US20090199796A1 - Engine valve device - Google Patents

Engine valve device Download PDF

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Publication number
US20090199796A1
US20090199796A1 US12/308,716 US30871607A US2009199796A1 US 20090199796 A1 US20090199796 A1 US 20090199796A1 US 30871607 A US30871607 A US 30871607A US 2009199796 A1 US2009199796 A1 US 2009199796A1
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United States
Prior art keywords
hydraulic
valve
engine
hydraulic oil
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US12/308,716
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English (en)
Inventor
Youhei Hisada
Hideaki Tachibana
Etsuro Sato
Kunio Horiai
Jun Maruyama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Komatsu Ltd
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Komatsu Ltd
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Filing date
Publication date
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Assigned to KOMATSU LTD. reassignment KOMATSU LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HISADA, YOUHEI, HORIAI, KUNIO, MARUYAMA, JUN, SATO, ETSURO, TACHIBANA, HIDEAKI
Publication of US20090199796A1 publication Critical patent/US20090199796A1/en
Abandoned legal-status Critical Current

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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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/146—Push-rods
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/16—Controlling lubricant pressure or quantity
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L2001/34446—Fluid accumulators for the feeding circuit
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers

Definitions

  • the present invention relates to an engine valve device and technology allowing variable motion of the engine valve device.
  • FIG. 7 is a sectional side view showing a structure of a known engine valve device.
  • FIG. 8 is a circuit diagram showing a configuration of a fluid circuit of the engine valve device shown in FIG. 7 .
  • an engine valve device 100 is configured to maintain an open state of an intake valve 103 by a fluid actuator 101 via a rocker arm 102 .
  • this engine valve device 100 includes the fluid actuator 101 that follows the rocker arm 102 , a direction control valve 105 that stops a flow of fluid from fluid actuator 101 at a predetermined timing, and a fluid source that supplies fluid to the direction control valve 105 .
  • the direction control valve 105 stops the flow of fluid from the fluid actuator 101 at the predetermined timing, and the fluid actuator 101 acts on the rocker arm 102 . Therefore, the engine valve device 100 can maintain the open state of the intake valve 103 .
  • the fluid source used as such usage is, for example shown in FIG. 8 , a part of a lubrication unit 107 , which is attached to the engine to supply lubricating oil to the engine, and is capable of supplying pressurized oil of a pressure from about 210 KPa to 620 KPa.
  • a pump may be provided separately from the lubrication unit 107 attached to the engine to supply pressurized oil of a pressure from 10 MPa to 35 MPa to the direction control valve 105 (for example, see Patent Document 1).
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2003-328715
  • a piston 106 cannot follow an open-close motion of the intake valve 103 when the engine is at a high revolution, for example, over 1000 rpm. Therefore, the piston 106 can not reach to a predetermined position and can not put the intake valve into the open state at a desired amount of opening.
  • the pump is provided separately from the lubrication unit 107 attached to the engine to supply pressurized oil of a pressure from 10 MPa to 35 MPa, it is subject to a considerable increase in cost as well as the engine becomes larger. Also, because the lubrication unit 107 attached to the engine supplies and discharges pressurized oil every time the fluid actuator 101 acts on, an energy loss becomes tremendously large.
  • the present invention is made in view of the above problems and an object of the present invention is to provide an engine valve device which is capable of following a high revolution of an engine and of highly efficient operating although the engine valve device is configured to vary a motion, utilizing a part of a lubricating oil unit attached to the engine as an oil source.
  • an engine valve device includes a cam which rotates by engaging with a crankshaft, a rocker arm which follows a movement of the cam, and an intake valve which opens and closes an intake port by interacting the rocker arm and a spring.
  • the engine valve device comprises: a piston which is movable in a same direction as the intake valve; a cylinder which houses the piston such that the piston is movable inside the cylinder; a hydraulic actuator including the piston and the cylinder; a hydraulic pipe line which communicates with a pressure chamber formed by the piston and the cylinder; an accumulation unit which accumulates hydraulic oil flowed out from the pressure chamber via the hydraulic pipe line; and an electromagnetic on-off valve which controls a flow of the hydraulic oil between the pressure chamber and the accumulation unit.
  • the hydraulic actuator, the hydraulic pipe line, the accumulation unit, and the electromagnetic on-off valve make up a hydraulic circuit.
  • the electromagnetic on-off valve is arranged on the hydraulic pipe line between the hydraulic actuator and the accumulation unit.
  • an engine valve device includes a cam which rotates by engaging with a crankshaft, a rocker arm which follows a movement of the cam, an intake valve which opens or closes an intake port by interacting the rocker arm and a spring, and a hydraulic circuit.
