EP2719883B1 - Système motorisé - Google Patents

Système motorisé Download PDF

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Publication number
EP2719883B1
EP2719883B1 EP13188298.7A EP13188298A EP2719883B1 EP 2719883 B1 EP2719883 B1 EP 2719883B1 EP 13188298 A EP13188298 A EP 13188298A EP 2719883 B1 EP2719883 B1 EP 2719883B1
Authority
EP
European Patent Office
Prior art keywords
crankshaft
rotation
cam
intake
exhaust
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP13188298.7A
Other languages
German (de)
English (en)
Other versions
EP2719883A1 (fr
Inventor
Takahiro Masuda
Kouji Sakai
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Yamaha Motor Co Ltd
Original Assignee
Yamaha Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Yamaha Motor Co Ltd filed Critical Yamaha Motor Co Ltd
Publication of EP2719883A1 publication Critical patent/EP2719883A1/fr
Application granted granted Critical
Publication of EP2719883B1 publication Critical patent/EP2719883B1/fr
Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/04—Introducing corrections for particular operating conditions
    • F02D41/06—Introducing corrections for particular operating conditions for engine starting or warming up
    • F02D41/062—Introducing corrections for particular operating conditions for engine starting or warming up for starting
    • 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
    • F02N11/04—Starting of engines by means of electric motors the motors being associated with current generators
    • 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
    • F02N19/005—Aiding engine start by starting from a predetermined position, e.g. pre-positioning or reverse rotation
    • 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
    • F02N99/00—Subject matter not provided for in other groups of this subclass
    • F02N99/002—Starting combustion engines by ignition means
    • F02N99/008—Providing a combustible mixture outside the cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F01L1/34413—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 composite camshafts, e.g. with cams being able to move relative to the camshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • 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
    • 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
    • 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
    • F02N19/005—Aiding engine start by starting from a predetermined position, e.g. pre-positioning or reverse rotation
    • F02N2019/007—Aiding engine start by starting from a predetermined position, e.g. pre-positioning or reverse rotation using inertial reverse rotation
    • 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
    • F02N99/00—Subject matter not provided for in other groups of this subclass
    • F02N99/002—Starting combustion engines by ignition means
    • F02N99/004—Generation of the ignition spark

Definitions

  • the present invention relates to an engine system.
  • a saddle-straddling type motor vehicle including a single-cylinder engine such as a motorcycle or the like in which a generator having the function of a starter motor (hereinafter referred to as a starter/generator) is provided at a crankshaft.
  • a starter/generator a generator having the function of a starter motor
  • a torque is directly transmitted from the starter/generator to the crankshaft without a reduction gear.
  • the torque transmitted to the crankshaft is markedly smaller than a torque transmitted to the crankshaft from the starter motor separately provided from the generator via the reduction gear.
  • the crankshaft is rotated in a reverse direction to a predetermined position by the starter/generator provided at the crankshaft after the engine is stopped, and the crankshaft is rotated in the forward direction from the position at the engine start-up.
  • a rotor position of the starter/generator is detected by a rotor sensor, and a rotation direction of the engine is determined based on an output signal of the rotor sensor.
  • a fuel injection and ignition are prohibited during the reverse rotation of the engine based on its determination result.
  • US 2007/204827 A1 describes an engine starting device which injects fuel in preparation for ignition performed in a cylinder of an engine after starting a starter motor in a forward rotational direction so as to start the engine, and which performs ignition in a suitable ignition position at the time of engine start while the starter motor is driven in a forward rotational direction.
  • the engine starting device continues driving the starter motor in a direction for starting the engine, even when a crankshaft stops before a piston in a cylinder of the engine reaches a top dead center of a compression stroke.
  • US 2010/275872 A1 describes a method for starting an internal combustion engine having at least one cylinder, an inlet and an outlet valve, and a piston interacting with a crankshaft.
  • the piston is moved into a defined starting position against a normal rotational direction of the crankshaft by means of a drive, fuel is injected, and the fuel is ignited.
  • EP 1 840 369 A1 describes an engine starting system including restart control means and a starter motor.
  • the restart control means is operable to execute a backed-up starting control strategy of activating the starter motor at a given timing in a course of an automatic restart control process in such a manner that the backed-up starting control strategy is determined to be necessary, when any of the cylinders passes beyond a top dead center due to continuation of a reverse rotation state of the engine after combustion for reversely rotating the engine, and a timing of applying a driving force from the starter motor in the backed-up starting control strategy is set around a time when the engine is shifted from the reverse rotation state to a normal rotation state.
  • JP 2007-092720 A describes starting an engine by effectively utilizing a compression stroke cylinder after reversing to normal rotation from reverse rotation. Fuel for restarting is injected into the compression stroke cylinder. Air is introduced into the compression stroke cylinder by opening an intake valve of the compression stroke cylinder when the engine reversely rotates when beginning the restarting, and fuel for the normal rotation is injected. When meeting with the first top dead center, compressed self-ignition is performed by the compression stroke cylinder.
  • the drive wheel is rotated by the power generated by the engine system. This causes the main body to move.
  • the engine system according to the one aspect of the present invention described above is used, the engine can be stably started and the size of the engine can be reduced.
  • the present invention enables the engine to be stably started and an increase in size of the engine to be suppressed.
  • Fig. 1 is a schematic side view showing the schematic configuration of the motorcycle according to one embodiment of the present invention.
  • a front fork 2 is provided at the front of a vehicle body 1 to be swingable from side to side.
  • a handle 4 is attached to the upper end of the front fork 2
  • a front wheel 3 is attached to the lower end of the front fork 2 to be rotatable.
  • a seat 5 is provided at the substantially center of the upper portion of the vehicle body 1.
  • An ECU (Engine Control Unit) 6 is arranged at the lower portion behind the seat 5, and a single-cylinder engine 10 is provided below the seat 5.
