US20100242878A1 - Variable valve apparatus for internal combustion engine - Google Patents
Variable valve apparatus for internal combustion engine Download PDFInfo
- Publication number
- US20100242878A1 US20100242878A1 US12/814,139 US81413910A US2010242878A1 US 20100242878 A1 US20100242878 A1 US 20100242878A1 US 81413910 A US81413910 A US 81413910A US 2010242878 A1 US2010242878 A1 US 2010242878A1
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- United States
- Prior art keywords
- rocker arm
- internal combustion
- combustion engine
- valve
- continuous variable
- 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
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
-
- 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
-
- 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
-
- 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
-
- 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
- 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
- F01L13/065—Compression release engine retarders of the "Jacobs Manufacturing" type
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- 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
- F02D13/0203—Variable control of intake and exhaust valves
- F02D13/0207—Variable control of intake and exhaust valves changing valve lift or valve lift and timing
-
- 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
- F01L2001/186—Split rocking arms, e.g. rocker arms having two articulated parts and means for varying the relative position of these parts or for selectively connecting the parts to move in unison
-
- 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
- F01L2800/00—Methods of operation using a variable valve timing mechanism
- F01L2800/10—Providing exhaust gas recirculation [EGR]
-
- 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
- F02D13/0273—Multiple actuations of a valve within an engine cycle
-
- 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
- F02D13/04—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation using engine as brake
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/01—Internal exhaust gas recirculation, i.e. wherein the residual exhaust gases are trapped in the cylinder or pushed back from the intake or the exhaust manifold into the combustion chamber without the use of additional passages
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- 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 apparatus for an internal combustion engine which makes it possible to change drive phases and valve lifts of an air intake valve, an exhaust valve, and the like.
- variable valve apparatus which changes drive phases and lifts of intake/exhaust valves depending on driving states of the internal combustion engine to purify an exhaust gas discharged from the engine or to reduce a fuel consumption of the automobile.
- variable valve apparatus a variable valve apparatus having a continuous variable rocker arm mechanism in which a third arm is arranged between a first arm which drives a valve and a second arm caused to oscillate by a cam, the valve is driven through the third arm, and a fulcrum of oscillation of the second arm is displaced to continuously change the phase and lift of the valve (for example, see Jpn. Pat. Appln. KOKAI Publication No. 2004-339079).
- variable valve apparatus having the continuous variable rocker arm mechanism adjusts the lift and phase of a valve to purify an exhaust gas and adjusts an opening valve angle to make it possible to improve a fuel consumption.
- variable valve apparatus having a switching rocker arm mechanism
- a mechanism which selectively transmits displacement is arranged between the first arm which drives the valve and the second arm caused to oscillate by the cam to operate or stop the first arm (for example, see Jpn. Pat. Appin. KOKAI Publication No. 2005-105953).
- variable valve apparatus having the switching rocker arm mechanism performs internal EGR by opening an exhaust valve in an intake stroke to make it possible to purify an exhaust gas and opens the exhaust valve at a compression top dead center to make it possible to apply the engine braking.
- variable valve apparatus as described above must select any one of a switching rocker arm mechanism 40 and a continuous variable rocker arm mechanism 50 , and can exert only one of the functions of the mechanisms. Furthermore, although the switching rocker arm mechanism 40 can be instantaneously operated, the switching rocker arm mechanism 40 cannot be finely adjusted in lift and phase of the valve. On the other hand, although the continuous variable rocker arm mechanism 50 can be finely adjusted in lift and phase, the continuous variable rocker arm mechanism 50 requires about one second for an operation and has poor responsiveness.
- variable valve apparatus for an internal combustion engine which can execute internal EGR and apply engine braking and can simultaneously exert a plurality of functions such as improvement in fuel consumption and purification of an exhaust gas.
- variable valve apparatus for an internal combustion engine of the present invention has the following configuration.
- a variable valve apparatus for an internal combustion engine comprises a cam shaft arranged to be rotatable on a cylinder head of the internal combustion engine; a rocker shaft arranged to be capable of oscillation in the internal combustion engine; a continuous variable rocker arm mechanism which is driven by a cam formed on the cam shaft, opens or closes at least one of an air intake valve and an exhaust valve, and continuously makes a lift of the valve variable; and a switching rocker arm mechanism which is driven by the cam formed on the cam shaft, opens or closes at least one of the air intake valve and the exhaust valve, and switches the lift of the valve in a stepwise manner.
- FIG. 1 is a plan view showing a main part of a cylinder block in which a variable valve apparatus according to the present invention is incorporated.
- FIG. 2 is a sectional view showing the cylinder head block cut along line A-A in FIG. 1 when viewed in a direction given by an arrow.
- FIG. 3 is a sectional view showing the cylinder head block cut along line B-B in FIG. 1 when viewed in a direction given by an arrow.
- FIG. 4 is a perspective view showing the variable valve apparatus.
- FIG. 5 is an exploded perspective view showing the variable valve apparatus.
- FIG. 6 is an explanatory diagram showing a control concept in execution of internal EGR.
- FIG. 7 is an explanatory diagram showing a control concept in execution of internal EGR.
- FIG. 8 is a sectional view showing an operation of a switching rocker arm mechanism in a normal operation.
- FIG. 9 is a sectional view showing an operation of a continuous variable rocker arm mechanism in a normal operation.
- FIG. 10 is a sectional view showing an operation of the switching rocker arm mechanism in execution of internal EGR.
- FIG. 11 is a sectional view showing an operation of the continuous variable rocker arm mechanism in execution of internal EGR.
- FIG. 12 is an explanatory diagram showing a control concept in application of engine braking.
- FIG. 13 is an explanatory diagram showing a control concept in application of engine braking.
- FIG. 14 is a sectional view showing an operation of the switching rocker arm mechanism in application of engine braking.
- FIG. 15 is a sectional view showing an operation of the continuous variable rocker arm mechanism in application of engine braking.
- FIG. 1 is a plan view showing a main part of a cylinder head 10 in which a variable valve apparatus 20 for an internal combustion engine according to a first embodiment of the invention is incorporated
- FIG. 2 is a sectional view showing the cylinder head 10 cut along line A-A in FIG. 1 when viewed in a direction given by an arrow
- FIG. 3 is a sectional view showing the cylinder head 10 cut along line B-B in FIG. 1 when viewed in a direction given by an arrow
- FIG. 4 is a perspective view showing the variable valve apparatus 20
- FIG. 5 is an exploded perspective view showing the variable valve apparatus 20 .
- one pair of air intake valves 12 and 13 and one pair of exhaust valves 14 and 15 are arranged on the cylinder head 10 .
- the air intake valves 12 and 13 are arranged in an intake path 10 a of the cylinder head 10 such that the air intake valves 12 and 13 can be reciprocated in an axial direction, and the air intake valves 12 and 13 are always biased in such a direction that the intake path 10 a is closed by valve springs 12 a and 13 a .
- the exhaust valves 14 and 15 are arranged in an exhaust path 10 b of the cylinder head 10 such that the exhaust valves 14 and 15 can be reciprocated in the axial direction, and the exhaust valves 14 and 15 are always biased in such a direction the intake path 10 a is closed by valve springs 14 a and 15 a .
- the cylinder 11 is attached to a cylinder block (not shown) located below the cylinder head 10 .
- the variable valve apparatus 20 is a valve operation apparatus which opens/closes valves of an internal combustion engine.
- One pair of variable valve apparatuses 20 is arranged to sandwich the cylinder 11 . Since the one pair of variable valve apparatuses 20 has a structure symmetrical with reference to the cylinder 11 , only the variable valve apparatus 20 on the exhaust valves 14 and 15 side will be explained, and an explanation of the variable valve apparatus 20 on the air intake valves 12 and 13 side is not explained.
