WO2005068789A1 - 内燃機関の動弁装置 - Google Patents
内燃機関の動弁装置 Download PDFInfo
- Publication number
- WO2005068789A1 WO2005068789A1 PCT/JP2005/001033 JP2005001033W WO2005068789A1 WO 2005068789 A1 WO2005068789 A1 WO 2005068789A1 JP 2005001033 W JP2005001033 W JP 2005001033W WO 2005068789 A1 WO2005068789 A1 WO 2005068789A1
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- WIPO (PCT)
- Prior art keywords
- exhaust
- intake
- valve
- cam
- control
- Prior art date
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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
- 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
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/022—Chain drive
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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
- 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
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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
- 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
- F01L13/0021—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 by modification of rocker arm ratio
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/0476—Camshaft bearings
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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
- F01L2305/00—Valve arrangements comprising rollers
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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
- F01L2305/00—Valve arrangements comprising rollers
- F01L2305/02—Mounting of rollers
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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
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/03—Auxiliary actuators
- F01L2820/032—Electric motors
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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
- This effort relates to a valve operating device for an internal combustion engine that has a variable valve characteristic mechanism that controls the valve operating characteristics of the intake valve and the exhaust valve. Specifically, the variable valve characteristic mechanism controls the intake valve and the exhaust valve.
- the present invention relates to a valve gear for an internal combustion engine in which the internal EGR rate is controlled by controlling the overlap period and the non-overlap period by changing the opening / closing timing.
- a device for controlling valve operating characteristics of an intake valve and an exhaust valve for performing internal EGR there is, for example, a variable valve device for an internal combustion engine disclosed in Japanese Patent Application Laid-Open No. 2001-003721.
- This variable valve device includes variable valve mechanisms on the intake valve side and the exhaust valve side.
- Each variable valve mechanism includes an eccentric cam fixed to a drive shaft that rotates in conjunction with a crankshaft, a ring-shaped link rotatably fitted around the outer periphery of the eccentric cam, and is disposed substantially parallel to the drive shaft.
- a rocker arm rotatably fitted to the outer periphery of a drive cam eccentrically fixed to the control shaft and being pivotally connected at one end to a ring-shaped link; and a rocker arm rotatably fitted to the drive shaft and rotatably fitted to the drive shaft.
- a swing cam connected to the other end via a link.
- the swing cam that opens and closes the intake valve and the exhaust valve rotates the control shaft in accordance with the engine operating state, and changes the distance between the swing center of the mouth arm and the rotation center of the drive shaft. And swing to change the maximum lift and operating angle of the exhaust valve. And, as the maximum lift amount of the intake valve and the exhaust valve becomes smaller, the control shaft moves the maximum lift timing to the retard side in the intake valve, and the maximum lift timing in the exhaust valve. Is controlled to move to the advance side. As a result, the opening timing of the intake valve is retarded by a width greater than the advance of the closing timing, and the closing timing of the exhaust valve is greater than the retardation of the opening timing. It is possible to improve fuel efficiency and purify exhaust gas by using the combustion gas remaining in the combustion chamber, which is advanced by the width.
- the drive shaft and the control shaft are provided in the respective variable valve mechanisms on the intake valve side and the exhaust valve side, so that the valve operating characteristics of the intake valve and the exhaust valve are controlled.
- Variable mechanism becomes larger. Furthermore, when the opening / closing timing of the intake valve or the exhaust valve is advanced or retarded, if the opening timing of the exhaust valve is too late, the exhaust loss of the combustion gas increases, the thermal efficiency decreases, and the intake valve If the opening timing is too early, sufficient fresh air will not be sucked in, and the output will decrease or combustion will be unstable. Disclosure of the invention
- the present invention has been made in view of such circumstances, and it is an object of the present invention to prevent or suppress the blowback of intake air by causing the intake valve to open in a state where the pressure of the combustion chamber is low. And Furthermore, the purpose is to reduce the size of the variable valve characteristic mechanism and simplify its structure. Another object is to simplify the structure of the variable valve characteristic mechanism.
- variable valve characteristic mechanism for controlling valve operation characteristics of an intake valve and an exhaust valve, respectively, wherein the variable valve characteristic mechanism changes the opening / closing timing of the intake valve and the exhaust valve.
- the pulp characteristic variable mechanism interlocks with a crankshaft of the internal combustion engine. rotation A camshaft, an intake interlocking mechanism connected to an intake cam that opens and closes the intake valve according to rotation of the camshaft, and an exhaust cam that opens and closes the exhaust valve according to rotation of the force shaft.
- An exhaust interlocking mechanism to be connected, a control mechanism that swings each of the interlocking mechanisms around the force axis, and a drive mechanism that drives the control mechanism.
- the amount of retard of the opening timing of the intake valve by the intake interlock mechanism is A valve operating device for an internal combustion engine, wherein the driving mechanism and each of the interlocking mechanisms are connected to each other so as to be greater than the advance amount of the closing timing of the exhaust valve.
- variable valve mechanism when the variable valve mechanism reduces the overlap period or increases the non-overlap period in the direction in which the internal EGR rate increases, the amount of retardation of the opening timing of the intake valve is reduced by the exhaust valve.
- the retarded amount when the intake valve is opened increases when the exhaust valve closes.
- the intake valve opens when the pressure in the combustion chamber is lower than when the valve advance angle is less than the advance amount.
- the control mechanism is driven by the drive mechanism and is parallel to a reference plane including a rotation centerline of the camshaft.
- a control member movable in any direction; an intake control link pivotally connected to the control member at a first intake connection portion and pivotally connected to the intake interlocking mechanism at a second intake connection portion;
- An exhaust control link pivotally connected to a control member and pivotally connected to the exhaust interlocking mechanism at a second exhaust connection portion, wherein a pivot centerline of the first intake connection portion and a pivot of the first exhaust connection portion are provided.
- the dynamic center line is disposed on one side of the reference plane in parallel with the rotation center line, the pivot center line of the second intake connection portion is disposed on the one side, and the second exhaust The pivot centerline of the connecting portion is disposed on the other side with respect to the reference plane, so that When the control member moves, the intake interlocking mechanism swings around the cam shaft by a larger swing amount than the exhaust interlocking mechanism.
- the intake interlocking mechanism and the exhaust interlocking mechanism are required.
- the pivot centerline of the first intake connection and the pivot centerline of the first exhaust connection are arranged on one side with respect to the reference plane, and the pivot of the second intake connection is arranged.
- a dynamic center line is disposed on the one side, and a pivot center line of the second exhaust connection portion is disposed on the other side with respect to the reference plane, so that the intake control link and the exhaust control link each include a reference plane.
- the intake interlocking mechanism and the exhaust interlocking mechanism that are pivotally connected at the pivot center line of the second intake connection and the pivot center line of the second exhaust connection, Swing about the cam shaft so that the moving amount is larger than the swing amount of the exhaust interlocking mechanism.
- the control mechanism is driven by the drive mechanism and is parallel to a reference plane including a rotation centerline of the camshaft.
- a control member movable in any direction; an intake control link pivotally connected to the control member at a first intake connection portion and pivotally connected to the intake interlocking mechanism at a second intake connection portion;
- An exhaust control link pivotally connected to a control member and pivotally connected to the exhaust interlocking mechanism at a second exhaust connection portion, wherein a pivot centerline of the first intake connection portion and a pivot of the first exhaust connection portion are provided.
- the dynamic center line is disposed parallel to the rotation center line, the pivot center line of the second intake connection portion is disposed on one side with respect to the reference plane, and the pivot center of the second exhaust connection portion A line is arranged on the other side with respect to the reference plane, and the link length of the intake control link
- the intake interlocking mechanism swings about the force axis with a larger V and a swing amount than the exhaust interlocking mechanism. It is.
- a control member common to the intake interlocking mechanism and the exhaust interlocking mechanism is moved in order to obtain valve operating characteristics in which the amount of retardation of the opening timing of the intake valve is greater than the amount of advancement of the timing of closing the exhaust valve.
- the intake control link and the exhaust control link whose link lengths are longer than the exhaust control link are respectively connected to the pivotal center line of the second intake connection section, which is distributed on both sides of the reference plane.
- the intake interlocking mechanism and the exhaust interlocking mechanism, which are pivotally connected at the pivot center line of the exhaust connection are centered on the cam shaft so that the amount of movement of the intake interlocking mechanism is larger than that of the exhaust interlocking mechanism.
- the intake interlocking mechanism may be configured such that the intake interlocking mechanism is swung by the control mechanism.
- An intake pivoting unit having a pivoting center line that pivots about a rotation centerline of the force axis, wherein the exhaust interlocking mechanism is configured such that when the exhaust interlocking mechanism is swung by the control mechanism,
- An exhaust pivot unit having a pivot center line swinging about the rotation center line, wherein a distance between the pivot center line of the intake pivot unit and the rotation center line is equal to or smaller than that of the exhaust pivot unit.