  • An engine system 200 is constituted by the ECU 6 and the engine 10.
  • a rear wheel 7 is attached to the lower portion of the rear end of the vehicle body 1 to be rotatable. The rear wheel 7 is rotated by power generated by the engine 10.
  • Fig. 2 is a schematic diagram for explaining the configuration of the engine system 200.
  • the engine 10 includes a piston 11, a connecting rod 12, a crankshaft 13, a starter/generator 14, an intake valve 15, an exhaust valve 16, a valve driver 17, an ignition plug 18 and an injector 19.
  • the piston 11 is provided to be reciprocatable in a cylinder 31 and connected to the crankshaft 13 via the connecting rod 12.
  • the reciprocating motion of the piston 11 is transformed into the rotational motion of the crankshaft 13.
  • the starter/generator 14 is provided at the crankshaft 13.
  • the starter/generator 14 is a generator having the function of a starter motor, rotates the crankshaft 13 in forward and reverse directions and generates electric power by the rotation of the crankshaft 13.
  • the starter/generator 14 directly transmits a torque to the crankshaft 13 without a reduction gear therebetween.
  • a one-way clutch (not shown) is provided between the crankshaft 13 and the rear wheel 7.
  • the rotation of the crankshaft 13 in the forward direction (hereinafter referred to as a forward rotation) is transmitted to the rear wheel 7 through the one-way clutch, and the rotation of the crankshaft 13 in the reverse direction (hereinafter referred to as a reverse rotation) is not transmitted to the rear wheel 7.
  • a combustion chamber 31a is formed on the piston 11.
  • the combustion chamber 31a communicates with an intake passage 22 through an intake port 21 and communicates with an exhaust passage 24 through an exhaust port 23.
  • An intake valve 15 is provided to open and close the intake port 21, and an exhaust valve 16 is provided to open and close the exhaust port 23.
  • the intake valve 15 and the exhaust valve 16 are driven by the valve driver 17.
  • a throttle valve SL for adjusting an amount of air flowing in from the outside is provided at the intake passage 22.
  • the ignition plug 18 is configured to ignite a fuel-air mixture in the combustion chamber 31a.
  • the injector 19 is configured to inject fuel into the intake passage 22.
  • the ECU 6 includes a CPU (Central Processing Unit) and a memory, for example.
  • a microcomputer may be used instead of the CPU or the memory.
  • a starter switch 41, an intake pressure sensor 42, a crank angle sensor 43 and a current sensor 44 are electrically connected to the ECU 6.
  • the starter switch 41 is provided at the handle 4 of Fig. 1 , for example, and is operated by a driver.
  • the intake pressure sensor 42 detects pressure in the intake passage 22.
  • the crank angle sensor 43 detects a rotation angle of the crankshaft 13.
  • the current sensor 44 detects a current that flows in the starter/generator 14 (hereinafter referred to as a motor current).
  • the operation of the starter switch 41 is supplied to the ECU 6 as an operation signal, and the detection results of the intake pressure sensor 42, the crank angle sensor 43 and the current sensor 44 are supplied to the ECU 6 as detection signals.
  • the ECU 6 controls the starter/generator 14, the ignition plug 18 and the injector 19 based on the supplied operation signal and the detection signals.
  • Figs. 3 and 4 are diagrams for explaining the operation of the engine 10.
  • Fig. 3 shows the operation of the engine 10 during normal running
  • Fig. 4 shows the operation of the engine 10 during the start-up.
  • the normal running refers to the state in which the engine 10 stably operates after the start-up of the engine 10.
  • a rotation angle in a range of two rotations (720 degrees) of the crankshaft 13 is shown by one circle.
  • the two rotations of the crankshaft 13 are equivalent to one cycle of the engine 10.
  • the one cycle of the engine 10 includes an intake stroke, a compression stroke, a combustion stroke and an exhaust stroke.
  • the rotation angle of the crankshaft 13 is referred to as a crank angle.
  • the crank angle sensor 43 of Fig. 2 detects the rotation angle in a range of one rotation (360 degrees) of the crankshaft 13.
  • the ECU 6 determines which one of the two rotations of the crankshaft 13 equivalent to the one cycle of the engine 10 the crank angle detected by the crank angle sensor 43 corresponds to, based on the pressure in the intake passage 22 detected by the intake pressure sensor 42. Thus, the ECU 6 can obtain the rotation angle in the range of the two rotations (720 degrees) of the crankshaft 13.
  • an angle A0 is the crank angle when the piston 11 ( Fig. 2 ) is positioned at an exhaust top dead center
  • an angle A2 is the crank angle when the piston 11 is positioned at a compression top dead center
  • angles A1, A3 are the crank angles when the piston 11 is positioned at a bottom dead center.
  • An arrow R1 indicates the direction of the change of the crank angle during the forward rotation of the crankshaft 13
  • an arrow R2 indicates the direction of the change of the crank angle during the reverse rotation of the crankshaft 13.
  • Arrows P1 to P4 indicate the moving direction of the piston 11 during the forward rotation of the crankshaft 13
  • arrows P5 to P8 indicate the moving direction of the piston 11 during the reverse rotation of the crankshaft 13.
  • the crankshaft 13 ( Fig. 2 ) is rotated in the forward direction.
  • the crank angle changes in the direction of the arrow R1.
  • the piston 11 ( Fig. 2 ) falls in a range from the angle A0 to the angle A1
  • the piston 11 rises in a range from the angle A1 to the angle A2
  • the piston 11 falls in a range from the angle A2 to the angle A3
  • the piston 11 rises in a range from the angle A3 to the angle A0.
  • the fuel is injected into the intake passage 22 ( Fig. 2 ) by the injector 19 ( Fig. 2 ).
  • the angle A11 is positioned at the further advanced angle than the angle A0.
