WO2013046332A1 - 可変動弁装置の制御装置 - Google Patents
可変動弁装置の制御装置 Download PDFInfo
- Publication number
- WO2013046332A1 WO2013046332A1 PCT/JP2011/072061 JP2011072061W WO2013046332A1 WO 2013046332 A1 WO2013046332 A1 WO 2013046332A1 JP 2011072061 W JP2011072061 W JP 2011072061W WO 2013046332 A1 WO2013046332 A1 WO 2013046332A1
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- WIPO (PCT)
- Prior art keywords
- phase
- engine
- valve timing
- advance
- time
- Prior art date
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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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
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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
- F01L1/185—Overhead end-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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
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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
- F01L1/053—Camshafts overhead type
- F01L2001/0537—Double overhead camshafts [DOHC]
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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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
- F01L2001/34453—Locking means between driving and driven members
- F01L2001/34466—Locking means between driving and driven members with multiple locking devices
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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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
- F01L2001/34453—Locking means between driving and driven members
- F01L2001/34469—Lock movement parallel to camshaft axis
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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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
- F01L2001/34453—Locking means between driving and driven members
- F01L2001/34476—Restrict range locking means
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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
- F01L2250/00—Camshaft drives characterised by their transmission means
- F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2800/00—Methods of operation using a variable valve timing mechanism
- F01L2800/03—Stopping; Stalling
Definitions
- the present invention includes a hydraulic phase change mechanism, a phase fixing mechanism that fixes the valve timing to a specific angle phase that is more advanced than the most retarded phase, and a valve timing that varies with cam torque variation from the most retarded phase to a specified angle.
- the present invention relates to a control device for a variable valve operating apparatus including a self-advanced advance mechanism that advances an angle toward a phase.
- variable valve operating device As the variable valve operating device, the one described in Patent Document 1 is known.
- variable valve device of the same document fixes the valve timing to a specific angle phase by using the advance angle of the valve timing accompanying the fluctuation of the cam torque at the time of engine start where the valve timing is not fixed to the specific angle phase.
- the resistance force against the advance angle of the valve timing due to cam torque fluctuation at the start of the engine is determined by the amount of hydraulic oil remaining in the retard chamber of the phase change mechanism or the hydraulic oil pressure. As it grows, it grows.
- the present invention is a technique for solving the above-described problems, and an object thereof is to provide a control device for a variable valve operating apparatus that can suppress a decrease in startability of an internal combustion engine.
- the present invention includes a hydraulic phase change mechanism that changes the valve timing of an internal combustion engine by supplying or discharging hydraulic oil to or from an advance chamber or a retard chamber, and the valve timing is advanced from the most retarded phase. And a self-advanced advancing mechanism for advancing the valve timing from the most retarded phase toward the specific angle phase in accordance with cam torque fluctuations.
- a control device wherein the amount of hydraulic oil remaining in the retarding chamber is defined as a residual oil amount, and the pressure of the hydraulic fluid remaining in the retarding chamber is defined as a residual hydraulic pressure, the control device starts the engine
- the residual oil amount or the residual hydraulic pressure is large at the time, the amount of hydraulic oil supplied to the advance chamber is increased compared to when the residual oil amount or the residual hydraulic pressure is small when the engine is started. It is characterized in.
- the resistance force to the advance angle of the valve timing due to cam torque fluctuations that occur when the engine is started changes depending on the amount of residual oil or residual oil pressure. That is, the resistance force increases as the residual oil amount or residual hydraulic pressure at the time of starting the engine increases.
- the amount of hydraulic oil supplied to the advance chamber is increased when compared to when the residual oil amount or residual hydraulic pressure at the time of engine starting is small.
- the control device for the variable valve operating apparatus is configured such that when the residual oil amount or the residual hydraulic pressure at the time of starting the engine is equal to or greater than a reference value, the residual oil amount or the residual hydraulic pressure at the time of starting the engine is less than the reference value. It is preferable to increase the amount of hydraulic oil supplied to the advance chamber as compared to the time.
- the control device for the variable valve operating device is configured such that, after the start of the internal combustion engine in a state where the residual oil amount or the residual hydraulic pressure is less than the reference value, the valve timing according to the cam torque variation is the specific angle phase. It is preferable that the phase fixing mechanism fixes the valve timing to the specific angle phase when the angle is advanced to.
- the fluctuation range of the valve timing is compared with a configuration in which the valve timing is not fixed by the phase fixing mechanism when the engine is started. Becomes smaller.
- the control device of this variable valve operating apparatus sets the operating state of the phase locking mechanism that does not fix the valve timing to the specific angle phase as a phase released state, and the residual oil amount or the residual hydraulic pressure is When the value is equal to or greater than a reference value, the phase locking mechanism is preferably in the phase release state.
- the control device of this variable valve operating apparatus uses the predetermined phase range that is more advanced than the most retarded phase and includes the specific angle phase as the specific phase range, and the residual oil amount or the residual hydraulic pressure is the reference value After the start of the internal combustion engine in the above state, when the valve timing is advanced to the specific phase range, the valve timing is preferably held in the specific phase range by the hydraulic pressure of the phase change mechanism.
- the valve timing is held in the specific phase range by the hydraulic pressure of the phase change mechanism when the engine is started, the valve timing is held at a phase retarded from the specific phase range when the engine is started. Compared with, the startability of the internal combustion engine is increased.
- control device for the variable valve device estimates at least one of the remaining oil amount and the remaining hydraulic pressure at the time of starting the engine based on a fluctuation range of the valve timing at the time of starting the engine.
- the fluctuation range of the valve timing at the time of engine start shows different magnitudes depending on the residual oil amount and residual oil pressure at the time of engine start. For this reason, it is possible to estimate at least one of the residual oil amount and the residual hydraulic pressure at the time of engine start based on the fluctuation range of the valve timing at the time of engine start.
- the control device for this variable valve operating apparatus starts the start of the internal combustion engine this time with a history indicating that the fluctuation range of the valve timing at the time of the last engine stop transition being equal to or greater than a predetermined fluctuation range Later, when the valve timing is advanced to the specific angle phase due to the cam torque fluctuation and when there is a history at the time of stop, it is preferable that the phase fixing mechanism fixes the valve timing to the specific angle phase. .
- the fluctuation range of the valve timing at the time of engine stop transition becomes larger as the remaining oil amount and the remaining oil pressure become smaller. Therefore, when the fluctuation range of the valve timing at the time of the last engine stop transition is large, it can be estimated that at least one of the residual oil amount and the residual hydraulic pressure at the time of the current engine start is small.
- the valve timing when there is a history of stoppage, the valve timing is advanced by cam torque fluctuation at the time of the current engine start, and the valve timing is fixed to a specific angle phase by the phase fixing mechanism. For this reason, when at least one of the remaining oil amount and the remaining oil pressure at the time of engine start is small, the valve timing is fixed at a specific angle phase earlier than the configuration in which the valve timing is advanced by hydraulic control of the phase change mechanism. Will be more frequent.
- the control device for the variable valve operating device includes at least one of the remaining oil amount and the remaining hydraulic pressure at the time of the last engine stop, and the retard chamber in a period from the last engine stop to the engine start. It is preferable to estimate at least one of the residual oil amount and the residual hydraulic pressure at the time of starting the engine based on the amount of hydraulic oil flowing out.
- the hydraulic oil remaining in the retarded angle chamber at the time of engine stop is released from the clearance of the phase change mechanism to the outside. Flows out. For this reason, at least one of the residual oil amount and the residual hydraulic pressure at the time of starting the engine is estimated based on the residual oil amount at the time of the last engine stop and the outflow amount of hydraulic oil during the period when the rotation of the internal combustion engine is stopped. be able to.
- the block diagram which shows typically the structure of an internal combustion engine provided with this about the control apparatus of the variable valve apparatus of one Embodiment of this invention.
- Sectional drawing which shows the cross-sectional structure about the variable valve apparatus of the embodiment.
- Sectional drawing which shows the cross-sectional structure which follows the AA line of FIG. 2 about the variable valve apparatus of the embodiment.
- Sectional drawing which shows the cross-sectional structure which follows the AA line of FIG. 2 about the variable valve apparatus of the embodiment.
- the map which shows the area
- the flowchart which shows the procedure of the "transition control designation
- the flowchart which shows the procedure of the "starting-time control selection process” performed by the control apparatus about the variable valve apparatus of the embodiment.
- the internal combustion engine 1 includes an engine main body 10 that rotates a crankshaft 15 by combustion of an air-fuel mixture, a variable valve operating device 20 that includes each element of a valve operating system, and a hydraulic mechanism 80 that supplies hydraulic oil to the engine main body 10 and the like. And a control device 90 for comprehensively controlling various devices including these devices.
- the engine body 10 includes a cylinder block 11 in which the air-fuel mixture is combusted, a cylinder head 12 to which the variable valve device 20 is assembled, and an oil pan 13 that stores hydraulic oil supplied to each part of the engine body 10. .