- the intake interlocking mechanism When the control mechanism is driven by the driving mechanism, the intake interlocking mechanism is moved around the camshaft by the exhaust interlocking mechanism when the control mechanism is driven by the driving mechanism by being shorter than the distance between the pivot center line and the rotation center line. With a larger displacement than the oscillating exhaust cam, the intake cam is It swings around the cam shaft.
- the intake interlocking mechanism pivots to a position closer to the rotation center line of the cam shaft as compared to the pivoting center line of the exhaust interlocking mechanism. Because of the center line, the control mechanism moves the intake cam and the exhaust cam through the intake interlocking mechanism and the exhaust interlocking mechanism so that the swing amount of the intake cam becomes larger than the swing amount of the exhaust cam. Swing as center.
- FIG. 1 is a schematic right side view of a motorcycle equipped with the internal combustion engine of the present invention.
- FIG. 2 is a cross-sectional view of the internal combustion engine shown in FIG. 1 taken along the line II-II of FIG. 6, and partially passing through the central axis of the valve stem of the intake valve and the exhaust valve and the central axis of the control shaft.
- FIG. 1 is a cross-sectional view of the internal combustion engine shown in FIG. 1 taken along the line II-II of FIG. 6, and partially passing through the central axis of the valve stem of the intake valve and the exhaust valve and the central axis of the control shaft.
- FIG. 3 is a schematic view of a throttle body of the internal combustion engine of FIG.
- FIGS. 4 (A) to 4 (D) illustrate a control form in the control of the internal combustion engine of FIG. 1, and FIG. 4 (A) shows a warm-up map of the throttle opening degree map.
- Fig. 4 (B) shows the post-warm-up map of the throttle opening map, and
- Fig. 4 (C) shows the control mode for the overlap period and the non-overlap period during warm-up.
- FIG. 4D is a diagram showing a control mode during the overlap period and the non-overlap period after the warm-up.
- FIG. 5 is a cross-sectional view taken along the line Va-Va of FIG. 10 in the internal combustion engine of FIG. 1, and is a partial cross-sectional view taken along the line Vb-Vb.
- FIG. 6 is a cross-sectional view taken along the line VI-VI in FIG. 2 of the valve train with the head cover removed in the internal combustion engine of FIG. 1, and partially shows the components of the valve train as appropriate. It is the figure shown by the section.
- FIG. 7 is a view of the power shaft holder attached to the cylinder head in the internal combustion engine of FIG. 1 as viewed from the head cover side along the cylinder axis.
- FIG. 8 (A) is a view of the exhaust drive cam of the variable valve characteristic mechanism in the valve train of the internal combustion engine of FIG. 1 viewed from the camshaft direction
- FIG. 8 (B) is a view of the internal combustion engine of FIG.
- FIG. 4 is a view showing a state in which the exhaust link mechanism and the exhaust cam of the variable valve characteristic mechanism are appropriately pivoted in the valve gear of FIG.
- FIG. 9A is a cross-sectional view taken along the line IXA of FIG. 8B
- FIG. 9B is a cross-sectional view taken along the line IXB of FIG. 8B
- FIG. 9 is a sectional view taken along the line IXC of FIG. 8B
- FIG. 9D is a sectional view taken along the line IXD of FIG.
- FIG. 10 is a view of the internal combustion engine of FIG. 1 when the head cover is viewed from the front along the cylinder axis, and is partially cut away to show a drive mechanism of the valve characteristic variable mechanism.
- FIG. 11 is a diagram illustrating valve operating characteristics of an intake valve and an exhaust valve by the valve train of the internal combustion engine of FIG.
- FIG. 12 (A) is an explanatory view of the main part of the valve characteristic variable mechanism when the maximum valve operating characteristic is obtained for the intake valve in the valve train of the internal combustion engine of FIG. 1
- FIG. 12 (B) is FIG. 3 is an explanatory view of a main part of a valve characteristic variable mechanism when a maximum valve operating characteristic is obtained for an exhaust valve in the valve train of the internal combustion engine of FIG. 1 and is a view corresponding to an enlarged view of the main part of FIG.
- Fig. 13 (A) is a diagram corresponding to Fig. 12 (A) when the minimum valve operation characteristic is obtained for the intake valve
- Fig. 13 (B) is a diagram when the minimum valve operation characteristic is obtained for the exhaust valve.
- FIG. 12 is a diagram corresponding to FIG.
- Fig. 14 (A) is a diagram corresponding to Fig. 12 (A) when the decompression operation characteristic is obtained for the intake valve
- Fig. 14 (B) is a diagram when the decompression operation characteristic is obtained for the exhaust valve. It is a figure corresponding to 12 (B).
- symbol in a figure shows the following.
- Valve operating chamber, 26 Air cleaner, 27 ... Slot reporter, 28 ... Exhaust Pipe, 29... Cam shaft holder, 30 ... Throttle valve,... Throttle opening detection means, 33... Electric motor, 34, 35... Gear, 40... Valve drive, 41, 42... Main rocker arm, 43... Rocker shaft, 44 ... Bearing, 50 ... Cam shaft, 51, 52 ... Driving cam, 53 ... Intake cam, 54 ...
- Driving mechanism M3 ... Control mechanism, M4 ... Transmission mechanism, H0 ... Reference plane, Hl, H2 ⁇ orthogonal plane, R1 ... Rotation direction, R2 ... Counter rotation direction, Kimax, Kemax ... Maximum valve operation characteristics, Kimin, Kemin... Minimum valve operating characteristics,... Opening, 0 iomax, ⁇ icrain,
- FIG. 1 an internal combustion engine E to which the present invention is applied is mounted on a motorcycle V as a vehicle.
- the motorcycle V has a body frame 1 having a front frame 1a and a rear frame 1b, and an upper end of a front fork 3 rotatably supported by a head pipe 2 connected to a front end of the front frame 1a.
- Handle 4 fixed to the front part, a front wheel 7 rotatably supported at the lower end of the front fork 3, a power unit U supported by the body frame 1, and a swingably supported by the body frame 1.
- a rear wheel 8 rotatably supported by the rear end of the swing arm 5, a rear cushion 6 for connecting the rear frame 1b to the rear of the swing arm 5, and a body force bar 9 covering the body frame 1 are provided. .
- the power unit U includes a horizontally disposed internal combustion engine E having a crankshaft 15 extending in the left-right direction of the motorcycle V, and a transmission having a transmission for transmitting the power of the internal combustion engine E to the rear wheels 8.
- the internal combustion engine E includes a crankcase 10 that forms a crank chamber for accommodating a crankshaft 15 and also serves as a transmission case, a cylinder 11 that is connected to the crankcase 10 and extends forward, and a cylinder 11 that is connected to a front end of the cylinder 11. Cylinder head 12 to be mated, and a head coupled to the front end of cylinder head 12 A cover 13 is provided.
- the cylinder spring L1 of the cylinder 11 extends obliquely upward and slightly upward with respect to the horizontal direction toward the front (see FIG. 1). Then, the rotation of the crankshaft 15, which is rotationally driven by the piston 14 (see FIG. 2), is shifted by the transmission and transmitted to the rear wheel 8, and the rear wheel 8 is driven.
- the internal combustion engine ⁇ is an SOHC type air-cooled, single-cylinder, four-stroke internal combustion engine, and a cylinder 11 is formed with a cylinder hole 11 a in which a piston 14 is fitted so as to reciprocate.
- a combustion chamber 16 is formed on a surface facing the cylinder hole 11a in the cylinder axial direction A1, and an intake port 17 and an exhaust port each having an intake port 17a opened to the combustion chamber 16 are provided.
- An exhaust port 18 having 18a is formed.
- the ignition plug 19 facing the combustion chamber 16 is inserted into a mounting hole 12 c formed in the cylinder head 12 and mounted on the cylinder head 12.
- the combustion chamber 16 forms a combustion space together with the cylinder hole 11a between the piston 14 and the cylinder head 12.
- the cylinder head 12 is supported by the valve guides 20 i and 20 e so as to be able to reciprocate, and is one engine valve 22 which is an engine valve constantly urged by the valve panel 21 in the valve closing direction.
- One exhaust valve 23 is provided.
- the intake valve 22 and the exhaust valve 23 are opened and closed by a valve train 40 provided in the internal combustion engine E to open and close the intake port 17a and the exhaust port 18a formed by the valve sheet 24, respectively.
- the valve train 40 is disposed in a valve train chamber 25 formed by the cylinder head 12 and the head cover 13.
- An air cleaner 26 (see FIG. 1) is provided on the upper surface 12a, which is one side of the cylinder head 12 where the inlet 17b of the intake port 17 is open, to guide air taken in from the outside to the intake port 17.
- An intake device equipped with a throttle pod 27 (see FIG. 1) is attached, and the lower surface 12b, which is the other side of the cylinder head 12 where the outlet 18b of the exhaust port 18 opens, is connected to the exhaust port 18 from the combustion chamber 16.