- the cylinder head 10 comprises one pair of cam shafts 21 arranged to be rotatable, one pair of rocker shafts 30 arranged to be capable of oscillation, one pair of switching rocker arm mechanisms 40 which are driven by a cam 22 formed on the cam shaft 21 and open and close the air intake valves 12 and 13 and the exhaust valves 14 and 15 and switch lifts of the air intake valves 12 and 13 and the exhaust valves 14 and 15 in a stepwise manner, and one pair of continuous variable rocker arm mechanisms 50 which are driven by a cam 23 formed on the cam shaft 21 and open and close the air intake valves 12 and 13 and the exhaust valves 14 and 15 and continuously make the lifts variable.
- the switching rocker arm mechanisms 40 and the continuous variable rocker arm mechanisms 50 share a rocker arm 60 .
- the cam shafts 21 and the rocker shafts 30 are connected to a crank shaft (not shown) of an internal combustion engine through a cam chain, gears, and the like.
- a crank shaft not shown
- the cams 22 and 23 having different cam profiles are rotationally driven in a direction indicated by an arrow R.
- the cams 22 and 23 drive the variable valve apparatus 20 at a predetermined timing described later.
- An oil path 31 to which engine oil is supplied is arranged inside the rocker shaft 30 .
- An oil pressure supply mechanism 80 which supplies the engine oil to the oil path 31 is connected to the oil path 31 .
- the rocker shaft 30 comprises a drive mechanism 90 which controls a rotational angle position about a shaft center line of the rocker shaft 30 . Furthermore, a notch 32 is formed in the rocker shaft 30 at a position corresponding to the continuous variable rocker arm mechanism 50 .
- the switching rocker arm mechanism 40 comprises the shared rocker arm 60 supported by the rocker shafts 30 to be capable of oscillation and formed to make it possible to drive the exhaust valves 14 and 15 , and a switching rocker arm 41 driven by the cam 22 and arranged to be capable of oscillation on the rocker shaft 30 .
- a boss portion 41 a supported by the rocker shaft 30 to be capable of oscillation is formed; a strike arm 41 b which projects upwardly from the boss portion 41 a , enters a window portion 71 b of a vertical piston structure 70 serving as a transmission mechanism described later, and retreats from the window portion 71 b is formed; and a roller 41 c capable of oscillation is formed.
- the roller 41 c is brought into contact with the cam 22 to rotate the cam 22 , the switching rocker arm 41 is caused to oscillate by using a shaft center line of the rocker shaft 30 as a fulcrum.
- a trench 41 d is formed in the switching rocker arm 41 .
- Reference number 42 in FIG. 5 denotes a torsion coil spring.
- a bent portion 42 a is formed on one end side of the spring, and a moving portion 42 b extending in an axial direction of the rocker shafts 30 and bent to the outside in the radial direction is formed on the other end side of the spring.
- the bent portion 42 a is inserted into the cylinder head 10 .
- the shared rocker arm 60 comprises a boss portion 61 fitted in the rocker shaft 30 portion to be capable of oscillation, arms 62 and 63 extending from the boss portion 61 to the exhaust valves 14 and 15 , and a pressed portion 64 pressed by a pressing portion 53 b described later.
- a flow path 61 a which guides the engine oil from the oil path 31 is formed.
- the vertical piston structure 70 comprises a storage tube 71 having a hollow portion 71 a continuing to an internal surface of the boss portion 61 and the window portion 71 b on the side surface, a lid member 72 which blocks an upper-end opening of the hollow portion 71 a of the storage tube 71 , a piston 73 reciprocatingly stored in the hollow portion 71 a , and a spring 74 arranged on the lid member 72 to bias the piston 73 on the boss portion 61 side.
- a notch 73 a is formed in the piston 73 .
- the notch 73 a is generally set such that the notch 73 a is located at a position of the window portion 71 b by the operation of the spring 74 .
- oil pressure is applied by the oil pressure supply mechanism 80 , engine oil is supplied from the oil path 31 to the hollow portion 71 a to compress the spring 74 and push up the piston 73 .
- a circumference of the piston 73 is exposed to the window portion 71 b .
- the piston 73 is pushed down by the operation of the spring 74 .
- An on/off operation of the oil pressure can be instantaneously performed.
- the strike arm 41 b is arranged to face the window portion 71 b .
- the strike arm 41 b is formed to have a shape such that the strike arm 41 b idly moves in the notch 73 a when the notch 73 a is positioned at the window portion 71 b and moves while being struck on the circumference portion of the piston 73 when the circumference portion is positioned at the window portion 71 b.
- An oil discharge chamber 32 having a width larger than that of the flow path 61 a is formed in the rocker shaft 30 on the downstream side of the oil path 31 , so that the engine oil can be supplied to the hollow portion 71 a even when the position of the flow path 61 a is changed by oscillation of the rocker shaft 30 itself or oscillation of the switching rocker arm 41 with rotation of the cam 22 .
- the width of the oil discharge chamber 32 is preferably larger than a distance of oscillation of the switching rocker arm 41 and preferably set to a width at which the engine oil can be supplied to the flow path 61 a even when the rocker shaft 30 reaches the position of maximum oscillation.
- an oil supply chamber 75 having a width larger than that of the flow path 61 a is formed in the vertical piston structure 70 on an upstream side of the hollow portion 71 a . Even when the switching rocker arm 41 is caused to oscillate with rotation of the cam 22 to change the position of the flow path 61 a , the engine oil can be supplied to the hollow portion 71 a .
- the width of the oil supply chamber 75 is preferably larger than a distance of oscillation of the switching rocker arm 41 .
- the continuous variable rocker arm mechanism 50 will be explained with reference to FIGS. 3 and 5 .
- the continuous variable rocker arm mechanism 50 comprises the shared rocker arm 60 supported by the rocker shaft 30 to be capable of oscillation and formed to make it possible to drive the exhaust valves 14 and 15 , a continuous variable arm 53 driven by the cam 23 and arranged to be capable of oscillation about a fulcrum Q set on the rocker shaft 30 side, and an intermediate arm 51 which is arranged between the shared rocker arm 60 and the continuous variable arm 53 and transmits oscillation displacement of the continuous variable arm 53 to the shared rocker arm 60 to drive the shared rocker arm 60 .
- the intermediate arm 51 comprises an annular shaft fitting portion 51 a and a pressing portion 51 b projecting from the shaft fitting portion 51 a in a radial direction.
- a roller 51 c is arranged on the pressing portion 51 b .
- the continuous variable arm 53 comprises a connection member 54 which connects the continuous variable arm 53 and the rocker shaft 30 .
- the connection member 54 is a stud bolt, has a spherical universal coupling 54 a on one end side thereof, is screwed into a screw hole 33 formed in the notch 32 of the rocker shaft 30 , and is fixed by a lock nut 54 b .
- the universal coupling 54 a functions as the fulcrum Q.
- Reference number 55 in FIG. 5 denotes a torsion coil spring.
- the torsion coil spring 55 has a bent portion 55 a formed on one end side thereof, and a moving portion 55 b formed on the other end side thereof, extending in an axial direction of the rocker shaft 30 and bent to the outside in the radial direction.
- the bent portion 55 a is inserted into the cylinder head 10 .
- the continuous variable arm 53 is formed to have an almost laterally-facing U shape in a side view.
- a laterally-facing U-shaped base end 53 a is formed on a lower side in FIG. 5
- a contact portion 53 b is formed on an upper side in FIG. 5 .
- the base end 53 a has a recessed portion 53 c formed on an upper surface thereof.
- the recessed portion 53 c is formed to have an almost semi-spherical shape corresponding to the spherical shape of the universal coupling 54 a and incorporated to be capable of oscillation by using the universal coupling 54 a as a fulcrum.
- a roller 53 d is arranged to be capable of oscillation at an intermediate position between the base end 53 a and the contact portion 53 b .
- the continuous variable arm 53 is caused to oscillate by using the center of the universal coupling 54 a as a fulcrum.
- Reference number 56 in FIG. 5 denotes a transformation member.
- the transformation member 56 is formed to have a triangular tabular shape which is long on one end side, and a slide surface portion 56 a is formed on an upper-side surface in FIG. 5 , and a transmission surface portion 56 b is arranged on a lower-side surface in FIG. 5 .
- the slide surface portion 56 a is formed to have a curvature equal to that of a pad 57 (see FIG. 9 ) fixed to the cylinder head 10 and slidably moves along an arc-like lower surface of the pad 57 .
