WO2014112055A1 - 内燃機関の制御装置 - Google Patents
内燃機関の制御装置 Download PDFInfo
- Publication number
- WO2014112055A1 WO2014112055A1 PCT/JP2013/050691 JP2013050691W WO2014112055A1 WO 2014112055 A1 WO2014112055 A1 WO 2014112055A1 JP 2013050691 W JP2013050691 W JP 2013050691W WO 2014112055 A1 WO2014112055 A1 WO 2014112055A1
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- WIPO (PCT)
- Prior art keywords
- torque
- rotating body
- camshaft
- valve
- oil
- 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
- 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
- F02D13/0215—Variable control of intake and exhaust valves changing the valve timing only
- F02D13/0219—Variable control of intake and exhaust valves changing the valve timing only by shifting the phase, i.e. the opening periods of the valves are constant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N11/00—Starting of engines by means of electric motors
- F02N11/08—Circuits or control means specially adapted for starting of engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N19/00—Starting aids for combustion engines, not otherwise provided for
- F02N19/004—Aiding engine start by using decompression means or variable valve actuation
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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
- F02D2041/001—Controlling intake air for engines with variable valve actuation
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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
- F02D2250/00—Engine control related to specific problems or objectives
- F02D2250/06—Reverse rotation of engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N2250/00—Problems related to engine starting or engine's starting apparatus
- F02N2250/04—Reverse rotation of the engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N2300/00—Control related aspects of engine starting
- F02N2300/10—Control related aspects of engine starting characterised by the control output, i.e. means or parameters used as a control output or target
- F02N2300/104—Control of the starter motor torque
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention provides an internal combustion engine provided with a variable valve mechanism having a first rotating body that rotates integrally with a camshaft, and a second rotating body that can rotate relative to the first rotating body and rotate integrally with a crankshaft. It relates to the control device.
- a variable valve mechanism that controls the hydraulic pressure supplied to the retarded angle chamber to change the opening / closing timing of the valve.
- a lock mechanism provided in such a variable valve mechanism, a lock mechanism that switches to a lock state in which relative rotation between the vane rotor and the housing is prohibited by fitting a lock pin provided in the vane rotor into a recess provided in the housing. It has been known.
- Patent Document 1 As a control apparatus for an internal combustion engine provided with such a variable valve mechanism with a lock mechanism, when the lock mechanism is not in a locked state when the internal combustion engine is started, the cranking speed of the internal combustion engine is decreased and increased multiple times.
- Patent Document 2 A control device that controls a starter to be executed is known (see Patent Document 1).
- Patent Document 2 there is Patent Document 2 as a prior art document related to the present invention.
- the cranking speed is reduced when the top of the cam nose contacts the valve lifter. Then, the housing and the vane rotor are rotated relative to each other by utilizing the change in the rotational speed of the camshaft caused by the decrease in the rotational speed of the crankshaft and the fluctuation of the cam torque.
- the cam torque when the apex of the cam nose contacts the valve lifter is zero, there is a possibility that fluctuations in the cam torque cannot be effectively utilized for the relative rotation between the vane rotor and the housing.
- an object of the present invention is to provide a control device for an internal combustion engine that can effectively utilize fluctuations in cam torque for the relative rotation of the first rotating body and the second rotating body of the variable valve mechanism.
- the control device of the present invention includes a camshaft provided with a cam that drives a valve for opening and closing a cylinder against a valve spring, a first rotating body that rotates integrally with the camshaft, and the first rotating body.
- a second rotating body provided so as to be relatively rotatable with respect to the crankshaft and a part of a lock pin provided on one of the first rotating body and the second rotating body are provided in the first rotating body.
- the relative rotational phase between the first rotating body and the second rotating body is set between the most retarded angle phase and the most advanced angle phase by fitting into a recess provided on the other of the rotating body and the second rotating body.
- a lock that can be switched between a locked state that locks to an intermediate phase set in the middle and an unlocked state that allows the second rotating body to rotate relative to the first rotating body when the lock pin comes out of the recess.
- a variable valve mechanism having a mechanism; In a control device that is applied to an internal combustion engine that is provided and that has a starting means that starts the internal combustion engine by driving the crankshaft with an electric motor when a predetermined start condition is satisfied, the cam is operated during the operation of the internal combustion engine.