- the exhaust system is equipped with an exhaust pipe 28 (see Fig. 1) that guides the exhaust gases flowing out through the internal combustion engine E. It is attached.
- the intake device is provided with a fuel injection valve which is a fuel supply device for supplying liquid fuel to the intake air.
- the air sucked through the air cleaner 26 and the throttle body 27 is drawn into the combustion chamber 16 from the suction port 17 through the intake valve 22 opened in the intake stroke in which the piston 14 descends, and the biston 14 rises
- the fuel is compressed while being mixed with fuel.
- the air-fuel mixture is ignited by the ignition plug 19 at the end of the compression stroke and burns, and the piston 14 driven by the pressure of the combustion gas rotates the crankshaft 15 in the expansion stroke in which the piston 14 descends.
- the burned gas is exhausted from the combustion chamber 16 to the exhaust port 18 as exhaust gas through the exhaust valve 23 that is opened during the exhaust stroke in which the piston 14 rises.
- a mouth position sensor 32) is provided.
- the throttle control mechanism T includes an electric motor 33 which is an actuator controlled by an electronic control unit (hereinafter referred to as “ECU”) 92 (see FIG. 5) as a control device, and a throttling force of the electric motor 33.
- ECU electronice control unit
- a reduction gear train comprising a series of gears 34 and 35 constituting a transmission mechanism for transmitting to the valve 30.
- the EC U 92 includes a required output amount detection means 95 for detecting an operation amount D of a throttle drip as an output operation member operated by a driver, and detecting a warm-up state of the internal combustion engine E.
- Each of the operating state detecting means for detecting the operating state of the internal combustion engine E includes an engine temperature detecting means 96 (for example, a lubricating oil temperature detecting means) as a warming-up state detecting means and a throttle opening detecting means 32.
- the detection signal is input.
- the operation amount D is a required amount of the engine output by the driver
- the throttle grip is an output setting means for setting the required amount.
- the storage device of the EC U92 stores a throttle opening map in which the opening amount of the throttle valve 30] 3 is set using the operation amount D as a parameter.
- this throttle opening map includes a warming-up map used when the internal combustion engine E is warmed up, and the completion of the warming-up of the internal combustion engine E. It consists of a post-warm-up map used later.
- the electric motor 33, the operation amount and D to be detected by the output demand detection unit 95 in response to the actual opening of the throttle valve 30 detected by the throttle opening detecting means 3 2, the throttle valve 30
- the ECU 92 controls the opening and closing of the slot notch valve 30 so that the opening becomes the opening 3 set by the throttle opening map.
- the EC U92 selects a warm-up map when the engine temperature is detected by the engine temperature detecting means 96 to be a state in which the engine temperature is lower than the predetermined temperature, and the engine temperature detecting means 96 selects the engine temperature. If it is detected that the temperature is after the warm-up, which is equal to or higher than the predetermined temperature, a post-warm-up map is selected. According to the warm-up map, the opening characteristic of the throttle valve 30 is directly proportional to the operation amount D so that the opening of the throttle valve 30 increases as the operation amount D increases over the entire load range of the internal combustion engine E. Is set.
- the electric motor 33 has an operation amount D detected by the output demand detection means 95 which is also a load detection means for detecting an engine load, that is, an opening degree which increases as the engine load increases, over the entire load range.
- the opening of the throttle valve 30 is controlled so that
- the throttle valve 30 changes from the idle opening degree as the manipulated variable D (engine load) increases according to the post-warm-up map.
- the opening characteristic is set so that the throttle valve 30 is fully opened regardless of the manipulated variable D in the second load area Fb that exceeds the predetermined load Da and is fully opened at the predetermined load Da. Therefore, the electric motor 33 controls the opening of the throttle valve 30 so that the throttle valve 30 is fully opened from the idling opening to the predetermined load Da as the operation amount D increases in the first load region Fa, and the second load region At Fb, the throttle valve 30 is controlled to be kept fully open.
- the valve train 40 abuts a valve stem 22 a for opening and closing the intake valve 22.
- a variable valve characteristic mechanism for controlling valve operation characteristics including the maximum lift amount.
- the intake main mouth sucker arm 41 and the exhaust main mouth sucker arm 2 are swingably supported by a pair of mouth sucker shafts 43 fixed to the cam shaft holder 29 at fulcrum portions 41a and 42a at the center, respectively.
- the adjustment screws 4 lb and 42 b forming the working portion at one end abut against the valve stems 22 a and 23 a, and the rollers 41 c and 42 c forming the contact portions at the other end form the intake cam 53 and the exhaust cam. Touch cam 54.
- the variable valve characteristic mechanism M includes an internal mechanism housed in the valve operating chamber 25, and an electric motor 80 which is an external mechanism disposed outside the valve operating chamber 25 and is an electric actuator driving the internal mechanism.
- the internal mechanism includes one camshaft 50 rotatably supported by the cylinder head 12 and driven to rotate in conjunction with the crankshaft 15, and provided on the camshaft 50 to rotate integrally with the camshaft 50.
- Drive cams 51 and 52 which are driven cams, link mechanisms Mli and Mle, which are pivotally supported by the camshaft 50 and can swing about the camshaft 50, and link mechanisms Mli and M
- the intake cam 53 and the exhaust cam 54 which are valve cams pivotally supported by a camshaft 50 connected to the le and operating the intake main rocker arm 41 and the exhaust main rocker arm 42, respectively, and the link mechanisms Mli and Mle are cams.
- a drive mechanism M2 (see FIG. 5) having an electric motor 80 as a drive source for swinging about the axis 50, and an electric motor 80 interposed between the drive mechanism M2 and the link mechanisms Mli and Mle.
- the camshaft 50 is connected to the cylinder head 12 and the cylinder head 12 via a pair of bearings 56 disposed at both ends thereof. It is rotatably supported by the holder 29 and rotates at the rotation speed of 1Z2 in conjunction with the crankshaft 15 by the power of the crankshaft 15 (see Fig. 1) transmitted via the valve train transmission mechanism. Driven.
- the valve train transmission mechanism includes a force sprocket 57 integrally connected to a tip end of a left end which is one end of the camshaft 50, a drive sprocket integrally connected to the crankshaft 15, and a force sprocket 57. And a timing tune 58 wound around the driving sprocket.
- the transmission mechanism for a valve train is formed by a cylinder 11 and a cylinder head 12, and is provided on the left side of the cylinder 11 and the cylinder head 12 which is one side with respect to the first orthogonal plane H1. It is housed in the located transmission room.
- the transmission chamber 59 formed in the cylinder head 12 of the transmission chamber is arranged to rotate in the radial direction (hereinafter, referred to as “radial direction”) around the cylinder axis L 1 and to rotate the camshaft 50.
- the direction A 2 of the center line L 2 (hereinafter referred to as “cam shaft direction A 2”) ′ is adjacent to the valve train chamber 25.
- the first orthogonal plane H1 is a plane that includes the cylinder axis L1 and is orthogonal to a reference plane HO described later.
- the members related to the intake valve 22 and the members related to the exhaust valve 23 include members corresponding to each other, and therefore, the intake drive cam 51, the exhaust drive cam 52, the link mechanisms Mli, Mle, and the intake mechanism. Since the cam 53 and the exhaust cam 54 have the same basic structure, in the following description, the members related to the exhaust valve 23 will be mainly described, and the members related to the intake valve 22 and related descriptions will be described in parentheses as necessary. It is written in
- the exhaust drive cam 52 (intake drive cam 51), which is press-fitted and fixed in the housing, has a cam surface formed over the entire outer peripheral surface.
- the cam surface has a base circular portion 52a (51a) that does not swing the exhaust cam 54 (intake cam 53) via the link machine Mle (Mli) and an exhaust via the link mechanism Mle (Mli).
- Composed of a cam crest 52b (51b) for driving the cam 54 (intake cam 53) Is done.
- the base circle portion 52a (51a) has a cross-sectional shape formed by an arc having a constant radius from the rotation center line L2, and the cam ridge portion 52b (51b) has a half-section from the rotation center line L2. It has a cross-sectional shape whose diameter decreases after increasing in the rotation direction R1 of the camshaft 50. Then, the base circle portion 52a (51a) is exhausted so that the exhaust main port opening arm 42 (intake main rocking arm 41) comes into contact with the base portion 54a (53a) of the exhaust cam 54 (intake cam 53). The swing position of the cam 54 (intake cam 53) is set, and the cam crest 52b (51b) is fitted with the exhaust main rocker arm 42 (intake main rocker arm 41).
- the link mechanisms Mli and Mle include an intake link mechanism Mli connected to the intake cam 53 and an exhaust link mechanism Mle connected to the exhaust cam 54.