  • the angle A11 is an example of a fourth range.
  • the intake port 21 ( Fig. 2 ) is opened by the intake valve 15 ( Fig. 2 ).
  • the angle A12 is positioned at the further retarded angle than the angle A11 and at the further advanced angle than the angle A0
  • the angle A13 is positioned at the further retarded angle than the angle A1.
  • the range from the angle A12 to the angle A13 is an example of a second range.
  • the fuel-air mixture including air and the fuel is introduced into the combustion chamber 31a ( Fig. 2 ) through the intake port 21.
  • the fuel-air mixture in the combustion chamber 31a ( Fig. 2 ) is ignited by the ignition plug 18 ( Fig. 2 ).
  • the angle A14 substantially matches with the angle A2.
  • This causes an explosion in the combustion chamber 31a.
  • Energy generated by the explosion is turned into the driving force for the piston 11.
  • the exhaust port 23 ( Fig. 2 ) is opened by the exhaust valve 16 ( Fig. 2 ).
  • the angle A15 is positioned at the further advanced angle than the angle A3
  • the angle A16 is positioned at the further retarded angle than the angle A0.
  • the range from the angle A15 to the A16 is an example of a first range. This causes the combusted gas to be exhausted from the combustion chamber 31 a through the exhaust port 23.
  • crankshaft 13 ( Fig. 2 ) is first rotated in the forward or reverse direction such that the crank angle is adjusted to an angle A30.
  • the angle A30 is positioned between the angle A1 and the angle A2. Then, the crankshaft 13 is rotated in the reverse direction from the angle A30.
  • the crank angle changes in the direction of the arrow R2.
  • the piston 11 falls in a range from the angle A2 to the angle A1
  • the piston 11 rises in a range from the angle A1 to the angle A0
  • the piston 11 falls in a range from the angle A0 to the angle A3
  • the piston 11 rises in a range from the angle A3 to the angle A2.
  • the moving direction of the piston 11 during the reverse rotation of the crankshaft 13 is opposite to the moving direction of the piston 11 during the forward rotation of the crankshaft 13.
  • the fuel is injected into the intake passage 22 ( Fig. 2 ) by the injector 19 ( Fig. 2 ).
  • the angle A23 is positioned at the further advanced angle than the angle A0.
  • the angle A23 is an example of a fifth range.
  • the intake port 21 ( Fig. 2 ) is opened by the intake valve 15 ( Fig. 2 ).
  • the angles A21, A22 are positioned at the further retarded angle than the angle A0.
  • the rotation direction of the crankshaft 13 is switched from the reverse direction to the forward direction.
  • the angle A31 is positioned at a slightly further advanced angle than the angle A2.
  • the crank angle changes in the direction of the arrow R1.
  • the fuel-air mixture in the combustion chamber 31a is ignited by the ignition plug 18 ( Fig. 2 ). This causes the explosion in the combustion chamber 31a to be carried out and the crankshaft 13 to be driven.
  • a time point at which the crank angle is the angle A31 is an example of a second time point.
  • the fuel-air mixture in the combustion chamber 31a is ignited by the ignition plug 18 after the reverse rotation of the crankshaft 13 is stopped.
  • the crankshaft 13 can be reliably driven in the forward direction. If the crankshaft 13 can be driven in the forward direction by adjusting the timing of the ignition or the like, the fuel-air mixture in the combustion chamber 31a may be ignited by the ignition plug 18 before the reverse rotation of the crankshaft 13 is stopped.
  • the similar operation to Fig. 3 is performed. Specifically, the fuel is injected into the intake passage 22 ( Fig. 2 ) at the angle A11 of Fig. 3 , and the fuel-air mixture is introduced into the combustion chamber 31a in the range from the angle A12 to the angle A13. Next, the fuel-air mixture in the combustion chamber 31a is ignited by the ignition plug 18 ( Fig. 2 ) at the angle A14, and the combusted gas is exhausted from combustion chamber 31a through the exhaust port 23 in a range of the angle A15 to the angle A16. Thereafter, the engine 10 is changed to the normal running.
  • the fuel-air mixture is led to the combustion chamber 31a while the crankshaft 13 is rotated in reverse by the starter/generator 14, and thereafter, the fuel-air mixture in the combustion chamber 31a is ignited while the piston 11 is close to the compression top dead center.
  • the piston 11 is driven such that the crankshaft 13 is rotated in the forward direction, whereby an enough torque in the forward direction can be obtained.
  • the piston 11 can easily go over the first compression top dead center.
  • the exhaust port 23 may be opened by the exhaust valve 16 in the range from the angle A15 to the angle A16, after the rotation direction of the crankshaft 13 is switched from the reverse direction to the forward direction at the angle A31 and before the intake port 21 is opened by the intake valve 15 in the range from the angle A12 to the angle A13 of Fig. 3 .
  • the combusted gas due to the ignition at the angle A31 is exhausted from the combustion chamber 31a before the intake is performed in the range from the angle A12 to the angle A13.
  • Figs. 5 to 7 are flowcharts of the first example of the engine start-up processing.
  • the engine start-up processing is started by turning a main switch (not shown) on, for example.
  • the ECU 6 first determines whether or not the current crank angle is stored in the memory (step S1).
  • the current crank angle is previously stored in the memory when the engine 10 is stopped last time, for example. If the current crank angle is stored, the ECU 6 controls the starter/generator 14 such that the current crank angle matches with the angle A30 of Fig. 4 (step S2).
  • the ECU 6 controls the starter/generator 14 such that the crankshaft 13 is rotated in the forward direction (step S3).
  • a torque of the starter/generator 14 is adjusted based on the detection signal from the current sensor 44 ( Fig. 2 ) such that the piston 11 does not go over the compression top dead center (the angle A2 of Figs. 3 and 4 ).