  • the hydraulic circuit includes: a hydraulic actuator which is activated by an open and close motion of the intake valve, the hydraulic actuator stopping a closing motion of the intake valve in an open state when hydraulic oil is sealed in a pressure chamber; an accumulation unit which accumulates the hydraulic oil flowed out from the pressure chamber of the hydraulic actuator when the intake valve moves to close, and which provides the hydraulic oil to the pressure chamber of the hydraulic actuator when the intake valve moves to open; and an electromagnetic on-off valve which controls a flow of the hydraulic oil from the hydraulic actuator to the accumulation unit.
  • the electromagnetic on-off valve is arranged between the hydraulic actuator and the accumulation unit.
  • the invention described above further comprises a hydraulic oil supply unit which provides the hydraulic oil to the hydraulic circuit.
  • the hydraulic oil supply unit is a lubrication unit which provides lubricating oil to an engine and is attached to the engine.
  • the invention described above further comprises an auxiliary pipe line which allows the flow of the hydraulic oil from the pressure chamber of the hydraulic actuator to the accumulation unit.
  • the auxiliary pipe line includes a port which opens when the piston of the hydraulic actuator comes to a predetermined interval, the piston of the hydraulic actuator follows the intake valve moving to a closing direction.
  • the invention described above further comprises a check valve which supplies the hydraulic oil from the hydraulic oil supply unit to the hydraulic circuit only if an oil pressure of the hydraulic circuit is lower than that of the hydraulic oil supply unit, and the check valve is arranged between the hydraulic oil supply unit and the hydraulic circuit.
  • the pressure chamber of the hydraulic actuator is configured to cushion a shock when the intake valve closes.
  • the invention described above further comprises: a push rod which transmits motion from the cam to the rocker arm, the push rod being disposed between the cam and the rocker arm; and a biasing unit which biases the rocker arm to tightly contact with the push rod.
  • the engine valve device includes the hydraulic circuit including the accumulation unit which accumulates hydraulic oil flowed out from the pressure chamber of the hydraulic actuator when the intake valve moves to close, and provides hydraulic oil to the pressure chamber of the hydraulic actuator when the intake valve moves to open, and the electromagnetic on-off valve which controls a flow of the hydraulic oil from the hydraulic actuator to the accumulation unit.
  • the electromagnetic on-off valve is arranged between the hydraulic actuator and the accumulation unit. Accordingly, to precisely make the intake valve an open state, the engine valve device can follow a high revolution of the engine and be efficiently operated.
  • the lubrication unit which is attached to the engine and provides lubricating oil to the engine, provides hydraulic oil to the hydraulic circuit. Accordingly, there is no need to provide an oil pump separately from the lubrication unit attached to the engine, there is no need to grow in size, and an increase in cost is suppressed.
  • FIG. 1 is a schematic view of an engine valve device according to an embodiment of the present invention
  • FIG. 2A is a view showing a behavior of the engine valve device shown in FIG. 1 and showing a close state of an intake valve;
  • FIG. 2B is a view showing a behavior of the engine valve device shown in FIG. 1 and showing a full open state of the intake valve;
  • FIG. 2C is a view showing a behavior of the engine valve device shown in FIG. 1 and showing a close starting state of the intake valve;
  • FIG. 2D is a view showing a behavior of the engine valve device shown in FIG. 1 and showing a state in which the intake valve is closed to a predetermined gate opening;
  • FIG. 2E is a view showing a behavior of the engine valve device shown in FIG. 1 and showing a full close state of the intake valve;
  • FIG. 3 is a view showing a hydraulic circuit of the engine valve device shown in FIG. 1 ;
  • FIG. 4 is a view showing a relation between a cam rotating angle and an amount of valve lift for an intake stroke of the engine valve device shown in FIG. 1 ;
  • FIG. 5 is a flowchart showing control of the engine valve device shown in FIG. 1 ;
  • FIG. 6 is a timing chart showing a control timing of the engine valve device shown in FIG. 1 ;
  • FIG. 7 is a sectional side view showing a structure of a known engine valve device
  • FIG. 8 is a view showing a configuration of a fluid circuit of the engine valve device shown in FIG. 7 ;
  • FIG. 1 is a schematic view of an engine valve device according to an embodiment of the present invention
  • FIG. 2 is a view showing a behavior of the engine valve device shown in FIG. 1
  • FIG. 3 is a view showing a hydraulic circuit of the engine valve device shown in FIG. 1
  • FIG. 4 is a view showing a relationship between a cam rotating angle and an amount of valve lift for an intake stroke of the engine valve device shown in FIG. 1
  • FIG. 5 is a flowchart showing control of the engine valve device shown in FIG. 1
  • FIG. 6 is a timing chart showing control timing of the engine valve device shown in FIG. 1
  • An engine valve device 1 according to an embodiment of the present invention is applied to an engine valve device of a four-cycle diesel engine.
