closing action area A (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 23c of the piston 23 is gradually accommodated in the cylinder portion 22, and the hydraulic oil in the pressurizing chamber 22a of the cylinder portion 22 is stored in the accumulator 50. Is done.
  • the hydraulic actuator 20 has a function of a piston pump, and hydraulic oil is stored in the accumulator 50 via the hydraulic control valve 30 and the hydraulic actuator 20.
  • the hydraulic control valve 30 When the hydraulic control valve 30 is excited at a predetermined position in the closing action area A in the closing action area A, the spool 31 of the hydraulic control valve 30 resists the biasing force of the spring 33 of the hydraulic control valve 30. Sliding along the sliding surface toward the blocking side, the hydraulic control valve 30 shifts from the hydraulic oil supply / discharge state to the hydraulic fluid cutoff state.
  • the piston 23 is pushed into the cylinder part 22 until the piston part 23a of the piston 23 closes the oil groove 22b1, and then the hydraulic oil is sealed in the pressurizing chamber 22a of the cylinder part 22, and the piston 23 is pressurized. The operation is stopped by the hydraulic oil sealed in the chamber 22a.
  • the rod portion 23c of the stopped piston 23 presses the cross head 5
  • the intake valve 3 maintains the open state of the intake port 2 at a predetermined opening degree
  • the closing timing of the intake port 2 in the intake stroke of the engine is Delay.
  • the intake port 2 can be kept open at the same opening degree for a predetermined time during which the hydraulic control valve 30 is excited.
  • the relationship between the rotation angle of the cam 18 and the valve lift at this time is the relationship shown in the blockage delay region of FIG. 3, 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 is closely contacted and controlled by the outer diameter shape (cam profile) of the cam 18, and the push rod 13 does not fall off from the rocker arm 9, so that there is a gap between the cross head 5 and the rocker arm 9. Operates to occur.
  • 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 in the cylinder portion 22 again, and the hydraulic oil in the pressurizing chamber 22 a of the cylinder portion 22 is stored in the accumulator 50.
  • 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. 3, 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 (For convenience of explanation, it is referred to as “VVA operation control”), and this control is performed in accordance with the engine operating state. It is possible to adjust the intake volume appropriately.
  • VVA is an abbreviation for Variable Valve Actuation.
  • the hydraulic control valve 30 may be kept off, the oil film formed on the sliding surface of the spool portion 34 of the hydraulic control valve 30 may be cut off, and the initial operation may not be stable.
  • the spool 31 may not operate smoothly, and the return (sliding toward the open side) of the spool 31 may be extended.
  • FIG. 4 is an explanatory diagram illustrating an example of a measurement signal measured by each sensor and a command signal output to the hydraulic control valve 30 in accordance with the above-described operation of the variable valve device 1.
  • FIG. 4A shows an example of the TDC detection sensor signal 100 measured by the TDC detection sensor 70
  • FIG. 4B shows the rotation speed detection signal 110 measured by the crank angle detection sensor 72
  • FIG. 4C is a diagram illustrating an example
  • FIG. 4C is a diagram illustrating an example of the VVA activation signal 120 generated and output by the controller 90
  • FIG. 4D is a valve lift amount signal 130 measured by the gap sensor 24. It is a figure which shows an example.
  • the control of the variable valve device 1 is performed by the controller 90 based on various measurement signals measured by various sensors of the variable valve device 1.
  • the controller 90 performs the VVA operation control
  • the TDC detection sensor signal 100 (see FIG. 4A) output from the TDC detection sensor 70 and the rotation speed detection signal 110 (see FIG. 4) output from the crank angle detection sensor 72. 4 (b)) is monitored, and when the TDC detection sensor signal 100 is detected, the engine speed is calculated based on the rotation speed detection signal 110, and the number of pulses of the rotation speed detection signal 110 is counted up.
  • the control for determining the execution timing of the VVA operation control of the cylinder in which the TDC detection sensor signal 100 is detected is performed.
  • the operation of the intake valve 3 during this period is measured by the gap sensor 24 as a closed region and an open action region of the valve lift amount signal 130.