- the direction in which the shaft rotates is defined as the normal rotation direction
- the rotation direction opposite to the normal rotation direction is defined as the reverse rotation direction
- the torque acting on the cam shaft so that the cam shaft rotates in the normal rotation direction is defined as the positive torque.
- the torque acting on the camshaft so that the camshaft rotates in the reverse rotation direction is set as a negative torque, and the torque applied to the camshaft is changed to the positive torque side and the torque is increased.
- the torque applied to the camshaft changes to the negative torque side the torque is reduced, the starter is at the start of the internal combustion engine, and the lock mechanism is In the locked state, when the torque applied from the valve to the camshaft is switched from increase to decrease, the output torque of the electric motor decreases and the torque applied from the valve to the camshaft decreases.
- Rotational speed variation means is provided for controlling the electric motor so that the output torque of the electric motor increases when the motor is switched to increase.
- the output torque of the motor when the torque (cam torque) applied from the valve to the cam shaft is switched from increase to decrease, that is, when the cam torque reaches the maximum value, the output torque of the motor is decreased. Further, when the cam torque is switched from the decrease to the increase, that is, when the cam torque becomes the minimum value, the output torque of the electric motor is increased. In this way, by changing the output torque of the electric motor, the difference between the torque acting on the first rotating body and the torque acting on the second rotating body can be enlarged. Therefore, according to the present invention, cam torque variation can be effectively utilized for the relative rotation of the first rotating body and the second rotating body. In addition, by increasing the difference between the torque acting on the first rotating body and the torque acting on the second rotating body in this way, the first rotating body and the second rotating body can be relatively moved even if the cam torque fluctuation is small. Can be rotated.
- the first rotating body has a vane extending in a radial direction
- the second rotating body has an advance chamber on a side of the vane in the reverse rotation direction, the vane.
- the first rotating body is accommodated so as to be relatively rotatable inside such that a retarded angle chamber is formed at each side of the forward rotation direction of the oil, and oil is contained in both the advanced angle chamber and the retarded angle chamber.
- Oil flow control means is further provided that can be switched to an advanced state in which oil flow is controlled so that oil is not discharged from the advance chamber and oil is discharged from the retard chamber while being supplied.
- the rotation speed variation means switches the oil flow control means to the advance angle state when rotating the first rotating body in the forward rotation direction with respect to the second rotating body, and from the valve to the Increased torque applied to camshaft
- the motor output torque is greater than a predetermined reference torque, and when the torque applied from the valve to the camshaft is reduced, the motor output torque is smaller than the reference torque. May be controlled. According to this embodiment, since the oil supplied to the advance chamber is not discharged from the advance chamber, the first rotating body can be rotated in the normal rotation direction, that is, the advance side with respect to the second rotating body.
- the first rotating body has a vane extending in a radial direction
- the second rotating body has an advance chamber on a side of the vane in the reverse rotation direction, the vane.
- the first rotating body is accommodated so as to be relatively rotatable inside such that a retarded angle chamber is formed at each side of the forward rotation direction of the oil, and oil is contained in both the advanced angle chamber and the retarded angle chamber.
- Oil flow control means is further provided that can be switched to a retarded state in which the oil flow is controlled so that oil is not discharged from the retard chamber and oil is drained from the advance chamber while being supplied.
- the rotation speed changing means switches the oil flow control means to the retard state when rotating the first rotating body in the reverse rotation direction with respect to the second rotating body, and from the valve to the cam Increased torque applied to the shaft
- the motor output torque is greater than a predetermined reference torque, and when the torque applied from the valve to the camshaft is reduced, the motor output torque is smaller than the reference torque. May be controlled. According to this aspect, since the oil supplied to the retarding chamber is not discharged from the retarding chamber, the first rotating body can be rotated in the reverse direction, that is, the retarding side with respect to the second rotating body.
- control device further comprises lock determination means for determining whether or not the lock mechanism has been switched to the locked state when the internal combustion engine is started, and the start means is configured so that the lock determination means uses the lock mechanism.