  • the diesel engine includes a cylinder block and a cylinder head CH.
  • the cylinder block is provided with a cylindrically shaped cylinder which allows an engine piston EP slides in up-and-down direction.
  • the cylinder head is provides with a pair of intake ports 2 which are in communication with an outside of the cylinder and a pair of exhaust ports which is not shown in the figure.
  • an intake valve 3 is provided such that the intake valve 3 closes or opens the intake port 2 by moving up and down with respect to FIG. 1 .
  • an exhaust valve is provided such that the exhaust valve closes or opens the exhaust port by moving up and down.
  • the intake valve 3 and the exhaust valve are poppet valves which are formed in an umbrella shape, and include valve portions (umbrella shaped portion) 3 a that close the intake port 2 and the exhaust port and stems (rod shaped portion) 3 b that slides through the cylinder head CH.
  • the stem 3 b of the intake valve 3 which is in communication with the intake port 2 is provided with a valve spring 4 , and the valve portion 3 a of the intake valve 3 is biased to close the intake port 2 .
  • the stem of the exhaust valve which is in communication with the exhaust port is provided with a valve spring, not shown in the figure, and the valve portion of the exhaust valve is biased to close the exhaust port.
  • a crosshead 5 which has a side view of a T shape and pushes the ends of stems of the pair of the intake valves 3 at the same time is provides.
  • the crosshead 5 is guided by a shaft 6 provided to be placed parallel to a moving direction of the intake valve 3 and the exhaust valve, and is allowed to move up and down with respect to FIG. 1 . Therefore, the crosshead 5 pushes the ends of the stems of the intake valves 3 to open the intake valves 3 against biasing forces of the valve springs 4 when the crosshead 5 moves down.
  • One side of arm 5 a of the crosshead 5 (left side arm in FIG. 1 ) is provided with an adjustable screw 7 such that the crosshead 5 closely contacts with the intake valve 3 .
  • the adjustable screw 7 can be screwed with respect to the crosshead 5 to adjust a clearance of one of the pear of the intake valves 3 (left side intake valve in FIG. 1 ).
  • it is adjustable such that one of the intake valves 3 opens the intake port 2 at the same time the other of the intake valves 3 opens the intake port 2 .
  • a locknut 8 is threadably mounted on the adjustable screw 7 to prevent from loosening by closely sticking the locknut 8 to the crosshead 5 after adjusting.
  • a rocker arm 9 is provided above the crosshead 5 as shown in FIG. 1 .
  • the rocker arm 9 is rotatable around a rocker shaft 10 as an axis.
  • the rocker arm 9 includes a pressing portion 9 a which pushes the crosshead 5 on an end portion (left side portion in FIG. 1 ) and an action portion 9 b on the other end portion.
  • the pressing portion 9 a of the rocker arm 9 is allowed to push around a central portion of the crosshead 5 .
  • the rocker arm 9 rotates counterclockwise with respect to FIG. 1
  • the pressing portion 9 a of the rocker arm 9 pushes the crosshead 5
  • the intake valve 3 opens the intake port 2 .
  • the rocker arm 9 rotates clockwise with respect to FIG.
  • the intake valve 3 closes the intake port 2 by the biasing force of the valve spring 4 and moves up the crosshead 5 .
  • a groove 9 c which has a planar view of a U shape is formed.
  • An adjust screw 11 is threadably mounted on the action portion 9 b of the rocker arm 9 to adjust a clearance between the pressing portion 9 a and the crosshead 5 .
  • the adjust screw 11 includes a hemisphere portion on an end portion and a male screw on the other end portion.
  • a locknut 12 is threadably mounted on the adjust screw 11 which is threadably mounted on the other end portion of the rocker arm 9 .
  • the adjust screw 11 is allowed to prevent from loosening by closely sticking the locknut 12 to the rocker arm 9 .
  • the end portion of hemisphere of the adjust screw 11 is housed in an end portion of a push rod 13 .
  • the end portion of the push rod 13 is provided with a concave portion 13 a of hemisphere and has a capacity of housing the end portion of hemisphere of the adjust screw 11 .
  • the push rod 13 rotates the rocker arm 9 counterclockwise with respect to FIG. 1 .
  • the other end portion 13 b of the push rod 13 is housed in a push rod housing 14 a provided above an arm portion of a tappet arm 14 .