- the variable valve system 20 includes an intake valve 21 that opens and closes an intake port of the combustion chamber 14, an exhaust valve 23 that opens and closes an exhaust port of the combustion chamber 14, an intake camshaft 22 that pushes down the intake valve 21, And an exhaust camshaft 24 that pushes down the exhaust valve 23.
- a hydraulic phase change mechanism 30 that changes the rotation phase of the intake camshaft 22 relative to the rotation phase of the crankshaft 15 (hereinafter, “valve timing VT”), and a phase fixing mechanism 40 that fixes the valve timing VT. And have.
- the phase changing mechanism 30 sets the valve timing VT from the most advanced valve timing (hereinafter, “most advanced angle phase VTmax”) to the most retarded valve timing (hereinafter, “most delayed angle phase VTmin”). Change with.
- the phase fixing mechanism 40 fixes the valve timing VT to a specific valve timing (hereinafter, “intermediate angle phase VTmdl”) between the most advanced angle phase VTmax and the most retarded angle phase VTmin.
- the intermediate angle phase VTmdl corresponds to a “specific angle phase”.
- a valve timing VT capable of starting the internal combustion engine 1 in a cold region is set.
- the former is greater than the latter.
- the startability of the internal combustion engine 1 is higher.
- the hydraulic mechanism 80 includes an oil pump 81 that discharges the hydraulic oil from the oil pan 13, an oil control valve 82 that controls the supply and discharge modes of the hydraulic oil for the phase change mechanism 30, and the hydraulic oil for the phase fixing mechanism 40. And an oil switching valve 83 for controlling the supply mode and the discharge mode.
- a supply oil passage 84 that supplies hydraulic oil discharged from the oil pump 81 to each part of the internal combustion engine 1 and a discharge oil path 88 that discharges hydraulic oil from each part of the internal combustion engine 1 to the oil pan 13.
- the advance oil passage 85 connects the advance chamber 37 of the phase change mechanism 30 and the oil control valve 82 to each other.
- the retard oil path 86 connects the retard chamber 38 of the phase change mechanism 30 and the oil control valve 82 to each other.
- the phase lock oil passage 87 connects the first release chamber 54 and the second release chamber 64 of the phase lock mechanism 40 and the oil switching valve 83 to each other.
- the control device 90 includes an electronic control device 91 that performs various arithmetic processes for controlling the internal combustion engine 1, a crank position sensor 92, a cam position sensor 93, a coolant temperature sensor 94, and an accelerator position sensor 95. And various sensors.
- crank position sensor 92 outputs a signal corresponding to the rotation angle of the crankshaft 15 (hereinafter “crank angle CA”) to the electronic control unit 91.
- the cam position sensor 93 outputs a signal corresponding to the rotation angle of the intake camshaft 22 (hereinafter “cam angle DA”) to the electronic control unit 91.
- the cooling water temperature sensor 94 outputs a signal corresponding to the temperature of the cooling water in the vicinity of the cooling water outlet of the cylinder head 12 (hereinafter referred to as “cooling water temperature TW”) to the electronic control unit 91.
- the accelerator position sensor 95 outputs a signal corresponding to the amount of depression of the accelerator pedal 2 (hereinafter referred to as “accelerator depression amount AP”), that is, a signal corresponding to the amount of accelerator operation to the electronic control unit 91.
- engine start period the period required from the start request of the internal combustion engine 1 to the completion of the start operation of the internal combustion engine 1 is referred to as “engine start period”. Further, a period from when the stop request for the internal combustion engine 1 is set to when the rotation of the crankshaft 15 stops is referred to as an “engine stop transition period”. A period during which the rotation of the internal combustion engine 1 is stopped is referred to as an “engine stop period”. The engine operation period excluding the engine start period, engine stop period, and idle operation period is referred to as a “normal engine operation period”.
- the electronic control unit 91 calculates the following parameters based on the output of each sensor.
- A Based on the output of the crank position sensor 92, a calculation value corresponding to the crank angle CA is calculated.
- B Based on the calculated value of the crank angle CA, a calculated value corresponding to the rotational speed of the crankshaft 15 (hereinafter referred to as “engine rotational speed NE”) is calculated.
- C Based on the output of the cam position sensor 93, a calculation value corresponding to the cam angle DA is calculated.
- a calculation value corresponding to the valve timing VT is calculated based on the crank angle CA and the cam angle DA.
- E Based on the output of the coolant temperature sensor 94, a calculation value corresponding to the coolant temperature TW is calculated.
- F Based on the output of the accelerator position sensor 95, a calculated value corresponding to the accelerator depression amount AP is calculated.
- the electronic control unit 91 controls the valve timing control for controlling the operation of the phase changing mechanism 30 and the phase fixing mechanism 40 based on the engine operating state, and the start time control selection process for selecting the advance method of the valve timing VT at the time of engine start. And do.
- the parameters that define the engine operating state include the engine speed NE and the engine load.
- Valve timing control includes phase advance control for advancing valve timing VT during normal engine operation, phase retard control for retarding valve timing VT during normal engine operation, and valve timing VT during normal engine operation. Includes phase hold control for holding by hydraulic pressure. Further, phase fixing control for fixing the valve timing VT to the intermediate angle phase VTmdl by the phase fixing mechanism 40 and phase release control for releasing the fixation of the valve timing VT to the intermediate angle phase VTmdl by the phase fixing mechanism 40 are performed. Including.
- phase advance angle control and the phase delay angle control are requests that advance the valve timing VT (hereinafter, “phase advance angle request”) or requests that delay the valve timing VT (hereinafter, “phase delay control”).
- phase advance angle request a target valve timing VT (hereinafter,“ target angle phase VTTrg ”) is set based on the engine operating state.
- the oil control valve 82 for controlling the phase change mechanism 30 to advance or retard is controlled.
- the phase holding control is an oil for causing the phase changing mechanism 30 to perform a holding operation when a request for holding the valve timing VT at a predetermined phase by hydraulic pressure (hereinafter referred to as “phase holding request”) is set by a separately executed control.
- the control valve 82 is controlled.
- the phase maintenance request is set based on, for example, that an idle operation condition is established.
- the holding operation indicates the operation of the phase changing mechanism 30 for holding the valve timing VT at a predetermined phase within the range from the most retarded phase to the most advanced angle phase.
- the phase locking control is an oil switching for causing the phase locking mechanism 40 to perform a fixed operation when a request for fixing the valve timing VT to the intermediate angle phase VTmdl (hereinafter referred to as “phase locking request”) is set by a separately executed control.
- the valve 83 is controlled.
- the phase lock request is set based on whether the engine stop condition is satisfied or the idle operation condition is satisfied.
- the fixing operation indicates the operation of the phase fixing mechanism 40 for fixing the valve timing VT to the intermediate angle phase VTmdl.
- phase release request when a request for releasing the fixation of the valve timing VT to the intermediate angle phase VTmdl (hereinafter, “phase release request”) is set by a separately executed control, the phase release mechanism 40 is caused to perform the release operation.
- the oil switching valve 83 is controlled.
- the phase cancellation request is set based on a change from the idle operation state to the normal engine operation state, that is, the accelerator depression amount AP increases in the idle operation state.
- the unlocking operation indicates the operation of the phase locking mechanism 40 for releasing the fixing of the valve timing VT to the intermediate angle phase VTmdl.
- phase changing mechanism 30 The structure of the phase changing mechanism 30 will be described with reference to FIG.
- the phase change mechanism 30 forces the housing rotor 31 that rotates in synchronization with the crankshaft 15 in FIG. 1, the vane rotor 35 that rotates in synchronization with the intake camshaft 22, and the vane rotor 35 so that the valve timing VT is advanced. And an assist spring (not shown).
- valve timing VT is changed according to the rotational phase of the vane rotor 35 with respect to the housing rotor 31.
- an arrow DR in the drawing indicates the rotation direction of the sprocket 33 (crankshaft 15) and the intake camshaft 22.
- the housing rotor 31 includes a housing main body 32 serving as a main body, a sprocket 33 fixed to one end of the housing main body 32 in the axial direction, and a cover 34 fixed to the other end of the housing main body 32 in the axial direction. (See FIG. 3).
- the housing main body 32 has three partition walls 32A that protrude in the radial direction of the rotation shaft of the housing rotor 31.
- the housing main body 32, the sprocket 33, and the cover 34 are fixed to each other by three bolts inserted in the axial direction.
- the vane rotor 35 is disposed in a space in the housing main body 32. Further, it is fixed to the end of the intake camshaft 22.
- the vane rotor 35 has three vanes 35 ⁇ / b> A that protrude toward the housing body 32.
- the phase changing mechanism 30 has three storage chambers 36.
- Each housing chamber 36 is formed by being surrounded by the outer peripheral wall portion of the housing body 32, the adjacent partition wall 32 ⁇ / b> A, the wall portion around the rotation axis of the vane rotor 35, the sprocket 33, and the cover 34.