  • the TDC detection sensor signal 100 is a measurement signal output from the TDC detection sensor 70 when the engine piston 80 in the intake stroke is located at the top dead center for each cylinder of the engine.
  • VVA activation setting pulse a preset number of pulses
  • the controller 90 It is determined that the output timing of a command signal (referred to as “VVA start signal” for convenience of explanation) 120 for exciting the hydraulic control valve 30 (referred to as “excitation instruction timing (Pcom)” for convenience of explanation) has been reached.
  • VVA start signal referred to as “VVA start signal” for convenience of explanation
  • Pcom excitation instruction timing
  • 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.
  • the excitation current corresponding to the voltage value Vc of the VVA activation signal 120 is applied to the hydraulic control valve 30 during the period when the VVA activation signal 120 is set to ON.
  • the hydraulic control valve 30 is excited by being output to the solenoid 32, and the spool 31 of the hydraulic control valve 30 slides to the blocking side and is held on the blocking side.
  • the output of the excitation current to is stopped, the hydraulic control valve 30 is demagnetized, and the spool 31 slides to the open side and is held on the open side.
  • the hydraulic control valve 30 is excited for a predetermined time (referred to as “VVA holding time” for convenience) TW from the excitation instruction timing (Pcom) by the VVA activation signal 120, and the spool 31 is moved to the blocking side.
  • VVA holding time TW is held.
  • 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 in which the hydraulic control valve 30 is excited, and the closing movement of the intake valve 3 is also stopped, and the intake port 2 is opened. The state is maintained, and the closing timing of the intake port 2 is delayed.
  • the operation of the intake valve 3 during this period is measured as a closed delay region (solid line portion) of the valve lift amount signal 130 (see FIG. 4D).
  • the intake valve 3 is attached to the valve spring 4 and the return spring 15 of the intake valve 3 after the operation corresponding to the closed region and the open action region of the valve lift amount signal 130.
  • the crosshead 5, the rocker arm 9, the push rod 13, and the tappet arm 14 are operated following the cam 18 by the force, and the intake valve 3 moves upward (closed movement) to gradually close the intake port 2. Therefore, the operation of the intake valve 3 during this period is measured as a blocking action region A (curve extending from the point P to the point R via the point Q) of the valve lift amount signal 130 (see FIG. 4D). .
  • VVA start signal 120 is set to ON (ON)
  • VVA hold time TW elapses
  • VVA start signal 120 is set to OFF (OFF)
  • the hydraulic control valve 30 is demagnetized.
  • the operation of the intake valve 3 during this period is measured as the blocking action region B of the valve lift amount signal 130 (see FIG. 4D).
  • FIG. 5 is an explanatory diagram showing a delay in the closing timing of the intake valve 3 due to the extension of the return of the spool 31.
  • FIG. 5A is a diagram showing an example of the VVA activation signal 120
  • FIG. 5B is a diagram showing an example of the valve lift amount signal 131 when there is no delay in the return of the spool 31
  • FIG. (C) is a figure which shows an example of the valve lift amount signal 132 when the return of the spool 31 is extended.
  • the spool 31 slides to the open side after the blocking side, if an oil film is formed on the sliding surface of the spool portion 34, the spool 31 smoothly slides on the sliding surface. Even if it slides from the open side to the blocking side and further slides to the open side, no extension occurs in the return of the spool 31, so that the intake valve 3 is connected to the valve lift amount signal 131 (see the solid line portion in FIG. 5B). ) And the closed end of the intake valve 3 is at a predetermined timing S1.
  • the spool 31 may not slide smoothly on the sliding surface. In this state, the spool 31 slides from the open side to the blocking side, If the slider 31 is further slid to the open side after this, it may take time to return the spool 31 and may be extended.
  • the intake valve 3 operates as indicated by the valve lift amount signal 132 (see the solid line portion in FIG. 5C), and the closed end of the intake valve 3 is a timing that is greatly delayed from the predetermined timing S1. S2.
