WO2006030707A1 - 車両の制御装置 - Google Patents
車両の制御装置 Download PDFInfo
- Publication number
- WO2006030707A1 WO2006030707A1 PCT/JP2005/016604 JP2005016604W WO2006030707A1 WO 2006030707 A1 WO2006030707 A1 WO 2006030707A1 JP 2005016604 W JP2005016604 W JP 2005016604W WO 2006030707 A1 WO2006030707 A1 WO 2006030707A1
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- WO
- WIPO (PCT)
- Prior art keywords
- internal combustion
- valve
- compression ratio
- combustion engine
- deceleration request
- Prior art date
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Classifications
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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
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D41/0005—Controlling intake air during deceleration
-
- 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
- F01L1/185—Overhead end-pivot rocking arms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
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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
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length
-
- 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
- F02D13/0211—Variable control of intake and exhaust valves changing valve lift or valve lift and timing the change of valve timing is caused by the change in valve lift, i.e. both valve lift and timing are functionally related
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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
- F02D13/0276—Actuation of an additional valve for a special application, e.g. for decompression, exhaust gas recirculation or cylinder scavenging
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D15/00—Varying compression ratio
- F02D15/04—Varying compression ratio by alteration of volume of compression space without changing piston stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/021—Introducing corrections for particular conditions exterior to the engine
- F02D41/0215—Introducing corrections for particular conditions exterior to the engine in relation with elements of the transmission
- F02D41/0225—Introducing corrections for particular conditions exterior to the engine in relation with elements of the transmission in relation with the gear ratio or shift lever position
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
- F01L2001/0537—Double overhead camshafts [DOHC]
-
- 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
-
- 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
-
- 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
-
- 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
- F01L2820/04—Sensors
- F01L2820/041—Camshafts position or phase sensors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D2041/001—Controlling intake air for engines with variable valve actuation
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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
-
- 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
- Y02T10/40—Engine management systems
Definitions
- the present invention relates to a vehicle control device that controls a valve lift of an intake / exhaust valve of an internal combustion engine, a cam phase of an intake / exhaust cam, a compression ratio of the internal combustion engine, and the like.
- Patent Document 1 a control device that controls the valve lift of an intake valve and the cam phase of an intake cam.
- the valve lift is controlled to decrease and the cam phase is controlled to retard.
- the engine braking force is sufficiently obtained by increasing the bombing loss.
- the high-speed gear stage is often used at the time of deceleration, and in this case, almost no engine braking force is obtained. As a result, the foot brake is used more frequently and its life may be shortened.
- engine rotational speed the rotational speed of the internal combustion engine
- engine rotational speed the rotational speed of the internal combustion engine
- a tendency that the change in the engine braking force with respect to the change in the engine rotational speed is large is accompanied by a variable lift mechanism. This is particularly noticeable in internal combustion engines. For this reason, a sudden change in the engine braking force at low revolutions can cause a jerky feeling and quickly Tea may be deteriorated.
- the present invention has been made in order to solve the above-described problems, and it is possible to extend the life of the foot brake by obtaining an appropriate engine braking force when the driver requests deceleration.
- a first object is to provide a vehicle control device.
- the speed of the driver is requested to be reduced, if the internal combustion engine speed is relatively low, it is possible to suppress a jerky feeling due to a sudden change in the engine brake force, thereby ensuring good drivability.
- a second object of the present invention is to provide a vehicle control device that can perform the above-mentioned.
- Patent Document 1 Japanese Patent Application Laid-Open No. 2002-89302
- the invention according to claim 1 includes a transmission 90 that changes the power of the internal combustion engine 3 at one of a plurality of predetermined gear ratios according to the intention of the driver.
- a transmission 90 that changes the power of the internal combustion engine 3 at one of a plurality of predetermined gear ratios according to the intention of the driver.
- the valve lift Liftin which is the lift of at least one of the intake valve 4 and the exhaust valve 7 of the internal combustion engine 3, and the intake valve 4 and the exhaust valve 7, respectively.
- a control device 1 for a vehicle V that controls at least one of a cam phase Cai n that is a phase with respect to one crankshaft 3d and a compression ratio Cr of the internal combustion engine 3, and includes a valve lift Liftin, a cam phase Cain, and a compression ratio Cr
- the setting means previously in the embodiment (hereinafter the same in this section) ECU2, FIG. 27, FIG. 28, FIG. 29), and the transmission 90 Shifting Gear ratio detection means for detecting the ratio (ECU2, step 20 in FIG. 20, FIG. 21), deceleration request determination means for determining whether a deceleration request from the driver is generated (ECU2, FIG.
- determining means for determining based on the setting by the setting means according to the value (NGEAR).
- At least one of the valve lift, the cam phase, and the compression ratio is set in advance by the setting means to a value different from each other for each of a plurality of speed ratios.
- the deceleration request determination means determines whether or not the driver has requested deceleration, and when it is determined that the driver has requested deceleration, the valve lift, cam phase, and compression ratio are determined. At least one of these is determined by the determining means based on the setting by the setting means in accordance with the detected gear ratio. Since the valve lift, the cam phase, and the compression ratio are parameters that affect the engine brake force, as described above, at least one of these parameters is set to a different value for each of a plurality of gear ratios.
- the invention according to claim 2 is the control device 1 for the vehicle V according to claim 1, wherein the setting means has a larger engine braking force of the internal combustion engine 3 as the gear ratio of the transmission 90 is larger.
- the valve lift Liftin, the cam phase Cain, and the compression ratio Cr is set (FIGS. 27, 28, and 29).
- the lower the gear ratio on the lower speed side the larger the gear ratio, and the greater the engine braking force by requiring a higher rotational speed of the internal combustion engine relative to the vehicle speed.
- at least one of the valve lift, the cam phase, and the compression ratio is set so that the engine braking force increases as the speed ratio increases.
- the invention according to claim 3 relates to a valve lift Liftin, an intake valve 4 and an exhaust valve which are lifts of at least one of the intake valve 4 and the exhaust valve 7 of the internal combustion engine 3.
- At least one of the cam phase Cain, which is the phase of at least one of the intake cam 6 and the exhaust cam 9 that drives the clutch 7, and the compression ratio Cr of the internal combustion engine 3 is at least Is a control device 1 for the vehicle V that controls one of the above, the number of revolutions detecting means (crank angle sensor 20, ECU2) for detecting the number of revolutions of the internal combustion engine 3, and whether or not a deceleration request from the driver is generated.
- the lower the detected rotational speed (engine speed NE) of the internal combustion engine 3 the lower the Setting means for setting at least one of the valve lift Liftin, the force phase Cain and the compression ratio Cr so that the engine braking force of the internal combustion engine 3 is reduced (ECU2, steps 26 to 28 in FIG. 20, steps 26 to 28, FIG. 27, FIG. 28, Figure 29), and the special feature is to remove them.
- the setting means sets at least one of the valve lift, the cam phase, and the compression ratio so that the engine braking force becomes smaller as the rotational speed of the internal combustion engine becomes lower.
- the invention according to claim 4 is directed to a valve lift Liftin, an intake valve 4 and an exhaust valve that are lifts of at least one of the intake valve 4 and the exhaust valve 7 of the internal combustion engine 3.
- Control device 1 for vehicle V that controls at least one of the cam phase Cain, which is the phase of at least one of the intake cam 6 and exhaust cam 9 that respectively drive 7 and the clutch shaft 3d, and the compression ratio Cr of the internal combustion engine 3 1
- a speed reduction request is generated by a speed detection means for detecting the speed of the internal combustion engine 3, a deceleration request determination means for determining whether or not a deceleration request is generated from the driver, and a deceleration request determination means.
- valve lift Liftin When the rotational speed of the internal combustion engine 3 is determined to be within a predetermined rotational speed range (the first rotational speed range Al, the second rotational speed range A2, and the third rotational speed range A3), the valve lift Liftin , Cam phase Cain and compression ratio Cr Setting means (ECU2, steps 26 to 28 in FIG. 20, FIG. 20) for setting at least one of the above items so that the amount of change with respect to the rotational speed of the internal combustion engine 3 is smaller than when no deceleration request is generated. 27, FIG. 28, and FIG. 29).