- the transmission surface portion 56 b is formed such that a distance between the transmission surface portion 56 b and the slide surface portion 56 a has a predetermined value along the slide surface portion 56 a . More specifically, the transmission surface portion 56 b is formed such that, when the transformation member 56 is slidably moved along an arc-like lower surface of the pad 57 , a member being in contact with the transmission surface portion 56 b at a predetermined position makes a predetermined motion in a direction perpendicular to the pad 57 with the movement of the transformation member 56 .
- a trench 56 c is formed in the transmission surface portion 56 b , and the moving portion 55 b of the torsion coil spring 55 is engaged in the trench 56 c .
- the torsion coil spring 55 biases the transformation member 56 such that the transformation member 56 moves to the continuous variable arm 53 side.
- a semi-cylindrical joint 57 is arranged between the transformation member 56 and the contact portion 53 b of the continuous variable arm 53 .
- the joint 57 is attached to the contact portion 53 b of the continuous variable arm 53 and slidably fitted on the transformation member 56 .
- the joint 57 is designed to absorb a change in a contact angle between the transformation member 56 and the contact portion 53 b and to transmit a pressing operation of the continuous variable arm 53 to the transformation member 56 .
- the base end 53 a is pulled to the left by the universal coupling 54 a , and the continuous variable arm 53 moves to the left as a whole.
- the transformation member 56 is biased by the torsion coil spring 55 on the continuous variable arm 53 side. For this reason, the transformation member 56 is brought into tight contact with the pad 57 , and the roller 53 d is brought into contact with the cam 23 .
- the cam shafts 21 rotate counterclockwise, an angle between a start point of a cam nose and a contact point between the roller 53 d and the cam 23 is set to be widest, and the continuous variable arm 53 is driven by the cam 23 later than that in the neutral state. As a result, the valve opening timing or the valve closing timing are retarded.
- the universal coupling 54 a of the connection member 54 is caused to oscillate in such a direction that the universal coupling 54 a goes away from the exhaust valves 14 and 15 side with reference to the neutral position.
- the base end 53 a is pulled to the right by the universal coupling 54 a , and the continuous variable arm 53 moves to the right as a whole.
- the transformation member 56 is biased by the torsion coil spring 55 on the continuous variable arm 53 side. For this reason, the transformation member 56 is brought into tight contact with the pad 57 , and the roller 53 d is brought into contact with the cam 23 .
- the retarding and advancing adjustments are continuously performed by continuously adjusting an angle position of the rocker shaft 30 .
- variable valve apparatus 20 can change a valve opening timing and a valve closing timing by making the drive mechanism 90 cause the rocker shaft 30 to oscillate. For this reason, the valve opening timing and the valve closing timing are changed to make it possible to increase an intake air flow and to achieve a reduction in fuel consumption.
- variable valve apparatus 20 having the switching rocker arm mechanism 40 and the continuous variable rocker arm mechanism 50 , the following control can be performed.
- FIG. 6 is a graph showing a relationship between the phase and lift of the cam shaft 21 .
- Reference symbol EX denotes opening valves (lifts) of the exhaust valves 14 and 15
- reference symbol IH denotes opening valves (lifts) of the air intake valves 12 and 13 .
- the cam shaft 21 causes an exhaust stroke which opens the exhaust valves 14 and 15 to slightly overlap an intake stroke performed by opening the air intake valves 12 and 13 .
- An operation of the switching rocker arm mechanism 40 at this time is shown in FIG. 8
- an operation of the continuous variable rocker arm mechanism 50 at this time is shown in FIG. 9 .
- an operation mode of the switching rocker arm mechanism 40 is set to be off
- an operation mode of the continuous variable rocker arm mechanism 50 is set to a normal (neutral) mode.
- the rocker shaft 30 is set at a neutral position by means of the drive mechanism 90 . Therefore, the roller 53 d moves along the cam 23 by rotation of the cam 23 rotated by the cam shaft 21 , and the continuous variable arm 53 oscillates about the rocker shaft 30 at predetermined intervals in a direction indicated by an arrow F in FIG. 9 . In this manner, motion of the continuous variable arm 53 is transmitted to the shared rocker arm 60 through the transformation member 56 and the intermediate arm 51 , and the air intake valves 12 and 13 and the exhaust valves 14 and 15 are driven along a profile of the cam 23 .
- the air intake valves 12 and 13 and the exhaust valves 14 and 15 are driven according to phases and lifts which change along a solid line S.
- the operation mode of the switching rocker arm mechanism 40 is set to be off, and the operation mode of the continuous variable rocker arm mechanism 50 is set to an early closing (advance) mode.
- the operation mode of the switching rocker arm mechanism 40 is set to be on, and the operation mode of the continuous variable rocker arm mechanism 50 is set to a normal (neutral) mode.
- a nose 22 a of the cam 22 corresponds to reference symbol P in FIG. 6 .
- the rocker shaft 30 is rotated counterclockwise by a predetermined angle by means of the drive mechanism 90 and set at an advance angle position.
- a fulcrum of oscillation of the continuous variable arm 53 is distanced from the air intake valves 12 and 13 .
- the roller 53 d moves along the cam 23 , and the continuous variable arm 53 oscillates about the rocker shaft 30 at predetermined intervals in a direction indicated by an arrow F in FIG. 11 .
- motion of the continuous variable arm 53 is transmitted to the shared rocker arm 60 through the transformation member 56 and the intermediate arm 51 , and the air intake valves 12 and 13 are driven while being advanced with respect to the profile of the cam 23 .
- the air intake valves 12 and 13 are driven by the continuous variable rocker arm mechanism 50 , and the exhaust valves 14 and 15 are driven by the switching rocker arm mechanism 40 . Therefore, the air intake valves 12 and 13 open according to phases and lifts indicated by reference symbol S in FIG. 6 , and the exhaust valves 14 and 15 open according to phases and lifts indicated by reference symbol P in FIG. 6 . More specifically, the exhaust valves 14 and 15 open at timings indicated by reference symbol P in FIG. 6 . That is, since the exhaust valves 14 and 15 open in the intake stroke, an exhaust gas temporarily exhausted from the cylinder 11 is taken into the cylinder 11 to cause an internal EGR operation.
- FIG. 7 shows a relationship between closing end phases and amounts of air of the air intake valves 12 and 13 and a relationship between the closing end phases and the amounts of internal EGR of the air intake valves 12 and 13 .
- the switching rocker arm mechanism 40 and the continuous variable rocker arm mechanism 50 are operated in conjunction with each other to make it possible to obtain a more appropriate amount of EGR and to purify an exhaust gas.
- FIG. 12 is a graph showing a relationship between the phase and lift of the cam shaft 21 .
- Reference symbol EX denotes opening valves (lifts) of the exhaust valves 14 and 15
- reference symbol IH denotes opening valves (lifts) of the air intake valves 12 and 13 .
- the cam shaft 21 causes an exhaust stroke which opens the exhaust valves 14 and 15 to slightly overlap an intake stroke performed by opening the air intake valves 12 and 13 .
- An operation of the switching rocker arm mechanism 40 at this time is shown in FIG. 8
- an operation of the continuous variable rocker arm mechanism 50 at this time is shown in FIG. 9 .
- an operation mode of the switching rocker arm mechanism 40 is set to be off
- an operation mode of the continuous variable rocker arm mechanism 50 is set to a normal (neutral) mode.
- the operation mode of the switching rocker arm mechanism 40 is set to be off, and the operation mode of the continuous variable rocker arm mechanism 50 is set to a normal (neutral) mode.
- the operation mode of the switching rocker arm mechanism 40 is set to be on, and the operation mode of the continuous variable rocker arm mechanism 50 is set to an early opening (advance) mode.
- the rocker shaft 30 is rotated counterclockwise by a predetermined angle by means of the drive mechanism 90 and set at an advance angle position.
- a fulcrum of oscillation of the continuous variable arm 53 is distanced from the air intake valves 12 and 13 .