- One vane 35 ⁇ / b> A is disposed in one accommodation chamber 36.
- Each storage chamber 36 is divided into an advance chamber 37 and a retard chamber 38 by a corresponding vane 35A.
- the advance chamber 37 is formed behind the vane 35 ⁇ / b> A in the rotation direction DR in the accommodation chamber 36.
- the retardation chamber 38 is formed in the accommodation chamber 36 on the front side in the rotational direction DR with respect to the vane 35A.
- the volumes of the advance chamber 37 and the retard chamber 38 change in accordance with the supply / discharge mode of the hydraulic oil with respect to the phase change mechanism 30.
- phase change mechanism 30 The operation of the phase change mechanism 30 will be described.
- the valve timing VT is changed.
- Advance When the vane rotor 35 rotates to the most advanced angle side with respect to the housing rotor 31, that is, when the rotation phase of the vane rotor 35 with respect to the housing rotor 31 is the most forward rotation phase in the rotation direction DR, the valve timing VT is the most advanced angle phase. Set to VTmax.
- the valve Timing VT is retarded.
- the vane rotor 35 rotates toward the retard side, that is, in the direction opposite to the rotational direction DR, with respect to the housing rotor 31 by discharging the hydraulic oil from the advance chamber 37 and supplying the hydraulic oil to the retard chamber 38.
- the valve Timing VT is retarded.
- the vane rotor 35 rotates most retarded with respect to the housing rotor 31, that is, when the rotational phase of the vane rotor 35 with respect to the housing rotor 31 is the rearmost rotational phase in the rotational direction DR
- the valve timing VT is the most retarded phase. Set to VTmin.
- phase locking mechanism 40 The configuration of the phase locking mechanism 40 will be described with reference to FIG.
- the phase fixing mechanism 40 includes a first fixing mechanism 50 that restricts the rotation range of the vane rotor 35 relative to the housing rotor 31, and a second fixing that restricts the rotation range of the vane rotor 35 relative to the housing rotor 31 to a range different from the first fixing mechanism 50. And a mechanism 60.
- an opening mechanism 70 (see FIG. 3) for promoting the discharge of hydraulic oil from the advance chamber 37 and the retard chamber 38 is provided.
- the first fixing mechanism 50 and the second fixing mechanism 60 are located in different vanes 35A.
- the rotational phase of the vane rotor 35 with respect to the housing rotor 31 is a rotational phase corresponding to the intermediate angle phase VTmdl (hereinafter referred to as “intermediate rotational phase”)
- the valve timing VT is obtained by the cooperation of the first fixing mechanism 50 and the second fixing mechanism 60. Is fixed to the intermediate angle phase VTmdl.
- FIGS. 3 and 4 show a state in which the rotational phase of the vane rotor 35 with respect to the housing rotor 31 is in the intermediate rotational phase.
- the direction in which the first fixing pin 51 of the first fixing mechanism 50 and the second fixing pin 61 of the second fixing mechanism 60 protrude from the vane 35A is referred to as a “projection direction ZA”, and the first fixing pin 51 and the second fixing pin 61
- accommodation direction ZB The direction in which the fixing pin 61 moves into the vane 35A.
- the first fixing mechanism 50 includes a first fixing pin 51 that moves in the axial direction of the vane rotor 35 with respect to the vane 35A, a first fixing spring 52 that pushes the first fixing pin 51 in the protruding direction ZA, and a first fixing It has the 1st fixed chamber 53 which accommodates the pin 51 and the 1st fixed spring 52, and the 1st engaging groove 56 formed corresponding to the locus
- the first fixing pin 51 moves in the protruding direction ZA and the receiving direction ZB with respect to the vane 35A and protrudes to the outside of the vane 35A, and the protruding direction ZA and the receiving direction with respect to the vane 35A in the vane 35A. And an outer pin 51B that moves to ZB.
- the first fixed spring 52 has an inner spring 52A for pushing the inner pin 51A in the protruding direction ZA and an outer spring 52B for pushing the outer pin 51B in the protruding direction ZA.
- the first fixed chamber 53 is formed in the vane 35A.
- the first fixing pin 51 is partitioned into a first release chamber 54 and a first spring chamber 55. Note that when it is assumed that no hydraulic fluid flows through the clearances of the components constituting the first fixing mechanism 50, the hydraulic fluid flows between the first release chamber 54 and the first spring chamber 55. Not.
- the first engagement groove 56 has two grooves having different depths, that is, a first lower groove 57 having a relatively large depth and a first upper groove 58 having a relatively small depth.
- the first upper groove 58 is formed on the retard side with respect to the first lower groove 57 in the circumferential direction of the housing rotor 31.
- the first advance angle end portion 56A which is the advance angle side end portion of the first lower groove 57, corresponds to the advance angle side end surface of the inner pin 51A of the first fixed pin 51 of the vane rotor 35 in the intermediate rotation phase. It is formed in the position to do.
- the first retarded angle end portion 56 ⁇ / b> B that is the retarded angle side end portion of the first upper groove 58 is formed on the retarded angle side with respect to the first advanced angle end portion 56 ⁇ / b> A in the circumferential direction of the housing rotor 31.
- the second retarded angle end portion 56 ⁇ / b> C which is the retarded end portion of the first lower groove 57, is formed between the first advanced angle end portion 56 ⁇ / b> A and the first retarded angle end portion 56 ⁇ / b> B in the circumferential direction of the housing rotor 31. Has been.
- the second fixing mechanism 60 includes a second fixing pin 61 that moves in the axial direction of the vane rotor 35 with respect to the vane 35A, a second fixing spring 62 that pushes the second fixing pin 61 in the protruding direction ZA, and a second fixing pin. It has the 2nd fixed chamber 63 which accommodates the pin 61 and the 2nd fixed spring 62, and the 2nd engaging groove 66 formed corresponding to the locus
- the second fixing pin 61 moves in the protruding direction ZA and the receiving direction ZB with respect to the vane 35A and protrudes to the outside of the vane 35A, and the protruding direction ZA and the receiving direction with respect to the vane 35A in the vane 35A. And an outer pin 61B that moves to ZB.
- the second fixed spring 62 has an inner spring 62A for pushing the inner pin 61A in the protruding direction ZA and an outer spring 62B for pushing the outer pin 61B in the protruding direction ZA.
- the second fixed chamber 63 is formed in the vane 35A.
- the second fixing pin 61 divides the second release chamber 64 and the second spring chamber 65. When it is assumed that no hydraulic oil flows through the clearances of the parts constituting the second fixing mechanism 60, the hydraulic oil flows between the second release chamber 64 and the second spring chamber 65. Not formed.
- the second engagement groove 66 has two grooves having different depths, that is, a second lower groove 67 having a relatively large depth and a second upper groove 68 having a relatively small depth.
- the second upper groove 68 is formed on the retard side with respect to the second lower groove 67 in the circumferential direction of the housing rotor 31.
- the first fixing pin 51, the first engaging groove 56, the second fixing pin 61, and the second engaging groove 66 correspond to a “self-standing advance mechanism”.
- the fourth retarded angle end 66C which is the retarded end of the second lower groove 67, corresponds to the retarded end face of the inner pin 61A of the second fixed pin 61 of the vane rotor 35 in the intermediate rotational phase. It is formed in the position to do.
- the third retarded angle end portion 66 ⁇ / b> B which is the retarded end portion of the second upper groove 68, is formed on the retarded angle side with respect to the fourth retarded angle end portion 66 ⁇ / b> C in the circumferential direction of the housing rotor 31.
- the second advance angle end portion 66 ⁇ / b> A that is the end portion on the advance angle side of the second lower groove 67 is formed on the advance angle side with respect to the fourth retard angle end portion 66 ⁇ / b> C in the circumferential direction of the housing rotor 31.
- phase locking mechanism 40 The operation of the phase locking mechanism 40 will be described with reference to FIGS.
- the inner pin 51 ⁇ / b> A of the first fixing pin 51 has a tip extending from the position where the tip contacts the bottom surface of the first lower groove 57 of the first engagement groove 56 (hereinafter, “the protruding position of the first fixing pin 51”). It moves in the axial direction with respect to the vane 35 ⁇ / b> A within a range up to a position accommodated inside (hereinafter referred to as “accommodating position of the first fixing pin 51”). Further, the position of the inner pin 51 ⁇ / b> A with respect to the vane 35 ⁇ / b> A changes according to the relationship between the force acting based on the hydraulic pressure of the first release chamber 54 and the elastic force of the first fixed spring 52.
- the outer pin 51B of the first fixing pin 51 moves in the axial direction in conjunction with the inner pin 51A when the first fixing pin 51 is in a position corresponding to the first lower groove 57 in the circumferential direction of the housing rotor 31.
- the force acting on the basis of the hydraulic pressure of the first release chamber 54 and the elastic force of the first fixing spring 52 is allowed to move in the axial direction independently of the inner pin 51A in accordance with the relationship.