- lock determination means for determining whether or not the lock mechanism has been switched to the locked state when the internal combustion engine is started, and the start means is configured so that the lock determination means uses the lock mechanism.
- the control of the electric motor by the rotation speed variation means may be prohibited, and the operation of the electric motor may be controlled so that the reference torque is output from the electric motor.
- the locking mechanism is switched to the locked state, relative rotation between the first rotating body and the second rotating body is prohibited by the locking mechanism. Therefore, in this case, control of the electric motor by the rotation speed variation means is prohibited. Thereby, it can avoid changing the output torque of an electric motor wastefully.
- the figure which shows the internal combustion engine in which the control apparatus which concerns on one form of this invention was integrated.
- the figure which shows the cross section of the variable valve timing mechanism in the III-III line of FIG. The figure which shows the cross section of the variable valve timing mechanism in the IV-IV line of FIG.
- the figure for demonstrating the flow of oil when controlling a variable valve timing mechanism to the advance side The figure for demonstrating the flow of oil when controlling a variable valve timing mechanism to the retard side.
- the flowchart which shows the starting control routine which ECU performs.
- FIG. 1 shows an internal combustion engine in which a control device according to one embodiment of the present invention is incorporated.
- the internal combustion engine (hereinafter sometimes referred to as an engine) 1 is configured as a spark ignition type four-cycle internal combustion engine mounted on a vehicle as a driving power source.
- the engine 1 includes four cylinders 2. In FIG. 1, only one of the four is shown. Cylinder numbers # 1 to # 4 are assigned to the cylinders from one end to the other end in the arrangement direction to distinguish them from each other.
- the explosion interval between the # 1 cylinder 2 and the # 4 cylinder 2 is shifted by 360 ° CA (meaning a crank angle), and the explosion timing of the # 3 cylinder 2 and the # 2 cylinder 2 is # 1.
- the explosion at equal intervals for each 180 ° CA is realized.
- the explosion order is set so that explosion occurs in each cylinder 2 in the order of # 1, # 3, # 4, and # 2.
- the piston 3 is inserted into each cylinder 2 so as to be able to reciprocate. Thereby, a combustion chamber 4 is formed in the cylinder 2.
- the piston 3 is connected to the crankshaft 6 via a connecting rod 5.
- Each cylinder 2 is connected with an intake passage and an exhaust passage (both not shown).
- Each cylinder 2 is provided with an intake valve 7 for opening and closing the intake passage for the combustion chamber 4 and an exhaust valve 8 for opening and closing the exhaust passage for the combustion chamber 4.
- a valve lifter 7 a is provided at the upper end of the intake valve 7 so as to be able to reciprocate integrally with the intake valve 7.
- the intake valve 7 is urged in the valve closing direction by a valve spring 7b.
- a valve lifter 8 a is provided at the upper end of the exhaust valve 8 so as to be able to reciprocate integrally with the exhaust valve 8.
- the intake valve 8 is urged in the valve closing direction by a valve spring (not shown).
- the engine 1 is provided with a starter S that can drive the crankshaft 6 when the engine 1 is started.
- the starter S is configured to be able to adjust the rotation speed.
- the engine 1 is provided with a valve operating mechanism 10 for opening and closing the intake valve 7 and the exhaust valve 8.
- the valve operating mechanism 10 includes an intake valve cam shaft 11 and an exhaust valve cam shaft 12.
- the intake valve camshaft 11 is provided with a plurality of cams 11 a for opening and closing the intake valves 7 of the respective cylinders 2.
- the exhaust valve camshaft 12 is provided with a plurality of cams 12a for opening and closing the exhaust valve 8 of each cylinder 2.
- a variable valve timing mechanism 20 is provided on one end side of the cam shaft 11.
- the variable valve timing mechanism 20 is provided on the transmission path of the rotational movement from the crankshaft 6 through the timing chain 9 to the camshafts 11 and 12, and changes the relationship between the phase of the crankshaft 6 and the phase of the cam 11a. The timing at which the intake valve 7 opens and closes is changed.
- variable valve timing mechanism 20 will be described with reference to FIGS.
- FIG. 2 shows the variable valve timing mechanism 20 in an enlarged manner.
- FIG. 3 shows a cross section of the variable valve timing mechanism 20 taken along line III-III in FIG.