  • a return spring 15 is tacked between the action portion 9 b of the rocker arm 9 and the cylinder head CH.
  • the return spring 15 pushes the rocker arm 9 clockwise with respect to FIG. 1 , and is capable of maintaining to house the end portion of the adjust screw 11 in the concave portion 13 a of the push rod 13 .
  • the return spring 15 is to push the rocker arm 9 clockwise with respect to FIG. 1 , and the return spring 15 is replaced by a torsion coil spring which is wound around the rocker shaft 10 .
  • an end of the coil spring is fixed to the rocker arm 9 , and the other end is fixed to the cylinder head CH.
  • a tappet arm 14 is rotatably attached to a tappet shaft as an axis.
  • the tappet arm 14 rotates clockwise with respect to FIG. 2
  • the tappet arm 14 pushes up the push rod 13 and causes the rocker arm 9 to rotate counterclockwise with respect to FIG. 2 .
  • a roller follower 17 is rotatably attached below an arm portion of the tappet arm 14 .
  • a cam 18 is rotatably provided to allow a rolling contact with the roller follower 17 .
  • the cam 18 rotates by engaging with a crankshaft, not shown in the figure, of the engine.
  • the cam 18 moves (lifts) the intake valve 3 via the tappet arm 14 , the push rod 13 , the rocker arm 9 , and the crosshead 5 , thereby, allowing the intake port 2 to open.
  • an opening timing of the intake port 2 and a valve lift amount of the intake valve 3 are controlled by a surface configuration (cam profile) of the cam 18 .
  • the valve lift amount describes an action toward an open direction at a closing time of 0 as a lift, and takes a positive value at the moment.
  • the crankshaft is connected to the other end portion of a con-rod of which an end portion is connected to the engine piston EP sliding in the cylinder.
  • the intake valve 3 can be opened and closed in the intake stroke, and the intake valve 3 can be closed in a compression stroke, a combustion stroke, and an exhaust stroke.
  • an hydraulic actuator 20 is provided above the crosshead 5 .
  • the hydraulic actuator 20 is arranged such that a tip of a rod portion 23 c of a piston 23 contacts with the crosshead 5 and is capable of engaging with a movement of the crosshead 5 .
  • the hydraulic actuator 20 pushes the crosshead 5 at a predetermined timing and maintains an open state of the intake valve 3 regardless of movements of the cam 18 , the tappet arm 14 , the push rod 13 , and the rocker arm 9 .
  • the hydraulic actuator 20 applied to the embodiment is a single acting type.
  • a cylinder portion 22 is integrally formed with a block 21 , and an electromagnetic on-off valve 30 can be housed to be attached.
  • a supply discharge pipe line 21 d which communicates with an output port 30 b of the electromagnetic on-off valve 30 is formed on the block 21 . Also, a first pipe line 21 b which communicates with an output port 50 a of an accumulator 50 , which will be explained later in detail, is formed. The first pipe line 21 b communicates with an intake port 30 a of the electromagnetic on-off valve 30 and a flow pipe line 21 e , which will be explained later in detail, by a second pipe line 21 c.
  • the cylinder portion 22 includes a small diameter chamber 22 a and a large diameter chamber 22 b , which constitute a pressure chamber and have cylindrical shapes.
  • One end of the large diameter chamber 22 b is opened to accept an insertion of the piston 23 , and closed by the piston 23 .
  • the other end of the large diameter chamber 22 b is formed such that the small diameter chamber 22 a coincides and communicates with an axis of the large diameter chamber 22 b .
  • the small diameter chamber 22 a communicates with the supply discharge pipe line 21 d .
  • a step 22 c is formed on a border of the large diameter chamber 22 b and the small diameter chamber 22 a.
  • An oil groove 22 b 1 is formed on a predetermined section of the large diameter chamber 22 b .
  • the flow pipe line 21 e which communicates with a second pipe line 21 c is formed on the oil groove 22 b 1 .
  • the cylinder portion 22 houses the piston 23 which slides in an axial direction of the large diameter chamber 22 b and the small diameter chamber 22 a (up and down direction with respect to FIG. 1 ).
  • the piston 23 includes a piston portion 23 a , a buffering portion 23 b , and a rod portion 23 c .
  • the piston portion 23 a is a portion which slides in the large diameter chamber 22 b of the cylinder portion 22 .
  • the buffering portion 23 b is a portion which is housed in the small diameter chamber 22 a of the cylinder portion 22 , and is provided to one end of axial direction (above the piston portion in FIG. 1 ) of the piston portion 23 a .