- the position where the outer pin 51B has moved to the maximum in the protruding direction ZA within the vane 35A is referred to as an “opening position of the outer pin 51B”. Further, the position where the outer pin 51B has moved to the maximum in the accommodating direction ZB in the vane 35A is referred to as the “closed position of the outer pin 51B”.
- the inner pin 61 ⁇ / b> A of the second fixing pin 61 has a tip extending from the position where the tip contacts the bottom surface of the second lower groove 67 of the second engagement groove 66 (hereinafter “the protruding position of the second fixing pin 61”). It moves in the axial direction with respect to the vane 35 ⁇ / b> A within a range up to a position accommodated therein (hereinafter, “accommodated position of the second fixing pin 61”). Further, the position of the inner pin 61 ⁇ / b> A with respect to the vane 35 ⁇ / b> A changes according to the relationship between the force acting based on the hydraulic pressure of the second release chamber 64 and the elastic force of the second fixed spring 62.
- the outer pin 61B of the second fixing pin 61 moves in the axial direction in conjunction with the inner pin 61A when the second fixing pin 61 is in a position corresponding to the second lower groove 67 in the circumferential direction of the housing rotor 31.
- the force acting on the basis of the hydraulic pressure of the second release chamber 64 and the elastic force of the second fixing spring 62 It is allowed to move in the axial direction independently of the inner pin 61A in accordance with the relationship.
- the position where the outer pin 61B has moved to the maximum in the protruding direction ZA within the vane 35A is referred to as an “opening position of the outer pin 61B”. Further, the position where the outer pin 61B has moved to the maximum in the accommodating direction ZB within the vane 35A is referred to as the “closed position of the outer pin 61B”.
- the operating state of the phase locking mechanism 40 is defined.
- phase fixing mechanism 40 The operation state of the phase fixing mechanism 40 when the first fixing pin 51 and the second fixing pin 61 are located at the accommodation position is referred to as a “phase releasing state of the phase fixing mechanism 40”.
- phase fixing state of the phase fixing mechanism 40 The operation state of the phase fixing mechanism 40 when the first fixing pin 51 and the second fixing pin 61 are located at the protruding positions is referred to as “phase fixing state of the phase fixing mechanism 40”.
- FIG. 3 shows an example of the phase release state of the phase locking mechanism 40.
- FIG. 4 shows the phase locking state of the phase locking mechanism 40.
- the operation of the first fixing pin 51 will be described. Since the second fixing pin 61 operates in accordance with the following operation of the first fixing pin 51, the description of the operation of the second fixing pin 61 is omitted here.
- the force for moving the first fixing pin 51 in the protruding direction ZA is the first fixing.
- the first fixing pin 51 In the circumferential direction of the housing rotor 31, the first fixing pin 51 is located at a position corresponding to the first lower groove 57, and in the axial direction of the housing rotor 31, the first fixing pin 51 is located at the receiving position, and
- the force for moving the first fixing pin 51 in the protruding direction ZA is acting on the first fixing pin 51, the inner pin 51A moves from the housing position shown in FIG. 3 to the protruding position shown in FIG. Further, the outer pin 51B moves from the closed position to the open position in conjunction with the movement of the inner pin 51A.
- the force for moving the first fixing pin 51 in the accommodation direction ZB is the first fixing.
- the first fixing pin 51 is located at the protruding position in the axial direction of the housing rotor 31 and the force for moving the first fixing pin 51 in the housing direction ZB is acting on the first fixing pin 51, the inner pin 51A moves from the protruding position shown in FIG. 4 to the accommodation position shown in FIG. Further, the outer pin 51B moves from the open position to the closed position in conjunction with the movement of the inner pin 51A.
- the vane rotor 35 When the first fixing pin 51 is located at the protruding position, the vane rotor 35 is restricted from rotating relative to the housing rotor 31 in the advance direction with respect to the intermediate rotation phase. Further, when the second fixing pin 61 is located at the protruding position, the vane rotor 35 is restricted from rotating with respect to the housing rotor 31 in the retard direction with respect to the intermediate rotation phase.
- the vane rotor 35 cannot rotate with respect to the housing rotor 31 from an intermediate rotation phase to an advance direction and a retard direction. . That is, the valve timing VT is fixed to the intermediate angle phase VTmdl.
- phase changing mechanism 30 when the engine is started will be described.
- the hydraulic oil in the advance angle chamber 37 and the retard angle chamber 38 of the phase change mechanism 30 is sufficiently less than that during normal engine operation.
- the state where the amount of hydraulic oil is sufficiently low indicates a state where the amount of hydraulic oil is reduced to such an extent that it is difficult to appropriately control the valve timing VT by the hydraulic pressure of the phase change mechanism 30.
- the advance amount of the valve timing VT accompanying the torque fluctuation of the intake camshaft 22 (hereinafter referred to as “intake cam torque fluctuation”) becomes larger than that during normal engine operation.
- intake cam torque fluctuation the valve timing VT is adjusted to the phase fixing mechanism 40 by using the advance angle of the valve timing VT accompanying the intake cam torque fluctuation.
- the intermediate angle phase VTmdl can be fixed.
- self-sustained advance angle an operation in which the valve timing VT is advanced in accordance with intake cam torque fluctuation is referred to as “self-sustained advance angle”.
- phase fixing mechanism 40 when the phase changing mechanism 30 advances independently is shown below.
- the vane rotor 35 advances from the rotational phase corresponding to the most retarded phase VTmin due to intake cam torque fluctuation. Rotate to the corner. Then, the valve timing VT is fixed to the intermediate angle phase VTmdl by operating the first fixing pin 51 and the second fixing pin 61 in the following order (A) to (D).
- the vane rotor 35 advances from the intermediate rotation phase with respect to the housing rotor 31 in the advance direction and the retard direction. Can not rotate. That is, the valve timing VT is fixed to the intermediate angle phase VTmdl.
- the opening mechanism 70 includes a first opening mechanism 71 that communicates the advance chamber 37 and the retard chamber 38 with each other via the first spring chamber 55 of the vane 35A provided with the first fixing mechanism 50, and a second fixing mechanism. And a second opening mechanism 72 that allows the advance chamber 37 and the retard chamber 38 to communicate with each other via the second spring chamber 65 of the vane 35 ⁇ / b> A provided with 60.
- the first opening mechanism 71 includes an advance chamber opening passage 71A that allows the first spring chamber 55 and the advance chamber 37 to communicate with each other, and a retard chamber opening passage that allows the first spring chamber 55 and the retard chamber 38 to communicate with each other. 71B and the outer pin 51B of the first fixing mechanism 50.
- the second opening mechanism 72 includes an advance chamber opening passage 72A that allows the second spring chamber 65 and the advance chamber 37 to communicate with each other, and a retard chamber opening passage that allows the second spring chamber 65 and the retard chamber 38 to communicate with each other. 72B and an outer pin 61B of the second fixing mechanism 60.
- the operation of the first opening mechanism 71 will be described with reference to FIG. Since the second opening mechanism 72 operates according to the following operation of the first opening mechanism 71, the description of the operation of the second opening mechanism 72 is omitted here.
- the first fixing pin 51 when the operation state of the phase fixing mechanism 40 is the phase release state, the first fixing pin 51 is positioned at a position corresponding to the first lower groove 57 in the circumferential direction of the housing rotor 31. And when the force which moves the 1st fixing pin 51 to the accommodation direction ZB is acting on the 1st fixing pin 51, the outer side pin 51B is located in a closed position. For this reason, the advance chamber opening passage 71A and the retard chamber opening passage 71B are closed by the outer pin 51B. That is, the first spring chamber 55 and the advance chamber 37 and the retard chamber 38 are blocked from each other.
- the operation state of the phase fixing mechanism 40 is the phase release state
- the first fixing pin 51 is positioned in a position not corresponding to the first lower groove 57 in the circumferential direction of the housing rotor 31.
- the outer side pin 51B is located in an open position.
- the advance chamber opening passage 71A and the retard chamber opening passage 71B are opened from the outer pin 51B. That is, the first spring chamber 55 and the advance chamber 37 and the retard chamber 38 communicate with each other.
- the operation state of the phase locking mechanism 40 is in the phase release state when the engine is started. There are cases.
- hydraulic oil is supplied to one of the advance chamber 37 and the retard chamber 38 via the oil control valve 82.
- the hydraulic oil is also supplied to the other of the advance chamber 37 and the retard chamber 38 via the first spring chamber 55. For this reason, the amount of hydraulic oil supplied to the other of the advance chamber 37 and the retard chamber 38 is larger than when the advance chamber 37 and the retard chamber 38 are not in communication with each other.
- the oil control valve 82 connects an advance port connecting the advance oil passage 85 and the supply oil passage 84 or the discharge oil passage 88 to each other, and connects a retard oil passage 86 and the supply oil passage 84 or the discharge oil passage 88 to each other. And a retarding port.
- the connection relationship between the advance oil passage 85 and the retard oil passage 86 and the supply oil passage 84 and the discharge oil passage 88 and the passage areas of the advance port and the retard port are used as command signals output from the electronic control unit 91. It changes according to the duty ratio.