- FIG. 4 shows a cross section of the variable valve timing mechanism 20 taken along line IV-IV in FIG.
- the variable valve timing mechanism 20 includes a vane rotor 21 and a housing 22 in which the vane rotor 21 is accommodated coaxially.
- the vane rotor 21 is fixed to the tip of the cam shaft 11 with a center bolt (not shown). Therefore, the vane rotor 21 rotates integrally with the cam shaft 11.
- the vane rotor 21 is accommodated in the housing 22 so as to be rotatable relative to the housing 22.
- the vane rotor 21 includes a cylindrical rotor main body 23 and three vanes 24 that extend radially outward from the rotor main body 23.
- the housing 22 includes a sprocket 25 supported by the camshaft 11 so as to be relatively rotatable, a housing main body 26, and a lid portion 27.
- a timing chain 9 is wound around the sprocket 25.
- the housing 22 rotates together with the crankshaft 6.
- the housing body 26 includes a cylindrical outer wall portion 26 a and three partition walls 26 b extending radially inward from the outer wall portion 26 a.
- three housing chambers 28 are formed inside the housing body 26.
- the vane rotor 21 is combined with the housing body 26 so that the vane 24 is disposed in the accommodation chamber 28. As shown in FIG.
- each storage chamber 28 is divided into an advance chamber 29 and a retard chamber 30 by the vane 24. Oil is supplied to the advance chamber 29 and the retard chamber 30.
- the variable valve timing mechanism 20 adjusts the hydraulic pressure supplied to the advance chamber 29 or the retard chamber 30 to rotate the vane rotor 21 relative to the housing 22.
- the phase of the camshaft 11 relative to the crankshaft 6 is changed to the advance side or the retard side.
- the cam shaft 11 rotates in the direction of arrow F in FIG.
- this direction may be referred to as the forward rotation direction.
- the forward direction may be referred to as the reverse direction
- the arrow R direction in FIG. 2 may be referred to as the reverse direction.
- the phase of the cam shaft 11 with respect to the crankshaft 6 is most retarded.
- this phase may be referred to as the most retarded phase.
- the phase of the cam shaft 11 is advanced with respect to the crank shaft 6, the vane rotor 21 is rotated in the normal rotation direction with respect to the housing 22.
- the phase of the cam shaft 11 with respect to the crankshaft 6 is in the most advanced state.
- the phase at this time may be referred to as a most advanced angle phase.
- the variable valve timing mechanism 20 has a relative rotation of the vane rotor 21 with respect to the housing 22 so that the phase of the camshaft 11 with respect to the crankshaft 6 is fixed at an intermediate phase set between the most advanced angle phase and the most retarded angle phase.
- a lock mechanism 31 for prohibiting the above.
- the intermediate phase is set so that the intake valve 7 opens and closes at a timing suitable for starting the engine 1.
- the lock mechanism 31 includes a cylinder 32 provided in one of the three vanes 24 and a lock pin 33 inserted into the cylinder 32.
- the cylinder 32 is formed so as to penetrate the vane 24 in the direction of the rotation axis Ax.
- the lock pin 33 is inserted into the cylinder 32 so as to be movable in the direction of the rotation axis Ax.
- the lock pin 33 is provided so that a part of the lock pin 33 protrudes from the cylinder 32 and fits into a lock hole 34 provided in the sprocket 25. In this way, when the lock pin 33 is fitted in the lock hole 34, relative rotation of the vane rotor 21 with respect to the housing 22 is prohibited.
- this state may be referred to as a phase locked state.
- a state in which the lock pin 33 comes out of the lock hole 34 and the vane rotor 21 can rotate relative to the housing 22 may be referred to as an unlocked state.
- the lock hole 34 is provided in the sprocket 25 so that the phase of the camshaft 11 with respect to the crankshaft 6 is fixed at an intermediate phase.
- a spring (not shown) is provided in the cylinder 32. This spring is disposed in the cylinder 32 so that the lock pin 33 is biased toward the sprocket 25 side.
- an operating chamber (not shown) for pulling out the lock pin 33 from the lock hole 34 by applying oil hydraulic pressure is provided at the tip of the lock pin 33.