- a predetermined rotational speed range the first rotational speed range Al, the second rotational speed range A2, and the third rotational speed range A3
- the deceleration request determination means determines whether or not the driver has requested deceleration. In addition, it is determined that a driver's deceleration request has occurred, and When the output speed of the internal combustion engine is within a predetermined speed range, at least one of the valve lift, the cam phase, and the compression ratio is set to the speed of the internal combustion engine more than when no deceleration request is generated. Set the amount of change to be small.
- the valve lift and cam At least one of the phase and compression ratio is set so that the amount of change with respect to the rotational speed of the internal combustion engine is smaller than when no deceleration request is generated.
- the valve lift or cam phase is set in this way, the engine brake force can be prevented from suddenly decreasing.
- the compression ratio is set as described above, the engine brake force can be prevented from increasing suddenly. As a result, the engine braking force can be changed smoothly, so that a good driver spirit can be ensured.
- the invention controls a valve lift Liftin that is a lift of at least one of the intake valve 4 and the exhaust valve 7 of the internal combustion engine 3,
- a control device 1 for a vehicle V that controls the compression ratio Cr of the internal combustion engine 3 by changing the stroke of the internal combustion engine 3, and includes a deceleration request determination means for determining whether or not a deceleration request from the driver is generated, and a deceleration Setting means for setting the valve lift Liftin to the decreasing side and setting the compression ratio Cr to the increasing side (ECU2, steps 26 and 28 in FIG. 20) when the request determining means determines that a deceleration request has occurred. , Fig. 27 and Fig. 29).
- the setting means is provided.
- the valve lift is set to the decreasing side and the compression ratio is set to the increasing side.
- the bombing loss increases, so the engine braking force increases.
- the compression ratio is set to the increase side.
- the invention according to claim 6 is the control device 1 for the vehicle V according to claim 5, further comprising a rotational speed detection means for detecting the rotational speed of the internal combustion engine 3, wherein the setting means The lower the speed of the combustion engine 3, the higher the valve lift Liftin and / or the lower the compression ratio Cr (steps 26, 28, 27, 29 in Fig. 20). It is a sign.
- the lower the detected rotation speed of the internal combustion engine the larger the valve lift and / or the smaller the compression ratio.
- the rotational speed of the internal combustion engine is low, the bonder loss and / or the engine friction is reduced, so that the engine braking force can be reduced, thereby suppressing the above-mentioned jerky feeling caused by the sudden change in the engine braking force. it can. Therefore, it is possible to secure good drivability.
- FIG. 1 is a diagram showing a schematic configuration of a vehicle to which a control device of the present invention is applied.
- FIG. 2 is a schematic diagram showing a schematic configuration of the internal combustion engine of FIG. 1.
- FIG. 3 is a block diagram showing a schematic configuration of a control device.
- FIG. 4 is a cross-sectional view showing a schematic configuration of a variable intake valve mechanism and an exhaust valve mechanism of an internal combustion engine.
- FIG. 5 is a cross-sectional view showing a schematic configuration of a variable valve lift mechanism of a variable intake valve operating mechanism.
- FIG. 6 is a diagram showing (a) a state in which the short arm of the lift actuator is in contact with the maximum lift stock, and (b) a state in which the short arm is in contact with the minimum lift stock.
- FIG. 7 (a) The intake valve is open when the lower link of the variable valve lift mechanism is at the maximum lift position, and (b) The intake valve is open when it is at the minimum lift position. is there.
- FIG. 8 is a diagram showing the valve lift curve (solid line) of the intake valve when the lower link of the variable valve lift mechanism is at the maximum lift position and the valve lift curve (two-dot chain line) when at the minimum lift position. .
- FIG. 9 is a diagram schematically showing a schematic configuration of a variable cam phase mechanism.
- FIG. 10 is a schematic view of the planetary gear device viewed from the direction along the line AA in FIG.
- FIG. 11 is a schematic view of the electromagnetic brake as viewed from the direction along line BB in FIG.
- FIG. 12 is a characteristic curve showing the operating characteristics of the variable cam phase mechanism.
- FIG. 13 The valve lift curve (solid line) when the cam phase is set to the most retarded angle value and the intake air when the cam phase is set to the most advanced angle value by the variable cam phase mechanism. It is a figure which shows the valve lift curve (two-dot chain line) of a valve.
- FIG. 14 (a) A diagram schematically showing the overall configuration of the variable compression ratio mechanism when the compression ratio is set to the minimum value, and (b) when the compression ratio is set to the maximum value. It is a figure which shows the structure of the compression ratio actuator vicinity in a variable compression ratio mechanism.
- FIG. 15 is a flowchart showing a variable mechanism control process.
- FIG. 16 is a diagram showing an example of a table used for calculating a target valve lift Liftin_cmd for starting the engine.
- FIG. 17 A table used to calculate the target cam phase Cain-cmd for starting the engine. It is a figure which shows an example.
- FIG. 18 is a diagram showing an example of a map used for calculating a target valve lift Liftin_cmd for catalyst warm-up control.
- FIG. 19 is a diagram showing an example of a map used for calculating a target cam phase Cain_cmd for catalyst warm-up control.
- FIG. 20 is a flowchart showing a target value calculation process for normal time.
- FIG. 21 is a diagram showing an example of a map used for setting a gear position estimated value NGEAR.
- FIG. 22 is a flowchart showing a deceleration request determination process.
- FIG. 23 is a diagram showing an example of a map used for calculating a deceleration request determination value AP-EBK.
- FIG. 24 is a diagram showing an example of a map used for calculating a target valve lift for normal operation Liftin-cmd.
- FIG. 25 is a diagram showing an example of a map used for calculating a target cam phase Cain-cmd for normal use.
- FIG. 26 is a diagram showing an example of a map used for calculating a target compression ratio Cr-cmd for normal use.
- FIG. 27 is a diagram showing an example of a map used for calculating a target valve lift Liftin-cmd for requesting deceleration.
- FIG. 28 is a diagram showing an example of a map used for calculating a target cam phase Cain_cmd for requesting deceleration.
- FIG. 29 is a diagram showing an example of a map used for calculating a target compression ratio Cr_cmd for requesting deceleration.
- FIG. 1 shows a schematic configuration of a vehicle V to which the vehicle control device 1 of the present invention is applied.
- vehicle V is equipped with an internal combustion engine (hereinafter referred to as “engine”) 3 and a transmission 90.
- engine internal combustion engine
- This speed change device 90 is of an automatic type, and shifts the power of the engine 3 by one of a plurality of predetermined speed change ratios and transmits it to the drive wheels W, W.
- the transmission 90 is also connected to the first speed ⁇ 6 gear stages consisting of 5th speed and reverse are selectively set, and the operation of the transmission 90 depends on the shift position of a shift lever (not shown) operated by the driver. It is controlled by an ECU 2 described later of the control device 1 (see FIG. 3).
- the engine 3 is a straight IJ 4-cylinder DOHC type gasoline engine having four cylinders 3a and pistons 3b (only one is shown).
- Engine 3 also includes an intake valve 4 and an exhaust valve 7 for opening and closing the intake port and the exhaust port of each cylinder 3a, respectively, and an intake camshaft 5 and an intake cam 6 for driving the intake valve 4.
- a fuel injection valve 10 and a spark plug 11 are provided.
- the stem 4a of the intake valve 4 is slidably fitted to the guide 4b, and the guide 4b is fixed to the cylinder head 3c.
- the intake valve 4 is provided with upper and lower spring seats 4c, 4d and a valve spring 4e disposed between them (see FIG. 5).
- the intake valve 4 is closed by the valve spring 4e. Energized in the valve direction.
- Each of the intake camshaft 5 and the exhaust camshaft 8 is rotatably attached to the cylinder head 3c via a holder (not shown).
- An intake sprocket 5a is coaxially disposed at one end of the intake camshaft 5 and is rotatably provided (see FIG. 9).
- the intake sprocket 5a is connected to the crankshaft 3d through a timing belt 5b, and is connected to the intake camshaft 5 through a variable cam phase mechanism 70 described later (see FIG. 9).
- the intake camshaft 5 rotates once every two rotations of the crankshaft 3d.