- the roller 53 d moves along the cam 23 , and the continuous variable arm 53 oscillates about the rocker shaft 30 at predetermined intervals in a direction indicated by an arrow F in FIG. 15 .
- motion of the continuous variable arm 51 is transmitted to the shared rocker arm 60 through the transformation member 56 and the intermediate arm 51 , and the air intake valves 12 and 13 are driven while being advanced with respect to the profile of the cam 23 .
- the air intake valves 12 and 13 are driven by the continuous variable rocker arm mechanism 50
- the exhaust valves 14 and 15 are driven by both the switching rocker arm mechanism 40 and the continuous variable rocker arm mechanism 50 . Therefore, the air intake valves 12 and 13 open according to phases and lifts indicated by reference symbol N in FIG. 12
- the exhaust valves 14 and 15 open according to phases and lifts indicated by reference symbols M and L in FIG. 12 . More specifically, the switching rocker arm mechanism 40 opens the exhaust valves 14 and 15 at timings indicated by reference symbol L in FIG. 12 . That is, the exhaust valves 14 and 15 open at a compression top dead center (TDC) to operate a compression brake. Since the lifts of the exhaust valves 14 and 15 are constant, the braking effect is constant.
- TDC compression top dead center
- FIG. 13 shows a relationship between opening start phases of the exhaust valves 14 and 15 and the exhaust energy (amount of air) and a relationship between the opening start phases of the exhaust valves 14 and 15 and the engine braking force.
- variable valve apparatus 20 for an internal combustion engine As described above, according to the variable valve apparatus 20 for an internal combustion engine according to the embodiment, a plurality of functions such as execution of internal EGR, application of engine braking, improvement in fuel consumption, and purification of an exhaust gas can be simultaneously exerted.
- valves are opened or closed by using both the switching rocker arm mechanism and the continuous variable rocker arm mechanism to make it possible to realize a plurality of functions such as instantaneous switching of opening/closing timings of the valves and fine control of lifts.
- transmission of oscillation displacement is selectively performed as needed to make it possible to open or close a valve without delay.
- the transmission of oscillation displacement is continuously performed to make it possible to finely control the drive phase and lift of the valve.
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Abstract
In order to simultaneously exert a plurality of functions such as execution of internal EGR, application of engine braking, improvement in fuel consumption and purification of exhaust gas, a variable valve apparatus for an internal combustion engine of the invention includes a cam shaft arranged to be rotatable on a cylinder head of the internal combustion engine, a rocker shaft arranged to be capable of oscillation in the internal combustion engine, a continuous variable rocker arm mechanism which is driven by a cam formed on the cam shaft, opens or closes air intake valves and exhaust valves, and continuously makes a lift of the valves variable, and a switching rocker arm mechanism which is driven by the cam formed on the cam shaft, opens or closes the air intake valves and the exhaust valves, and switches the lift of the valves in a stepwise manner.
Description
- This is a Continuation application of PCT Application No. PCT/JP2008/073635, filed Dec. 25, 2008, which was published under PCT Article 21(2) in Japanese.
- This application is based upon and claims the benefit of priority from prior Japanese Patent Applications No. 2007-338360, filed Dec. 27, 2007; and No. 2008-004745, filed Jan. 11, 2008, the entire contents of both of which are incorporated herein by reference.
- 1. Field of the Invention
- The present invention relates to a variable valve apparatus for an internal combustion engine which makes it possible to change drive phases and valve lifts of an air intake valve, an exhaust valve, and the like. 2. Description of the Related Art
- In an internal combustion engine such as an automobile engine, a variable valve apparatus is known which changes drive phases and lifts of intake/exhaust valves depending on driving states of the internal combustion engine to purify an exhaust gas discharged from the engine or to reduce a fuel consumption of the automobile.
- As the variable valve apparatus, a variable valve apparatus having a continuous variable rocker arm mechanism is known in which a third arm is arranged between a first arm which drives a valve and a second arm caused to oscillate by a cam, the valve is driven through the third arm, and a fulcrum of oscillation of the second arm is displaced to continuously change the phase and lift of the valve (for example, see Jpn. Pat. Appln. KOKAI Publication No. 2004-339079).
- The variable valve apparatus having the continuous variable rocker arm mechanism adjusts the lift and phase of a valve to purify an exhaust gas and adjusts an opening valve angle to make it possible to improve a fuel consumption.
- On the other hand, a variable valve apparatus having a switching rocker arm mechanism is known in which a mechanism which selectively transmits displacement is arranged between the first arm which drives the valve and the second arm caused to oscillate by the cam to operate or stop the first arm (for example, see Jpn. Pat. Appin. KOKAI Publication No. 2005-105953).
- The variable valve apparatus having the switching rocker arm mechanism performs internal EGR by opening an exhaust valve in an intake stroke to make it possible to purify an exhaust gas and opens the exhaust valve at a compression top dead center to make it possible to apply the engine braking.
- However, the variable valve apparatus as described above must select any one of a switching
rocker arm mechanism 40 and a continuous variablerocker arm mechanism 50, and can exert only one of the functions of the mechanisms. Furthermore, although the switchingrocker arm mechanism 40 can be instantaneously operated, the switchingrocker arm mechanism 40 cannot be finely adjusted in lift and phase of the valve. On the other hand, although the continuous variablerocker arm mechanism 50 can be finely adjusted in lift and phase, the continuous variablerocker arm mechanism 50 requires about one second for an operation and has poor responsiveness. - Therefore, it is an object of the present invention to provide a variable valve apparatus for an internal combustion engine which can execute internal EGR and apply engine braking and can simultaneously exert a plurality of functions such as improvement in fuel consumption and purification of an exhaust gas.
- In order to solve the problem and achieve the object, the variable valve apparatus for an internal combustion engine of the present invention has the following configuration.
- A variable valve apparatus for an internal combustion engine, comprises a cam shaft arranged to be rotatable on a cylinder head of the internal combustion engine; a rocker shaft arranged to be capable of oscillation in the internal combustion engine; a continuous variable rocker arm mechanism which is driven by a cam formed on the cam shaft, opens or closes at least one of an air intake valve and an exhaust valve, and continuously makes a lift of the valve variable; and a switching rocker arm mechanism which is driven by the cam formed on the cam shaft, opens or closes at least one of the air intake valve and the exhaust valve, and switches the lift of the valve in a stepwise manner.