- the relative rotation of the vane rotor 21 is prohibited by being biased by a spring and the lock pin 33 fitting into the lock hole 34.
- a ratchet groove 35 formed so that the bottom of the lock hole 34 is the latest is provided on the side of the lock hole 34.
- the ratchet groove 35 is provided so that the opening of the lock hole 34 is enlarged toward the retard side.
- Oil is supplied to the advance chamber 29 and the retard chamber 30 by the oil supply device 40 shown in FIG.
- the oil supply device 40 includes an oil pump OP that pumps oil from an oil pan 1 a of the internal combustion engine 1 through a strainer 41.
- the oil pump OP is a known pump that is driven by the crankshaft 6.
- the discharge side of the oil pump OP is connected to an oil control valve (OCV) 44 through a valve operating oil passage 43.
- OCV oil control valve
- a check valve 42 is provided in the valve operating oil passage 43. The check valve 42 allows the oil flow from the oil pump OP to the OCV 44 and blocks the oil flow from the OCV 44 to the oil pump OP.
- the OCV 44 includes a valve main body 45 and a valve body 46 that can move in the left-right direction in the figure in the valve main body 45.
- the valve body 45 is provided with an introduction port 45a, a discharge port 45b, a first return port 45c, and a second return port 45d.
- a valve operating oil passage 43 is connected to the introduction port 45a.
- a supply passage 47 is connected to the discharge port 45b.
- the supply passage 47 is branched into a first branch passage 47a and a second branch passage 47b along the way.
- the first branch passage 47 a is connected to the advance chamber 29.
- the first branch passage 47 a is provided with a check valve 48 that allows the oil flow from the OCV 44 to the advance chamber 29 and prevents the oil flow from the advance chamber 29 to the OCV 44.
- a first return passage 49 is branched from a section of the first branch passage 47 a closer to the advance chamber 29 than the check valve 48.
- the first return passage 49 is connected to the first return port 45c.
- the second branch passage 47 b is connected to the retard chamber 30.
- the second branch passage 47b is provided with a check valve 50 that allows the oil flow from the OCV 44 to the retard chamber 30 and prevents the oil flow from the retard chamber 30 to the OCV 44.
- a second return passage 51 is branched from a section of the second branch passage 47b closer to the retarding chamber 30 than the check valve 50 is.
- the second return passage 51 is connected to the second return port 45d.
- the valve body 46 is provided so as to be movable between the advance position shown in FIG. 5 and the retard position shown in FIG.
- the introduction port 45a, the discharge port 45b, and the second return port 45d are connected as shown in FIG.
- the portion where the first return port 45 c is provided is divided by the valve body 46.
- the oil in the retard chamber 30 is returned to the OCV 44 via the second return passage 51.
- the oil in the advance chamber 29 cannot return to the OCV 44 via the first return passage 49. Therefore, the vane rotor 21 rotates in the normal rotation direction with respect to the housing 22. Therefore, the phase of the cam shaft 11 is advanced with respect to the crank shaft 6.
- valve body 46 when the valve body 46 is in the retarded position as shown in FIG. 6, the introduction port 45a, the discharge port 45b, and the first return port 45c are connected. A portion where the second return port 45 d is provided is divided by the valve body 46.
- the oil in the advance chamber 29 is returned to the OCV 44 via the first return passage 49.
- the oil in the retard chamber 30 cannot return to the OCV 44 through the second return passage 51. Therefore, the vane rotor 21 rotates in the reverse direction with respect to the housing 22. Therefore, the phase of the cam shaft 11 is retarded with respect to the crank shaft 6.
- FIG. 7 shows an example of the time variation of the lift amount of the intake valve 7 at the start of the engine 1, the torque applied from the intake valve 7 to the camshaft 11, and the output torque of the starter S.
- the lift amount of the intake valve 7 means the amount of protrusion of the intake valve 7 to the combustion chamber 4.
- the starter S is controlled according to the torque acting on the camshaft 11, whereby the phase is quickly switched to the intermediate phase.
- the output torque of the starter S is made larger than a predetermined reference torque T0.
- the torque output from the starter S during this period P1 may be referred to as a first torque T1.
- the rotational speed of the crankshaft 6 increases.