  • the ECU 6 determines whether or not a specified time period has elapsed since the rotation of the crankshaft 13 was started in the step S3 (step S4). If the specified time period has not elapsed, the ECU 6 controls the starter/generator 14 such that the rotation of the crankshaft 13 in the forward direction continues. When the specified time period has elapsed, the ECU 6 controls the starter/generator 14 such that the rotation of the crankshaft 13 is stopped (step S5). Thus, the crank angle is adjusted to be close to the angle A30 of Fig. 4 .
  • the crank angle may be detected when the crankshaft 13 is rotated in the forward direction, and the crank angle may be adjusted to the angle A30 of Fig. 4 based on its detected value.
  • the ECU 6 determines whether or not predetermined start-up condition of the engine 10 is satisfied (step S6).
  • the start-up condition of the engine 10 is that the starter switch 41 ( Fig. 2 ) is turned on, for example.
  • Another condition for example when a brake switch (not shown) is turned off, an accelerator grip (not shown) is operated, or voltage of a battery (not shown) is reduced, may be set as the start-up condition of the engine 10.
  • step S7 When the start-up condition of the engine 10 is satisfied, the ECU 6 performs a timeout setting for the engine start-up processing (step S7). Specifically, an elapsed time period is measured from that time point. When the elapsed time period reaches a predetermined end time period, the engine start-up processing is forcibly terminated (step S17 described below).
  • the ECU 6 controls the starter/generator 14 such that the crankshaft 13 is rotated in the reverse direction (step S8). Then, the ECU 6 determines whether or not the current crank angle has reached the angle A23 of Fig. 4 based on the detection signals from the intake pressure sensor 42 ( Fig. 2 ) and the crank angle sensor 43 ( Fig. 2 ) (step S9). The ECU 6 repeats the processing of the step S9 until the current crank angle reaches the angle A23. When the current crank angle reaches the angle A23, the ECU 6 controls the injector 19 such that the injection of the fuel into the intake passage 22 ( Fig. 2 ) is started (step S10).
  • the ECU 6 determines whether or not a predetermined injection time period has elapsed since the injection of the fuel was started in the step S10 (step S11).
  • the ECU 6 controls the injector 19 such that the injection of the fuel continues until the predetermined injection time period elapses.
  • the ECU 6 controls the injector 19 such that the injection of the fuel is stopped (step S12).
  • the ECU 6 determines whether or not the motor current has reached a predetermined threshold value based on the detection signal from the current sensor 44 (step S13). In this case, the closer the crank angle comes to the angle A2 of Fig. 4 , the larger the motor current becomes. In this example, when the crank angle reaches the angle A31 of Fig. 4 , the motor current reaches the threshold value.
  • the ECU 6 controls the starter/generator 14 such that the rotation of the crankshaft 13 in the reverse direction is stopped (step S14) and starts to energize the ignition plug 18 (step S15).
  • the ECU 6 determines whether or not a predetermined energization time period has elapsed since the energization was started in the step S15 (step S16). The ECU 6 continues to energize the ignition plug 18 until the predetermined energization time period elapses. When the predetermined energization time period has elapsed, the ECU 6 stops the energization of the ignition plug 18 (step S17).
  • step S18 the ECU 6 controls the starter/generator 14 such that the crankshaft 13 is rotated in the forward direction.
  • the ECU 6 terminates the engine start-up processing.
  • the ECU 6 performs the control operation corresponding to the operation during the normal running of Fig. 3 .
  • the driving of the crankshaft 13 by the starter/generator 14 is stopped after a predetermined time period has elapsed since the processing of the step S18, for example.
  • the ECU 6 determines whether or not the predetermined end time period has elapsed since the timeout setting in the step S7 of Fig. 6 (step S19).
  • the predetermined end time period may elapse since the timeout setting when the electric current flowing in the starter/generator 14 does not reach the threshold value due to trouble with the engine 10.
  • the trouble with the engine 10 includes an operational problem with the starter/generator 14, an operational problem of the valve driver 17 or the like. If the end time period has not elapsed, the ECU 6 returns to the processing of the step S13.
  • the ECU 6 controls the starter/generator 14 such that the rotation of the crankshaft 13 in the reverse direction is stopped (step S20), and warns the driver that the trouble with the engine 10 has occurred (step S21). Specifically, a warning lamp (not shown), for example, is lit. Thus, the ECU 6 terminates the engine start-up processing.
  • Fig. 8 is a flowchart of the second example of the engine start-up processing.
  • the ECU 6 may perform the processing of the steps S31 to S41 of Fig. 8 instead of the steps S13 to S21 of Fig. 7 .
  • the ECU 6 determines whether or not the crankshaft 13 has been rotated a predetermined angle of reverse rotation after the reverse rotation of the crankshaft 13 was started in the step S8 of Fig. 6 based on the detection signal from the crank angle sensor 43 ( Fig. 2 ) (step S31).
  • the angle of reverse rotation is equivalent to the angle from the angle A30 to the angle A31 of Fig. 4 . If a prescribed number of pulses that corresponds to the angle of reverse rotation is supplied from the crank angle sensor 43 as the detection signal after the reverse rotation of the crankshaft 13 is started, for example, the ECU 6 determines that the crankshaft 13 has been rotated the angle of reverse rotation.
  • step S32 the ECU 6 controls the starter/generator 14 such that the rotation of the crankshaft 13 in the reverse direction is stopped (step S32) and starts to energize the ignition plug 18 (step S33).
  • the ECU 6 determines whether or not the crankshaft 13 has been rotated a predetermined energization angle after the energization was started in the step S33 (step S34).
  • the energization angle is equivalent to the angle by which the crankshaft 13 is rotated in the energization time period in the step S16 of Fig. 7 .
  • the ECU 6 determines that the crankshaft 13 has been rotated the energization angle if a prescribed number of pulses that corresponds to the energization angle is supplied from the crank angle sensor 43 as the detection signal after the energization is started, for example.