- the exhaust link mechanism Mle (the intake link mechanism Mli) includes a holder 60 e (60 i) pivotally supported by the cam shaft 50 and swinging about the cam shaft 50, An exhaust saprocker arm 66 e (intake sub rocker arm 66 i) pivotally supported by the holder 60 e (60 i) and driven by the exhaust drive cam 52 (intake drive cam 51) to swing, and an exhaust at one end.
- a connecting link 67 e pivotally connected to the sub-mouther arm 66 e (intake sub-mouth arm 66 i) and at the other end to the exhaust cam 54 (intake cam 53); e (the intake sub-rocker arm 66 i) is pressed against the exhaust drive cam 52 (the intake drive cam 51).
- 60 e (60 i) is a pair of first and second plates 61 e (61 i) and 62 e (62 i) separated in the cam axis direction A 2, and a first plate 61 e (61 i)
- a second plate 62e (62i) is connected at a predetermined interval in the cam axis direction A2, and a connecting member is provided for pivotally supporting the exhaust sub-port arm 66e (the intake sub-rocker arm 66i).
- the connecting member defines a predetermined distance between the two plates 61 e (61 i) and 62 e (62 i) and supports the exhaust sub-opener arm 66 e (the intake sub-rocker arm 66 i).
- the exhaust control link 71 e (intake control link 71 i) of the control mechanism M 3 is pivotally connected to the first plate 61 e (61 i), and the exhaust control link 71 e (intake control The link 71 i) and the first plate 6 le (61 i) are connected so as to be relatively movable at the connecting portions 71e2 (71 ⁇ 2) and 61el (61i l).
- a first plate 61 e (61 i) as a holder-side connecting portion is provided in a hole of a connecting portion 71 e 2 (71 i 2) of an exhaust control link 71 e (an intake control link 71 i) as a control mechanism side connecting portion.
- the connecting pin 61ela (61i la) press-fitted into the hole of the connecting portion 61el (61i l) is inserted so as to be relatively rotatable.
- the second plate 62e (62i) includes a small opening of the intake valve 22 and the exhaust valve 23 in the compression stroke at the start of the internal combustion engine E to reduce the compression pressure and facilitate the start.
- the decompression cam 62el (62il) (see FIGS. 8A, 8B, 12A, and 12B) is formed.
- the second plate 62e is provided with a detected part 62e2 which is detected by the detecting part 94a of the swing position detecting means 94 (see FIGS. 14 (A) and 14 (B)).
- the detected portion 62e2 is configured by a tooth portion that engages in the swing direction of the second plate 62e by mating with the tooth portion forming the detection portion 94a.
- the second plate 61i is also provided with a portion 62i2 corresponding to the detected portion 62e2.
- the collar 63e (63i) has a first panel holding portion 76 for holding one end of a control spring 68 made of a compression coil panel, and a movable panel holding portion 78 for holding one end of a pressing panel 55 made of a compression coil panel.
- the spring holding portions 76 and 78 are arranged adjacent to the fulcrum portion 66ea (66ia) of the exhaust sub-rocker arm 66e (the intake sub-rocker arm 66i) in the cam axis direction A2, and the collar 63e (63i). ) Are arranged at intervals in the circumferential direction (see Fig. 6).
- the rocker arm 66 i) is formed at a position distant from the swing center line L 3e (L 3i).
- the convex portion 63el (63i l) and the hole 62e4 (62i4) are located around the swing center line L 3 e (L 3i) between the second plate 62 e (62 i) and the collar 63 e (63 i). It constitutes an engaging portion for preventing relative rotation of.
- FIG. 5 FIG. 6, FIG. 8 (A), FIG. 8 (B), FIG. 9 (A) to FIG. 9 (D), FIG. 12 (A), and FIG.
- the camshaft direction A2 between the first and second plates 61e (61i) and 62e (62i) together with the exhaust cam ⁇ 4 (intake cam 53) and the exhaust drive cam 52 (intake drive cam 51).
- the exhaust sub-rocker arm 66 e (the intake sub-rocker arm 66 i), which is disposed in the exhaust drive cam 52 (the intake drive cam 51), and is pivotally supported by a collar 63e (63i) at a fulcrum 66ea (66ia) at one end, and a connecting link 67e (67i) at a connecting portion 66ec (66ic) at the other end. Is pivotally supported by a connecting pin 72 fixed to one end of the connector. Therefore, the exhaust sub-rocker arm 66 e (the intake sub-rocker arm 66 i) pivots around the collar 63 e (63 i) by rotating the exhaust drive cam 52 (the intake drive cam 51) with the cam shaft 50. Rocks.
- the exhaust cam 54 (the intake cam 53) pivotally supported by the connection pin 73 fixed to the other end of the connection link 67e (67i) is supported by the camshaft 50 via the bearing 44 so that the camshaft is supported. It is composed of a swing cam that can swing about 50, and a cam surface is formed on a part of its outer peripheral surface. The cam surface keeps the exhaust valve 23 (intake valve 22) closed.
- Base circle portion 5 4 a (53 a) has a cross-sectional shape radius from the rotational center line L 2 is formed of a predetermined arc, the cam crest portion 54 b (53 b), from the center of rotation f Izumi L 2 Has a cross-sectional shape that increases the radius of the camshaft 50 in the anti-rotation direction R 2 (rotation direction R 1). Therefore, in the cam crest 54b (53b) of the exhaust cam 54 (intake cam 53), the lift amount of the exhaust valve 23 (intake valve 22) gradually increases in the counter-rotation direction R2 (rotation direction R1). It has a shape.
- the exhaust cam 54 (intake cam 53) is driven by the drive mechanism M2 transmitted through the control mechanism M3 to move the camshaft 50 around the cam shaft 50 with the same amount of movement together with the exhaust link mechanism Mle (intake link mechanism Mli). While being swung by the exhaust drive cam 52 (intake drive cam 51), the swing is centered on the cam shaft 50 by the exhaust sub rocker arm 66e (intake sub port arm 66i). Then, the exhaust cam 54 (the intake cam 53) swinging with respect to the camshaft 50 swings the exhaust main rocker arm 42 (the intake main rocker arm 41) to open and close the exhaust valve 23 (the intake valve 22). .
- the exhaust cam 54 (the intake cam 53) is sequentially transmitted through the holder 60e (60i), the exhaust sub-rock arm 66e (the intake sub-rocker arm 66i), and the connecting link 67e (67i).
- the exhaust drive cam 52 (intake drive) which is oscillated by the drive force of the drive mechanism M2 and sequentially transmitted through the exhaust sub-rocker arm 66e (intake sub-rocker arm 66i) and the connecting link 67e (67i). It is swung by the driving force of the cam 51).
- the control spring 68 that generates a panel force that presses the rollers 66eb (66ib) of the air sub-rocker arm 66e (the intake sub-rocker arm 66i) against the exhaust drive cam 52 (the intake drive cam 51) has a collar 63e (63i) and an exhaust. is disposed between the cam 54, which is stretchable in the circumferential direction of the cam shaft 50 corresponding to a swing of the exhaust supplicant rocker arm 66 e (intake sub rocker arm 6 6 i).
- control panel 68 The other end of the control panel 68, one end of which is held by the first panel holding portion 76, is connected to a second spring holding portion 77 provided on a shelf-shaped protrusion integrally formed with the exhaust cam 54 (intake cam 53). Is held.
- a pressing spring 55 that constantly acts on the exhaust link mechanism Mle (the intake link mechanism Mli) to apply a torque directed in one direction in the swing direction of the pressing spring 55 has one end of the holder 60 e (60 i). The other end is held by the movable-side panel holder 78, and the other end is held by the fixed-side panel holder 79 provided on the camshaft holder 29, which is a fixed member fixed to the cylinder head 12.
- the spring of the pressing spring 55 that presses the exhaust link mechanism Mle (the intake link mechanism Mli) against the cylinder 11 acts directly on the holder 60 e (60 i) to move the holder 60 e (60 i) toward the cylinder 11.
- the torque applied to the holder 60e (60i) by the spring force is directed to the one direction.
- the exhaust cam 54 the intake cam 53
- the one direction acts on the exhaust cam 54 (the intake cam 53) from the exhaust valve 23 (the intake valve 22).
- the reaction force is set to the same direction as the torque acting on the exhaust force 54 (the intake cam 53).
- connection portion 71e2 (71i2) and 61el (61i l) where there is a slight gap due to pivotal connection one connection portion 61el (61i l) is connected to the other connection portion 71e2 (71i2).
- first plate 61 e (61 i) is swung by the exhaust control link 71 e (intake control link 71 i), the connecting portion 71e2 (7U2) and the connecting portion 61el (61 il), the effect of the clearance (play) is eliminated, and the movement of the exhaust control link 71e (the intake control link 71i) is transmitted to the holder 60e (60i) with high accuracy.
- the control mechanism M3 includes a cylindrical control shaft 70 as a control member driven by the drive mechanism M2, and a control mechanism M3.