- the output torque of the starter S is made smaller than the predetermined reference torque T0 during the period until the cam torque becomes the minimum value, in other words, during the period P2 when the cam torque decreases.
- the torque output from the starter S during this period P2 may be referred to as the second torque T2.
- the first torque T1 and the second torque T2 are set so as to be the reference torque T0 when averaged.
- the output torque of the starter S is increased from the second torque T2 to the first torque T1.
- the cam torque is the maximum value
- the output torque of the starter S is reduced from the first torque T1 to the second torque T2.
- Such switching of the output torque of the starter S may be performed based on, for example, the crank angle.
- the period during which the intake valve 7 of each cylinder 2 is opened is determined by the specifications of the engine 1. The period is specified by the crank angle. Therefore, the time when the cam torque becomes the minimum value and the time when the cam shaft becomes the maximum value can be specified by the crank angle. Therefore, the output torque of the starter S may be controlled based on the crank angle. Further, the output torque of the starter S may be controlled based on the cam angle correlated with the crank angle instead of the crank angle.
- the OCV 44 is appropriately controlled according to the direction in which the vane rotor 21 should be rotated.
- the vane rotor 21 is rotated in the forward rotation direction with respect to the housing 22, that is, when the vane rotor 21 is advanced, the valve body 46 of the OCV 44 is switched to the advanced position.
- oil can be introduced into the advance chamber 29 and the vane rotor 21 can be prevented from returning to the retard side.
- the control of the starter S and the OCV 44 may be referred to as relative torque increase control.
- the starter S and OCV 44 are controlled by an engine control unit (ECU) 60.
- the ECU 60 is a computer unit including a microprocessor and peripheral devices such as RAM and ROM necessary for its operation.
- the ECU 60 controls various control objects provided in the engine 1 according to a predetermined control program, thereby controlling the engine 1.
- Various sensors for acquiring the operating state of the engine 1 are connected to the ECU 60.
- a crank angle sensor 61, a cam angle sensor 62, an accelerator opening sensor 63, and the like are connected to the ECU 60.
- the crank angle sensor 61 outputs a signal corresponding to the angle (crank angle) of the crankshaft 6.
- the cam angle sensor 62 outputs a signal corresponding to the angle (cam angle) of the cam shaft 11.
- the accelerator opening sensor 63 outputs a signal corresponding to the accelerator opening.
- various sensors are connected to the ECU 60, but their illustration is omitted.
- FIG. 8 shows a start control routine executed by the ECU 60 to start the engine 1. This routine is repeatedly executed at a predetermined cycle regardless of the operating state of the engine 1.
- the ECU 60 first acquires the state of the engine 1 in step S11. As the state of the engine 1, for example, a crank angle, a cam angle, an accelerator opening, and the like are acquired. In the next step S12, the ECU 60 determines whether or not the engine 1 is stopped. If it is determined that the engine 1 is in operation, the current control routine is terminated.
- the process proceeds to step S13, and the ECU 60 determines whether or not a predetermined start condition is satisfied. It is determined that the predetermined start condition is satisfied when an operation for requesting start of the engine 1 is performed, for example, an operation of turning on an ignition switch. Further, the engine 1 is a control target of so-called idle stop control, which is a control for stopping the operation of the engine 1 when a predetermined stop condition is satisfied and restarting the engine 1 when a predetermined restart condition is satisfied. In this case, the restart condition is also included in the predetermined start condition.
- the engine 1 when the engine 1 is mounted on a hybrid vehicle, it is determined that a predetermined start condition is satisfied when the required driving force to the vehicle becomes equal to or greater than a predetermined determination value when traveling with the electric motor. . If it is determined that the start condition is not established, the current control routine is terminated.
- step S14 the ECU 60 determines whether or not the state of the variable valve timing mechanism 20 is the phase locked state.
- the phase locked state the phase of the camshaft 11 with respect to the crankshaft 6 is an intermediate phase. Therefore, by comparing the crank angle and the cam angle, it can be determined whether or not the state of the variable valve timing mechanism 20 is in the phase locked state.
- step S15 the ECU 60 executes the relative torque increase control described above.
- step S16 the process proceeds to step S16, and the ECU 60 executes normal control.