  • step S35 the ECU 6 stops the energization to the ignition plug 18 (step S35), controls the starter/generator 14 such that the crankshaft 13 is rotated in the forward direction (step S36) and terminates the engine start-up processing.
  • step S31 if the crankshaft 13 has not been rotated the angle of reverse rotation, the ECU 6 determines whether or not a predetermined first end time period since the timeout setting in the step S7 has elapsed (step S37). If the first end time period has not elapsed, the ECU 6 returns to the processing in the step S31. When the first end time period has elapsed, the ECU 6 controls the starter/generator 14 such that the rotation of the crankshaft 13 in the reverse direction is stopped (step S38), warns the driver that the trouble with the engine 10 has occurred (step S41) and terminates the engine start-up processing.
  • step S34 if the crankshaft 13 has not been rotated the energization angle, the ECU 6 determines whether or not a predetermined second end time period has elapsed since the timeout setting in the step S7 (step S39).
  • the second end time period is set longer than the first end time period described above. If the second end time period has not elapsed, the ECU 6 returns to the processing in the step S34.
  • the ECU 6 stops the energization to the ignition plug 18 (step S40), warns the driver that the trouble with the engine 10 has occurred (step S41) and terminates the engine start-up processing.
  • the reverse rotation of the crankshaft 13 is stopped based on the detection signal from the crank angle sensor 43 (steps S31, S32). Further, the energization to the ignition plug 18 is stopped based on the detection signal from the crank angle sensor 43 (steps S34, S35). Thus, the reverse rotation of the crankshaft 13 and the energization to the ignition plug 18 can be stopped at an appropriate time.
  • the energization to the ignition plug 18 is stopped in the step S40.
  • the energization to the ignition plug 18 is prevented from continuing for a long period of time.
  • Fig. 9 is a schematic side view for explaining the specific example of the valve driver 17.
  • the valve driver 17 of Fig. 9 is a camshaft that drives the intake valve 15 and the exhaust valve 16 of Fig. 2 via an intake rocker arm 510 ( Fig. 10 ) and an exhaust rocker arm 520 ( Fig. 10 ) described below.
  • the valve driver 17 is provided in a cylinder head 32 to be rotatable.
  • the valve driver 17 has a sprocket 17a, and the crankshaft 13 has a sprocket 13a.
  • a chain 25 with no ends is attached to the sprocket 13a and the sprocket 17a.
  • the rotation speed of the valve driver 17 is half of the rotation speed of the crankshaft 13.
  • Fig. 10 is a cross sectional view of the valve driver 17 and its peripheral portions.
  • the valve driver 17 as viewed from the direction of the arrow G of Fig. 9 is shown.
  • the intake rocker arm 510 and the exhaust rocker arm 520 are provided in the cylinder head 32.
  • the intake rocker arm 510 is provided to be swingable with a shaft 511 as a center.
  • a roller 512 is provided at one end of the intake rocker arm 510 and an adjuster 513 is provided at the other end. The roller 512 abuts against a main-intake cam 240 or a sub-intake cam 245 of the valve driver 17.
  • the adjuster 513 abuts against the upper end of the intake valve 15.
  • the intake valve 15 is energized in a direction of closing the intake port 21 by a valve spring 15a. In this case, force is applied from the intake valve 15 to the intake rocker arm 510 in a direction of pushing up the adjuster 513. This causes the roller 512 of the intake rocker arm 510 to be pressed against the main-intake cam 240 or the sub-intake cam 245.
  • the exhaust rocker arm 520 is provided to be swingable with a shaft 521 as a center.
  • a roller 522 is provided at one end of the exhaust rocker arm 520, and an adjuster 523 is provided at the other end.
  • the roller 522 abuts against an exhaust cam 230 of the valve driver 17. Details of the exhaust cam 230 will be described below.
  • An adjuster 523 abuts against the upper end of the exhaust valve 16.
  • the exhaust valve 16 is energized in a direction of closing the exhaust port 23 by a valve spring 16a.
  • force is applied from the exhaust valve 16 to the exhaust rocker arm 520 in a direction of pushing up the adjuster 523, and the roller 522 of the exhaust rocker arm 520 is pressed against the exhaust cam 230.
  • the valve driver 17 is rotated in a first direction Q1 during the forward rotation of the crankshaft 13 ( Fig. 9 ), and the valve driver 17 is rotated in a second direction Q2 during the reverse rotation of the crankshaft 13.
  • the valve driver 17 is rotated such that the main-intake cam 240 and the sub-intake cam 245 swing the intake rocker arm 510 and the exhaust cam 230 swings the exhaust rocker arm 520.
  • the intake valve 15 opens and closes the intake port 21, and the exhaust valve 16 opens and closes the exhaust port 23.
  • Fig. 11 is a external perspective view of the valve driver 17, and Fig. 12 is a cross sectional view of the valve driver 17.
  • Figs. 13 and 14 are partially exploded perspective views of the valve driver 17 as viewed from the directions different from each other.
  • the valve driver 17 includes the sprocket 17a, a shaft member 210, a spring fixing member 220, the exhaust cam 230, the sub-intake cam 245, a spring fixing member 250 and a switching mechanism 300.
  • the shaft member 210 is substantially cylindrical and has a through hole 210a along an axis.
  • an axial direction means a direction parallel to the axis of the shaft member 210
  • a circumferential direction means a circumferential direction with the axis of the shaft member 210 as a center.
  • the main-intake cam 240 is integrally provided at the shaft member 210.
  • the exhaust cam 230 and the spring fixing member 220 are attached to a portion of the shaft member 210 on one side of the main-intake cam 240.
  • the sub-intake cam 245 and the spring fixing member 250 are attached to a portion of the shaft member 210 on the other side of the main-intake cam 240.