  • the buffering portion 23 b is capable of, by interaction between the buffering portion 23 b and the small diameter chamber 22 a of the cylinder portion 22 , cushioning a shock caused when the intake valve 3 closes.
  • the pressure chamber is configured to cushion the shock caused when the intake valve 3 is closed.
  • the buffering portion 23 b includes a buffering shape which cushions the shock caused when the intake valve 3 is closed (when the intake valve 3 seats).
  • the buffering shape is, for example, a plurality of longitudinal grooves 23 b 1 (four longitudinal grooves in this embodiment) which are formed from a circumferential root to a tip of the buffering portion 23 b .
  • the shock caused when the buffering portion 23 b is housed into the small diameter chamber 22 a is cushioned by flowing out hydraulic oil accumulated in an upper end corner portion of the large diameter chamber 22 b via the longitudinal grooves 23 b 1 . Accordingly, the shock caused when the intake valve 3 engaging the piston 23 of the hydraulic actuator 20 is closed is cushioned, and a valve portion 3 a is protected from a crash by the shock caused when the valve portion 3 a seats.
  • the buffering shape is not limited to the longitudinal groove 23 b 1 , and may be formed in a tapered shape which gradually tapers from the circumferential root to the tip of the buffering portion 23 b .
  • the buffering shape may be formed in a tapered shape in which the small diameter chamber 22 a gradually gets thick from a bottom portion to the large diameter chamber 22 b .
  • the rod portion 23 c is a portion which extends outside of the cylinder portion 22 , and is provided to an end opposite to the buffering portion 23 b in axial direction of the piston portion 23 a (below the piston portion 23 a with respect to FIG. 1 ).
  • the rod portion 23 c is formed in a taper shape which gradually tapers from the root to the tip.
  • the rod portion 23 c is capable of pushing the crosshead 5 without interference of the rocker arm 9 by inserting the groove 9 c formed on the pressing portion 9 a of the rocker arm 9 .
  • the rod portion 23 c is capable of pushing the crosshead 5 separately from the rocker arm 9 .
  • a gap sensor (clearance measurement means) 24 is provided on a side of the rod portion 23 c of the piston 23 .
  • the gap sensor 24 measures a clearance between the rod portion 23 c and the gap sensor 24 , and is connected to an engine control unit (ECU) 40 .
  • the gap sensor 24 is capable of measuring the clearance, for example, by measuring a current surge.
  • the engine control unit 40 is capable of monitoring an action of the hydraulic actuator 20 by monitoring the clearance of the rod portion 23 c measured by the gap sensor 24 .
  • the clearance becomes small when the rod portion 23 c protrudes from the cylinder portion 22 , and the clearance becomes large when the rod portion 23 c recedes in the cylinder portion 22 , the monitoring of the hydraulic-actuator 20 can be achieved by monitoring the clearance.
  • the electromagnetic on-off valve 30 is housed in the concave portion 21 a of the block 21 .
  • the electromagnetic on-off valve 30 is a two port type electromagnetic on-off valve which includes an intake port 30 a and an output port 30 b .
  • the intake port 30 a communicates with the second pipe line 21 c of the block 21
  • the output port 30 b communicates with the supply discharge pipe line 21 d of the block 21 .
  • the electromagnetic on-off valve 30 includes inside a spool 31 as well as a spring and a solenoid, not shown in the figure.
  • the spring pushes the spool 31 to connect the intake port 30 a and the output port 30 b when a normal condition, and the spool 31 cuts off the communication between the intake port 30 a and the output port 30 b against a biasing force of the spring when the solenoid is excited.
  • the electromagnetic on-off valve 30 is capable of switching between a hydraulic oil supply discharge condition and a hydraulic oil cut off condition.
  • the intake port 30 a and the output port 30 b returns to a condition in which the intake port 30 a and the output port 30 b are in communication.
  • the piston 23 moves upward and hydraulic oil flows out from the supply discharge pipe line 21 d of the block 21 .
  • the flowed hydraulic oil flows out outside of the hydraulic actuator 20 via the output port 30 b and intake port 30 a of the electromagnetic on-off valve 30 , the second pipe line 21 c , and the first pipe line 21 b .
  • the buffering portion 23 b of the piston 23 is housed in the small diameter chamber 22 a of the cylinder portion 22 , and a sequence of functions of the hydraulic actuator 20 ends.
  • the electromagnetic on-off valve 30 is connected to the engine control unit 40 .
  • the engine control unit 40 controls an exciting timing and an exciting time period of the electromagnetic on-off valve 30 , and is capable of controlling the electromagnetic on-off valve 30 in units of milliseconds ( 1/1000 seconds) as desired.