- the electronic control unit 91 changes the operation state of the oil control valve 82 (hereinafter referred to as “OCV operation mode”) by changing the duty ratio output to the actuator of the oil control valve 82.
- OCV operation mode As the OCV operation mode selected by the electronic control unit 91, an advance angle mode, a retard angle mode, and a holding mode are prepared in advance.
- the connection relationship between the advance oil passage 85 and the retard oil passage 86 and the supply oil passage 84 and the discharge oil passage 88 and the passage areas of the advance port and the retard port are reduced. Be changed.
- the oil control valve 82 has a retarded angle zone, a dead zone, and an advanced angle zone as operating regions corresponding to the duty ratio.
- the retarded angle zone has a range from the minimum duty ratio in the duty ratio changeable region to a predetermined first duty ratio.
- the oil control valve 82 connects the advance oil passage 85 and the discharge oil passage 88 to each other, and connects the retard oil passage 86 and the supply oil passage 84 to each other when the duty ratio of the retarded zone is output. .
- the dead zone has a range from a predetermined first duty ratio to a predetermined second duty ratio.
- the oil control valve 82 blocks the advance oil passage 85 and the retard oil passage 86 from the supply oil passage 84 and the discharge oil passage 88 when the duty ratio of the dead zone is output.
- the advance angle sensitive zone has a range from a predetermined second duty ratio to a maximum duty ratio in a changeable range of the duty ratio.
- the oil control valve 82 connects the advance oil passage 85 and the supply oil passage 84 to each other, and connects the retard oil passage 86 and the discharge oil passage 88 to each other when the duty ratio of the advance angle sensing zone is output. .
- the electronic control unit 91 outputs the following duty ratio according to the OCV operation mode.
- the flow rate of the hydraulic oil in the advance oil passage 85 increases as the passage area of the advance port increases.
- the passage area of the advance port is increased as the duty ratio in the advance zone becomes closer to the maximum duty ratio, or as the duty ratio in the retard zone becomes closer to the minimum duty ratio. growing.
- the flow rate of the hydraulic oil in the retard oil passage 86 increases as the passage area of the retard port increases.
- the passage area of the retard port is increased as the duty ratio in the retard zone approaches the minimum duty ratio, or as the duty ratio in the advance zone approaches the maximum duty ratio. growing.
- the electronic control unit 91 changes the magnitude of the duty ratio in the advance angle zone when it is necessary to change the amount of hydraulic oil supplied to the advance chamber 37 in the advance mode. Further, when it is necessary to change the amount of hydraulic oil supplied to the retard chamber 38 in the retard mode, the magnitude of the duty ratio in the retard angle zone is changed.
- OSV operation mode changes the operation state of the oil switching valve 83 (hereinafter referred to as “OSV operation mode”) by changing the command signal for the actuator of the oil switching valve 83.
- valve timing control Details of valve timing control will be explained.
- the advance angle mode is selected as the OCV operation mode. Further, the phase cancellation mode is selected as the OSV operation mode.
- the retard mode is selected as the OCV operation mode. Further, the phase cancellation mode is selected as the OSV operation mode.
- the holding mode is selected as the OCV operation mode.
- the phase cancellation mode is selected as the OSV operation mode. Note that when the absolute value of the difference between the average value of the valve timing VT and the target angular phase VTtrg is greater than or equal to a predetermined value due to the variation of the valve timing VT, feedback control is performed to bring the average value closer to the target angular phase VTtrg. Is called.
- the OSV operation mode is changed from the phase fixed mode to the phase release mode. Further, the advance angle mode, the retard angle mode, and the hold mode are selected as the OCV operation mode according to any of the phase advance angle request, the phase delay angle request, and the phase hold request.
- phase fixing mode is selected as the OSV operation mode.
- the start release condition is set as a condition for confirming that there is little possibility that the valve timing VT becomes unstable even when the operation state of the phase locking mechanism 40 is changed to the phase release state when the engine is started. .
- the state in which the valve timing VT is unstable indicates a state in which the variation in the valve timing VT is large because the advance chamber 37 and the retard chamber 38 are not filled with hydraulic fluid.
- the valve timing VT is fixed to the intermediate angle phase VTmdl by the self-advanced advance angle without controlling the OCV operation mode and the OSV operation mode at the time of engine start.
- the OCV operation If the mode and the OSV operation mode are not controlled, the following problem may occur.
- the state in which the OCV operation mode and the OSV operation mode are not controlled is determined by determining whether a predetermined condition defined in advance is satisfied according to the engine operation state or the like, and the operation mode is determined according to the result. Indicates that the control to be changed is not executed.
- the control of the OCV operation mode at the time of engine start is not performed, so that the retard angle mode as the OCV operation mode selected at the time of the last engine stop is maintained, and the retard at the start of engine start.
- the amount of hydraulic fluid in the chamber 38 is large, the hydraulic fluid in the retard chamber 38 is difficult to be discharged.
- the resistance to the advance angle of the valve timing VT accompanying the intake cam torque fluctuation increases, so that the self-sustained advance angle is hindered.
- the first phase at the start of the engine start when the phase release mode as the OSV operation mode selected at the last engine stop is maintained.
- the amount of hydraulic fluid in at least one of the release chamber 54 and the second release chamber 64 is large, at least one of the first fixing pin 51 and the second fixing pin 61 does not move to the protruding position. For this reason, even if the vane rotor 35 advances to the intermediate rotation phase due to the intake cam torque fluctuation, the valve timing VT is not fixed to the intermediate angle phase VTmdl.
- the advance timing mode is selected as the OCV operation mode and the phase is set as the OSV operation mode in order to increase the frequency at which the valve timing VT is fixed at the intermediate angle phase VTmdl by the self-advance at the start of the engine. Select fixed mode.
- phase difference VTD the DUTY ratio of the oil control valve 82 is controlled based on the phase difference VTD. Specifically, as the phase difference VTD increases, that is, as the amount of hydraulic oil remaining in the retard chamber 38 (hereinafter, “residual oil amount Q”) increases, the hydraulic fluid to the advance chamber 37 is increased. The DUTY ratio of the oil control valve 82 is controlled so that the supply amount of the oil increases.
- the electronic control unit 91 performs oil control so that the amount of hydraulic oil supplied to the advance angle chamber 37 in the advance angle control at start-up is greater than the amount of hydraulic oil supplied to the advance angle chamber 37 in the self-advanced advance angle control.
- the duty ratio of the valve 82 is controlled. For this reason, the force for advancing the valve timing VT by the hydraulic pressure of the advance angle chamber 37 in the starting advance angle control is larger than the force for advancing the valve timing VT by the oil control valve 82 in the self-supporting advance angle control. Therefore, even when the amount of hydraulic oil in the retard chamber 38 is large at the start of engine starting, the valve timing VT is quickly changed to the intermediate angle phase VTmdl by the starting advance angle control.
- One engine index for evaluating the startability of the internal combustion engine 1 is the engine start period. In order to satisfy the startability required for the internal combustion engine 1, it is necessary to start the internal combustion engine 1 so that the actual engine start period is equal to or shorter than the required start period under various start environments.
- the main factor affecting the engine start period is the valve timing VT at the time of engine start. Therefore, the internal combustion engine 1 performs phase lock control for fixing the valve timing VT at the time of engine start to the intermediate angle phase VTmdl with the intention of completing the start within the required start period.
- the intermediate angle phase VTmdl is adapted as a valve timing VT that enables the engine start to be completed within the required start period even in a low temperature environment where the combustibility of the air-fuel mixture is greatly reduced.
- the low temperature environment is an environment where the outside air temperature is below freezing.
- valve timing VT is fixed to the intermediate angle phase VTmld during the engine stop transition period, so that the OCV operation mode and the OSV operation mode are controlled based on the phase lock request set according to the engine stop condition.
- valve timing VT is fixed to the intermediate angle phase VTmdl at the time of the last engine stop transition, that is, when the valve timing VT is fixed to the intermediate angle phase VTmdl at the start of the current engine start, The start of the internal combustion engine 1 is completed within the required start period.
- valve timing VT is fixed to the intermediate angle phase VTmdl at the start of the engine start, so that within the required start period in a low temperature environment.
- the start of the internal combustion engine 1 can also be completed.
- fixed period the period required from the start of engine start until the valve timing VT is fixed to the intermediate angle phase VTmdl (hereinafter referred to as “fixed period”) falls within the required fixed period. . That is, even when the valve timing VT is fixed to the intermediate angle phase VTmdl after the start of the engine start, there is a high possibility that the engine start period exceeds the required start period when the fixed period exceeds the required fixed period. This tendency is particularly remarkable in a low temperature environment.
- the electronic control unit 91 fixes the valve timing VT to the intermediate angle phase VTmdl within the required fixed period.
- a start time control selection process is performed as a process for selecting a corner method.