  • a flange portion 211, a cam attachment portion 212 and a bearing portion 213 are provided at a portion of the shaft member 210 on the one side of the main-intake cam 240.
  • An outer diameter of the cam attachment portion 212 is smaller than an outer diameter of the flange portion 211, and an outer diameter of the bearing portion 213 is smaller than the outer diameter of the cam attachment portion 212.
  • a through hole 210b is formed at the cam attachment portion 212. The through hole 210a and the through hole 210b communicate with each other as described below.
  • the exhaust cam 230 is substantially annular. An inner diameter of the exhaust cam 230 is substantially equal to the outer diameter of the cam attachment portion 212 of the shaft member 210.
  • the exhaust cam 230 is positioned on the cam attachment portion 212 of the shaft member 210 to abut against the flange portion 211. As described below, the exhaust cam 230 is provided to be rotatable in the circumferential direction in a predetermined angular range with respect to the shaft member 210.
  • the spring fixing member 220 is substantially cylindrical. An inner diameter of the spring fixing member 220 is substantially equal to an outer diameter of the bearing portion 213 of the shaft member 210.
  • the spring fixing member 220 is positioned on the bearing portion 213 of the shaft member 210 to abut against the side surface of the cam attachment portion 212.
  • the spring fixing member 220 is provided not to be rotated in the circumferential direction with respect to the shaft member 210.
  • a flange portion 221 is provided at the end of the spring fixing member 220.
  • a twisted coil spring 225 is arranged on the outer peripheral surface of the spring fixing member 220 except for the flange portion 221. As shown in Fig. 12 , one end of the twisted coil spring 225 is fixed to the flange portion 221 of the spring fixing member 220, and the other end is fixed to the side surface of the exhaust cam 230.
  • the exhaust cam 230 is energized in the second direction Q2 ( Fig. 10 ) with respect to the shaft member 210 by the twisted coil spring 225.
  • a cam attachment portion 214, a spring attachment portion 215 and a bearing portion 216 are provided at a portion of the shaft member 210 on the other side of the main-intake cam 240.
  • An outer diameter of the spring attachment portion 215 is smaller than an outer diameter of the cam attachment portion 214, and an outer diameter of the bearing portion 216 is smaller than an outer diameter of the spring attachment portion 215.
  • a sub-intake cam 245 is substantially annular. An inner diameter of the sub-intake cam 245 is substantially equal to the outer diameter of the cam attachment portion 214 of the shaft member 210. The sub-intake cam 245 is positioned on the cam attachment portion 214 of the shaft member 210 to abut against the main-intake cam 240. A long-sized opening 246 in the circumferential direction is formed at the sub-intake cam 245. Further, a fitting pin 241 ( Fig. 12 ) is fixed to the main-intake cam 240 to project from the other side. A tip end of the fitting pin 241 is fitted into the opening 246 of the sub-intake cam 245. Details of the sub-intake cam 245 will be described below.
  • the spring fixing member 250 is substantially annular. An inner diameter of the spring fixing member 250 is substantially equal to an outer diameter of the spring attachment portion 215 of the shaft member 210.
  • the spring fixing member 250 is positioned on the spring attachment portion 215 to abut against the side surface of the cam attachment portion 214.
  • the spring fixing member 250 is provided not to be rotated in the circumferential direction with respect to the shaft member 210.
  • a projection 251 is provided at the end of the spring fixing member 250.
  • a twisted coil spring 255 is arranged on the outer peripheral surface of the spring fixing member 250. As shown in Fig. 12 , one end of the twisted coil spring 255 is fixed to the projection 251 of the spring fixing member 250, and the other end is fixed to the side surface of the sub-intake cam 245.
  • the sub-intake cam 245 is energized by the twisted coil spring 255 in the first direction Q1 ( Fig. 10 ) with respect to the shaft member 210.
  • the sprocket 17a is arranged at one end of the bearing portion 213 of the shaft member 210 to be vertical to the axial direction.
  • An opening 17b is formed at the center of the sprocket 17a.
  • a screw thread is formed at the inner peripheral surface of one end of the through hole 210a.
  • a volt 260 is screwed into the through hole 210a through the opening 17b of the sprocket 17a.
  • the sprocket 17a is fixed to the shaft member 210.
  • a bearing B1 is provided to abut against the outer peripheral surface of the bearing portion 213 of the shaft member 210, and a bearing B2 is provided to abut against the outer peripheral surface of the bearing portion 216.
  • the shaft member 210 is held by the bearings B1, B2 to be rotatable in the circumferential direction.
  • Fig. 15 is an external perspective view of the switching mechanism 300
  • Fig. 16 is a cross sectional view of the switching mechanism 300.
  • the switching mechanism 300 includes a spring engaging member 310, a spring 315, a moving member 320, a fitting member 330, a spring 335, a pressure mechanism 340 and a sliding mechanism 350.
  • the spring engaging member 310 is arranged to be opposite to a tip end of the volt 260 of Fig. 12 in the through hole 210a of the shaft member 210.
  • One end of the spring 315 is engaged with the spring engaging member 310.
  • the moving member 320 is arranged to be adjacent to the spring engaging member 310 and movable in the axial direction in the through hole 210a of the shaft member 210.
  • the moving member 320 has a movement blocking portion 321, a spring engaging portion 322, a first abutment portion 323, a tapered portion 324, a second abutment portion 325 and a pressure receiving portion 326.
  • the movement blocking portion 321 is provided to project from the spring engaging portion 322 in the axial direction.
  • An outer diameter of the spring engaging portion 322 is larger than an outer diameter of the movement blocking portion 321 and substantially equal to an inner diameter of the through hole 210a.
  • the spring 315 is arranged to surround the outer peripheral surface of the movement blocking portion 321, and the other end of the spring 315 is engaged with the spring engaging portion 322.