  • An output port 50 a of the accumulator 50 is connected to the first pipe line 21 b of the block 21 .
  • the accumulator 50 is an accumulating means for accumulating oil pressure, and the accumulator 50 according to the embodiment is a mechanical accumulator.
  • the accumulator 50 includes the output port 50 a explained above, an output pipe line 50 b which extends from the output port 50 a , an input pipe line 50 c which crosses to the output pipe line 50 b , and a input port 50 d which communicates with the input pipe line 50 c .
  • the input pipe line 50 c communicates with a pressure accumulating portion 52 .
  • the pressure accumulating portion 52 includes a cylinder 55 formed on a body of the accumulator 50 .
  • the cylinder 55 communicates with the input pipe line 50 c , and is configured such that hydraulic oil provided from the input port 50 d and hydraulic oil provided from the output port 50 a can flow in.
  • the cylinder 55 includes inside a plunger 56 which slides in an axial direction of the cylinder 55 and a compression spring 57 which pushes the plunger 56 toward a bottom wall of the cylinder 55 (toward left in the figure).
  • hydraulic oil is provided from the input port 50 d of the accumulator 50 and hydraulic oil pushes plunger 56 toward the side (right side with respect to FIG. 1 ), the plunger 56 can not resist a basing force of the compression spring 57 , and hydraulic oil flows out from the output port 50 a .
  • hydraulic oil which is flowed out from the hydraulic actuator 20 and posses a higher oil pressure than an oil pressure of hydraulic oil provided from the input port 50 d
  • the hydraulic oil pushes the plunger 56 toward the side (right side with respect to FIG. 1 ), and the plunger 56 moves toward the side (toward left in the figure) against the biasing force of the compression spring 57 .
  • hydraulic oil is accumulated (pressure accumulation) in the pressure accumulating portion 52 .
  • the hydraulic actuator 20 , the electromagnetic on-off valve 30 , and the accumulator 50 make up a hydraulic circuit 60 , as shown in FIG. 3 .
  • a lubrication unit 61 which is attached to the engine and provides lubricating oil to the engine is capable of providing low pressure hydraulic oil to the hydraulic circuit 60 .
  • a check valve 62 is arranged between the lubrication unit 61 attached to the engine and the hydraulic circuit 60 . The check valve 62 allows providing hydraulic oil to the hydraulic circuit 60 from the lubrication unit 61 attached to the engine only if an oil pressure of the hydraulic circuit 60 is lower than that of the lubrication unit 61 attached to the engine, and does not allow hydraulic oil to flow from the hydraulic circuit 60 side to the lubrication unit 61 attached to the engine.
  • a relief valve 63 is provided between the check valve 62 and the hydraulic circuit 60 explained above.
  • the relief valve 63 is capable of discharging hydraulic oil of the hydraulic circuit 60 to an oil pan 64 of the engine when the oil pressure of the hydraulic circuit 60 becomes higher than a predetermined pressure.
  • the engine control unit 40 connected to the gap sensor 24 and the electromagnetic on-off valve 30 is configured to detect which cylinder has the engine piston EP come to a top dead center, based on a cylinder determination signal (G signal) entered from TDC (Top Dead Center) sensor (cylinder determination signal output means), as shown in FIG. 6 . Also, the engine control unit 40 calculates a revolution based on a revolution detection signal (Ne signal) entered from a crank angle sensor (revolution detection signal output means), not shown in the figure. The engine control unit 40 is configured to start to count number of pulses of the revolution detection signal (square wave) when the engine piston EP of a cylinder to delay a closing timing (for example, cylinder 5 in FIG. 6 ) comes to the upper dead center.
  • the engine control unit 40 turns on a VVA activation signal and excites the electromagnetic on-off valve 30 for a preset VVA holding time Tw.
  • the lubrication unit 61 attached to the engine provides hydraulic oil to the hydraulic circuit 60 by starting the engine.
  • hydraulic oil is provided to in order of the accumulator 50 , the electromagnetic on-off valve 30 , and the hydraulic actuator 20 via the check valve 62 .
  • hydraulic oil is filled in the electromagnetic on-off valve 30 and the hydraulic actuator 20 .
  • the intake valve 3 opens and closes the intake port 2 during the intake stroke of the engine, and the intake valve 3 closes the intake port 2 during the compression stroke, the combustion stroke, and the exhaust stroke of the engine.
  • the intake valve 3 closes the intake port 2 by the biasing force of the valve spring 4 .
  • a relation between a rotational angle of the cam 14 and the valve lift amount has a relation shown by a close area in FIG. 4 . More specifically, it has a relation in which the valve lift amount is 0 regardless of the rotational angle of the cam 18 .