- the intake cam 6 is provided integrally with the intake camshaft 5 for each cylinder 3a.
- the variable intake valve mechanism 40 opens and closes the intake valve 4 of each cylinder 3 a as the intake cam 6 rotates, and changes the lift and valve timing of the intake valve 4 steplessly. Details will be described later.
- the lift of the intake valve 4 (hereinafter referred to as “Banolev lift”) Liftin represents the maximum stroke of the intake valve 4.
- the stem 7a of the exhaust valve 7 is slidably fitted to the guide 7b, and the guide 7b is fixed to the cylinder head 3c.
- the exhaust valve 7 has upper and lower spring seats 7c, 7d. And a valve spring 7e disposed between them. The exhaust valve 7 is urged in the valve closing direction by the valve spring 7e.
- the exhaust camshaft 8 has an exhaust sprocket (not shown) integral with the exhaust camshaft 8, and is connected to the crankshaft 3d via the exhaust sprocket and the timing belt 5b, whereby the crank Every time the shaft 3d rotates twice, it rotates once.
- the exhaust cam 9 is provided integrally with the exhaust camshaft 8 for each cylinder 3a.
- the exhaust valve mechanism 30 has a rocker arm 31, which is an exhaust cam.
- the fuel injection valve 10 is provided for each cylinder 3a, is attached to the cylinder head 3c in an inclined state, and injects fuel directly into the combustion chamber. That is, the engine 3 is configured as a direct injection engine. Further, the valve opening time and valve opening timing of the fuel injection valve 10 are controlled by the ECU 2.
- An ignition plug 11 is also provided for each cylinder 3a and attached to the cylinder head 3c.
- the ignition timing of the ignition plug 11 is also controlled by the ECU 2.
- the engine 3 is provided with a crank angle sensor 20 (rotational speed detection means) and a water temperature sensor 21.
- the crank angle sensor 20 includes a magnet rotor and an MRE pickup, and outputs a CRK signal and a TDC signal, both of which are pulse signals, to the ECU 2 as the crankshaft 3d rotates.
- the CRK signal is output every predetermined crank angle (for example, 10 °), and the ECU 2 calculates the engine speed (hereinafter referred to as "engine speed") NE of the engine 3 based on the CRK signal.
- engine speed hereinafter referred to as "engine speed"
- the TDC signal is a signal that indicates that the piston 3b of each cylinder 3a is at a predetermined crank angle position slightly ahead of the TDC position at the start of the intake stroke. Output every 180 °.
- the water temperature sensor 21 is composed of, for example, a thermistor and outputs a detection signal representing the engine water temperature TW to the ECU 2.
- This engine water temperature TW represents the temperature of the cooling water circulating in the cylinder block 3h of the engine 3.
- the intake pipe 12 of the engine 3 is not provided with a throttle valve mechanism, and its intake
- the air passage 12a is formed with a large diameter, so that the airflow resistance is set smaller than that of a normal engine.
- the intake pipe 12 is provided with an air flow sensor 22.
- the air flow sensor 22 is constituted by a hot-wire air flow meter, and outputs a detection signal representing the flow rate Gin of the air flowing in the intake passage 12a to the ECU 2.
- variable intake valve mechanism 40 includes an intake camshaft 5, an intake cam 6, a variable valve lift mechanism 50, a variable cam phase mechanism 70, and the like.
- variable valve lift mechanism 50 opens and closes the intake valve 4 as the intake cam 6 rotates, and sets the valve lift Liftin between a predetermined maximum value Liftin-H and a predetermined minimum value Liftin-L. It has a four-bar linkage type mouth cam mechanism 51 provided for each cylinder 3a and a lift actuator 60 that drives these rocker arm mechanisms 51 at the same time. ing.
- Each rocker arm mechanism 51 includes a rocker arm 52 and upper and lower links 53 and 54.
- One end of the upper link 53 is rotatably attached to a rocker arm shaft 56 fixed to the cylinder head 3c, and the other end is rotated to the upper end of the rocker arm 52 via an upper pin 55. It is attached freely.
- a roller 57 is rotatably provided on the upper pin 55 of the rocker arm 52. This roller 57 is in contact with the cam surface of the intake cam 6 and rolls on the intake cam 6 while being guided by the force surface when the intake cam 6 rotates. As a result, the rocker arm 52 is driven in the vertical direction and rotates about the upper link 53 force rocker arm shaft 56.
- an adjustment bolt 52a is attached to the end of the rocker arm 52 on the intake valve 4 side.
- the adjustment bolt 52a is in contact with the stem 4a of the intake valve 4.
- One end of the lower link 54 is rotatably attached to the lower end of the rocker arm 52 via the lower pin 58, and the connecting shaft 59 is rotated to the other end of the lower link 54. It is mounted freely.
- the lower link 54 is connected to the rear of the lift actuator 60 via the connecting shaft 59. It is connected to the short arm 65 described below.
- the lift actuator 60 is driven by the ECU 2, and includes a motor 61, a nut 62, a link 63, a long arm 64, and a short arm 65 as shown in FIG. .
- the motor 61 is connected to the ECU 2 and arranged outside the head cover 3g of the engine 3.
- the rotation shaft of the motor 61 is a screw shaft 61a in which a male screw is formed, and a nut 62 is screwed to the screw shaft 61a.
- One end of the link 63 is rotatably attached to the nut 62 via a pin 63a, and the other end is rotatably attached to one end of the long arm 64 via a pin 63b.
- the rotating shaft 66 is formed in a circular shape in cross section and is rotatably supported by the head cover 3g of the engine 3.
- the long arm 64 and the short arm 65 rotate integrally with the rotating shaft 66 as a center.
- the connecting shaft 59 is attached to the end of the short arm 65 opposite to the rotating shaft 66, so that the short arm 65 is interposed via the connecting shaft 59.
- a minimum lift stopper 67a and a maximum lift stopper 67b are provided in the vicinity of the short arm 65 with a space therebetween, and the rotation range of the short arm 65 is described later by these two stoppers 67a and 67b. To be regulated.
- variable valve lift mechanism 50 configured as described above.
- variable valve lift mechanism 50 when a lift control input Uliftin, which will be described later, is input from the ECU 2 to the lift actuator 60, the screw shaft 61a of the motor 61 rotates, and the nut 62 moves accordingly.
- the long arm 64 and the short arm 65 rotate around the rotation shaft 66, and the movement of the connecting shaft 59 accompanying the rotation of the short arm 65 causes the rocker arm mechanism 5 1 to have a lower link 54 force lower pin 58. Rotates as the center. That is, the lower link 54 is driven by the lift actuator 60.
- the intake valve 4 opens with a larger valve lift Liftin than when the lower link 54 is at the minimum lift position.
- the intake valve 4 opens according to the valve lift curve shown by the solid line in FIG. Indicates the value Liftin_H.
- the valve lift Liftin indicates the minimum value Liftin_L.
- the valve lift L iftin is obtained by rotating the lower link 54 between the maximum lift position and the minimum lift position via the actuator 60. It can be changed steplessly between the maximum value Liftin_H and the minimum value Liftin_L.
- variable valve lift mechanism 50 is provided with a lock mechanism (not shown), and when the lift control input Uliftin force is set to a failure value Uliftin_fs, which will be described later, or the wire breaks.
- Uliftin_fs failure value
- the variable valve lift mechanism 50 When it is not input to the lift actuator 60 due to, for example, the operation of the variable valve lift mechanism 50 is locked. That is, the variable valve lift mechanism The change of the valve lift Liftin by 50 is prohibited, and the valve lift Liftin is held at the minimum value Liftin_L.
- this minimum value Liftin_L secures a predetermined intake air amount for failure when the cam phase Cain is held at the most retarded angle value Cain_L described later and the compression ratio Cr is held at the minimum value Cr_L. Is set to be.
- the intake air amount for failure is set so that the idling operation and the engine starting can be appropriately performed while the vehicle is stopped, and the low-speed traveling state can be maintained while traveling.
- the engine 3 is provided with a rotation angle sensor 23 (see Fig. 3).
- This rotation angle sensor 23 detects the rotation angle ⁇ lift of the short arm 65 and detects it.