- the resistance force against the advance angle of the valve timing VT due to intake cam torque fluctuation at the time of engine start varies depending on the residual oil amount Q. Therefore, the advance speed of the valve timing VT based on phase advance control (hereinafter referred to as “hydraulic advance speed”) and the advance speed of the valve timing VT caused by intake cam torque fluctuation (hereinafter referred to as “self-sustained advance speed”) are as follows. The following relationship is established according to the residual oil amount Q.
- an advance method of the valve timing VT at the time of starting the engine is selected based on the relationship between the hydraulic advance angle speed and the independent advance angle speed. Specifically, the residual oil amount Q at the time when the starting operation of the internal combustion engine 1 is started, that is, the residual oil amount Q at the time of starting the engine, is compared with a reference oil amount QA as a preset determination value, When the remaining oil amount Q is equal to or greater than the reference oil amount QA, the valve timing VT is advanced by start-up advance angle control. On the other hand, when the remaining oil amount Q is less than the reference oil amount QA, the valve timing VT is advanced by the self-standing advance angle. At this time, as the control of the variable valve operating apparatus 20, the self-advanced advance angle control is performed.
- the reference oil amount QA corresponds to a “reference value”.
- the remaining oil amount Q at the time of engine start is the remaining oil amount Q at the time of completion of the last engine stop (hereinafter, “residual oil amount Q at the time of the last engine stop”) and the engine stop period, that is, the completion of the last engine stop It can be calculated as the difference from the amount of hydraulic oil flowing out from the retard chamber 38 to the outside (hereinafter referred to as “the amount of outflow at the time of stop”) in the period from the start of the engine to the start of the current engine start. Further, the outflow amount at the time of stop is the speed at which hydraulic oil in the retard chamber 38 flows out from the clearance of the phase change mechanism 30 during the engine stop period (hereinafter referred to as “outflow speed at stop”) and the length of the engine stop period. It can be calculated as a product. As the outflow speed at stop, a speed that represents the outflow speed of hydraulic oil during the engine stop period can be used.
- cooling water temperature difference TWD the absolute value of the difference between the cooling water temperature TW when the engine is stopped and the cooling water temperature TW when the engine is started (hereinafter referred to as “cooling water temperature difference TWD”) is used as an index of the engine stop period.
- the outside air temperature TA at the time of engine start is used as an index of the outflow speed at the time of stoppage, and the relationship between these indices and the valve timing advance method at the time of engine start is defined in the control region map of FIG.
- the “cooling water temperature TW when the engine is stopped” specifically indicates “the cooling water temperature TW when the engine is stopped”.
- the “cooling water temperature TW at the time of starting the engine” specifically indicates “the cooling water temperature TW at the start of the engine starting”.
- the “outside air temperature TA at the time of starting the engine” specifically indicates “the outside air temperature TA at the start of the engine starting”.
- the degree of decrease in the coolant temperature TW during the engine stop period increases as the engine stop period becomes longer. For this reason, the change in the direction in which the coolant temperature difference TWD increases on the control region map indicates that the engine stop period is long.
- the outflow speed at the time of stop increases as the viscosity of the hydraulic oil decreases during the engine stop period. Further, the viscosity of the hydraulic oil during the engine stop period has a correlation with the temperature of the hydraulic oil during the engine stop period. Further, the temperature of the hydraulic oil during the engine stop period has a correlation with the coolant temperature TW during the engine stop period. Further, the coolant temperature TW during the engine stop period has a correlation with the coolant temperature TW at the current engine start. Further, the coolant temperature TW at the current engine start has a correlation with the outside air temperature TA at the current engine start. For this reason, the change in the direction in which the outside air temperature TA increases on the control region map indicates that the outflow speed at the time of stop is high.
- the control region map shows that the residual oil amount Q at engine start is less than the reference oil amount QA (Hereinafter referred to as “self-sustained advance angle region RA”) and a region (hereinafter referred to as “hydraulic advance angle region RB”) in which the residual oil amount Q at the time of engine start is estimated to be equal to or greater than the reference oil amount QA. It is divided.
- the self-sustained advance angle area AR is an advance angle of the valve timing VT at the time of starting the engine based on the fact that the residual oil amount Q is less than the reference oil amount QA is suggested by the cooling water temperature difference TWD and the outside air temperature TA. As a method, it is set as an area for designating a self-supporting advance angle.
- the hydraulic advance angle region RB is an advance angle of the valve timing VT at the start of the engine based on the fact that the residual oil amount Q is equal to or greater than the reference oil amount QA based on the coolant temperature difference TWD and the outside air temperature TA. As a method, it is set as an area for designating phase advance control.
- the start time control selection process it is determined whether the coolant temperature difference TWD and the outside air temperature TA at the time of engine start belong to the self-advanced advance region RA or the hydraulic advance region RB.
- the independent advance angle is selected as the advance method of the valve timing VT.
- the advance angle control at the start is performed as the control of the phase changing mechanism 30.
- the phase advance control is selected as the advance method of the valve timing VT.
- the electronic control unit 91 is based on the remaining oil amount Q at the time of engine stop, separately from the start time control selection process using the control region map. It has a stop transition control designation process (FIG. 7) for selecting an advance angle method.
- phase fluctuation width FW the fluctuation range of the valve timing VT at the time of the engine stop transition
- a self-advanced advance angle can be designated as the advance method of the valve timing VT.
- the phase fluctuation width FW can be calculated as an absolute value of a difference between the maximum value and the minimum value of the valve timing VT during a period in which the crank angle CA changes over a predetermined amount.
- the stop transition control designating process when the phase fluctuation width FW at the time of engine stop indicates that the residual oil amount Q at the time of engine stop is less than the reference oil amount QA, a history indicating that is stored. To do. Then, when the same history is confirmed at the time of the engine start this time, the self-sustained advance angle is selected as the advance method of the valve timing VT. Note that selection of the advance angle method based on the history is performed in preference to selection of the advance angle method using the control region map.
- step S11 it is determined whether or not it is during the engine stoppage transition period.
- the engine stop transition period is in progress.
- step S11 When it is determined in step S11 that the engine stop transition period is in progress, whether or not the valve timing VT is fixed to the intermediate angle phase VTmdl by the phase fixing mechanism 40 in step S12, that is, the operation state of the phase fixing mechanism 40 is phase fixed. It is determined whether or not it is in a state.
- valve timing VT is fixed at the intermediate angle phase VTmdl based on the state where the valve timing VT is maintained at the intermediate angle phase VTmdl for a predetermined period or longer.
- step S12 When it is determined in step S12 that the valve timing VT is not fixed to the intermediate angle phase VTmdl, it is determined in step S13 whether or not the phase fluctuation width FW is equal to or larger than the determination value FWX.
- step S13 when it is determined that the phase fluctuation range FW is equal to or larger than the determination value FWX, the residual oil amount Q when the engine is stopped is estimated to be less than the reference oil amount QA. For this reason, it can be estimated that the residual oil amount Q at the time of engine start is less than the reference oil amount QA.
- step S14 when it is determined in step S13 that the phase fluctuation range FW is less than the determination value FWX, the residual oil amount Q when the engine is stopped is estimated to be greater than or equal to the reference oil amount QA.
- the oil amount determination flag is set to ON. The oil amount determination flag corresponds to “history at stop”.
- step S21 it is determined whether the oil amount determination flag is set to ON.
- step S21 when it is determined in step S21 that the oil amount determination flag is set to OFF, that is, when there is a history indicating that the remaining oil amount Q at the time of the last engine stop is less than the reference oil amount QA, the process proceeds to step S32. Transition.
- step S21 when it is determined that the oil amount determination flag is set to ON, that is, there is a history indicating that the remaining oil amount Q at the time of the last engine stop is equal to or greater than the reference oil amount QA.
- the process proceeds to step S22.
- step S22 based on the cooling water temperature difference TWD and the outside air temperature TA, whether or not the condition for executing the starting advance angle control is satisfied, that is, whether or not the residual oil amount Q is equal to or greater than the reference oil amount QA. Determine.
- step S32 self-supporting advance angle control is performed. That is, the advance angle mode is selected as the OCV operation mode, and the phase lock mode is selected as the OSV operation mode.
- step S31 start-up advance angle control is performed in step S31. That is, the advance angle mode is selected as the OCV operation mode, and the phase cancellation mode is selected as the OSV operation mode. Further, when the valve timing VT reaches the intermediate angle phase VTmdl, the OSV operation mode is changed from the advance angle mode to the hold mode. In step S33, the hydraulic pressure determination flag is set to OFF.
- the internal combustion engine 1 of the present embodiment has the following effects.
- valve timing VT is advanced by the oil pressure of the phase change mechanism 30 when the phase fixing mechanism 40 is in a phase-released state and the residual oil amount Q is equal to or greater than the reference oil amount QA when the engine is started. According to this configuration, it is possible to suppress the startability of the internal combustion engine 1 from being deteriorated due to the hydraulic oil remaining in the retard chamber 38.