- the starter S is controlled so that the reference torque T0 is output from the starter S.
- step S17 the ECU 60 determines whether or not the engine 1 has been started. Completion of the start of the engine 1 is determined based on the fact that the rotational speed of the engine 1 exceeds a predetermined determination value. The determination value is set to a rotation speed at which the operation can be continued without the assistance of the starter S. If it is determined that the engine 1 has not been started, the process returns to step S13, and the processes of steps S13 to S17 are repeatedly executed until the start of the engine 1 is completed. On the other hand, if it is determined that the engine 1 has been started, the current control routine is terminated.
- the output torque of the starter S is increased from the second torque T2 to the first torque T1, and when the cam torque is the maximum value, the output torque of the starter S is increased.
- the first torque T1 is reduced to the second torque T2.
- the difference of the torque which acts on the vane rotor 21 and the torque which acts on the housing 22 can be expanded.
- the viscosity of the oil increases, so that the camshaft 11 is difficult to rotate. In this case, the variation in cam torque may be reduced.
- an engine with a small lift amount of the intake valve 7 may be mounted on the hybrid vehicle.
- the torque applied from the intake valve 7 to the camshaft 11 is small, so the cam torque fluctuation is small.
- the combustion temperature is low, so that the temperature is unlikely to rise at the start.
- the viscosity of the oil may increase and the cam torque fluctuation may decrease.
- the vane rotor 21 can be rotated relative to the housing 22 by effectively utilizing the cam torque fluctuation. Therefore, the state of the variable valve timing mechanism 20 can be quickly switched to the phase locked state.
- the vane rotor 21 can be rotated in the reverse rotation direction with respect to the housing 22, that is, the vane rotor 21 can be retarded. .
- the valve body 46 of the OCV 44 is switched to the retard position.
- the output torque of the starter S is switched to the first torque T1 during the period P1 during which the cam torque increases, and during the period P2 during which the cam torque decreases.
- the output torque of S may be switched to the second torque T2.
- variable valve timing mechanism 20 corresponds to the variable valve mechanism of the present invention.
- the vane rotor 21 corresponds to the first rotating body of the present invention
- the housing 22 corresponds to the second rotating body of the present invention.
- the lock hole 34 corresponds to the recess of the present invention.
- the OCV 44, the check valve 48, and the check valve 50 correspond to the oil flow control means of the present invention.
- the starter S corresponds to the electric motor of the present invention.
- the forward rotation torque corresponds to the positive torque of the present invention, and the reverse rotation torque corresponds to the negative torque of the present invention.
- the present invention can be implemented in various forms without being limited to the above-described forms.
- the internal combustion engine to which the present invention is applied is not limited to a four-cylinder internal combustion engine.
- the present invention may be applied to a single cylinder internal combustion engine or various internal combustion engines having two or more cylinders.
- the internal combustion engine to which the present invention is applied is not limited to a spark ignition type internal combustion engine.
- the present invention may be applied to a diesel internal combustion engine.
- the control of the starter shown in the above embodiment is applied to various electric motors used for starting an internal combustion engine.
- the internal combustion engine is started by the motor / generator.
- the starter control of the above-described form is applied to this motor generator.
- the state of the variable valve timing mechanism provided on the camshaft on the intake valve side is controlled.
- the state of the variable valve timing mechanism provided on the camshaft on the exhaust valve side may be controlled according to the present invention. .