- the detection signal indicating is output to ECU2.
- the rotation angle ⁇ lift of the short arm 65 represents the position of the short arm 65 between the maximum lift position and the minimum lift position.
- ECU2 is based on this rotation angle ⁇ lift. Calculate the valve lift Liftin.
- variable cam phase mechanism 70 is of an electromagnetic type that changes the cam phase Cain steplessly by electromagnetic force, and includes a planetary gear device 71 and an electromagnetic brake 72.
- the planetary gear device 71 transmits rotation between the intake camshaft 5 and the sprocket 5a, and includes a ring gear 71a, three planetary pinion gears 71b, a sun gear 71c, and a planetary carrier 71d.
- the ring gear 71a is connected to an after-shake 73 described later of the electromagnetic brake 72, and rotates coaxially and integrally therewith.
- the sun gear 71c is attached to the tip of the intake camshaft 5 so as to rotate coaxially and integrally.
- the planetary carrier 71d is formed in a substantially triangular shape, and shafts 7le project from the three corners thereof.
- the planetary carrier 71d is connected to the sprocket 5a via these shafts 71e, and is thus configured to rotate coaxially and integrally with the sprocket 5a.
- Each planetary pinion gear 71b is rotatably supported by each shaft 71e of the planetary carrier 71d, and is disposed between the sun gear 71c and the ring gear 71a, and always meshes with them.
- the electromagnetic brake 72 is driven by the ECU 2, and has an attacking 73, a core 74, an electromagnet 75, and a return spring 76.
- the working casing 73 is formed in a hollow shape, and a core 74 is rotatably provided therein.
- the core 74 includes a base 74a having a circular cross section and two arms 74b and 74b extending radially. The base 74a of the core 74 is attached to the planetary carrier 71d, and thereby rotates coaxially and integrally with the planetary carrier 71d.
- a total of two sets of struts with 73b as one set are provided so as to face each other in the radial direction.
- the stoppers 73a and 73b of each set are spaced from each other, and the arms 74b of the core 74 are disposed therebetween.
- the core 74 is in contact with the most retarded angle position (a position indicated by a solid line in FIG. 11) where the arm 74b abuts on the most retarded angle stopper 73a and is engaged, and on the most advanced angle stopper 73b. It is configured such that it can rotate relative to the warning 73 between the most advanced angle position (the position indicated by the two-dot chain line in FIG. 11).
- the return spring 76 is stretched between one most advanced angle stopper 73b and an arm 74b opposite to the most advanced angle stopper 73b, and the return spring 76 is biased by an urging force Fsp r.
- the arm 74b is urged toward the most retarded angle stopper 73a.
- the electromagnet 75 is attached to the most advanced angle stopper 73b on the opposite side of the return spring 76.
- the electromagnet 75 is installed on the end of the most advanced angle stop 73b facing the arm 74b in a flush state. It has been.
- the electromagnet 75 is excited by the phase control input Ucain from the ECU 2, the electromagnetic force Fsol attracts the opposing arm 74b against the urging force Fs pr of the return spring 76, and the most advanced angle stagger 73b Turn to the side.
- variable cam phase mechanism 70 configured as described above will be described.
- the core 74 is the slowest in which its arm 74b comes into contact with the most retarded angle stud 73a by the urging force Fspr of the return spring 76.
- the cam phase Cain is held at the most retarded angle value Cain_L (see FIG. 12).
- the electromagnetic force Fsol of the electromagnet 75 causes an error in the core 74.
- the rod 74b is attracted to the most advanced angle stopper 73b side, that is, the most advanced angle position side while resisting the urging force Fspr of the return spring 76, and rotates to a position where the electromagnetic force Fsol and the urging force Fspr balance each other.
- the combating 73 rotates relative to the core 74 in the direction opposite to the arrow Y1.
- the ring gear 71a rotates in the direction of the arrow Y2 in FIG. 10 relative to the planetary carrier 71d, and accordingly, the planetary pinion gear 71b rotates in the direction of the arrow Y3 in FIG.
- the sun gear 71 c rotates in the direction of arrow Y4 in FIG.
- the intake force mushaft 5 force is rotated relative to the sprocket 5a in the direction of rotation of the sprocket (that is, the direction opposite to the arrow Y2 in FIG. 10), and the cam phase Cain is advanced.
- the rotation of the cooling 73 is transmitted to the intake camshaft 5 via the ring gear 71a, the planetary pinion gear 71b, and the sun gear 71c.
- the shaft 5 rotates by an angle obtained by amplifying the rotation angle of the attacking 73 with respect to the sprocket 5a. That is, the actual advance amount of the force phase Cain of the intake cam 5 is a value obtained by amplifying the rotation angle of the warning 73. This is because there is a limit to the distance that the electromagnetic force Fsol of the electromagnet 75 can act, so that this can be compensated and the cam phase Cain can be changed over a wider range.
- the electromagnetic force Fsol acts in the direction to advance the cam phase Cain, and the urging force Fspr of the return spring 76 acts in the direction to retard the cam phase Cain.
- the cam phase Cain is maintained at a value in which the electromagnetic force Fsol and the biasing force Fspr are balanced with each other.
- the rotation range of the core 74 is restricted to a range between the most retarded angle position shown by the solid line and the most advanced angle position shown by the two-dot chain line in FIG. 11 by the two staggers 73a and 73b.
- the control range of the cam phase Cain is also restricted to a range between the most retarded value Cain L and the most advanced value Cain H.
- the cam phase Cain is the most retarded value Cain_L (for example, cam angle 0 °) when the phase control input Ucain to the electromagnet 75 is smaller than the predetermined value Ucainl.
- the most advanced angle value Cain_H (for example, cam angle 55 °) is held.
- this variable force phase mechanism 70 has a so-called hysteresis characteristic that is slightly different when the value S of the cam phase Cain relative to the phase control input Ucain and when the phase control input Ucain increases and decreases. have.
- variable cam phase mechanism 70 when the phase control input Ucain is set to a failure value Ucain—fs described later, and when it is not input to the electromagnet 75 due to disconnection or the like, the cam phase Cain is The most retarded angle value is held at Cain—L. As described above, the most retarded angle value Cain- L is obtained when the valve lift Liftin is held at the minimum value Liftin- L and the compression ratio Cr is held at the minimum value Cr-L. It is set to ensure sufficient intake air volume.
- variable valve lift mechanism 50 changes the valve lift Liftin force steplessly between the aforementioned maximum value Liftin_H and minimum value Liftin_L.
- variable cam phase mechanism 70 changes the cam phase Cain steplessly between the aforementioned most retarded angle value Cain_L and the most advanced angle value Cain_H.
- a cam angle sensor 24 (see FIG. 3) is provided at the end of the intake camshaft 5 opposite to the variable cam phase mechanism 70.
- This cam angle sensor 24 is composed of, for example, a magnet rotor and an MRE pickup, and the CAM signal, which is a pulse signal, is sent to the ECU 2 every predetermined cam angle (for example, 1 °) as the intake camshaft 5 rotates. Output.
- the ECU 2 calculates the cam phase Cain based on this CAM signal and the aforementioned CRK signal.
- variable compression ratio mechanism 80 determines the top dead center position of the piston 3b, that is, the stroke of the piston 3b.
- the compression ratio Cr By changing the compression ratio Cr, it is steplessly changed between a predetermined maximum value Cr_H and a predetermined minimum value Cr_L, and is a composite connected between the piston 3b and the crankshaft 3d of each cylinder 3a.
- a link mechanism 81 and a compression ratio actuator 85 connected to the composite link mechanism 81 are provided.
- the composite link mechanism 81 includes an upper link 82, a lower link 83, a control link 84, and the like.
- the upper link 82 corresponds to a so-called connecting rod, and its upper end is rotatably connected to the piston 3b via the piston pin 3f, and its lower end is connected to one end of the lower link 83 via the pin 83a. Is pivotally connected to the motor.
- the lower link 83 has a triangular shape, and the two end portions other than the connecting portion with the upper link 82 are respectively connected to the crankshaft 3d via the crank pin 83b and controlled via the control pin 83c.
- One end of 84 is rotatably connected.