-
FIG. 1 is a plan view showing a main part of a cylinder block in which a variable valve apparatus according to the present invention is incorporated. -
FIG. 2 is a sectional view showing the cylinder head block cut along line A-A inFIG. 1 when viewed in a direction given by an arrow. -
FIG. 3 is a sectional view showing the cylinder head block cut along line B-B inFIG. 1 when viewed in a direction given by an arrow. -
FIG. 4 is a perspective view showing the variable valve apparatus. -
FIG. 5 is an exploded perspective view showing the variable valve apparatus. -
FIG. 6 is an explanatory diagram showing a control concept in execution of internal EGR. -
FIG. 7 is an explanatory diagram showing a control concept in execution of internal EGR. -
FIG. 8 is a sectional view showing an operation of a switching rocker arm mechanism in a normal operation. -
FIG. 9 is a sectional view showing an operation of a continuous variable rocker arm mechanism in a normal operation. -
FIG. 10 is a sectional view showing an operation of the switching rocker arm mechanism in execution of internal EGR. -
FIG. 11 is a sectional view showing an operation of the continuous variable rocker arm mechanism in execution of internal EGR. -
FIG. 12 is an explanatory diagram showing a control concept in application of engine braking. -
FIG. 13 is an explanatory diagram showing a control concept in application of engine braking. -
FIG. 14 is a sectional view showing an operation of the switching rocker arm mechanism in application of engine braking. -
FIG. 15 is a sectional view showing an operation of the continuous variable rocker arm mechanism in application of engine braking. -
FIG. 1 is a plan view showing a main part of acylinder head 10 in which avariable valve apparatus 20 for an internal combustion engine according to a first embodiment of the invention is incorporated,FIG. 2 is a sectional view showing thecylinder head 10 cut along line A-A inFIG. 1 when viewed in a direction given by an arrow,FIG. 3 is a sectional view showing thecylinder head 10 cut along line B-B inFIG. 1 when viewed in a direction given by an arrow,FIG. 4 is a perspective view showing thevariable valve apparatus 20, andFIG. 5 is an exploded perspective view showing thevariable valve apparatus 20. - As shown in
FIGS. 1 to 3 , one pair ofair intake valves exhaust valves cylinder head 10. Theair intake valves cylinder head 10 such that theair intake valves air intake valves valve springs exhaust valves cylinder head 10 such that theexhaust valves exhaust valves valve springs cylinder 11 is attached to a cylinder block (not shown) located below thecylinder head 10. - The
variable valve apparatus 20 is a valve operation apparatus which opens/closes valves of an internal combustion engine. One pair ofvariable valve apparatuses 20 is arranged to sandwich thecylinder 11. Since the one pair ofvariable valve apparatuses 20 has a structure symmetrical with reference to thecylinder 11, only thevariable valve apparatus 20 on theexhaust valves variable valve apparatus 20 on theair intake valves - The
cylinder head 10 comprises one pair ofcam shafts 21 arranged to be rotatable, one pair ofrocker shafts 30 arranged to be capable of oscillation, one pair of switchingrocker arm mechanisms 40 which are driven by acam 22 formed on thecam shaft 21 and open and close theair intake valves exhaust valves air intake valves exhaust valves rocker arm mechanisms 50 which are driven by acam 23 formed on thecam shaft 21 and open and close theair intake valves exhaust valves rocker arm mechanisms 40 and the continuous variablerocker arm mechanisms 50 share arocker arm 60. - The
cam shafts 21 and therocker shafts 30 are connected to a crank shaft (not shown) of an internal combustion engine through a cam chain, gears, and the like. When the crank shaft is rotated, thecams cams variable valve apparatus 20 at a predetermined timing described later. - An
oil path 31 to which engine oil is supplied is arranged inside therocker shaft 30. An oil pressure supply mechanism 80 which supplies the engine oil to theoil path 31 is connected to theoil path 31. Therocker shaft 30 comprises a drive mechanism 90 which controls a rotational angle position about a shaft center line of therocker shaft 30. Furthermore, anotch 32 is formed in therocker shaft 30 at a position corresponding to the continuous variablerocker arm mechanism 50. - With reference to
FIGS. 2 and 5 , the switchingrocker arm mechanism 40 will be explained. The switchingrocker arm mechanism 40 comprises the sharedrocker arm 60 supported by therocker shafts 30 to be capable of oscillation and formed to make it possible to drive theexhaust valves rocker arm 41 driven by thecam 22 and arranged to be capable of oscillation on therocker shaft 30. - In the switching
rocker arm 41, aboss portion 41 a supported by therocker shaft 30 to be capable of oscillation is formed; astrike arm 41 b which projects upwardly from theboss portion 41 a, enters awindow portion 71 b of avertical piston structure 70 serving as a transmission mechanism described later, and retreats from thewindow portion 71 b is formed; and aroller 41 c capable of oscillation is formed. When theroller 41 c is brought into contact with thecam 22 to rotate thecam 22, the switchingrocker arm 41 is caused to oscillate by using a shaft center line of therocker shaft 30 as a fulcrum. Atrench 41 d is formed in the switchingrocker arm 41. -
Reference number 42 inFIG. 5 denotes a torsion coil spring. Abent portion 42 a is formed on one end side of the spring, and a movingportion 42 b extending in an axial direction of therocker shafts 30 and bent to the outside in the radial direction is formed on the other end side of the spring. Thebent portion 42 a is inserted into thecylinder head 10. When the movingportion 42 b of thetorsion coil spring 42 is engaged in thetrench 41 d, thetorsion coil spring 42 biases the switchingrocker arm 41 such that theroller 41 c moves along the lines of thecam 22. - The shared
rocker arm 60 comprises aboss portion 61 fitted in therocker shaft 30 portion to be capable of oscillation,arms boss portion 61 to theexhaust valves portion 64 pressed by apressing portion 53 b described later. In theboss portion 61, aflow path 61 a which guides the engine oil from theoil path 31 is formed. - In the
boss portion 61, as a transmission mechanism to selectively transmit displacement from the switchingrocker arm 41 to the sharedrocker arm 60, the cylindricalvertical piston structure 70 is arranged. Thevertical piston structure 70 comprises astorage tube 71 having ahollow portion 71 a continuing to an internal surface of theboss portion 61 and thewindow portion 71 b on the side surface, alid member 72 which blocks an upper-end opening of thehollow portion 71 a of thestorage tube 71, apiston 73 reciprocatingly stored in thehollow portion 71 a, and aspring 74 arranged on thelid member 72 to bias thepiston 73 on theboss portion 61 side. Anotch 73 a is formed in thepiston 73. Thenotch 73 a is generally set such that thenotch 73 a is located at a position of thewindow portion 71 b by the operation of thespring 74. When oil pressure is applied by the oil pressure supply mechanism 80, engine oil is supplied from theoil path 31 to thehollow portion 71 a to compress thespring 74 and push up thepiston 73. In this manner, a circumference of thepiston 73 is exposed to thewindow portion 71 b. In contrast to this, when the oil pressure is released, thepiston 73 is pushed down by the operation of thespring 74. An on/off operation of the oil pressure can be instantaneously performed. - The
strike arm 41 b is arranged to face thewindow portion 71 b. Thestrike arm 41 b is formed to have a shape such that thestrike arm 41 b idly moves in thenotch 73 a when thenotch 73 a is positioned at thewindow portion 71 b and moves while being struck on the circumference portion of thepiston 73 when the circumference portion is positioned at thewindow portion 71 b. - In this manner, in the structure, when the
strike arm 41 b of the switchingrocker arm 41 is not struck on thepiston 73, cam displacement from the switchingrocker arm 41 is not transmitted to the sharedrocker arm 60. When thestrike arm 41 b is struck on thepiston 73, the cam displacement from the switchingrocker arm 41 opens theexhaust valves rocker arm 60. Anoil discharge chamber 32 having a width larger than that of theflow path 61 a is formed in therocker shaft 30 on the downstream side of theoil path 31, so that the engine oil can be supplied to thehollow portion 71 a even when the position of theflow path 61 a is changed by oscillation of therocker shaft 30 itself or oscillation of the switchingrocker arm 41 with rotation of thecam 22. The width of theoil discharge chamber 32 is preferably larger than a distance of oscillation of the switchingrocker arm 41 and preferably set to a width at which the engine oil can be supplied to theflow path 61 a even when therocker shaft 30 reaches the position of maximum oscillation. - Furthermore, an
oil supply chamber 75 having a width larger than that of theflow path 61 a is formed in thevertical piston structure 70 on an upstream side of thehollow portion 71 a. Even when the switchingrocker arm 41 is caused to oscillate with rotation of thecam 22 to change the position of theflow path 61 a, the engine oil can be supplied to thehollow portion 71 a. The width of theoil supply chamber 75 is preferably larger than a distance of oscillation of the switchingrocker arm 41. - The continuous variable