- Control links 71 i and 71 e for transmitting the movement of the control shaft 70 to the link mechanisms Mli and Mle to swing the link mechanisms Mli and Mle about the camshaft 50 are provided.
- the control shaft 70 is movable in a direction parallel to the cylinder axis / line L1 and thus includes a rotation centerline L2 of the camshaft 50 and a reference plane HO parallel to the cylinder axis L1. It can move in parallel directions.
- the control links 71 i and 71 e include an intake control link 71 i and an exhaust control link 71 e.
- the intake control link 71i is pivotally connected to the control shaft 70 at a connection 71il as a first intake connection, and is connected to a first plate 61i of the intake link mechanism Mli at a connection 71i2 as a second intake connection. It is pivotally connected to the connecting part 61il.
- the exhaust control link 71e is pivotally connected to the control shaft 70 at a connecting portion 71el as a first exhaust connecting portion, and is connected to the first plate 61e of the exhaust link mechanism Mle at a connecting portion 71e2 as a second exhaust connecting portion. Connected to 61 e 1.
- the connecting portion 71 i 1 of the intake control link 71 i and the connecting portion 70 a of the control shaft 70 are respectively connected to one connecting pin 71 e 3 which is press-fitted and fixed in a hole of the connecting portion 71 el of the exhaust control link 71 e. It has a hole rotatably inserted and is pivotally supported by the connecting pin 71e3.
- the bifurcated connecting portions 71i2 and 71e2 are relatively rotatable with the connecting pins 61ila and 61ela of the connecting portions 71i2 and 71e2, respectively. And is pivotally supported by connecting pins 61ila and 61ela.
- the panel force of the pressing panel is such that the connecting portion 71el (71il) is constantly pressed against the connecting portion 70a at each of the connecting portions 71el (71il) and 70a where there is a slight gap due to pivotal connection.
- the effect of the gap (play) between the (71il) and the connecting portion 70a is eliminated, and the motion of the control shaft 70 is transmitted to the exhaust control link 71e (the intake control link 71i) with high accuracy.
- FIG. 7 the control axis The central axis 70, ⁇ L6, is parallel to the cylinder axis L 1, and is deviated toward the exhaust side by an amount e from the reference plane H 0.
- the intake side is a side where the intake valve 22 is arranged with respect to the reference plane HO
- the exhaust side is a side where the exhaust valve 23 is arranged with respect to the reference plane HO.
- the link length of the intake control link 71i which is the distance between the two pivot centerlines L4i and L5i
- the link length of the exhaust control link 71e which is the distance between the two pivot centerlines L4e and L5e. It is set longer than
- the two pivoting center lines L5i and L5e are arranged around the camshaft 50 on the same cylindrical surface from the rotation centerline L2, at the same distance from the rotation centerline L2, and at the same time as the rotation center and line.
- the control axis 70 and the pivotal center lines L4i, L4e are located on the second orthogonal plane H2 that includes L2 and is orthogonal to the reference plane H0. Further, the pivot center line L5i is located closer to the second orthogonal plane H2 than the pivot center line L5e.
- the pivot center lines L4i and L4e which are the common pivot center lines, are deviated toward the exhaust side by a predetermined deviation amount e with respect to the reference plane HO, or the link length of the intake control link 71i. Is set to be longer than the link length of the exhaust control link 71 e, so that, relative to the displacement of the control shaft 70 driven by the drive mechanism M 2, the pivot center line L 5i around the cam shaft 50.
- the swing amount of the intake link mechanism Mli and the intake cam 53 are larger than the swing amount of the exhaust link mechanism Mle and the exhaust cam 54.
- the driving mechanism M 2 for driving the control shaft 70 transmits the reverse rotation of the electric motor 80 attached to the head cover 13 and the rotation of the electric motor 80 to the control shaft 70. And a transmission mechanism M4. Then, the control mechanism M 3 and the drive mechanism M 2 are arranged on the opposite side to the cylinder 11 and the combustion chamber 16 with respect to the second orthogonal plane H 2.
- the electric motor 80 has a cylindrical main body 80a that houses a heat generating portion such as a coil portion and has a central axis parallel to the cylinder axis L1, and an output shaft 80b extending parallel to the cylinder axis L1. Is provided.
- the electric motor 80 is disposed radially outward of the valve chamber 25 with respect to the cylinder head 12 and the head cover 13.
- a transmission chamber 59 is disposed on the left side of the first orthogonal plane HI, and is disposed on the first orthogonal plane HI.
- the main body 80a and the spark plug 19 are arranged on the other side, on the right side.
- a through-hole 80a2 is formed in a mounting portion 80al that is radially protruded from the head cover 13 and coupled to the mounting portion 13a formed in an eaves shape, and the output shaft 80b is connected to the through-shade. Then, it penetrates through 80a2, protrudes outside the main body 80a, and extends into the valve operating chamber 25.
- the main body 80a is disposed at a position where the whole of the main body 80a is covered by the mounting portion when viewed in the cylinder axis direction A1 from the head cover 13 side or when viewed from the front of the head cover 13 (see FIG. 10).
- the transmission mechanism M 4 disposed between the camshaft holder 29 and the head cover 13 in the cylinder axis, the direction A 1 is Reduction gear 81 that engages with a drive gear 80bl formed on an output shaft 80b that extends through the head cover 13 into the valve operating chamber 25, and a camshaft holder 29 that engages with the reduction gear 81 and attaches to the cylinder head 12
- an output gear 82 rotatably supported via The reduction gear 81 is rotatably supported by a support shaft 84 that is supported by the head cover 13 and a cover 83 that covers the opening 13 c formed in the head cover 13, and is a large gear 81 a that is combined with the drive gear 80bl.
- the output gear 82 has a cylindrical boss portion 82 a rotatably supported via a bearing 89 on a holding cylinder 88 connected to the camshaft holder 29 by bolts.
- the output gear 82 and the control shaft 70 are drivingly connected via a feed screw mechanism as a motion conversion mechanism that converts the rotational motion of the output gear 82 into a linear reciprocating motion of the control shaft 70 parallel to the cylinder axis L1. Is done.
- the feed screw mechanism includes a female screw portion 82b formed of a trapezoidal screw formed on the inner peripheral surface of the boss portion 82a, and a trapezoidal screw formed on the outer peripheral surface of the control shaft 70 and screwed with the female screw portion 82b.
- Male thread portion 70 b comprising
- the control shaft 70 is slidably fitted on the outer periphery of a guide shaft 90 fixed to the boss portion 82a, and is formed on the cam shaft holder 29 while being guided in the moving direction by the inner shaft 90. Through the formed through hole 91 (see also FIG. 7), it can advance and retract with respect to the camshaft 50 in the cylinder axis direction A1.
- the electric motor 80 is controlled by an electronic control unit (hereinafter referred to as ECU) 92. Therefore, the EC U92 requires the output demand detection In addition to the means 95 and the engine temperature detecting means 96, detection signals from start detecting means for detecting the start of the internal combustion engine E constituting the operating state detecting means, engine rotational speed detecting means for detecting the engine rotational speed, and the like, Further, a swing position detecting means 94 for detecting a swing position, which is a swing angle of the exhaust link mechanism Mle 60 e and thus the exhaust cam 54 with respect to the force shaft 50, which is swung by the electric motor 80. (For example, composed of a potentiometer).
- the storage device of the ECU 92 stores a valve control map in which the swing position is set using the operation amount D as a parameter.
- the EC U 92 calculates the operation amount D detected by the required output amount detection means 95 and the actual swing position of the holder 60 e of the exhaust link mechanism Mli detected by the swing position detection means 94, that is, the exhaust cam.
- the electric motor 80 is controlled in accordance with the actual swing position of 54 so that the swing position is set by the valve control map. Therefore, when the position of the control shaft 70 driven by the electric motor 80 is changed, the relative rotation of the exhaust link mechanism Mle (the intake link mechanism Mli) and the air cam 54 (the intake cam 53) with respect to the cam shaft 50 is changed.
- the swing position which is the position, is changed according to the manipulated variable D, and the valve operating characteristics of the exhaust valve 23 (intake valve 22) are controlled according to the operating state of the internal combustion engine E.
- the intake valve and the exhaust valve have valve operating characteristics Ki and Ke that are controlled by a pulp characteristic variable mechanism M that changes the opening / closing timing and the maximum lift, respectively.
- Maximum valve operation characteristics Open / close operation with any intermediate valve operation characteristics between maximum valve operation characteristics Kimax, Kemax and minimum valve operation characteristics Kimin, Kemin, with Kitnax, Kemax and minimum pulp operation characteristics Kimin, Kemin as boundary values Is done. Therefore, as for the intake valve 22, as the opening timing is continuously retarded, the closing timing is continuously advanced, the valve opening period is continuously shortened, and the maximum lift is obtained.
- the rotation angle of the camshaft 50 (or the crank angle which is the rotation position of the crankshaft 15) is continuously retarded, and the maximum lift is continuously reduced.