  • the controller 90 of the variable valve device 1 operates to control only the spool 31 of the hydraulic control valve 30 at a timing that does not affect the operation of the intake valve 3 to prevent the oil film of the spool portion 34 from being cut (for convenience of explanation, “control”). "Valve stabilization control”).
  • FIG. 6 is a flowchart showing a control procedure of VVA operation control
  • FIG. 7 is a flowchart showing a control procedure of control valve stabilization control according to the present invention
  • FIGS. 8 to 10 are VVA operation control and control valve stabilization. It is explanatory drawing which shows an example of each measurement signal in the control procedure of optimization control.
  • the controller 90 detects whether or not a VVA operation execution command signal or a VVA operation stop command signal is received. If a VVA operation execution command signal is detected (YES in S100), the VVA operation When control is performed and a VVA operation stop command signal is detected (NO in S100 and YES in S109), control valve stabilization control is performed (S110).
  • the VVA operation execution command signal and the VVA operation stop command signal are output from, for example, a host control device (not shown) that controls the entire vehicle, and a VVA operation instruction switch (not shown) is turned on or off. You may make it output correspondingly, or you may make it output automatically according to an engine output state based on the engine output map which is not shown in figure for controlling an engine output state. It is assumed that the VVA operation stop command signal is output for a certain time when the engine speed is low after the engine is started.
  • the VVA operation control performed when the VVA operation execution command signal is detected is performed by the TDC detection sensor signal 100 (see FIG. 8A) output from the TDC detection sensor 70, and from the crank angle detection sensor 72.
  • the output rotation speed detection signal 110 (see FIG. 8B) or the like is monitored, and when the TDC detection sensor signal 100 is detected (YES in S100, S101), the rotation speed of the engine is based on the rotation speed detection signal 110. And the count-up of the number of pulses of the rotation speed detection signal 110 is started, and the output timing (excitation instruction timing (Pcom)) of the command signal (VVA start signal) for exciting the hydraulic control valve 30 is determined ( S102, S103).
  • the operation of the intake valve 3 is measured as a closed delay region of the valve lift amount signal 133 (see FIG. 8D).
  • the operation of the intake valve 3 during this period is measured as the blocking action region B of the valve lift amount signal 133 (see FIG. 8D).
  • VVA start signal 123 is set to OFF (OFF)
  • control end command is detected (NO in S108)
  • a hydraulic control valve provided with a VVA start signal similar to the VVA start signal 123 corresponding to each cylinder. 30 and the VVA operation control for each cylinder is repeated.
  • control valve stabilization control that is performed when the VVA operation stop command signal is detected (NO in S100 and YES in S109) is specifically performed from the TDC detection sensor 70 as shown in FIG.
  • the output TDC detection sensor signal 100 (see FIG. 9A), the rotation speed detection signal 110 output from the crank angle detection sensor 72 (see FIG. 9B), and the like are monitored.
  • S111 the engine speed is calculated based on the engine speed detection signal 110, and the pulse number of the engine speed detection signal 110 is counted up to stabilize the operation of the hydraulic control valve 30.
  • the output timing (control valve stabilization instruction timing (Pst)) of the command signal (control valve stabilization signal) is determined (S112, S113).
  • control valve stabilization start setting pulse a preset number of pulses (control valve stabilization start setting pulse) 113 (YES in S114)
  • the control valve stabilization signal 127 (see FIG. 9C) is generated and output to the hydraulic control valve 30 of the hydraulic circuit corresponding to the cylinder in which the TDC detection sensor signal 100 is detected (S115).
  • the hydraulic control valve 30 is excited for the control valve stabilization holding time Ts from the time (or crank angle) of the control valve stabilization instruction timing (Pst) by the excitation current output corresponding to the control valve stabilization signal 127. Is done.
  • control valve stabilization holding time Ts is set according to the rotational speed of the engine so that the spool 31 moves reliably and an oil film is formed on the sliding surface of the spool portion 34, and the low rotational speed. It is set so long that
  • the VVA activation signal 125 (see the broken line portion) indicates the waveform of the VVA activation signal generated when the VVA operation control is performed and its output timing (excitation instruction timing (Pcom)). Show.