- the compression ratio actuator 85 is a combination of a motor connected to the ECU 2 and a speed reduction mechanism (not shown), and is driven by the ECU 2 as described later.
- the compression ratio actuator 85 includes a casing 85a, an arm 85b, a control shaft 85c, and the like, and a motor and a speed reduction mechanism are incorporated in the casing 85a.
- One end of the arm 85b is fixed to the tip of the rotation shaft 85d of the speed reduction mechanism, whereby the arm 85b rotates around the rotation shaft 85d as the motor rotates.
- a control shaft 85c is rotatably connected to the other end of the arm 85b.
- the control shaft 85c extends in the depth direction of the drawing, and an end of the control link 84 opposite to the control pin 83c is connected to the control shaft 85c.
- a minimum compression ratio stopper 86a and a maximum compression ratio stopper 86b are provided at a distance from each other, and the arm 85b is rotated by these two stoppers 86a and 86b.
- Range is regulated. That is, the arm 85b is in contact with the minimum compression ratio stopper 86a and is locked when the motor is driven in the forward / reverse rotation direction by a compression ratio control input Ucr (described later) from the ECU 2. 14 (a), and the maximum compression ratio position (position shown in Fig. 14 (b)) that contacts and locks the maximum compression ratio stopper 86b. Rotate within the range between.
- variable compression ratio mechanism 80 when the rotary shaft 85d of the compression ratio actuator 85 rotates counterclockwise in FIG. 14 with the arm 85b on the minimum compression ratio stopper 86a side, As a result, the arm 85b rotates counterclockwise in the figure. As a result, as the entire control link 84 is pushed down, the lower link 83 rotates clockwise around the crank pin 83b, and the upper link 82 rotates counterclockwise around the piston pin 3f. Rotate. As a result, the piston pin 3f, the upper pin 83a, and the crank pin 83b are more linear than the minimum compression ratio position, so that the piston pin 3f and the crank pin 83b when the piston 3b reaches the top dead center are obtained.
- the compression distance Cr is increased by increasing the linear distance connecting the cylinders (ie, increasing the stroke of the piston 3b) and decreasing the volume of the combustion chamber.
- the arm 85b rotates between the minimum compression ratio strobe 86a and the maximum compression ratio strobe 86b, so that the compression ratio Cr becomes the minimum value Cr_L and the maximum value. It is changed steplessly with Cr_H.
- variable compression ratio mechanism 80 is provided with a lock mechanism (not shown), and the compression ratio control input Ucr is set to a failure value Ucr_fs, which will be described later.
- the compression ratio control input Ucr is not input to the compression ratio actuator 85 due to disconnection or the like, the operation of the variable compression ratio mechanism 80 is locked. That is, change of the compression ratio Cr by the variable compression ratio mechanism 80 is prohibited, and the compression ratio Cr is held at the minimum value Cr_L.
- this minimum value Cr_L is used for failure when the valve lift Liftin is held at the minimum value Liftin_L and the cam phase Cain is held at the most retarded value Cain- L. It is set so that the amount of intake air can be secured.
- a control angle sensor 25 is provided in the casing 85a of the compression ratio actuator 85 (see Fig. 3), and this control angle sensor 25 is provided with a rotation angle ⁇ of the rotary shaft 85d, that is, the arm 85b.
- a detection signal representing cr is output to ECU2.
- the ECU 2 calculates the compression ratio Cr based on the detection signal of the control angle sensor 25.
- the ECU 2 includes an accelerator opening sensor 26 force accelerator pedal.
- a detection signal indicating AP and a detection signal indicating vehicle speed VP are output from the vehicle speed sensor 27, respectively (step not shown).
- the vehicle V is provided with an idle switch (hereinafter referred to as “IG ′ SW”) 28 and a brake switch (hereinafter referred to as “BK ′ SW”) 29.
- This IG. SW28 outputs a signal indicating the ON / OFF state to the ECU 2 in response to the operation of an ignition key (not shown).
- BK.SW29 outputs an ON signal to ECU2 when the brake pedal (not shown) is depressed more than a predetermined amount, and an OFF signal otherwise.
- the ECU 2 is composed of a microcomputer including a CPU, RAM, ROM, an I / O interface (not shown).
- the ECU 2 determines the operating state of the engine 3 according to the above-described various sensors and the detection signals of the switches 20 to 29 and the like, as well as the variable valve lift mechanism 50, the variable cam phase mechanism 70, and the variable compression ratio mechanism 80.
- the valve lift Liftin, cam phase Cain, and compression ratio Cr are controlled via
- the ECU 2 constitutes a setting means, a gear ratio detection means, a deceleration request determination means, a determination means, and a rotation speed detection means.
- the variable valve lift mechanism 50, the variable cam phase mechanism 70, and the variable compression ratio mechanism 80 are collectively referred to as “three variable mechanisms” as appropriate.
- variable mechanism control process executed by the ECU 2 calculates three control inputs Uliftin, Ucain, Ucr for controlling the three variable mechanisms, and is executed at a predetermined control cycle (for example, 5 msec).
- Step 1 it is determined whether or not the variable mechanism failure flag F_VDNG is “1”.
- This engine start flag F_ENGSTART is determined during engine start control, that is, cranking according to the detection signal of the engine speed NE and IG. SW28 in the determination process (not shown). It is set by determining whether or not it is in the middle. Specifically, the engine start flag F_ENGSTART is set to “1” when the engine start control is being performed, and to “0” otherwise.
- the target valve lift Liftin-cmd is calculated by searching the table shown in Fig. 16 according to the engine water temperature TW (step 3). .
- the target valve lift Liftin—cmd is set to a larger value when the engine coolant temperature TW is higher than the predetermined value TWREF1, and as the engine coolant temperature TW decreases, The predetermined value Lif tinref is set. This is to compensate for the fact that the friction of the variable valve lift mechanism 50 increases when the engine water temperature TW is low.
- the target cam phase Cain-cmd is calculated by searching the table shown in FIG. 17 according to the engine coolant temperature TW (step 4).
- the target cam phase Cain_cmd is set to a more retarded value as the engine coolant temperature TW is lower when the engine coolant temperature TW is higher than the predetermined value TWREF2, and within the range of TW ⁇ TWREF2, The value is set to Cainref. This is because when the engine coolant temperature TW is low, the force phase Cain is controlled to be retarded compared to when the engine coolant temperature TW is high, and the valve overlap is reduced to increase the intake flow velocity and stabilize combustion. This is for the purpose of illustration.
- the target compression ratio Cr_cmd is set to a predetermined starting value Cr_cmd_crk (Step 5).
- This starting value Cr_cmd_crk is set to a value on the low compression ratio side that can increase the engine speed NE during cranking and suppress the generation of unburned HC.
- the lift control input Uliftin, the phase control input Ucain, and the compression ratio control input Ucr which are the three control inputs, are calculated (step 6), and then the present process is terminated.
- These three control inputs Uliftin, Ucain and Ucr, respectively, are the actual valve lift Liftin and Based on the target valve lift Liftin_cmd, actual cam phase Cain and target cam phase Cain_cmd, and actual compression ratio Cr and target compression ratio Cr_cmd, a predetermined feedback control algorithm, for example, a target value filter type two-degree-of-freedom sliding mode control algorithm Calculated.
- the three control inputs Uliftin, Ucain, and Ucr are respectively set to the valve lift Liftin as the target valve lift Liftin_cmd, the cam phase Cain as the target cam phase Cain_cmd, and the compression ratio Cr as the target compression ratio Cr_cmd.
- step 7 it is determined whether or not the accelerator opening AP is smaller than a predetermined value APREF (step 7). If the answer is YES and the accelerator pedal is not depressed, it is determined whether or not the time value Teat of the catalyst warm-up timer is smaller than the predetermined value Tcatlm (step 8).
- This catalyst warm-up timer measures the execution time of the catalyst warm-up control process, and is composed of an up-count timer. The catalyst warm-up control process is performed in order to activate the exhaust gas purifying catalyst provided in the exhaust pipe of the engine 3.