- the remaining oil amount Q is greater than or equal to the reference oil amount QA as compared with the configuration in which the valve timing VT is advanced by the self-standing advance angle even when the remaining oil amount Q is greater than or equal to the reference oil amount QA when the engine is started. In this case, the advance speed of the valve timing VT is increased.
- the startability of the internal combustion engine 1 is less likely to be lower than that of the configuration to be compared.
- the assist spring having a smaller restoring force the resistance of the assist spring when retarding the valve timing VT during normal engine operation is reduced. For this reason, the loss accompanying the drive of the oil pump 81 is reduced.
- the phase fixing mechanism 40 sets the valve timing VT to the intermediate The angular phase is fixed at VTmdl. According to this configuration, the phase variation width FW is smaller than the configuration in which the valve timing VT is not fixed by the phase fixing mechanism 40 when the engine is started.
- the valve timing VT is changed to the intermediate angle phase VTmdl by the oil pressure of the phase changing mechanism 30. Hold. According to this configuration, the startability of the internal combustion engine 1 is improved as compared with a configuration in which the valve timing VT is held at a phase retarded from the intermediate angle phase VTmdl when the engine is started.
- the valve timing VT is advanced by a self-sustained advance angle when the engine is started.
- the intermediate angle is set at an early stage when the valve timing VT is early. The frequency of changing to the phase VTmdl increases.
- the conditions for selecting the control to be executed when the engine is started can be changed as follows.
- the pressure of the hydraulic oil remaining in the retarding chamber 38 is set as “residual hydraulic pressure P”
- the control is executed at the time of engine start based on the result of comparison between the residual hydraulic pressure P and the reference hydraulic pressure PA as the determination value.
- the reference hydraulic pressure PA is preset based on the result of a test or the like, and corresponds to a “reference value”.
- control is executed at the time of engine start according to the result of comparison between the residual oil pressure P and the reference oil pressure PA.
- Select control The control in this case corresponds to a control in which the residual oil amount Q in the control of the above embodiment is replaced with the residual oil pressure P.
- a control to be executed at the time of starting the engine is selected according to a result of comparison between the residual oil amount Q and the reference oil amount QA at the time of engine start and a result of comparison between the remaining oil pressure P and the reference oil pressure PA.
- the control indicates that at least one of the comparison between the residual oil amount Q and the reference oil amount QA and the comparison between the residual oil pressure P and the reference oil pressure PA suggests that the residual oil amount Q at the time of starting the engine is large.
- Advance angle control at start is selected.
- both the comparison between the residual oil amount Q and the reference oil amount QA and the comparison between the residual oil pressure P and the reference oil pressure PA indicate that the residual oil amount Q at the engine start is large, Select control.
- the remaining oil pressure P at the time of starting the engine is calculated based on at least one of the remaining oil amount Q and the remaining oil pressure P at the time of the last engine stop and the outflow amount at the time of stop. You can also
- the method of selecting the advance method can be changed as follows. That is, the engine stop period and the determination period can be compared, and the advance method can be selected according to the result. Specifically, when the engine stop period is equal to or longer than the determination period, that is, when the residual oil amount Q at the time of engine start is estimated to be less than the reference oil amount QA due to leakage of hydraulic oil during the engine stop period, the valve timing VT Select self-advance as the advance method.
- the advance method of the valve timing VT is selected based on the control region map To do. Note that when this selection method is adopted, the process of step S13 of the stop transition control designation process is omitted.
- the control area is defined by the cooling water temperature difference TWD and the outside air temperature TA, but the cooling water temperature TW at the time of starting the engine is used instead of the outside air temperature TA. You can also.
- the coolant temperature TW at the time of starting the engine is an index of the temperature of the hydraulic oil during the engine stop period similarly to the outside air temperature TA. Therefore, even if the map is adapted using the same coolant temperature TW instead of the outside air temperature TA. The same effect as the above embodiment can be obtained.
- the contents of the determination process in step S12 can be changed as follows. That is, the phase variation width FW when the engine is stopped is compared with the determination value when the engine is stopped, and based on the result, it is determined whether or not the valve timing VT is fixed to the intermediate angle phase VTmdl. Specifically, when the phase fluctuation width FW is equal to or smaller than the stop determination value, it is determined that the valve timing VT is fixed at the intermediate angle phase VTmdl. On the other hand, when the phase fluctuation width FW is larger than the stop determination value, it is determined that the valve timing VT is not fixed to the intermediate angle phase VTmdl.
- the stop determination value is set in advance based on a test or the like as a value for determining that the valve timing VT is fixed at the intermediate angle phase VTmdl.
- the contents of the determination process in step S22 can be changed as follows. That is, the phase variation width FW at the time of engine start is compared with the determination value at the time of start, and based on the result, it is determined whether or not the residual oil amount Q is greater than or equal to the reference oil amount QA. Specifically, when the phase variation width FW at the time of engine start is equal to or greater than the determination value at start, it is determined that the residual oil amount Q is equal to or greater than the reference oil amount QA.
- the phase fluctuation width FW at the time of starting the engine is less than the determination value at the time of starting, it is determined that the remaining oil amount Q is less than the reference oil amount QA.
- the starting determination value is set in advance based on a test or the like as a value for determining that the residual oil amount Q at the time of starting the engine is equal to or greater than the reference oil amount QA.
- step S31 of the start time control selection process of the above embodiment the valve timing VT is held at the intermediate angle phase VTmdl by the hydraulic pressure of the phase changing mechanism 30, but is advanced from the most retarded angle phase VTmin.
- the valve timing VT can also be maintained within a predetermined range including the intermediate angle phase VTmdl.
- step S31 of the start time control selection process of the above embodiment (FIG. 8) when the valve timing VT reaches the intermediate angle phase VTmdl according to the advance angle of the valve timing VT by the hydraulic pressure of the phase change mechanism 30, the hydraulic pressure Although the timing VT is maintained, the valve timing VT can be fixed to the intermediate angle phase VTmdl by the phase fixing mechanism 40.
- the assist spring can be omitted from the variable valve gear 20.
- the oil control valve 82 and the oil are controlled by a single oil control valve that controls the supply / discharge mode of the hydraulic oil in the advance chamber 37, the retard chamber 38, and the release chambers 54 and 64.
- the switching valve 83 can be used instead.
- a hole for fitting the first fixing pin 51 can be formed at a position corresponding to the intermediate rotation phase.
- the end of the first upper groove 58 is extended to the same hole.
- a hole for fitting the second fixing pin 61 may be formed at a position corresponding to the intermediate rotation phase.
- At least one of the first engaging groove 56 and the second engaging groove 66 is formed in the vane rotor 35, and at least one of the first fixing pin 51 and the second fixing pin 61 is a housing rotor. 31 can also be provided.
- the outer pin 51B, the outer spring 52B, and the first release mechanism 71 can be omitted from the first fixing mechanism 50. Further, the outer pin 61B, the outer spring 62B, and the second opening mechanism 72 can be omitted from the second fixing mechanism 60.
- At least one of the first fixing pin 51 and the second fixing pin 61 may be one that protrudes and accommodates in the radial direction with respect to the vane 35A.
- it corresponds to the engagement groove and the second engagement groove 66 corresponding to the first engagement groove 56.
- At least one of the engaging grooves is formed in the housing rotor 31.
- one of the first fixing mechanism 50 and the second fixing mechanism 60 can be omitted.
- the first fixing mechanism 50 or the second fixing mechanism 60 included in the variable valve operating apparatus 20 has the first engagement groove 56.
- a hole into which the first fixing pin 51 or the second fixing pin 61 is fitted is provided.
- the intermediate angle phase VTmdl is adopted as the valve timing VT to be fixed by the phase fixing mechanism 40, but other valve timings VT may be adopted instead.
- the other valve timing VT is any valve timing VT between the most retarded angle phase VTmin and the intermediate angle phase VTmdl within a range in which the valve timing VT can be fixed within the required fixed time, or Any one of the valve timings VT on the more advanced side than the intermediate angle phase VTmdl can be selected.
- phase fixing mechanism 50 ... first fixing mechanism, 51 ... first fixing pin (self-standing advance mechanism), 51A ... Inner pin, 51B ... outer pin, 52 ... first fixed spring, 52A ... inner spring, 52B ... outer spring, 53 ... first fixed chamber, 54 ... first release chamber, 55 ... first spring chamber 56 ... First engaging groove (self-standing advance mechanism), 56A ... First advance end, 56B ... First retard end, 56C ... Second retard end, 57 ... First lower step groove, 58 ... First upper groove, 60 ... second fixing mechanism, 61 ... second fixing pin (self-standing advance mechanism), 61A ... inner pin, 61B ... outer pin, 62 ... second fixing spring, 62A ... inner spring, 62B ...