  • the tapered portion 324 is provided between the first and second abutment portions 323, 325.
  • An outer diameter of the second abutment portion 325 is larger than an outer diameter of the first abutment portion 323.
  • the tapered portion 324 is formed such that its outer diameter gradually becomes larger from the first abutment portion 323 towards the second abutment portion 325.
  • the pressure receiving portion 326 is provided at the other end of the moving member 320.
  • the through hole 210b is formed at the shaft member 210 to vertically intersect with the through hole 210a.
  • the through hole 210b is opened on the outer peripheral surface of the cam attachment portion 212.
  • the fitting member 330 is arranged in the through hole 210b.
  • the fitting member 330 is constituted by an abutment portion 331 and a fitting portion 332.
  • An outer diameter of the abutment portion 331 is larger than an outer diameter of the fitting portion 332.
  • the abutment portion 331 has an abutment surface convexly curving.
  • the abutment surface of the abutment portion 331 abuts against the first abutment portion 323, the tapered portion 324 or the second abutment portion 325 of the moving member 320 depending on the position of the moving member 320 in the axial direction.
  • the spring 335 is arranged to surround the outer peripheral surface of the fitting member 332. One end of the spring 335 is engaged with the abutment portion 331, and the other end is engaged with a step formed at the end of the through hole 210b.
  • Fig. 17 is an explosive perspective view of the pressure mechanism 340.
  • the pressure mechanism 340 includes a cover member 410, a rotation member 420, an annular member 430, ball members 431a, 431b, a holding member 440 and a bar-shaped member 450.
  • the cover member 410 is substantially cylindrical.
  • an inner diameter of the cover member 410 is set to become smaller in steps from one end to the other end. Thus, steps 411, 412 are formed inside of the cover member 410.
  • the rotation member 420 is substantially columnar and has a ball receiving portion 421, a flange portion 422 and a sliding portion 423.
  • a pair of grooves 424a, 424b spirally extending is provided at the outer peripheral surface of the ball receiving portion 421 to be symmetrical with respect to an axis of the rotation member 420.
  • the holding member 440 is substantially cylindrical and has a ball holding portion 441 and a bar holding portion 442. Outer and inner diameters of the ball holding portion 441 are larger than outer and inner diameters of the bar holding portion 442, respectively.
  • the bar-shaped member 450 is inserted into the bar holding portion 442 of the holding member 440.
  • the bar holding portion 442 is inserted into the through hole 210a of the shaft member 210.
  • the bar-shaped member 450 is held by the bar holding portion 442 to extend in the axial direction of the shaft member 210.
  • One end of the bar-shaped member 450 abuts against the pressure receiving portion 326 of the moving member 320 in the through hole 210a.
  • a pair of recesses 41a, 441b is formed at the inner peripheral surface of the ball holding portion 441 of the holding member 440.
  • the ball members 431a, 431b are fitted into the recesses 441a, 441b, respectively.
  • the annular member 430 is arranged to abut against one end of the ball holding portion 441. Movement in the axial and circumferential directions of the ball members 431a, 431b with respect to the ball holding portion 441 is blocked by the recesses 441a, 441b of the ball holding portion 441 and the annular member 430.
  • One end of the ball receiving portion 421 of the rotation member 420 is inserted into the ball holding portion 441 of the holding member 440 and the ball members 431a, 431b are fitted into the grooves 424a, 424b, respectively.
  • the other end of the bar-shaped member 450 abuts against the end surface of the ball receiving member 421 of the rotation member 420.
  • the cover member 410 is attached to the holding member 440 and the rotation member 420 to cover the outer peripheral surface of the ball holding portion 441 of the holding member 440 and the outer peripheral surface of the ball receiving portion 421 of the rotation member 420.
  • An inner diameter of one end of the cover member 410 is substantially equal to outer diameters of the ball holding portion 441 of the holding member 440 and the annular member 430, and an inner diameter of the other end of the cover member 410 is substantially equal to an outer diameter of the sliding portion 423 of the rotation member 420.
  • An inner diameter of an intermediate portion of the cover member 410 is substantially equal to an outer diameter of the flange portion 422 of the rotation member 420.
  • the annular member 430 abuts against the step 411 of the cover member 410 in the cover member 410. Further, in the state of Fig. 16 , the flange portion 422 of the rotation member 420 abuts against the step 412. The sliding portion 423 of the rotation member 420 projects from the other end of the cover member 410 in the axial direction.
  • the pressure mechanism 340 is integrally rotated with the shaft member 210 except for the rotation member 420.
  • the rotation member 420 is provided to be able to rotate a predetermined angle with respect to the shaft member 210 in the circumferential direction.
  • the sliding mechanism 350 includes a fixing member 351 and a sliding member 352.
  • the fixing member 351 is substantially cylindrical and fixed to the cylinder head 32 of Fig. 10 to surround the outer peripheral surface of the sliding portion 423 of the rotation member 420.
  • the sliding member 352 is annular and attached to the inner peripheral surface of the fixing member 351.
  • the sliding member 352 is elastic and abuts against the outer peripheral surface of the sliding portion 423 of the rotation member 420.
  • the rotation member 420 is rotated with respect to the shaft member 210, whereby the rotation member 420 is moved in the axial direction with respect to the shaft member 210.
  • the rotation member 420 is rotated in the first direction Q1 with respect to the shaft member 210 such that the rotation member 420 is moved in a direction away from the shaft member 210.
  • the rotation member 420 is rotated in the second direction Q2 with respect to the shaft member 210 such that the rotation member 420 is moved in a direction closer to the shaft member 210.
  • the fitting portion 332 of the fitting member 330 is kept in a state of projecting from the outer peripheral surface of the cam attachment portion 212 of the shaft member 210 (hereinafter referred to as a rotation blocked state).