- the closing timing is continuously advanced and the valve opening period is continuously extended. Short Further, the rotation angle of the cam shaft 50 at which the maximum lift is obtained is continuously advanced, and the maximum lift is continuously reduced.
- FIGS. 12 (A) and 12 (B) the control shaft 70 and the intake control link 71i driven by the drive mechanism M2 are shown in FIGS. 12 (A) and (B).
- the opening timing of the intake valve 22 becomes the most advanced position S iotnax
- the closing timing becomes the most retarded position ⁇ icmax
- both the valve opening period and the maximum lift amount The maximum valve operation dynamic characteristic Kimax that maximizes is obtained, and at the same time, the opening timing of the exhaust valve 23 becomes the most advanced position 6 e 0raax , the closing timing becomes the most retarded position S ecmax, and the opening thereof.
- the maximum valve operation characteristic Keraax that maximizes both the period and the maximum lift is obtained.
- FIGS. 12 (A), 12 (B), 13 (A), and 13 (B) when the exhaust valve 23 (the intake valve 22) is closed,
- the states of the exhaust link mechanism Mle (the intake link mechanism Mli) and the exhaust main rocker arm 42 (the intake main port cam 41) are shown by solid and broken lines, and the exhaust valve 23 (the intake valve 22) is opened with the maximum lift.
- the outline of the state of the exhaust link mechanism Mle (the intake link mechanism Mli) and the exhaust main rocking arm 42 (the intake main rocker arm 41) at the time of the opening is shown by a two-dot chain line.
- the electric motor is used to shift from the state where the maximum valve operating characteristics Kimax and Kemax are obtained by the valve characteristic variable mechanism M to the state where the minimum valve operating characteristics Kimin and emin are obtained.
- 80 drives the output gear 72 to rotate, and the control shaft 70 advances toward the camshaft 50 by the feed screw mechanism.
- the control shaft 70 swings the intake link mechanism Mli and the intake cam 53 via the intake control link 71i in the rotation direction R1 about the camshaft 50.
- the exhaust link mechanism Mle and the exhaust cam 54 are rotated about the camshaft 50 in the anti-rotation direction R2 via the exhaust control link 71e.
- the electric motor 80 drives the output gear 82 to rotate in the opposite direction, and the control shaft 70 is moved from the cam shaft 50 by the feed screw mechanism.
- the control shaft 70 swings the intake link mechanism Mli and the intake cam 53 through the intake control link 71 i in the anti-rotation direction R2 about the cam shaft 50, and at the same time, controls the exhaust control link 71 e.
- the exhaust link mechanism Mle and the exhaust cam 54 are oscillated in the rotation direction R1 about the cam shaft 50 via.
- the maximum valve operation characteristic Kemax (Kimax) and the minimum valve operation characteristic Kemin (Kimin) of the exhaust valve 23 (intake valve 22) are determined.
- the opening timing, closing timing, valve opening period and the maximum lift amount in the range of the opening timing, closing timing, valve opening period and maximum lift amount are set. .
- the intake valve and the exhaust valve are each opened and closed with auxiliary operation characteristics by a valve characteristic variable mechanism M in addition to the basic operation characteristics. Specifically, the fact that the decompression operation characteristic is obtained as the auxiliary operation characteristic will be described with reference to FIGS. 14 (A) and (B).
- the electric motor 80 drives the output gear 82 to rotate in the reverse direction, and the control shaft 70 moves backward beyond the first position and away from the camshaft 50 at the position where the control shaft 70 moves backward. Occupies a decompression location.
- the overlap period Pa and the non-overlap period P of the intake valve 22 and the exhaust valve 23 near the intake top dead center are shown.
- b changes.
- the maximum valve operation characteristics K imax and Kemax provide the maximum overlap period P ax
- the minimum valve operation characteristics K imin and Kemin provide the maximum non-overlap period Pbx
- the intermediate valve operation between the two valve operation characteristics As for the characteristics, as the maximum valve operation characteristic Kimax, Kemax shifts to the minimum valve operation characteristic Kimmin, Kemin, the overlap period Pa decreases and becomes 0 (zero), and the non-overlap period Pb becomes 0 (zero).
- the maximum valve operation characteristic Kimax Kemax shifts to the minimum valve operation characteristic Kimmin, Kemin
- the overlap period Pa decreases and becomes 0 (zero)
- the non-overlap period Pb becomes 0 (zero).
- the overlap period Pa is the crank angle between the closing timing of the exhaust valve 23 and the opening timing of the intake valve 22 when both the exhaust valve 23 and the intake valve 22 are open near the intake top dead center.
- the non-overlap period Pb the exhaust valve 23 and the intake valve 22 are both closed near the intake top dead center, and the exhaust valve 23 is closed. It is a range of the crank angle (or the rotation angle of the cam angle) between the timing and the opening timing of the intake valve 22.
- the EC U 92 detects the temperature regardless of the manipulated variable D in the entire load range of the internal combustion engine E, as shown in FIG. 4 (C).
- the electric control is performed based on the valve control map. Controls motor 80.
- the valve characteristic variable mechanism M is configured so that the intake valve 22 and the exhaust valve 23 are opened and closed with the maximum valve operation characteristics Kimax and Kemax, so that the non-overlap period Pb The valve operating characteristics are controlled so that no is formed.
- the valve characteristic variable mechanism M operates the throttle valve over the entire load region.
- the overlap period Pa or the non-overlap period Pb should be controlled according to the manipulated variable D to control the engine output. Control operating characteristics. Referring to FIGS. 4 (A) to 4 (D) and FIG. 11, in the first load region F a, the overlap period P a decreases as the required amount increases in the first load region F a.
- the non-overlap period Pb increases, and the valve operation characteristic is controlled so that the maximum non-overlap period Pbx is obtained before the predetermined load Da is reached.
- the non-overlapping period P b decreases from the maximum non-overlapping period P bx to 0 (zero), and then the overlap period Pa increases and the maximum load ( (Maximum manipulated variable)
- the valve operating characteristics are controlled so that the maximum overlap period Pax is obtained with Db.
- the variable valve characteristic mechanism M controls the overlap period Pa and the non-overlap period Pb by changing the opening / closing time of the intake valve 22 and the opening / closing time of the exhaust valve 23. This controls the internal EGR rate N.
- the internal EGR rate N indicates the amount of fresh air in the combustion chamber 16 and the amount and ratio of burned gas remaining in the combustion chamber 16 and is defined by the following equation.
- N Vce / (Vc-Vca)
- V c Cylinder volume at bottom dead center of intake
- Vca Cylinder volume when the intake valve is at the effective lift
- Vce Cylinder volume when the exhaust valve is at the effective lift
- Effective lift amount of intake valve Lift amount of intake valve when fresh air substantially starts flowing from the intake port to the combustion chamber via the intake valve that is open.
- Effective lift amount of the exhaust valve Lift amount of the exhaust valve when the burned gas substantially stops flowing from the combustion chamber to the exhaust port via the exhaust valve in the open state.
- the internal EGR rate N is determined by the minimum internal EGR rate N n obtained by the maximum overlap period P ax at the maximum valve operation characteristics Kimax and Kemax and the maximum non-overlap period by the minimum valve operation characteristics Kimin and Kemin.
- the minimum internal EGR ratio N It increases continuously from n to the maximum internal EGR rate N x.
- valve characteristic variable mechanism M controls the overlap period Pa or the non-overlap period Pb according to the manipulated variable D, and according to the internal EGR rate N or The engine output is controlled by the internal EGR amount specified by the internal EGR rate N. More specifically, after the warm-up, the valve characteristic variable mechanism M changes the internal EGR rate N in the first load region Fa from the minimum internal EGR rate Nn at no load to the manipulated variable D as the manipulated variable D increases.
- the valve operating characteristics of the intake valve 22 and the exhaust valve 23 are controlled so that the maximum internal EGR rate Nx is obtained before the load E reaches the predetermined load Da, and in the second load region Fb, the internal EGR rate N However, the valve operation of the intake valve 22 and the exhaust valve 23 is reduced so that the minimum internal EGR rate Nn is obtained at the maximum load D from the maximum internal EGR rate Nx at the predetermined load D a and decreases as the manipulated variable D increases. Control characteristics.
- the effective opening timing, when the intake valve 22 opens with the effective lift amount, and the effective lift amount, when the exhaust valve 23 opens, with the effective lift amount By using the effective closing time, which is the time when the valve is opened, the overlap period Pa and the non-overlap period Pb can be represented by the effective overlap period Pae and the effective non-overlap period Pbe.
- the effective lift amounts of the intake valve 22 and the exhaust valve 23 have the same value.
- valve characteristic variable mechanism M operates the pulp of the intake valve 22 and the exhaust valve 23 so that the effective overlap period Pae and the effective non-overlap period Pbe are fixed to 0 (zero) over the entire load range during warm-up.