  • the rod portion 23 c of the piston 23 gradually protrudes (downward with respect to FIG. 1 ), contacting with the crosshead 5 , by gradually providing hydraulic oil accumulated in the accumulator 50 to the small diameter chamber 22 a and the large diameter chamber 22 b of the cylinder portion 22 .
  • hydraulic oil is provided to in order of the electromagnetic on-off valve 30 and the hydraulic actuator 20 .
  • hydraulic oil is gradually provided to the hydraulic circuit 60 from the lubrication unit 61 attached to the engine via the check valve 62 .
  • a relation between the cam rotational angle and the valve lift amount has a relation shown by a close function area in FIG. 4 . More specifically, it has a relation in which the valve lift amount gradually decreases as the rotational angle of the cam 18 increases.
  • the hydraulic actuator 20 has a function of a piston pump. To be more specific, hydraulic oil is accumulated in the accumulator 50 via the electromagnetic on-off valve 30 and the hydraulic actuator 20 .
  • the spool 31 cuts off the communication between the intake port 30 a and the output port 30 b against the biasing force of the spring. More specifically, the electromagnetic on-off valve 30 makes a transition from the hydraulic oil supply discharge state to the hydraulic oil cut off state. Then, the piston 23 is pushed into the cylinder portion 22 until the piston portion 23 a of the piston 23 closes the oil groove 22 b 1 communicated with the flow pipe line 21 e of the block 21 , and, afterward, hydraulic oil is sealed in the small diameter chamber 22 a and the large diameter chamber 22 b of the cylinder portion 22 . Thus, the piston 23 is stopped by hydraulic oil sealed in the small diameter chamber 22 a and the large diameter chamber 22 b.
  • the rod portion 23 c of the piston 23 pushes the crosshead 5 , and the intake valve 3 keeps to open at a predetermined gate opening, as shown in FIG. 2D . More specifically, the closing timing of the intake port 2 by the intake valve 3 during the intake stroke is delayed. Because of a mechanism in which the oil groove 22 b 1 is provided inside the cylinder portion 22 and the piston portion 23 a closes the oil groove 22 b 1 , the open state is maintained at the same gate opening. At this time, a relation between the cam rotational angle and the valve lift amount has a relation shown by a close delay area in FIG. 4 . More specifically, it has a relation in which the valve lift amount is constant although the rotational angle of the cam 18 increases.
  • the rocker arm 9 tightly contacts with the push rod 13 by the biasing force of the return spring 15 , and controlled by the surface configuration (cam profile) of the cam 18 .
  • the clearance is generated between the crosshead 5 and the rocker arm 9 without dropping the push rod 13 from the rocker arm 9 .
  • the intake port 30 a becomes in communication with the output port 30 b again.
  • the intake valve 3 gradually closes the intake port 2 by the biasing force of the valve spring 4 .
  • the engine control unit 40 starts to count the number of pulses of the revolution detection signal (Step S 2 ), when the engine piston EP of the cylinder to delay a closing timing (for example, cylinder 5 in FIG. 6 ) comes to the upper dead center (Step S 1 : Yes), as shown in FIG. 5 and FIG. 6 . Then, when the counted number of pulses of the revolution detection signal reaches to the preset VVA activation setup pulse (Step S 3 : Yes), the engine control unit 40 turns on the VVA activation signal (Step S 4 ).
  • Step S 5 when the VVA activation signal is turned on, the electromagnetic on-off valve 30 is excited for the preset VVA holding time Tw (Step S 5 ). Afterward, these routines are repeated to control the closing timing of the intake port 2 to be delayed by the intake valve 3 .
  • the intake valve 3 engages with the rocker arm 9 until the piston 23 of the hydraulic actuator 20 closes the oil groove 22 b 1 (flow pipe line 21 e ). After closing the oil groove 22 b 1 which is communicated with the flow pipe line 21 e , the open state of the intake valve 3 is maintained until the electromagnetic on-off valve 30 is opened. Thus, the open state of the intake port 2 is maintained at the preset amount of opening regardless of the closing timing of the electromagnetic on-off valve 30 .