  • the control valve stabilization signal 127 excites the hydraulic control valve 30 at a timing that does not affect the operation of the intake valve 3 so that the oil film on the sliding surface of the spool portion 34 of the hydraulic control valve 30 does not run out. This is a control signal for operating only the spool 31 of the valve 30.
  • the timing at which the above-described operation of the intake valve 3 is not affected is desirably that the intake valve 3 is fully closed (closed region).
  • the number of cylinders of the engine is 6, and the TDC detection sensor signal 100 corresponds to the combustion start order of each cylinder, the first cylinder, the fifth cylinder, the third cylinder, the sixth cylinder, and the second cylinder.
  • the control valve stabilization control is performed on the first cylinder, and then the TDC detection sensor signal 100 for the fifth cylinder is detected.
  • the rotation speed detection signal 110 Based on the rotation speed detection signal 110, the engine rotation speed is detected. A number is calculated.
  • a control valve stabilization signal 128 (see FIG. 9C) is generated, and the fifth Output to the hydraulic control valve 30 of the cylinder, and excite the hydraulic control valve 30 for the control valve stabilization holding time Ts to operate only the spool 31 of the hydraulic control valve 30 to implement the control valve stabilization control of the fifth cylinder To do.
  • control valve stabilization control for the fifth cylinder After the control valve stabilization control for the fifth cylinder, the control valve stabilization control similar to the above is repeatedly performed in the order of the third cylinder, the sixth cylinder, the second cylinder, and the fourth cylinder.
  • control valve stabilization control is sequentially performed for each cylinder of the engine corresponding to the order of combustion start of each cylinder, so that each of the hydraulic control valves 30 arranged corresponding to each cylinder can be controlled. Oil film breakage of the spool portion 34 can be prevented.
  • each hydraulic control valve 30 by preventing the oil film from running out of the spool portion 34 of each hydraulic control valve 30, the intake valve 3 is extended by the return of the spool 31 during the initial operation after each hydraulic control valve 30 continues to be in the OFF state. Variations in the closing timing can be prevented.
  • FIG. 10 is a diagram illustrating an example of the control of the execution timing of the VVA operation control and the control valve stabilization control.
  • FIG. 10A illustrates the control valve stabilization prior to the execution of the VVA operation control based on the VVA operation execution command.
  • FIG. 10B is a diagram illustrating an example of control valve stabilization control (part time) for performing control control, and FIG. 10B illustrates control valve stabilization control (full time) for performing control valve stabilization control except during VVA operation control. It is a figure which shows an example.
  • the control valve stabilization control (part time) is controlled so that the VVA operation control is performed after the control valve stabilization control is performed. It is a method to do.
  • the control valve stabilization control is performed according to the control procedure described above (see FIG. 7) prior to the VVA operation control. Thereafter, the control method is to repeatedly execute a series of controls for each cylinder in which the VVA operation control is performed in the control procedure (see FIG. 6) described above.
  • control valve stabilization control (full time) is performed except when the VVA operation control is performed, and when the VVA operation execution command signal is detected, the VVA operation control signal is detected. This is a method of performing control so that operation control is performed.
  • the control valve stabilization control is arbitrarily performed according to the control procedure described above (see FIG. 7).
  • This is a control method in which when the operation execution command signal is detected, the control for executing the VVA operation control according to the control procedure described above (see FIG. 6) is repeatedly executed for each cylinder.
  • 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 diagram showing the relationship between the cam rotation angle and the valve lift amount in the intake stroke.
  • FIG. 4 is an explanatory diagram showing an example of a measurement signal of each sensor and a command signal to the hydraulic control valve that accompany the operation of the variable valve device 1.
  • FIG. 5 is an explanatory diagram showing the closing timing of the intake valve 3 due to the extension of the return of the spool 31.
  • FIG. 6 is a flowchart showing a control procedure of VVA operation control.
  • FIG. 7 is a flowchart showing a control procedure of control valve stabilization control according to the present invention.