- the effective non-overlap period Pbe force increases as the manipulated variable D increases from 0 (zero) at no load to the maximum value at the given load Da
- the valve operation characteristic is controlled so that the effective non-overlap period pbe increases from the maximum value to 0 (at the maximum load at which the operation amount D becomes the maximum value as the operation amount D increases in the second load area Fb).
- the rotation angle (the crank angle) of the camshaft 50 at which both the effective overlap period Pae and the effective non-overlap period Pbe become 0 (zero) is the intake top dead center.
- the throttle control mechanism T controls the opening of the throttle valve 30 so that the opening increases with an increase in the manipulated variable D over the entire load range of the internal combustion engine E, and changes the valve characteristics.
- the mechanism M controls the bar / rev operation characteristics of the intake valve 22 and the exhaust valve 23 so that the non-overlap period Pb is not formed in the entire load region, and controls the internal EGR rate N within the control range of the internal EGR rate N.
- the internal EGR rate ⁇ is calculated when the non-overlapping period Pb is formed because the non-overlapping period Pb is not formed by the valve characteristic variable mechanism M.
- the internal EGR rate N Since control is performed so that it is minimized in the control range, the flammability is improved and the combustion temperature is also increased. In addition, the warming-up of the internal combustion engine is promoted, and the increase in the combustion temperature promotes the warming-up of the catalyst device, which is the exhaust gas purification device provided in the exhaust device. And the exhaust gas purification performance is improved.
- the throttle control mechanism T is throttled in the first load range Fa so that the throttle opening is fully opened from the idling opening to the predetermined load Da as the manipulated variable D increases.
- the throttle valve 30 is controlled to fully open in the second load area Fb while controlling the opening degree of the torval valve 30, and the valve characteristic variable mechanism M controls the overlap period P according to the manipulated variable D in the entire load area. a or the non-overlap period Pb so that the engine output is controlled by the partial EGR ratio N and the maximum internal EGR ratio NX by the maximum non-overlap period Pbx is obtained at a given load Da.
- the bombing loss is further reduced in the entire load range, particularly in the low load range F1, and the fuel efficiency is improved.
- the engine output is controlled at the internal EGR rate N by controlling the overlap period Pa and the non-overlap period Pb so that the engine output according to the manipulated variable D is obtained, so that the pumping loss is reduced.
- the internal EGR rate N becomes the maximum at the specified load Da, so the pumping loss and NOX occur in the low load region F1 near the specified load Da. The volume will be greatly reduced, and the cost performance and exhaust purification performance will be improved.
- the valve characteristic variable mechanism M in the first load region Fa, the internal EGR rate N increases from the minimum internal EGR rate Nn at no load as the operation amount D increases. Then, the valve operating characteristics of the intake valve 22 and the exhaust valve 23 are controlled so that the maximum internal EGR rate Nx is obtained at the predetermined load Da, and in the second load region Fb, the internal EGR rate N becomes the predetermined load. From the maximum internal EGR ratio N x at D a, the valve operation of the intake valve 22 and the exhaust valve 23 decreases so that the minimum internal EGR ratio N n is obtained at the maximum load D b, decreasing with an increase in the manipulated variable D. Control characteristics.
- the internal EGR ratio N is increased so as to suppress the flow of fresh air into the combustion chamber 16 due to the large opening of the throttle valve 30, so that the pumping loss is reduced.
- the manipulated variable D increases, the non-overlap period Pb decreases and the internal EGR rate N decreases in the second load area Fb, and the NOx is supplied to the combustion chamber 16.
- the internal EGR rate N increases as the load approaches the predetermined load D a, which reduces the amount of bombing loss and the amount of NOX generated, thereby improving fuel efficiency and exhaust purification performance.
- the high load area F3 a large engine output is obtained, and the required engine output according to the required amount is secured.
- variable valve characteristic mechanism M obtains the maximum internal EGR ratio Nx or the maximum non-overlap period Pbx and the maximum effective non-overlap period Pbex in the first load region Fa in a load region smaller than the predetermined load Da.
- the non-repeat characteristic variable mechanism M is configured such that the overlap period Pa decreases, the non-overlap period Pb increases, and the effective overlap period Pae and the effective non-overlap Pbe are all 0 (zero).
- the valve operation characteristics are controlled so that the maximum amount of lift of the intake valve 22 decreases.
- the non-overlap period Pb is small, when the effective non-overlap period Pbe is small, or when the internal EGR ratio N is small, the maximum lift of the intake valve 22 is large, so that the bombing loss decreases.
- variable valve characteristic mechanism M starts from a state where the overlap period Pa decreases, the non-overlap period Pb increases, the effective overlap period Pae and the effective non-overlap period Pbe are all 0 (zero).
- the overlap period Pa is large by controlling the valve operation characteristics so that the maximum lift of the exhaust valve 23 decreases as the effective non-overlap period Pbe of the valve increases or the internal EGR ratio N increases
- the non-overlap period Pb is small, when the effective non-overlap period Pbe is small, or when the internal EGR ratio N is small, the maximum lift of the exhaust valve 23 is large, so that the bombing loss is reduced.
- the valve characteristic variable mechanism M must control the valve operation characteristics so that the effective overlap period Pae and the effective non-overlap period Pbe become 0 at the maximum overlap period Pax or the minimum internal EGR rate Nn.
- the control range of the internal EGR rate N the outflow of burned gas from the combustion chamber 16 substantially stops, and the flow of fresh air into the combustion chamber 16 substantially starts. Since the control of the EGR rate N is started, the control accuracy of the internal EGR rate N is increased, and the control range can be increased.Therefore, the control of the internal EGR rate N or the control of the effective non-overlap period P be Control accuracy of the engine output can be improved.
- the control mechanism M3 operates in the direction in which the internal EGR rate N increases due to the decrease in the overlap period Pa and the addition of the non-overlap period Pb or the effective non-overlap period Pbe.
- the drive mechanism M 2 is controlled so that the amount of retard of the opening timing of the intake valve 22 by the intake link mechanism Mli is greater than the amount of advance of the close timing of the exhaust valve 23 by the exhaust link mechanism Mle.
- variable valve characteristic mechanism M reduces the overlap period Pa in the direction of increasing the internal EGR rate N and increases the non-overlap period Pb Or when the effective non-overlap period Pbe is increased, the amount of retardation of the opening timing of the intake valve 22 becomes larger than the amount of advancement of the closing timing of the exhaust valve 23, so that the closing timing of the exhaust valve 23 is advanced.
- the intake valve 22 is in a state where the pressure in the combustion chamber 16 is lower than when the retard amount when the intake valve 22 is opened is equal to or less than the advance amount when the exhaust valve 23 is closed. Since the opening of the valve is started at the same time, the return of the intake air is prevented or suppressed.
- the pivot center line L4i and the pivot center line L4e deviate toward the exhaust side with respect to the reference plane HO and are disposed parallel to the rotation center line L2, and the pivot center line L5i is disposed on the exhaust side. Since the pivot center line L5e is arranged on the intake side, when the control shaft 70 moves, the intake link 4 and several Mli swing around the camshaft 50 with a larger swing amount than the exhaust link mechanism Mle. And the amount of retardation of the opening timing of the intake valve 22 is greater than the amount of advancement of the closing timing of the exhaust valve 23.
- control shaft 70 of the control mechanism M3 is shared by the intake link mechanism Mli and the exhaust link mechanism Mle, and the pivot center line L4i, the pivot center
- the variable valve characteristic mechanism M is downsized and its structure is simplified.
- the pivot center line L4i and the pivot center line L4e are arranged parallel to the rotation center line L2, the pivot center line L5i is arranged on the exhaust side, and the pivot center line L5e is arranged on the intake side
- the link length of the intake control link 71 i is longer than the link length of the exhaust control link 71 e, so that when the control shaft 70 moves, the cam has a larger swing amount than the intake link mechanism Mli force exhaust link mechanism Mle.
- the pivot center line L5i and the pivot center line L5e are distributed and arranged on both sides of the reference plane HO, and the intake control link 71 Since the link length of i is longer than the link length of exhaust control link 71 e, The variable characteristic mechanism is downsized and its structure is simplified.
- variable valve characteristic mechanism M is further reduced in size, and its structure is further simplified.
- the exhaust link mechanism Mle (intake link mechanism Mli) is driven by the drive mechanism M2 in which the exhaust link mechanism Mle (intake link mechanism Mli) is driven.
- the control shaft 70 exhaust control link 7 1 e for transmitting the motion of (intake air control link 71 i) that, pivoted around which swings around a rotation center line L 2 of the cam shaft 50 Since the exhaust pivot portion (intake pivot portion) having a line is provided, the distance between the pivot center line of the intake pivot portion and the rotation center line L2 is determined by the pivot center of the exhaust pivot portion.