- step 8 When the answer to step 8 is YES and Teat is Tcatlmt, that is, when the catalyst warm-up control is being executed, the target valve lift Liftin—cmd is set to the time value of the catalyst warm-up timer Teat and the engine water temperature TW. Accordingly, the calculation is performed by searching the map shown in FIG. 18 (step 9).
- TW1 to TW3 are predetermined values of the engine coolant temperature TW (T WKTW2 TW3).
- the target valve lift Liftin_cmd is set to a larger value as the engine water temperature TW is lower. This is because the lower the engine water temperature TW, the longer the time required to activate the catalyst. Therefore, by increasing the exhaust gas volume, the time required to activate the catalyst is shortened.
- the target valve lift Liftin_cmd is set to a larger value as the time value Tcat is larger in the region where the time value Teat of the catalyst warm-up timer is small, and in the region where the time value Teat is large. The larger the measured value T cat is, the smaller the value is set. This is because the engine warm-up control becomes longer as the engine 3 warms up and the friction decreases, so the engine speed NE To maintain the target value This is to avoid the ignition timing being excessively retarded and the combustion state becoming unstable.
- the target cam phase Cain_cmd is calculated by searching the map shown in Fig. 19 according to the time value Teat of the catalyst warm-up timer and the engine water temperature TW (step 10).
- the target cam phase Cain_cmd is set to a more advanced value as the engine coolant temperature TW is lower. This is because, as the engine water temperature TW is lower, the time required for catalyst activation becomes longer as described above, and therefore, the time required for catalyst activation is shortened by increasing the intake air amount.
- the target cam phase Cain-cmd is set to a more retarded value as the time value Teat of the catalyst warm-up timer is smaller, and in the region, the time value Teat is larger. In a region where the value Teat is large, the value is set to a more advanced value as the time value Teat is larger. This is for the same reason described in the explanation of FIG.
- the target compression ratio Cr-cmd is set to a predetermined warm-up control value Cr-cmd-ast (step 11).
- This warm-up control value Cr-cmd-ast is set to a value on the low compression ratio side in order to reduce the thermal efficiency to shorten the time required for catalyst activation and to increase the exhaust gas temperature.
- the process is terminated.
- step 7 or 8 when the answer to step 7 or 8 is NO, that is, when the accelerator pedal is depressed, or when Tcat ⁇ Tcatlmt, a normal target value calculation process described later is executed. In addition to (Step 12), after executing Step 6 above, this process is terminated.
- step 1 when the answer to step 1 is YES and at least one of the three variable mechanisms has failed, the lift control input Uliftin is set to a predetermined failure value Uliftin_fs, and the phase control input Ucain is set to a predetermined value.
- the failure value Ucain_fs is set to the compression ratio control input Ucr to the predetermined failure value Ucr_fs (step 13), this process ends.
- the valve lift Liftin is maintained at the minimum value Liftin_L
- the cam phase Cain is maintained at the most retarded value Cain_L
- the compression ratio Cr is maintained at the minimum value Cr_L.
- idle operation and engine start are properly performed while the vehicle is stopped.
- the vehicle can travel at a low speed while traveling.
- step 20 the estimated gear stage value NGEAR (detected transmission gear ratio) is calculated by searching the NGEAR map shown in FIG. 21 according to the vehicle speed VP and the engine speed NE.
- This estimated gear stage value NGEAR represents the estimated current gear stage of the transmission 90.
- the NGEAR map defines multiple areas representing the six gear stages to be estimated, and assigns the estimated gear stage value NGEAR to each gear stage. It is. Specifically, the estimated gear stage value NGEAR is set to a value 1 to a value 5 when the gear stage is 1st to 5th speed, and to a value 1 when the gear stage is reverse. In addition, the region where the engine speed NE is lower than a predetermined value NEREF (for example, 450 rpm) and the region higher than the region corresponding to the fifth speed are considered neutral, and the estimated gear stage value NGE AR is The value is set to 0.
- NEREF for example, 450 rpm
- the gear stage estimation value NGEAR is uniformly set to a value of 0 in the extremely low rotation range lower than the predetermined value NEREF because the engine 3 rotation is unstable in the extremely low rotation range. If the value NGEAR is set according to the engine speed NE, the estimated gear stage value NGEAR changes frequently, so this is avoided.
- deceleration request determination processing is executed (step 21). This process determines whether or not the driver has requested deceleration.
- the deceleration request determination process will be described with reference to FIG.
- step 30 a deceleration request determination value AP_EBK is calculated by searching an AP_EBK map shown in FIG. 23 according to the vehicle speed VP and the gear position estimated value NGE AR.
- the deceleration request determination value AP_EBK is set to a larger value as the gear stage estimation value NGEAR is larger, that is, as the gear stage is on the higher speed side or the vehicle speed VP is higher.
- step 31 is the accelerator opening AP force S smaller than the calculated deceleration request judgment value AP EBK? Judgment is made (step 31). If the answer is YES, it is determined that a driver's deceleration request has occurred, and the deceleration request flag F_EBK_MODE is set to ⁇ 1 '' to indicate that (step 32), and then this process ends. .
- the deceleration request is not generated, generally, the operation is performed with the accelerator pedal opening AP being larger as the gear stage is on the higher speed side or the vehicle speed VP is higher.
- step 33 it is determined whether or not the F / C flag F—FC is “1” (step 33).
- This F / C flag F—FC is set to “1” when the fuel cut during deceleration (hereinafter referred to as “F / C”) is executed when the execution condition is satisfied.
- step 34 When the answer to step 34 is YES, it is determined that a deceleration request has occurred because the brake pedal has been depressed a predetermined amount or more, and after executing step 32, the present process is terminated. . On the other hand, when all of the answers to Steps 31, 33, and 34 are NO, it is determined that a deceleration request has not occurred. In order to express this, the deceleration request flag F_EBK_MODE is set to “0” (step 35), and then this process is terminated.
- step 22 it is determined whether or not the deceleration request flag F_EBK_MODE set in step 32 or 35 is “1”. If the answer is NO and no deceleration request is generated, the target valve lift Liftin_cmd, target cam phase Cain_cmd, and target compression ratio Cr_cmd for normal use are calculated in the next step 23 and thereafter.
- the target valve lift Liftin_cmd is checked for the map shown in FIG. 24 according to the engine speed NE and the accelerator pedal opening AP. Calculate by searching.
- AP1 to AP3 are first to third predetermined values (API, AP2, AP3) of the accelerator opening AP.
- the accelerator opening AP is other than the first to third predetermined values API, AP2, AP3, the target valve lift Liftin_cmd is obtained by interpolation calculation.
- the target valve lift Liftin_cmd is set to a larger value as the accelerator pedal opening AP is larger.
- AP second predetermined value AP2 and third predetermined value AP3
- engine 3 has a medium load or a high load
- the target valve lift Liftin_cmd increases as the engine speed NE increases. Is set to This is because the higher the engine speed NE or the greater the accelerator pedal opening AP, the greater the required output for the engine 3 and the greater the required intake air amount.
- NE2 for example, 3500i "pm
- NE1 for example, 2500rpm
- a predetermined low to medium rotation range hereinafter referred to as" the first rotation "
- A1 predetermined speed range
- NE ⁇ NE1 extremely low to low rotation range has a larger slope than NE> NE2 Is set to decrease at.
- the target valve lift Liftin-cmd is set to the predetermined values Liftin_a and Liftin_ ⁇ at the first and second predetermined values NE1 and NE2, respectively.
- the target valve lift Liftin_cmd is set in the first rotation speed range A1 as described above.
- the valve lift liftin is controlled to the high lift side to reduce the airflow resistance of the intake air. This is to improve fuel efficiency by reducing pumping loss.
- the target cam phase Cain_cmd is calculated by searching the map shown in FIG. 25 according to the engine speed NE and the accelerator pedal opening AP (step 24).
- the target cam phase Cain _cmd is calculated as NE> 4th speed NE4 (eg 5000rpm) as engine speed NE decreases. ) Is set to a substantially constant value in the middle to high rotation range, and the third and fourth predetermined values NE3 (for example, 3000 rpm) and the predetermined low to medium rotation range (hereinafter referred to as “first”) defined by NE4.