- outer Spring 63 ... second fixing chamber, 64 ... second release chamber, 65 ... second spring chamber, 66 ... second engaging groove (self-standing advance mechanism), 66A ... second advance end, 66B ... third Delay angle end portion, 66C ... Fourth retardation angle end portion, 67 ... Second lower groove, 68 ... Second upper groove, 70 ... Release mechanism, 71 ... First release mechanism, 71A ... Advance chamber opening passage, 71B ... Delay angle chamber opening passage, 72 ... second opening mechanism, 72A ... advance angle chamber opening passage, 72B ... retarding chamber opening passage, 80 ... hydraulic mechanism, 81 ... oil pump, 8 ... Oil control valve, 83 ... Oil switching valve, 84 ... Supply oil path, 85 ...
- Advance oil path 86 ... Delay oil path, 87 ... Release oil path, 88 ... Discharge oil path, 90 ... Control device, 91 ... Electronic control device, 92 ... crank position sensor, 93 ... cam position sensor, 94 ... cooling water temperature sensor, 95 ... accelerator position sensor.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
(A)クランクポジションセンサ92の出力に基づいて、クランク角度CAに相当する演算値を算出する。
(B)クランク角度CAの演算値に基づいて、クランクシャフト15の回転速度(以下、「機関回転速度NE」)に相当する演算値を算出する。
(C)カムポジションセンサ93の出力に基づいて、カム角度DAに相当する演算値を算出する。
(D)クランク角度CAおよびカム角度DAに基づいて、バルブタイミングVTに相当する演算値を算出する。
(E)冷却水温度センサ94の出力に基づいて、冷却水温度TWに相当する演算値を算出する。
(F)アクセルポジションセンサ95の出力に基づいて、アクセル踏込量APに相当する演算値を算出する。
本実施形態の内燃機関1は、以下の効果を奏する。
本発明の実施態様は上記実施形態に限られるものではなく、例えば以下に示すように変更することもできる。また以下の各変形例は、上記実施形態についてのみ適用されるものではなく、異なる変形例同士を互いに組み合わせて実施することもできる。
Claims (8)
- 進角室または遅角室についての作動油の供給または排出により内燃機関のバルブタイミングを変更する油圧式の位相変更機構と、前記バルブタイミングを最遅角位相よりも進角側の特定角位相に固定する位相固定機構と、カムトルク変動にともない前記バルブタイミングを前記最遅角位相から前記特定角位相に向けて進角させる自立進角機構とを備える可変動弁装置のための制御装置であって、
前記遅角室に残存している作動油の量を残存油量とし、前記遅角室に残存している作動油の圧力を残存油圧として、
前記制御装置は、機関始動時において前記残存油量または前記残存油圧が大きいとき、前記機関始動時において前記残存油量または前記残存油圧が小さいときと比較して、前記進角室への作動油の供給量を多くする
ことを特徴とする可変動弁装置の制御装置。 - 請求項1に記載の可変動弁装置の制御装置において、
前記機関始動時における前記残存油量または前記残存油圧が基準値以上のとき、前記機関始動時における前記残存油量または前記残存油圧が前記基準値未満のときと比較して、前記進角室への作動油の供給量を多くする
ことを特徴とする可変動弁装置の制御装置。 - 請求項2に記載の可変動弁装置の制御装置において、
前記残存油量または前記残存油圧が前記基準値未満の状態における前記内燃機関の始動の開始後において、前記カムトルク変動にともない前記バルブタイミングが前記特定角位相まで進角したとき、前記位相固定機構が前記バルブタイミングを前記特定角位相に固定する
ことを特徴とする可変動弁装置の制御装置。 - 請求項2または3に記載の可変動弁装置の制御装置において、
前記バルブタイミングを前記特定角位相に固定しない前記位相固定機構の動作状態を位相解除状態として、前記機関始動時において前記残存油量または前記残存油圧が前記基準値以上のとき、前記位相固定機構が前記位相解除状態にある
ことを特徴とする可変動弁装置の制御装置。 - 請求項2~4のいずれか一項に記載の可変動弁装置の制御装置において、
前記最遅角位相よりも進角側かつ前記特定角位相を含む所定の位相範囲を特定位相範囲として、前記残存油量または前記残存油圧が前記基準値以上の状態における前記内燃機関の始動の開始後において、前記バルブタイミングが前記特定位相範囲まで進角したとき、前記位相変更機構の油圧により前記バルブタイミングを前記特定位相範囲に保持する
ことを特徴とする可変動弁装置の制御装置。 - 請求項1~5のいずれか一項に記載の可変動弁装置の制御装置において、
前記機関始動時の前記バルブタイミングの変動幅に基づいて前記機関始動時の前記残存油量および前記残存油圧の少なくとも一方を推定する
ことを特徴とする可変動弁装置の制御装置。 - 請求項1~5のいずれか一項に記載の可変動弁装置の制御装置において、
最後の機関停止移行時における前記バルブタイミングの変動幅が所定変動幅以上であることを示す履歴を停止時履歴として、今回の前記内燃機関の始動の開始後において、前記カムトルク変動にともない前記バルブタイミングが前記特定角位相まで進角したとき、かつ前記停止時履歴があるとき、前記位相固定機構が前記バルブタイミングを前記特定角位相に固定する
ことを特徴とする可変動弁装置の制御装置。 - 請求項1~7のいずれか一項に記載の可変動弁装置の制御装置において、
最後の機関停止時における前記残存油量および前記残存油圧の少なくとも一方と、前記最後の機関停止時から前記機関始動時までの期間における前記遅角室からの作動油の流出量とに基づいて、前記機関始動時の前記残存油量および前記残存油圧の少なくとも一方を推定する
ことを特徴とする可変動弁装置の制御装置。
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CN201180019003.4A CN103124835B (zh) | 2011-09-27 | 2011-09-27 | 可变气门装置的控制装置 |
JP2012539116A JP5403168B2 (ja) | 2011-09-27 | 2011-09-27 | 可変動弁装置の制御装置 |
PCT/JP2011/072061 WO2013046332A1 (ja) | 2011-09-27 | 2011-09-27 | 可変動弁装置の制御装置 |
US13/637,871 US8857391B2 (en) | 2011-09-27 | 2011-09-27 | Controller for variable valve actuation device |
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PCT/JP2011/072061 WO2013046332A1 (ja) | 2011-09-27 | 2011-09-27 | 可変動弁装置の制御装置 |
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JP6273801B2 (ja) * | 2013-11-29 | 2018-02-07 | アイシン精機株式会社 | 弁開閉時期制御装置 |
CN110667560A (zh) * | 2019-09-26 | 2020-01-10 | 浙江吉利新能源商用车集团有限公司 | 一种车辆降噪方法、装置及车辆 |
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JPH09324612A (ja) * | 1996-04-03 | 1997-12-16 | Toyota Motor Corp | 内燃機関の可変バルブタイミング機構 |
JP2010223212A (ja) * | 2009-02-26 | 2010-10-07 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
JP2010261312A (ja) * | 2009-04-28 | 2010-11-18 | Toyota Motor Corp | 内燃機関の可変動弁装置 |
JP2011185100A (ja) * | 2010-03-04 | 2011-09-22 | Denso Corp | 内燃機関のバルブタイミング変更装置 |
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EP0799976B1 (en) * | 1996-04-03 | 2000-07-19 | Toyota Jidosha Kabushiki Kaisha | Variable valve timing mechanism for internal combustion engine |
JP2002047952A (ja) * | 2000-07-31 | 2002-02-15 | Toyota Motor Corp | 内燃機関のバルブタイミング制御装置 |
JP2006170085A (ja) | 2004-12-16 | 2006-06-29 | Aisin Seiki Co Ltd | 弁開閉時期制御装置及び最低トルクの設定方法 |
JP4358180B2 (ja) * | 2005-11-04 | 2009-11-04 | 株式会社日立製作所 | 内燃機関のバルブタイミング制御装置 |
JP2009024659A (ja) | 2007-07-23 | 2009-02-05 | Hitachi Ltd | 内燃機関のバルブタイミング制御装置 |
JP4985729B2 (ja) * | 2008-09-11 | 2012-07-25 | 株式会社デンソー | バルブタイミング調整装置 |
JP2010203315A (ja) | 2009-03-03 | 2010-09-16 | Toyota Motor Corp | 内燃機関の可変動弁装置 |
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2011
- 2011-09-27 WO PCT/JP2011/072061 patent/WO2013046332A1/ja active Application Filing
- 2011-09-27 US US13/637,871 patent/US8857391B2/en active Active
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Patent Citations (4)
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JPH09324612A (ja) * | 1996-04-03 | 1997-12-16 | Toyota Motor Corp | 内燃機関の可変バルブタイミング機構 |
JP2010223212A (ja) * | 2009-02-26 | 2010-10-07 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
JP2010261312A (ja) * | 2009-04-28 | 2010-11-18 | Toyota Motor Corp | 内燃機関の可変動弁装置 |
JP2011185100A (ja) * | 2010-03-04 | 2011-09-22 | Denso Corp | 内燃機関のバルブタイミング変更装置 |
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JPWO2013046332A1 (ja) | 2015-03-26 |
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