  • FIG. 8 is an explanatory diagram showing an example of each measurement signal in the control procedure of the VVA operation control.
  • FIG. 9 is an explanatory diagram showing an example of each measurement signal in the control procedure of the control valve stabilization control.
  • FIG. 10 is a diagram illustrating an example of the control of the execution timing of the VVA operation control and the control valve stabilization control.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

La présente invention concerne une distribution variable et un procédé de commande de la distribution variable. Selon ladite distribution, pour éviter le risque d'avoir un film d'huile insuffisant dans une section de tiroir, seul le tiroir de la soupape à solénoïde on/off est déplacé selon un calage n'affectant pas le fonctionnement de la soupape d'admission, pour stabiliser de cette façon le fonctionnement de la soupape à solénoïde on/off. La distribution variable selon l’invention comprend : un actionneur hydraulique équipé d'un mécanisme de commande de distribution pour déplacer une soupape d'admission d’air afin d’ouvrir ou de fermer un orifice d'admission d'air et d'une section tige de piston pour bloquer le mouvement de la soupape d'admission d'air ; une soupape de commande hydraulique pour commander la quantité d'huile hydraulique qui est alimentée à l'actionneur hydraulique ou évacuée de celui-ci, la soupape de commande hydraulique comprenant un élément de soupape et une surface de coulissement sur laquelle coulisse l'élément de soupape, l'élément de soupape étant configuré pour le déplacement entre une position d’interdiction dans laquelle le fonctionnement de la section tige de piston de l'actionneur hydraulique est interdit et une position d'autorisation dans laquelle le fonctionnement de la section tige de piston de l'actionneur hydraulique est autorisé ; et un moyen de commande de stabilisation de la commande de soupape pour faire coulisser l'élément de soupape de la soupape de commande hydraulique quand l’orifice d'admission d'air est entièrement fermé par la soupape d'admission d'air et le moyen en question assurant également la commande variable de la soupape pour son coulissement, après le fonctionnement de la commande de stabilisation de la soupape et pendant que la soupape de commande d'admission d'air est dans sa course de fermeture, afin de déplacer l'élément de soupape vers le côté d'interdiction pour interdire le fonctionnement de la section tige de piston, arrêtant le mouvement de fermeture de la soupape d'admission d'air et pour changer de cette façon le calage auquel l'ouverture d'admission d'air est entièrement fermée.
PCT/JP2009/069164 2008-11-20 2009-11-11 Distribution variable et son procédé de commande WO2010058720A1 (fr)

Priority Applications (3)

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US13/129,088 US20110214631A1 (en) 2008-11-20 2009-11-11 Variable valve device and method of controlling the same
CN2009801465944A CN102224326A (zh) 2008-11-20 2009-11-11 可变阀装置及其控制方法
EP09827501A EP2357327A4 (fr) 2008-11-20 2009-11-11 Distribution variable et son procédé de commande

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JP2008-297229 2008-11-20
JP2008297229A JP2010121570A (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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JP (1) JP2010121570A (fr)
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KR101528443B1 (ko) * 2012-01-11 2015-06-11 이턴 코포레이션 유압­작동형 스위칭 구성요소의 제어 방법 및 제어 시스템
CN103806973B (zh) * 2012-11-07 2016-04-27 广西玉柴机器股份有限公司 发动机电控液压配气系统
US9506382B2 (en) 2015-03-30 2016-11-29 Caterpillar Inc. Variable valve actuator
DE102016218835A1 (de) * 2016-09-29 2018-03-29 Ford Global Technologies, Llc Ölversorgungseinheit und Kraftfahrzeug
CN109357644B (zh) * 2018-11-16 2020-11-06 黑龙江大学 非接触式针阀升程测量方法

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See also references of EP2357327A4

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CN102224326A (zh) 2011-10-19
EP2357327A1 (fr) 2011-08-17
JP2010121570A (ja) 2010-06-03
EP2357327A4 (fr) 2012-09-05
US20110214631A1 (en) 2011-09-08

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