- NE4 predetermined speed range
- first predetermined low to medium rotation range
- the target cam phase Cain_cmd is set to a predetermined value Cain_ corresponding to the most advanced angle value at the third predetermined value NE3, and to a predetermined value Cain_ / 3 at the fourth predetermined value NE4. .
- the target cam phase Cain_cmd is set as described above in the second rotation speed range A2 because the boring loss is reduced by increasing the internal EGR amount by controlling the cam phase Cain to a large advance side. In order to improve fuel efficiency.
- the target cam phase Cain_cmd is set to a more retarded value as the engine speed NE is lower in order to ensure stable combustion in the extremely low to low engine speed range of NE and NE3.
- the target compression ratio Cr-cmd is calculated by searching the map shown in FIG. 26 according to the engine speed NE and the accelerator pedal opening AP (step 25), and then the present process is terminated.
- the target compression ratio Cr-cmd is set to a smaller value as the engine speed NE is higher or the accelerator pedal opening AP is larger. This is because knocking is more likely to occur as the load is higher. Therefore, by controlling the compression ratio Cr to the low compression ratio side, a reduction in combustion efficiency due to excessive retard control of the ignition timing should be avoided. This is to prevent the occurrence of knocking.
- the target compression ratio Cr-cmd is defined by the fifth and sixth predetermined values NE5 and NE6 (for example, 1500 i "pm and 4500 rpm, respectively).
- the third speed range A3 (predetermined speed range)
- the amount of change is larger than in other areas as the engine speed NE decreases.
- the predetermined values Cr_ ⁇ and Cr_j3 are set, respectively.
- the target compression ratio Cr_cmd is set to increase with a very large change amount as the engine speed NE decreases. This is because, as described above, in the second rotation speed range A2, which is the low to medium rotation range, the cam phase Cain is largely controlled to the advance side, so that combustion may become unstable. This is to avoid such a problem by greatly increasing the ratio Cr.
- step 26 the target bar for the deceleration request is issued in the next step 26 and subsequent steps.
- Lublift Liftin_cmd, target cam phase Cain_cmd and target compression ratio Cr_cmd are calculated.
- step 26 the target valve lift Liftin_cmd is calculated by searching the map shown in FIG. 27 according to the engine speed NE and the estimated gear stage value NGEAR.
- the target valve lift Liftin—cmd is set to a smaller value as the estimated gear stage value NGEAR is smaller, that is, as the gear stage of the transmission 90 is on the lower speed side.
- the lower the gear stage the higher the engine braking force because the valve lift Liftin is controlled to the lower lift side, increasing the ventilation resistance of the intake air and increasing the pumping loss. can get.
- the target valve lift Liftin-cmd is set to a larger value as the engine rotational speed NE is lower than the estimated gear stage values NGEAR.
- the lower the engine speed NE the more the valve lift Liftin is controlled to the higher lift side, thereby reducing the pumping loss and the engine braking force.
- the target valve lift Liftin_cmd for normal operation at low load is set to increase in the first rotation speed range A1 as the engine speed NE decreases.
- the area on both sides of the area is set to decrease. For this reason, when the normal target valve lift Liftin_cmd is used as it is at the time of deceleration request, when the engine speed NE decreases rapidly, the engine braking force is higher than the first engine speed range A1. It increases sharply in the high speed region, decreases sharply in the first rotational speed range A1, and increases rapidly in the low rotational speed region than the first rotational speed range A1.
- the engine braking force repeatedly increases and decreases in response to a rapid decrease in the engine speed NE, changes unnaturally, and gives the driver a sense of incongruity.
- the target valve lift Liftin_cmd for requesting deceleration is in the first rotation speed range A1 in which the amount of change with respect to the engine speed NE is smaller than that in the normal rotation in the first rotation speed range A1. It is set to increase gradually as the engine speed NE decreases in the entire engine speed range including. As a result, even if the engine speed NE decreases rapidly, the engine brake force can be reduced gradually. As a result, at the time of deceleration request, the engine braking force can be smoothly changed without causing a sense of incongruity, unlike the case of using the normal target valve lift Liftin-cmd.
- the target cam phase Cain-cmd is calculated by searching the map shown in FIG. 28 according to the engine speed NE and the gear position estimated value N GEAR (step 27).
- the target cam phase Cain-cmd is set to be more retarded as the estimated gear stage value NGEAR is smaller.
- the lower the gear stage is, the more the cam phase Cai n is controlled to be retarded, i.e., in the direction in which the valve overlap between the intake valve 4 and the exhaust valve 7 is reduced.
- the degree of sealing of the combustion chamber by the intake valve 4 in the vicinity of the start of the combustion increases.
- the energy used to expand the air in the cylinder 3a increases and the bonder loss increases, so that a larger engine braking force can be obtained.
- the target cam phase Cain_cmd is set to be more advanced with respect to each gear stage estimated value NGEAR as the engine speed NE is lower.
- the lower the engine speed NE the more the cam phase Cain is controlled to the more advanced side, resulting in a reduction in the bonder loss, resulting in a reduction in the engine braking force.
- the target cam phase Cain_c md is set to the retarded angle side relative to the target cam phase Cain_cmd for normal operation at the time of low load shown in FIG. 25 described above, regardless of the gear stage estimation value NGEAR, in the entire rotation speed range. ing.
- the engine braking force is increased by controlling the cam phase Cain to the retard side.
- the target cam phase Cain_cmd for normal operation at low load is advanced by a very large change amount in the second rotation speed range A2 as the engine speed NE decreases. It is set to change to the retarded angle side in the region of lower rotation than the second rotation speed range A2. For this reason, when the normal target valve lift Liftin_cmd is used as it is at the time of deceleration request, the engine braking force increases rapidly after the engine speed NE decreases rapidly, and changes unnaturally. .
- the target cam phase Cain_cmd for requesting deceleration is, in the second rotation speed range A2, the second rotation speed range in which the amount of change with respect to the engine speed NE is smaller than that in the normal speed range.
- the engine speed is set to gradually advance as the engine speed NE decreases.
- the engine braking force can be reduced gradually.
- the engine braking force can be smoothly changed without causing a sense of incongruity, unlike when the target cam phase Cain-cmd for normal use is used at the time of deceleration request.
- the target compression ratio Cr—cmd is calculated by searching the map shown in FIG. 29 according to the engine speed NE and the estimated gear stage value NGEAR (step 28), and then the process is terminated. .
- the target compression ratio Cr-cmd is set to a larger value as the estimated gear stage value NGEAR is smaller.
- the lower the gear stage the higher the compression ratio Cr is controlled to the higher compression ratio side, so that the engine 3 side torque resistance against the vehicle V when compressing the sucked air. Since the friction increases, a greater engine braking force can be obtained.
- the target compression ratio Cr_cmd is set to a smaller value as the engine speed NE is lower than the estimated gear stage value NGEAR.
- the compression ratio Cr is controlled to the lower compression ratio side, and as a result, the engine friction is reduced and the engine braking force is reduced.
- the target compression ratio Cr_cmd is the same as that described above regardless of the gear stage estimation value NGEAR in the middle to high engine speed range where the engine speed NE is higher than the eighth engine speed NE8 (NE5 and NE8 and NE6) (for example, 4000 rpm). It is set to a value larger than the target compression ratio Cr_cmd for normal use at low load shown in Fig. 26. As a result, when a deceleration request occurs, the compression ratio Cr By being controlled to increase, the engine braking force increases.
- the target compression ratio Cr_cmd for normal operation at low load is very large in the third rotational speed range A3 as the engine rotational speed NE decreases. It is set to change to a large value. For this reason, if the normal target compression ratio Cr_cmd is used as it is at the time of deceleration request, the engine braking force increases rapidly and changes unnaturally as the engine speed NE decreases rapidly.
- the target compression ratio Cr_cmd for requesting deceleration is smaller in the third rotation speed range A3 in the third rotation speed range A3. It is set to gradually decrease as the engine speed NE decreases in the entire engine speed range including. As a result, even if the engine speed NE drops rapidly, the engine braking force can be reduced gradually. As a result, at the time of deceleration request, the engine braking force can be smoothly changed without causing a sense of incongruity, unlike the case where the normal target compression ratio Cr-cmd is used.
- the lower the gear stage that is, the greater the gear ratio, the greater the valve.