  • an engine valve device of the present invention is applicable to an engine valve device which varies an action of an engine valve, especially, is adapted to an engine valve of a diesel engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
US12/308,716 2006-06-30 2007-06-22 Engine valve device Abandoned US20090199796A1 (en)

Applications Claiming Priority (3)

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JP2006182121 2006-06-30
JP2006-182121 2006-06-30
PCT/JP2007/062630 WO2008001699A1 (fr) 2006-06-30 2007-06-22 Dispositif de vanne de moteur

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US (1) US20090199796A1 (fr)
EP (1) EP2039892B1 (fr)
JP (1) JPWO2008001699A1 (fr)
KR (1) KR101083613B1 (fr)
CN (1) CN101473111B (fr)
WO (1) WO2008001699A1 (fr)

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US20110214631A1 (en) * 2008-11-20 2011-09-08 Komatsu Ltd. Variable valve device and method of controlling the same
US20110220045A1 (en) * 2008-11-20 2011-09-15 Komatsu Ltd. Variable valve device and control method thereof
US20120234271A1 (en) * 2011-03-14 2012-09-20 Schaeffler Technologies AG & Co. KG Pressure storage unit for a camshaft and piston for a pressure storage unit
US20140060477A1 (en) * 2012-08-31 2014-03-06 Yamada Manufacturing Co., Ltd Engine lubrication control system
US9109479B2 (en) 2012-08-31 2015-08-18 Yamada Manufacturing Co., Ltd. Engine lubrication control system
DE102016112447A1 (de) * 2016-07-07 2018-01-11 Man Diesel & Turbo Se Ventiltrieb für eine Brennkraftmaschine und Brennkraftmaschine
CN113818943A (zh) * 2021-11-25 2021-12-21 江苏卓联精密机械有限公司 专用固定式双活塞液压发动机气门驱动装置
US11976578B2 (en) 2021-11-25 2024-05-07 Jiangsu Jointek Precision Machinery Co., Ltd. Driving devices for a composite engine valve of a dedicated driving cam

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KR101382327B1 (ko) * 2012-10-17 2014-04-08 현대자동차 주식회사 가변 밸브 리프트 장치
FI20135003L (fi) * 2013-01-03 2014-07-04 Waertsilae Finland Oy Pakoventtiilijärjestely ja menetelmä pakoventtiilin sulkeutumisen kontrolloimiseksi
US8967103B2 (en) 2013-03-04 2015-03-03 Caterpillar Inc. Variable valve timing arrangement
CN104265395B (zh) * 2013-07-26 2017-01-11 皆可博车辆控制系统公司 用于多气缸内燃机的空气激活供油装置
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CN105804827A (zh) * 2016-05-04 2016-07-27 哈尔滨工程大学 压电控制增压式配气系统
CN110185513A (zh) * 2019-07-01 2019-08-30 贵州大学 一种电液式可变气门正时调节装置
CN111535894B (zh) * 2020-04-28 2021-02-19 一汽解放汽车有限公司 一种电控液压式气门系统及发动机

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US20110214631A1 (en) * 2008-11-20 2011-09-08 Komatsu Ltd. Variable valve device and method of controlling the same
US20110220045A1 (en) * 2008-11-20 2011-09-15 Komatsu Ltd. Variable valve device and control method thereof
US20120234271A1 (en) * 2011-03-14 2012-09-20 Schaeffler Technologies AG & Co. KG Pressure storage unit for a camshaft and piston for a pressure storage unit
US8910600B2 (en) * 2011-03-14 2014-12-16 Schaeffler Technologies Gmbh & Co. Kg Pressure storage unit for a camshaft and piston for a pressure storage unit
US20140060477A1 (en) * 2012-08-31 2014-03-06 Yamada Manufacturing Co., Ltd Engine lubrication control system
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US9109479B2 (en) 2012-08-31 2015-08-18 Yamada Manufacturing Co., Ltd. Engine lubrication control system
DE102016112447A1 (de) * 2016-07-07 2018-01-11 Man Diesel & Turbo Se Ventiltrieb für eine Brennkraftmaschine und Brennkraftmaschine
CN113818943A (zh) * 2021-11-25 2021-12-21 江苏卓联精密机械有限公司 专用固定式双活塞液压发动机气门驱动装置
US11970959B2 (en) 2021-11-25 2024-04-30 Jiangsu Jointek Precision Machinery Co., Ltd. Valve actuators for specialized stationary two-piston hydraulic engines
US11976578B2 (en) 2021-11-25 2024-05-07 Jiangsu Jointek Precision Machinery Co., Ltd. Driving devices for a composite engine valve of a dedicated driving cam

Also Published As

Publication number Publication date
WO2008001699A1 (fr) 2008-01-03
EP2039892A4 (fr) 2009-11-04
EP2039892B1 (fr) 2012-03-21
CN101473111B (zh) 2011-08-31
EP2039892A1 (fr) 2009-03-25
JPWO2008001699A1 (ja) 2009-11-26
CN101473111A (zh) 2009-07-01
KR20090027649A (ko) 2009-03-17
KR101083613B1 (ko) 2011-11-16

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