rocker arm mechanism 50 will be explained with reference toFIGS. 3 and 5 . The continuous variablerocker arm mechanism 50 comprises the sharedrocker arm 60 supported by therocker shaft 30 to be capable of oscillation and formed to make it possible to drive theexhaust valves variable arm 53 driven by thecam 23 and arranged to be capable of oscillation about a fulcrum Q set on therocker shaft 30 side, and anintermediate arm 51 which is arranged between the sharedrocker arm 60 and the continuousvariable arm 53 and transmits oscillation displacement of the continuousvariable arm 53 to the sharedrocker arm 60 to drive the sharedrocker arm 60. - The
intermediate arm 51 comprises an annular shaftfitting portion 51 a and apressing portion 51 b projecting from theshaft fitting portion 51 a in a radial direction. Aroller 51 c is arranged on thepressing portion 51 b. When theintermediate arm 51 is caused to oscillate about therocker shaft 30, thepressing portion 53 b presses the pressedportion 64 of the sharedrocker arm 60, and the sharedrocker arm 60 opens theexhaust valves - The continuous
variable arm 53 comprises aconnection member 54 which connects the continuousvariable arm 53 and therocker shaft 30. Theconnection member 54 is a stud bolt, has a sphericaluniversal coupling 54 a on one end side thereof, is screwed into ascrew hole 33 formed in thenotch 32 of therocker shaft 30, and is fixed by alock nut 54 b. When theconnection member 54 is fixed to therocker shaft 30, theuniversal coupling 54 a functions as the fulcrum Q. -
Reference number 55 inFIG. 5 denotes a torsion coil spring. Thetorsion coil spring 55 has abent portion 55 a formed on one end side thereof, and a movingportion 55 b formed on the other end side thereof, extending in an axial direction of therocker shaft 30 and bent to the outside in the radial direction. Thebent portion 55 a is inserted into thecylinder head 10. - The continuous
variable arm 53 is formed to have an almost laterally-facing U shape in a side view. A laterally-facing U-shaped base end 53 a is formed on a lower side inFIG. 5 , and acontact portion 53 b is formed on an upper side inFIG. 5 . Thebase end 53 a has a recessedportion 53 c formed on an upper surface thereof. The recessedportion 53 c is formed to have an almost semi-spherical shape corresponding to the spherical shape of theuniversal coupling 54 a and incorporated to be capable of oscillation by using theuniversal coupling 54 a as a fulcrum. - On the continuous
variable arm 53, aroller 53 d is arranged to be capable of oscillation at an intermediate position between thebase end 53 a and thecontact portion 53 b. When theroller 53 d is brought into contact with thecam 23 and thecam 23 is rotated, the continuousvariable arm 53 is caused to oscillate by using the center of theuniversal coupling 54 a as a fulcrum. -
Reference number 56 inFIG. 5 denotes a transformation member. Thetransformation member 56 is formed to have a triangular tabular shape which is long on one end side, and aslide surface portion 56 a is formed on an upper-side surface inFIG. 5 , and atransmission surface portion 56 b is arranged on a lower-side surface inFIG. 5 . Theslide surface portion 56 a is formed to have a curvature equal to that of a pad 57 (seeFIG. 9 ) fixed to thecylinder head 10 and slidably moves along an arc-like lower surface of thepad 57. - The
transmission surface portion 56 b is formed such that a distance between thetransmission surface portion 56 b and theslide surface portion 56 a has a predetermined value along theslide surface portion 56 a . More specifically, thetransmission surface portion 56 b is formed such that, when thetransformation member 56 is slidably moved along an arc-like lower surface of thepad 57, a member being in contact with thetransmission surface portion 56 b at a predetermined position makes a predetermined motion in a direction perpendicular to thepad 57 with the movement of thetransformation member 56. - A
trench 56 c is formed in thetransmission surface portion 56 b, and the movingportion 55 b of thetorsion coil spring 55 is engaged in thetrench 56 c. When the movingportion 55 b is engaged in thetrench 56 c, thetorsion coil spring 55 biases thetransformation member 56 such that thetransformation member 56 moves to the continuousvariable arm 53 side. - Furthermore, a semi-cylindrical joint 57 is arranged between the
transformation member 56 and thecontact portion 53 b of the continuousvariable arm 53. The joint 57 is attached to thecontact portion 53 b of the continuousvariable arm 53 and slidably fitted on thetransformation member 56. The joint 57 is designed to absorb a change in a contact angle between thetransformation member 56 and thecontact portion 53 b and to transmit a pressing operation of the continuousvariable arm 53 to thetransformation member 56. - An operation of the continuous variable
rocker arm mechanism 50 will be explained with reference toFIG. 9 . When a valve opening timing or a valve closing timing of the exhaust valve is to be retarded, therocker shaft 30 is caused to oscillate by the drive mechanism 90 in such a direction that theuniversal coupling 54 a of theconnection member 54 approaches theexhaust valves - The
base end 53 a is pulled to the left by theuniversal coupling 54 a, and the continuousvariable arm 53 moves to the left as a whole. On the other hand, thetransformation member 56 is biased by thetorsion coil spring 55 on the continuousvariable arm 53 side. For this reason, thetransformation member 56 is brought into tight contact with thepad 57, and theroller 53 d is brought into contact with thecam 23. At this time, since thecam shafts 21 rotate counterclockwise, an angle between a start point of a cam nose and a contact point between theroller 53 d and thecam 23 is set to be widest, and the continuousvariable arm 53 is driven by thecam 23 later than that in the neutral state. As a result, the valve opening timing or the valve closing timing are retarded. - On the other hand, when a valve opening or valve closing timing of an exhaust valve is to be advanced, the
universal coupling 54 a of theconnection member 54 is caused to oscillate in such a direction that theuniversal coupling 54 a goes away from theexhaust valves - The
base end 53 a is pulled to the right by theuniversal coupling 54 a, and the continuousvariable arm 53 moves to the right as a whole. On the other hand, thetransformation member 56 is biased by thetorsion coil spring 55 on the continuousvariable arm 53 side. For this reason, thetransformation member 56 is brought into tight contact with thepad 57, and theroller 53 d is brought into contact with thecam 23. - At this time, since the
cam shafts 21 rotate counterclockwise, an angle between a start point of a cam nose and a contact point between theroller 53 d and thecam 23 is set to be narrowest, and the continuousvariable arm 53 is driven by thecam 23 earlier than that in the neutral state. As a result, the valve opening timing or the valve closing timing are advanced. - The retarding and advancing adjustments are continuously performed by continuously adjusting an angle position of the
rocker shaft 30. - As described above, the
variable valve apparatus 20 can change a valve opening timing and a valve closing timing by making the drive mechanism 90 cause therocker shaft 30 to oscillate. For this reason, the valve opening timing and the valve closing timing are changed to make it possible to increase an intake air flow and to achieve a reduction in fuel consumption. - With this configuration, in the internal combustion engine comprising the
variable valve apparatus 20 having the switchingrocker arm mechanism 40 and the continuous variablerocker arm mechanism 50, the following control can be performed. - First, the operations of the switching
rocker arm mechanism 40 and the continuous variablerocker arm mechanism 50 performed when an amount of internal EGR is optimized will be explained while comparing a “normal operation” and an “internal EGR operation”.FIG. 6 is a graph showing a relationship between the phase and lift of thecam shaft 21. Reference symbol EX denotes opening valves (lifts) of theexhaust valves air intake valves - The
cam shaft 21 causes an exhaust stroke which opens theexhaust valves air intake valves rocker arm mechanism 40 at this time is shown inFIG. 8 , and an operation of the continuous variablerocker arm mechanism 50 at this time is shown inFIG. 9 . In the normal operation, on both theair intake valves exhaust valves rocker arm mechanism 40 is set to be off, and an operation mode of the continuous variablerocker arm mechanism 50 is set to a normal (neutral) mode. - More specifically, when the operation mode of the switching
rocker arm mechanism 40 is set to be off, oil pressure is not applied by the oil pressure supply mechanism 80, and engine oil is not supplied into thehollow portion 71 a in the switchingrocker arm mechanism 40. For this reason, thepiston 73 is biased downward by an elastic force of thespring 74, and thenotch 73 a is located at thewindow portion 71 b. On the other hand, theroller 41 c moves along thecam 22 by the rotation of thecam 22 rotated by thecam shaft 21, and the switchingrocker arm 41 oscillates about therocker shaft 30 at predetermined intervals in a direction indicated by an arrow E inFIG. 8 . However, even when thestrike arm 41 b is inserted into thewindow portion 71 b, thestrike arm 41 b is inserted into only thenotch 73 a but not brought into contact with thepiston 73. Therefore, motion of the switchingrocker arm 41 is not transmitted to the sharedrocker arm 60. Consequently, the switchingrocker arm mechanism 40 does not operate, and theair intake valves exhaust valves - In the continuous variable