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
Claims (4)
- 気筒開閉用のバルブをバルブスプリングに抗して駆動するカムが設けられたカム軸と、
前記カム軸と一体に回転する第1回転体と、前記第1回転体に対して相対回転可能に設けられるとともにクランク軸と一体に回転する第2回転体と、前記第1回転体及び前記第2回転体のいずれか一方に設けられたロックピンの一部が前記第1回転体及び前記第2回転体のいずれか他方に設けられた凹部に嵌って前記第1回転体と前記第2回転体との相対回転位相を最遅角位相と最進角位相との間の中間に設定された中間位相にロックするロック状態と前記ロックピンが前記凹部から抜けて前記第1回転体に対して前記第2回転体が相対回転可能になるアンロック状態とに切り替え可能なロック機構と、を有する可変動弁機構と、を備えた内燃機関に適用され、
所定の始動条件が成立した場合に、前記クランク軸を電動機で駆動して前記内燃機関を始動する始動手段を備えた制御装置において、
前記内燃機関の運転時に前記カム軸が回転する方向を正転方向とするとともに前記正転方向と反対の回転方向を逆転方向とし、前記カム軸が前記正転方向に回転するように前記カム軸に作用するトルクを正トルクとするとともに前記カム軸が前記逆転方向に回転するように前記カム軸に作用するトルクを負トルクとし、前記カム軸に付与されるトルクが前記正トルク側に変化することをトルクの増加とするとともに前記カム軸に付与されるトルクが前記負トルク側に変化することをトルクの減少とし、
前記始動手段は、前記内燃機関の始動時であり、かつ前記ロック機構が前記アンロック状態の場合に、前記バルブから前記カム軸に付与されるトルクが増加から減少に切り替わったときに前記電動機の出力トルクが減少し、かつ前記バルブから前記カム軸に付与されるトルクが減少から増加に切り替わったときに前記電動機の出力トルクが増加するように前記電動機を制御する回転速度変動手段を備えている制御装置。 - 前記第1回転体は、径方向に延びるベーンを有し、
前記第2回転体は、前記ベーンの前記逆転方向の側方に進角室が、前記ベーンの前記正転方向の側方に遅角室がそれぞれ形成されるように前記第1回転体を内部に相対回転可能なように収容し、
前記進角室及び前記遅角室の両方にオイルが供給されるとともに前記進角室からはオイルが排出されず、前記遅角室からはオイルが排出されるようにオイルの流れが制御される進角状態に切り替え可能なオイルフロー制御手段をさらに備え、
前記回転速度変動手段は、前記第1回転体を前記第2回転体に対して前記正転方向に回転させる場合に、前記オイルフロー制御手段を前記進角状態に切り替え、かつ前記バルブから前記カム軸に付与されるトルクが増加しているときには前記電動機の出力トルクが所定の基準トルクより大きく、前記バルブから前記カム軸に付与されるトルクが減少しているときには前記電動機の出力トルクが前記基準トルクより小さくなるように前記電動機を制御する請求項1に記載の制御装置。 - 前記第1回転体は、径方向に延びるベーンを有し、
前記第2回転体は、前記ベーンの前記逆転方向の側方に進角室が、前記ベーンの前記正転方向の側方に遅角室がそれぞれ形成されるように前記第1回転体を内部に相対回転可能なように収容し、
前記進角室及び前記遅角室の両方にオイルが供給されるとともに前記遅角室からはオイルが排出されず、前記進角室からはオイルが排出されるようにオイルの流れが制御される遅角状態に切り替え可能なオイルフロー制御手段をさらに備え、
前記回転速度変動手段は、前記第1回転体を前記第2回転体に対して前記逆転方向に回転させる場合に、前記オイルフロー制御手段を前記遅角状態に切り替え、かつ前記バルブから前記カム軸に付与されるトルクが増加しているときには前記電動機の出力トルクが所定の基準トルクより大きく、前記バルブから前記カム軸に付与されるトルクが減少しているときには前記電動機の出力トルクが前記基準トルクより小さくなるように前記電動機を制御する請求項1に記載の制御装置。 - 前記内燃機関の始動時に前記ロック機構が前記ロック状態に切り替わったか否か判定するロック判定手段をさらに備え、
前記始動手段は、前記ロック判定手段により前記ロック機構が前記ロック状態に切り替わったと判定された場合に、前記回転速度変動手段による前記電動機の制御を禁止し、前記電動機から前記基準トルクが出力されるように前記電動機の動作を制御する請求項2又は3に記載の制御装置。
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JP2007132272A (ja) * | 2005-11-10 | 2007-05-31 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
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JP4993041B2 (ja) * | 2010-02-10 | 2012-08-08 | トヨタ自動車株式会社 | 内燃機関の始動制御装置 |
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JP2007132272A (ja) * | 2005-11-10 | 2007-05-31 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
JP4993041B2 (ja) * | 2010-02-10 | 2012-08-08 | トヨタ自動車株式会社 | 内燃機関の始動制御装置 |
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