- the lift Lif tin is set to the lower lift side
- the force phase Cain is set to the more retarded side
- the compression ratio Cr is set to the higher compression ratio side, so that a larger engine braking force can be obtained.
- valve lift Liftin is set to the decreasing side and the compression ratio Cr is set to the increasing side, so the engine braking force by setting the valve lift Liftin and the engine braking force by setting the compression ratio Cr Greater engine braking force combined with power, therefore
- the lower the engine speed NE the more the valve lift Liftin is set to the higher lift side, the cam phase Cain is set to the more advanced side, and the compression ratio Cr is set to the lower compression ratio side. And reduce the engine braking force.
- the jerky feeling caused by a sudden change in engine braking force when the engine speed NE is low is achieved. Since it can suppress, a favorable driver spirit can be ensured.
- the valve lift Liftin, the cam phase Cain, and the compression ratio Cr are set to the engine speed NE in the first, second, and third engine speed ranges Al, A2, and A3, respectively.
- the amount of change with respect to the engine speed NE is set to be smaller than in normal times when there is no deceleration request.
- the setting of the valve lift Liftin and the cam phase Cain can prevent a rapid decrease in engine braking force, and the setting of the compression ratio Cr can prevent a rapid increase in engine braking force. As a result, the engine breaker can be smoothly changed, so that good drivability can be ensured.
- the present invention can be implemented in various modes without being limited to the embodiments described.
- the valve lift of the exhaust valve 7 may be controlled instead of, or together with, the force that controls the valve lift Liftin of the intake valve 4.
- the cam phase of the exhaust cam 9 may be controlled instead of or together with the force that controls the cam phase Cain of the intake cam 6.
- the target valve lift Liftin-cmd, the target cam phase Cain-cmd, and the target compression ratio Cr-cmd are set such that the smaller the gear estimated value NGEAR, that is, the larger the gear ratio, the greater the engine braking force.
- other setting methods are also within the scope of the present invention as long as they are set to different values for each gear ratio of the transmission 90.
- the force that controls all of the valve lift Liftin, the cam phase Cain, and the compression ratio Cr may control at least one of these.
- the embodiment is a force that is an example of an automatic transmission 90.
- the present invention is not limited to this, and may be applied to a manual transmission or a continuously variable transmission.
- the force obtained by estimating the speed ratio of the transmission 90 using the vehicle speed VP and the engine speed NE may be detected directly by a sensor or the like instead.
- the maps in FIGS. 27 to 29 are examples of setting the target valve lift Liftin_cmd, the target cam phase Cain_cmd, and the target compression ratio Cr_cmd.
- the control device extends the life of the foot brake by obtaining an appropriate engine braking force when the driver requests deceleration, and also provides an internal combustion engine when the driver requests deceleration.
- the engine speed is relatively low, it is extremely useful to suppress the jerky feeling caused by a sudden change in the engine braking force, thereby ensuring good drivability.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE602005022090T DE602005022090D1 (de) | 2004-09-14 | 2005-09-09 | Fahrzeugsteuerungssystem |
US11/662,500 US20080059031A1 (en) | 2004-09-14 | 2005-09-09 | Control System for Vehicle |
EP05781961A EP1801393B1 (en) | 2004-09-14 | 2005-09-09 | Vehicle control system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004267507A JP2006083729A (ja) | 2004-09-14 | 2004-09-14 | 車両の制御装置 |
JP2004-267507 | 2004-09-14 |
Publications (1)
Publication Number | Publication Date |
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WO2006030707A1 true WO2006030707A1 (ja) | 2006-03-23 |
Family
ID=36059960
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/016604 WO2006030707A1 (ja) | 2004-09-14 | 2005-09-09 | 車両の制御装置 |
Country Status (6)
Country | Link |
---|---|
US (1) | US20080059031A1 (ja) |
EP (1) | EP1801393B1 (ja) |
JP (1) | JP2006083729A (ja) |
CN (1) | CN101018935A (ja) |
DE (1) | DE602005022090D1 (ja) |
WO (1) | WO2006030707A1 (ja) |
Cited By (1)
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---|---|---|---|---|
CN101624939A (zh) * | 2008-07-07 | 2010-01-13 | 现代自动车株式会社 | 可变压缩比的装置 |
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JP4743169B2 (ja) | 2007-06-13 | 2011-08-10 | トヨタ自動車株式会社 | 内燃機関制御装置及び方法 |
JP5145789B2 (ja) * | 2007-06-22 | 2013-02-20 | スズキ株式会社 | 内燃機関の可変バルブタイミング制御装置 |
DE102009045415A1 (de) * | 2009-10-07 | 2011-04-14 | Robert Bosch Gmbh | Verfahren zum Betreiben eines bremskraftverstärkten Bremssystems eines Fahrzeugs und Steuervorrichtung für ein bremskraftverstärktes Bremssystems eines Fahrzeugs |
DE102011017197A1 (de) * | 2011-04-15 | 2012-10-18 | Daimler Ag | Hubkolben-Verbrennungskraftmaschine |
JP2013036449A (ja) * | 2011-08-10 | 2013-02-21 | Isuzu Motors Ltd | ディーゼルエンジンの補助ブレーキ装置 |
JP5874236B2 (ja) * | 2011-08-10 | 2016-03-02 | いすゞ自動車株式会社 | ディーゼルエンジン |
WO2016016228A1 (de) * | 2014-07-30 | 2016-02-04 | Fev Gmbh | Verbrennungskraftmaschine mit einstellbarem verdichtungsverhaeltnis und zuschaltnocken und verfahren zum betreiben einer derartigen verbrennungskraftmaschine |
KR20160064847A (ko) * | 2014-11-28 | 2016-06-08 | 현대자동차주식회사 | 연속 가변 밸브 듀레이션 장치 및 이를 이용한 제어방법 |
EP3103986B1 (en) * | 2015-06-08 | 2018-01-31 | Gomecsys B.V. | A four-stroke internal combustion engine including variable compression ratio and a vehicle |
US9702304B1 (en) | 2016-03-30 | 2017-07-11 | Toyota Motor Engineering & Manufacturing North America, Inc. | Automatic engine braking and increased regenerative capacity hybrid vehicle |
DE102017000245B4 (de) * | 2017-01-12 | 2018-10-04 | Audi Ag | Mehrgelenkskurbeltrieb für eine Brennkraftmaschine |
BR112020004056B1 (pt) * | 2017-08-30 | 2023-03-21 | Nissan Motor Co., Ltd | Método de controle para motor de combustão interna, e sistema de controle para motor de combustão interna |
CN110657024A (zh) * | 2018-12-30 | 2020-01-07 | 长城汽车股份有限公司 | 可变压缩比机构与发动机 |
CN110671199B (zh) * | 2018-12-30 | 2021-07-06 | 长城汽车股份有限公司 | 可变压缩比机构与发动机 |
US11339728B1 (en) * | 2020-12-08 | 2022-05-24 | Ford Global Technologies, Llc | Methods and systems for engine braking with reduced noise, vibration, and harshness |
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- 2005-09-09 CN CNA2005800307447A patent/CN101018935A/zh active Pending
- 2005-09-09 WO PCT/JP2005/016604 patent/WO2006030707A1/ja active Application Filing
- 2005-09-09 EP EP05781961A patent/EP1801393B1/en not_active Expired - Fee Related
- 2005-09-09 DE DE602005022090T patent/DE602005022090D1/de active Active
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Cited By (2)
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CN101624939A (zh) * | 2008-07-07 | 2010-01-13 | 现代自动车株式会社 | 可变压缩比的装置 |
CN101624939B (zh) * | 2008-07-07 | 2014-07-16 | 现代自动车株式会社 | 可变压缩比的装置 |
Also Published As
Publication number | Publication date |
---|---|
EP1801393A1 (en) | 2007-06-27 |
US20080059031A1 (en) | 2008-03-06 |
DE602005022090D1 (de) | 2010-08-12 |
EP1801393A4 (en) | 2009-04-08 |
CN101018935A (zh) | 2007-08-15 |
EP1801393B1 (en) | 2010-06-30 |
JP2006083729A (ja) | 2006-03-30 |
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