rocker arm mechanism 50, therocker shaft 30 is set at a neutral position by means of the drive mechanism 90. Therefore, theroller 53 d moves along thecam 23 by rotation of thecam 23 rotated by thecam shaft 21, and the continuousvariable arm 53 oscillates about therocker shaft 30 at predetermined intervals in a direction indicated by an arrow F inFIG. 9 . In this manner, motion of the continuousvariable arm 53 is transmitted to the sharedrocker arm 60 through thetransformation member 56 and theintermediate arm 51, and theair intake valves exhaust valves cam 23. - As described above, in the normal operation, by the continuous variable
rocker arm mechanism 50, theair intake valves exhaust valves - In an internal EGR operation, on the
air intake valves rocker arm mechanism 40 is set to be off, and the operation mode of the continuous variablerocker arm mechanism 50 is set to an early closing (advance) mode. On theexhaust valves rocker arm mechanism 40 is set to be on, and the operation mode of the continuous variablerocker arm mechanism 50 is set to a normal (neutral) mode. - The operations of the switching
rocker arm mechanism 40 and the continuous variablerocker arm mechanism 50 are summarized as follows. -
TABLE 1 Optimization of amount of internal EGR Switching rocker Continuous variable arm mechanism rocker arm mechanism Air intake valve OFF Early closing Exhaust valve ON Normal - When the operation mode of the switching
rocker arm mechanism 40 on theexhaust valves FIG. 10 , in the switchingrocker arm mechanism 40, engine oil is supplied into thehollow portion 71 a. For this reason, thepiston 73 rises against the elastic force of thespring 74, and the circumference of thepiston 73 is positioned at thewindow portion 71 b. On the other hand, theroller 41 c moves along thecam 22 by rotation of thecam 22 rotated by thecam shaft 21, and the switchingrocker arm 41 oscillates about therocker shaft 30 at predetermined intervals in a direction indicated by an arrow E inFIG. 8 . When thestrike arm 41 b is inserted into thewindow portion 71 b, thestrike arm 41 b is brought into contact with the circumference of thepiston 73. Therefore, motion of the switchingrocker arm 41 is transmitted to the sharedrocker arm 60, and theexhaust valves cam 22. Anose 22 a of thecam 22 corresponds to reference symbol P inFIG. 6 . - In the continuous variable
rocker arm mechanism 50 on theair intake valves rocker shaft 30 is rotated counterclockwise by a predetermined angle by means of the drive mechanism 90 and set at an advance angle position. A fulcrum of oscillation of the continuousvariable arm 53 is distanced from theair intake valves cam 23 rotated by thecam shaft 21, theroller 53 d moves along thecam 23, and the continuousvariable arm 53 oscillates about therocker shaft 30 at predetermined intervals in a direction indicated by an arrow F inFIG. 11 . In this manner, motion of the continuousvariable arm 53 is transmitted to the sharedrocker arm 60 through thetransformation member 56 and theintermediate arm 51, and theair intake valves cam 23. - As described above, in an intake stroke of the internal EGR operation, the
air intake valves rocker arm mechanism 50, and theexhaust valves rocker arm mechanism 40. Therefore, theair intake valves FIG. 6 , and theexhaust valves FIG. 6 . More specifically, theexhaust valves FIG. 6 . That is, since theexhaust valves cylinder 11 is taken into thecylinder 11 to cause an internal EGR operation. - Since the lifts of the
exhaust valves air intake valves air intake valves FIG. 7 shows a relationship between closing end phases and amounts of air of theair intake valves air intake valves air intake valves - As described above, the switching
rocker arm mechanism 40 and the continuous variablerocker arm mechanism 50 are operated in conjunction with each other to make it possible to obtain a more appropriate amount of EGR and to purify an exhaust gas. - Operations of the switching
rocker arm mechanism 40 and the continuous variablerocker arm mechanism 50 in an engine braking operation will be explained while comparing a “normal operation” and an “engine braking operation”.FIG. 12 is a graph showing a relationship between the phase and lift of thecam shaft 21. Reference symbol EX denotes opening valves (lifts) of theexhaust valves air intake valves - The
cam shaft 21 causes an exhaust stroke which opens theexhaust valves air intake valves rocker arm mechanism 40 at this time is shown inFIG. 8 , and an operation of the continuous variablerocker arm mechanism 50 at this time is shown inFIG. 9 . In the normal operation, on both theair intake valves exhaust valves rocker arm mechanism 40 is set to be off, and an operation mode of the continuous variablerocker arm mechanism 50 is set to a normal (neutral) mode. - The operation of the switching
rocker arm mechanism 40 and the operation of the continuous variablerocker arm mechanism 50 in the normal state will not be explained because the operations are the same as those inFIGS. 8 and 9 . - In an engine braking operation, on the
air intake valves rocker arm mechanism 40 is set to be off, and the operation mode of the continuous variablerocker arm mechanism 50 is set to a normal (neutral) mode. On theexhaust valves rocker arm mechanism 40 is set to be on, and the operation mode of the continuous variablerocker arm mechanism 50 is set to an early opening (advance) mode. - The operations of the switching
rocker arm mechanism 40 and the continuous variablerocker arm mechanism 50 are summarized as follows. -
TABLE 2 Engine braking operation Switching rocker Continuous variable arm mechanism rocker arm mechanism Air intake valve OFF Normal Exhaust valve ON Early opening - When the operation mode of the switching
rocker arm mechanism 40 on theexhaust valves FIG. 14 , in the switchingrocker arm mechanism 40, engine oil is supplied into thehollow portion 71 a. For this reason, thepiston 73 rises against the elastic force of thespring 74, and the circumference of thepiston 73 is positioned at thewindow portion 71 b. On the other hand, theroller 41 c moves along thecam 22 by rotation of thecam 22 rotated by thecam shaft 21, and the switchingrocker arm 41 oscillates about therocker shaft 30 at predetermined intervals in a direction indicated by an arrow E inFIG. 14 . When thestrike arm 41 b is inserted into thewindow portion 71 b, thestrike arm 41 b is brought into contact with the circumference of thepiston 73. Therefore, motion of the switchingrocker arm 41 is transmitted to the sharedrocker arm 60, and theexhaust valves cam 22. Thenose 22 a of thecam 22 corresponds to reference symbol L inFIG. 6 . - As shown in
FIG. 15 , in the continuous variablerocker arm mechanism 50 on theexhaust valves rocker shaft 30 is rotated counterclockwise by a predetermined angle by means of the drive mechanism 90 and set at an advance angle position. A fulcrum of oscillation of the continuousvariable arm 53 is distanced from theair intake valves cam 23 rotated by thecam shaft 21, theroller 53 d moves along thecam 23, and the continuousvariable arm 53 oscillates about therocker shaft 30 at predetermined intervals in a direction indicated by an arrow F inFIG. 15 . In this manner, motion of the continuousvariable arm 51 is transmitted to the sharedrocker arm 60 through thetransformation member 56 and theintermediate arm 51, and theair intake valves cam 23. - As described above, in the engine braking operation, the
air intake valves rocker arm mechanism 50, and theexhaust valves rocker arm mechanism 40 and the continuous variablerocker arm mechanism 50. Therefore, theair intake valves FIG. 12 , and theexhaust valves FIG. 12 . More specifically, the switchingrocker arm mechanism 40 opens theexhaust valves FIG. 12 . That is, theexhaust valves exhaust valves - On the other hand, since the operation state of the engine is not constant, a necessary braking force changes. For this reason, this fine adjustment is performed by the operations of the
exhaust valves rocker arm mechanism 50. More specifically, when theexhaust valves FIG. 13 shows a relationship between opening start phases of theexhaust valves exhaust valves - As described above, when the switching
rocker arm mechanism 40 and the continuous variablerocker arm mechanism 50 are operated in conjunction with each other, a more appropriate engine braking force can be obtained, and preferable drive feeling can be obtained. - As described above, according to the
variable valve apparatus 20 for an internal combustion engine according to the embodiment, a plurality of functions such as execution of internal EGR, application of engine braking, improvement in fuel consumption, and purification of an exhaust gas can be simultaneously exerted. - According to the present invention, valves are opened or closed by using both the switching rocker arm mechanism and the continuous variable rocker arm mechanism to make it possible to realize a plurality of functions such as instantaneous switching of opening/closing timings of the valves and fine control of lifts.