- the control axis 70 and And the exhaust control link 71 e (the intake control link 71 i) is driven by the drive mechanism M 2, the intake link mechanism Mli is moved by the exhaust link mechanism Mle from the exhaust cam 54 oscillated about the cam shaft 50.
- the intake cam 53 may swing about the cam shaft 50 with a large swing amount.
- the intake pivoting part is constituted by a connecting part 61il of the first plate 61i, a fulcrum part 66ia of the intake sub-mouth arm 66i and a supporting part 63i2 (see FIG. 6) of the collar 63i. Be composed.
- the pivot center lines of the intake pivot portions are a pivot center line L5i and a swing center line L3i.
- the exhaust pivoting portion is composed of a connecting portion 61el of the first plate 61e, a fulcrum portion 66ea of the intake sub-rocker arm 66e, and a supporting portion 63e2 of the collar 63e (see FIG. 6). Is done.
- the pivot center lines of the exhaust pivot portions are a pivot center line L5e and a swing center line L3e. Then, the distance between the pivot center line L5i and the rotation center line L2 is set shorter than the distance between the pivot center line L5e and the rotation center line L2, or the swing center line. The distance between L3i and the rotation center line L2 is set shorter than the distance between the swing center line L3e and the rotation center line L2. .
- the intake pivoting section of the intake link mechanism Mli is pivoted by the exhaust pivoting section of the exhaust link mechanism Mle.
- the control center M 3 has the intake cam 53 and the exhaust cam 53 because the pivot center lines L 5i and L 3i are located closer to the rotation center line L 2 of the cam shaft 50 than the moving center lines L 5e and L 3e.
- the piston 54 is swung about the cam shaft 50 via the intake link mechanism Mli and the exhaust link mechanism Mle so that the swing amount of the intake cam 53 becomes larger than the swing amount of the exhaust cam 54.
- the predetermined load Da may be a load in the medium load region F2.
- the fuel supply device may be a fuel injection valve that injects fuel directly into the combustion chamber.
- the internal combustion engine may be a multi-cylinder internal combustion engine. In addition, one cylinder has multiple intake valves
- the engine may be an internal combustion engine provided with one or more exhaust valves, or an internal combustion engine provided with a plurality of exhaust valves and one or more intake valves in one cylinder.
- the opening of the throttle valve 30 may be almost fully opened, and in the maximum overlap period Pax or the minimum internal EGR ratio Nn, the effective overlap period P ae and the effective non-overlap period Pbe may be substantially zero, and the internal EGR ratio N may be substantially minimum over the entire load region during warm-up.
- “almost” means that when the throttle valve 30 is fully opened, the effective overlap period Pae and the effective non-overlap period Pbe are 0, and the internal EGR ratio N is It means the range where there is no significant difference in the effect compared to when it is the minimum.
- variable valve characteristic mechanism is an internal E G
- the intake valve When controlling the overlap period and the non-overlap period in the direction in which the R ratio increases, the intake valve starts opening with the combustion chamber pressure being low. For this reason, backflow of intake air is prevented or suppressed.
- control members of the control mechanism are shared between the intake interlock mechanism and the exhaust interlock mechanism, and the pivot center line of the first intake connection, the pivot center line of the first exhaust connection, and the second intake connection Due to the arrangement of the pivot center line of the second exhaust connection portion and the pivot center line of the second exhaust connection portion with respect to the reference plane, the retard amount of the opening timing of the intake valve is larger than the advance amount of the closing timing of the exhaust valve.
- the variable valve characteristic mechanism for obtaining the desired valve operating characteristics is downsized and its structure is simplified.
- the pivot center line of the second intake connection part and the pivot center line force of the second exhaust connection part Since the intake control link is longer than the exhaust control link, the amount of delay in the opening timing of the intake valve is greater than the amount of advance in the timing of closing the exhaust valve.
- the variable valve characteristic mechanism for obtaining the desired valve operating characteristics is downsized, and its structure is simplified.
- the distance between the pivot centerline of the intake pivoting part of the intake interlocking mechanism and the rotation centerline of the camshaft is the distance between the pivoting centerline of the exhaust pivoting part of the exhaust interlocking mechanism and the rotation centerline of the force axis. Since the distance is shorter than the distance, the structure of the variable valve characteristic mechanism for obtaining the valve operating characteristic in which the retard amount of the opening timing of the intake valve is larger than the advance amount of the closing timing of the exhaust valve is simplified. .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004012498A JP4274425B2 (ja) | 2004-01-20 | 2004-01-20 | 内燃機関の動弁装置 |
JP2004-012498 | 2004-01-20 |
Publications (1)
Publication Number | Publication Date |
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WO2005068789A1 true WO2005068789A1 (ja) | 2005-07-28 |
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ID=34792382
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2005/001033 WO2005068789A1 (ja) | 2004-01-20 | 2005-01-20 | 内燃機関の動弁装置 |
Country Status (7)
Country | Link |
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JP (1) | JP4274425B2 (ja) |
KR (1) | KR100582654B1 (ja) |
CN (1) | CN100371573C (ja) |
AR (1) | AR047427A1 (ja) |
MY (1) | MY139856A (ja) |
TW (1) | TW200530490A (ja) |
WO (1) | WO2005068789A1 (ja) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JP4555803B2 (ja) * | 2005-08-15 | 2010-10-06 | 本田技研工業株式会社 | 内燃機関の可変動弁装置 |
JP5337065B2 (ja) * | 2010-01-22 | 2013-11-06 | 本田技研工業株式会社 | Egr率推測検知装置 |
JP2012180762A (ja) * | 2011-02-28 | 2012-09-20 | Honda Motor Co Ltd | スロットル制御装置 |
JP2014015879A (ja) * | 2012-07-06 | 2014-01-30 | Suzuki Motor Corp | 車両用エンジンのデコンプレッション装置 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH048807A (ja) * | 1990-04-27 | 1992-01-13 | Suzuki Motor Corp | 4サイクルエンジンの始動補助装置 |
JP2001512546A (ja) * | 1997-02-21 | 2001-08-21 | フェデラル−モウガル テクノロジー リミテッド | 弁用作動機構 |
JP2002276395A (ja) * | 2001-03-23 | 2002-09-25 | Nissan Motor Co Ltd | 内燃機関の吸気装置 |
JP2003269124A (ja) * | 2002-03-15 | 2003-09-25 | Nissan Motor Co Ltd | 内燃機関の可変動弁装置 |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3437330A1 (de) * | 1984-10-11 | 1986-04-24 | M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg | Luftverdichtende, selbstzuendende oder fremdgezuendete viertakt-brennkraftmaschine mit direkter kraftstoff-einspritzung, turboaufladung und lastabhaengiger innerer abgasrueckfuehrung |
SE501437C2 (sv) * | 1993-06-22 | 1995-02-13 | Volvo Ab | Ventilmekanism i en förbränningsmotor |
JP4157649B2 (ja) * | 1999-06-23 | 2008-10-01 | 株式会社日立製作所 | 内燃機関の可変動弁装置 |
-
2004
- 2004-01-20 JP JP2004012498A patent/JP4274425B2/ja not_active Expired - Fee Related
-
2005
- 2005-01-04 TW TW094100116A patent/TW200530490A/zh not_active IP Right Cessation
- 2005-01-17 KR KR1020050004279A patent/KR100582654B1/ko not_active IP Right Cessation
- 2005-01-17 CN CNB200510004441XA patent/CN100371573C/zh not_active Expired - Fee Related
- 2005-01-19 AR ARP050100179A patent/AR047427A1/es active IP Right Grant
- 2005-01-20 WO PCT/JP2005/001033 patent/WO2005068789A1/ja active Application Filing
- 2005-01-20 MY MYPI20050252A patent/MY139856A/en unknown
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH048807A (ja) * | 1990-04-27 | 1992-01-13 | Suzuki Motor Corp | 4サイクルエンジンの始動補助装置 |
JP2001512546A (ja) * | 1997-02-21 | 2001-08-21 | フェデラル−モウガル テクノロジー リミテッド | 弁用作動機構 |
JP2002276395A (ja) * | 2001-03-23 | 2002-09-25 | Nissan Motor Co Ltd | 内燃機関の吸気装置 |
JP2003269124A (ja) * | 2002-03-15 | 2003-09-25 | Nissan Motor Co Ltd | 内燃機関の可変動弁装置 |
Also Published As
Publication number | Publication date |
---|---|
KR100582654B1 (ko) | 2006-05-22 |
KR20050076633A (ko) | 2005-07-26 |
JP4274425B2 (ja) | 2009-06-10 |
TW200530490A (en) | 2005-09-16 |
AR047427A1 (es) | 2006-01-18 |
CN100371573C (zh) | 2008-02-27 |
JP2005207256A (ja) | 2005-08-04 |
MY139856A (en) | 2009-11-30 |
CN1644882A (zh) | 2005-07-27 |
TWI303285B (ja) | 2008-11-21 |
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