- Furthermore, transmission of oscillation displacement is selectively performed as needed to make it possible to open or close a valve without delay. The transmission of oscillation displacement is continuously performed to make it possible to finely control the drive phase and lift of the valve. When fine adjustment of an amount of EGR is performed while performing the internal EGR, an exhaust gas can be purified. Engine braking can be applied, and the effect can be enhanced.
Claims (5)
1. A variable valve apparatus for an internal combustion engine, comprising:
a cam shaft arranged to be rotatable on a cylinder head of the internal combustion engine;
a rocker shaft arranged to be capable of oscillation in the internal combustion engine;
a continuous variable rocker arm mechanism which is driven by a cam formed on the cam shaft, opens or closes at least one of an air intake valve and an exhaust valve, and continuously makes a lift of the valve variable; and
a switching rocker arm mechanism which is driven by the cam formed on the cam shaft, opens or closes at least one of the air intake valve and the exhaust valve, and switches the lift of the valve in a stepwise manner.
2. The variable valve apparatus for an internal combustion engine according to claim 1 , wherein
the switching rocker arm mechanism comprises:
a shared rocker arm which is supported on the rocker shaft to be capable of oscillation and configured to drive the valve;
a switching rocker arm which is driven by the cam and arranged to be capable of oscillation on the rocker shaft; and
a transmission mechanism which selectively transmits displacement from the switching rocker arm to the shared rocker arm.
3. The variable valve apparatus for an internal combustion engine according to claim 1 , wherein
the continuous variable rocker arm mechanism comprises:
a shared arm supported on the rocker shaft to be capable of oscillation and configured to drive the valve;
a continuous variable arm driven by the cam and arranged to be capable of oscillation about a fulcrum arranged on the rocker shaft side;
an intermediate arm supported by the rocker shaft to be capable of oscillation and arranged between the shared arm and the continuous variable arm;
a transformation member which is arranged between the intermediate arm and the continuous variable arm and transmits oscillation displacement of the continuous variable arm to the shared arm through the intermediate arm; and
a drive mechanism which causes the rocker shaft to oscillate to displace the fulcrum.
4. The variable valve apparatus for an internal combustion engine according to claim 1 , wherein
the internal combustion engine comprises the continuous variable rocker arm mechanism on an intake side and the switching rocker arm mechanism on an exhaust side, and
when the internal combustion engine is in an intake stroke, the exhaust valve is opened by the switching rocker arm mechanism, and the air intake valve is closed early by the continuous variable rocker arm mechanism.
5. The variable valve apparatus for an internal combustion engine according to claim 1 , wherein
the internal combustion engine comprises at least one of the exhaust valves driven by the switching rocker arm mechanism and at least one of the exhaust valves driven by the continuous variable rocker arm mechanism per cylinder, and
when the internal combustion engine is near a compression top dead center, the exhaust valve is opened by the switching rocker arm mechanism, and the exhaust valve is opened early by the continuous variable rocker arm mechanism.
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007338360 | 2007-12-27 | ||
JP2007-338360 | 2007-12-27 | ||
JP2008004745A JP5331343B2 (en) | 2007-12-27 | 2008-01-11 | Variable valve operating device for internal combustion engine |
JP2008-004745 | 2008-01-11 | ||
PCT/JP2008/073635 WO2009084598A1 (en) | 2007-12-27 | 2008-12-25 | Variable valve gear device for internal combustion engine |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2008/073635 Continuation WO2009084598A1 (en) | 2007-12-27 | 2008-12-25 | Variable valve gear device for internal combustion engine |
Publications (1)
Publication Number | Publication Date |
---|---|
US20100242878A1 true US20100242878A1 (en) | 2010-09-30 |
Family
ID=41029676
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/814,139 Abandoned US20100242878A1 (en) | 2007-12-27 | 2010-06-11 | Variable valve apparatus for internal combustion engine |
Country Status (3)
Country | Link |
---|---|
US (1) | US20100242878A1 (en) |
JP (1) | JP5331343B2 (en) |
DE (1) | DE112008003534T5 (en) |
Cited By (11)
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WO2012038190A1 (en) * | 2010-09-23 | 2012-03-29 | Avl List Gmbh | Four-stroke internal combustion engine comprising an engine brake |
WO2012038191A1 (en) * | 2010-09-23 | 2012-03-29 | Avl List Gmbh | Four-stroke internal combustion engine with engine brake |
WO2012038195A1 (en) * | 2010-09-23 | 2012-03-29 | Avl List Gmbh | Four-stroke internal combustion engine comprising an engine brake |
EP2495408A3 (en) * | 2011-03-02 | 2013-02-06 | Delphi Technologies, Inc. | Valve train system for an internal combustion engine |
EP2640938A1 (en) * | 2010-11-17 | 2013-09-25 | Mack Trucks, Inc. | Hinged rocker arm and valve openning arrangement including a hinged rocker arm |
EP2851525A1 (en) * | 2013-09-19 | 2015-03-25 | MAN Truck & Bus AG | Device and method for actuating at least one exhaust valve of a valve-controlled combustion engine |
CN104819021A (en) * | 2014-01-31 | 2015-08-05 | 曼卡车和巴士股份公司 | Apparatus and method for operating at least one exhaust valve of a valve-controlled combustion engine |
US9567881B2 (en) | 2014-09-03 | 2017-02-14 | GT Technologies | Valvetrain assembly |
US9657607B2 (en) | 2014-09-03 | 2017-05-23 | GT Technologies | Rocker arm assembly and valvetrain assembly incorporating the same |
US9863291B2 (en) | 2015-05-14 | 2018-01-09 | GT Technologies | Locator for use in a valvetrain of a cylinder head of an internal combustion engine |
US10954869B1 (en) * | 2020-02-18 | 2021-03-23 | Ford Global Technologies, Llc | System and method to reduce engine hydrocarbon emissions |
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WO2012038191A1 (en) * | 2010-09-23 | 2012-03-29 | Avl List Gmbh | Four-stroke internal combustion engine with engine brake |
WO2012038195A1 (en) * | 2010-09-23 | 2012-03-29 | Avl List Gmbh | Four-stroke internal combustion engine comprising an engine brake |
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EP2640938A1 (en) * | 2010-11-17 | 2013-09-25 | Mack Trucks, Inc. | Hinged rocker arm and valve openning arrangement including a hinged rocker arm |
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EP2495408A3 (en) * | 2011-03-02 | 2013-02-06 | Delphi Technologies, Inc. | Valve train system for an internal combustion engine |
EP2851525A1 (en) * | 2013-09-19 | 2015-03-25 | MAN Truck & Bus AG | Device and method for actuating at least one exhaust valve of a valve-controlled combustion engine |
RU2661921C2 (en) * | 2013-09-19 | 2018-07-23 | Ман Трак Унд Бас Аг | Device and method for actuating at least one exhaust valve of valve-controlled internal combustion engine |
CN104819021A (en) * | 2014-01-31 | 2015-08-05 | 曼卡车和巴士股份公司 | Apparatus and method for operating at least one exhaust valve of a valve-controlled combustion engine |
CN104819021B (en) * | 2014-01-31 | 2018-12-25 | 曼卡车和巴士股份公司 | Manipulate the device and method of at least one drain tap of the internal combustion engine of valve control |
US9657607B2 (en) | 2014-09-03 | 2017-05-23 | GT Technologies | Rocker arm assembly and valvetrain assembly incorporating the same |
US9567881B2 (en) | 2014-09-03 | 2017-02-14 | GT Technologies | Valvetrain assembly |
US9863291B2 (en) | 2015-05-14 | 2018-01-09 | GT Technologies | Locator for use in a valvetrain of a cylinder head of an internal combustion engine |
US10954869B1 (en) * | 2020-02-18 | 2021-03-23 | Ford Global Technologies, Llc | System and method to reduce engine hydrocarbon emissions |
Also Published As
Publication number | Publication date |
---|---|
DE112008003534T5 (en) | 2010-10-28 |
JP2009174319A (en) | 2009-08-06 |
JP5331343B2 (en) | 2013-10-30 |
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