  • the fitting portion 332 of the fitting member 330 is kept in a state of being stored in the through hole 210b of the shaft member 210 (hereinafter referred to as a rotatable state). Description will be made below of switching between the rotation blocked state and the rotatable state.
  • Figs. 18(a) and 18(b) are diagrams for explaining the main-intake cam 240 and the sub-intake cam 245.
  • the fitting pin 241 attached to the main-intake cam 240 is fitted into the opening 246 of the sub-intake cam 245.
  • the main-intake cam 240 is integrally provided with the shaft member 210, and the sub-intake cam 245 is rotatable in the circumferential direction with respect to the shaft member 210.
  • the sub-intake cam 245 is rotated with respect to the shaft member 210 such that the fitting pin 241 is moved in the circumferential direction in the opening 246.
  • a rotatable angular range of the sub-intake cam 245 with respect to the shaft member 210 depends on a length of the opening 246.
  • a cam nose 245T of the sub-intake cam 245 does not overlap with a cam nose 240T of the main-intake cam 240.
  • the position of the sub-intake cam 245 of Fig. 18(a) is an example of a first position.
  • the fitting pin 241 abuts against the other end CB of the opening 246 of the sub-intake cam 245 such that the rotation of the intake-cam 245 in the second direction Q2 is blocked.
  • the entire cam nose 245T of the sub-intake cam 245 overlaps with the cam nose 240T of the main-intake cam 240.
  • the position of the sub-intake cam 245 of Fig. 18(b) is an example of a second position.
  • a length from the axis of the shaft member 210 to the tip end of the cam nose 240T is larger than a length from the axis of the shaft member 210 to the tip end of the cam nose 245T.
  • the tip end of the cam nose refers to a portion of the outer peripheral surface of the cam nose which a length from the axis of the shaft member 210 is the largest.
  • a rise portion of the cam nose refers to a boundary portion between the cam nose and another portion and a portion of the outer peripheral surface of the cam nose which a length from the axis of the shaft member 210 is the smallest.
  • the sub-intake cam 245 is energized in the first direction Q1 ( Fig. 16 ) by the twisted coil spring 255 of Fig. 12 .
  • Energizing force in the first direction Q1 applied from the twisted coil spring 255 to the sub-intake cam 245 is smaller than force in the second direction Q2 applied from the intake rocker arm 510 of Fig. 10 to the sub-intake cam 245 as counterforce during the rotation of the valve driver 17. Therefore, if the force in the second direction Q2 is applied from the intake rocker arm 510 to the sub-intake cam 245 during the rotation of the valve driver 17, the sub-intake cam 245 is rotated in the second direction Q2 in a rotatable range with respect to the shaft member 210.
  • Figs. 19(a) to 19(d) are diagrams for explaining the function of the main-intake cam 240 and the sub-intake cam 245 during the forward rotation of the crankshaft 13
  • Figs. 20(a) to 20(d) are diagrams for explaining the function of the main-intake cam 240 and the sub-intake cam 245 during the reverse rotation of the crankshaft 13.
  • Figs. 21 (a) and 21 (b) are diagrams showing lift amounts of the intake-valve 15.
  • the shaft member 210 is rotated in the first direction Q1 during the forward rotation of the crankshaft 13.
  • the force in the second direction Q2 is not applied from the roller 512 to the sub-intake cam 245.
  • the fitting pin 241 is kept in a state of abutting against the one end CA of the opening 246 of the sub-intake cam 245 by the energizing force of the twisted coil spring 255 ( Fig. 12 ).
  • the intake valve 15 of Fig. 10 is not lifted and the intake port 21 is closed.
  • the position of the roller 512 while the valve 15 is not lifted is referred to as an initial position.
  • the shaft member 210 is rotated in the second direction Q2.
  • the roller 512 does not abut against the cam nose 245T of the sub-intake cam 245, similarly to the state of Fig. 19(a)
  • the force in the second direction Q2 is not applied from the roller 512 to the sub-intake cam 245.
  • the fitting pin 241 is kept in the state of abutting against the one end CA of the opening 246 of the sub-intake cam 245 by the energizing force of the twisted coil spring 255 ( Fig. 12 ).
  • both the main intake-cam 240 and the sub-intake cam 245 drive the intake rocker arm 510. Therefore, the intake valve 15 of Fig. 10 is lifted and the intake port 21 is opened in the ranges from the angle A13 to the angle A12 and from the angle A21 to the angle A22 of Fig. 21 (b) .
  • Figs. 22(a) to 22(d) are diagrams for explaining the exhaust cam 230.
  • the fitting pin 217 is fixed to the cam attachment portion 212 of the shaft member 210 to project from the outer peripheral surface in a direction vertical to the axis direction.
  • a groove 231 is formed at the inner peripheral surface of the exhaust cam 230 to extend in the circumferential direction.
  • the tip end of the fitting pin 217 is arranged in the groove 231 of the exhaust cam 230.
  • the exhaust cam 230 is rotated with respect to the shaft member 210 such that the fitting pin 217 is moved in the groove 231.
  • a rotatable angular range of the exhaust cam 230 with respect to the shaft member 210 depends on a length of the groove 231.
  • the fitting pin 217 abuts against one end DA of the groove 231 of the exhaust cam 230 such that the rotation of the exhaust cam 230 in the second direction Q2 with respect to the shaft member 210 is blocked. Further, as shown in Fig. 22(b) , the fitting pin 217 abuts against the other end DB of the groove 231 of the exhaust cam 230 such that the rotation of the exhaust cam 230 in the first direction Q1 with respect to the shaft member 210 is blocked.
  • the position of the exhaust cam 230 of Fig. 22(a) is an example of a fourth position
  • the position of the exhaust cam 230 of Fig. 22(b) is an example of a third position.
  • a recess 232 is formed at the inner peripheral surface of the exhaust cam 230. While the fitting pin 217 abuts against the one end DA of the groove 231 of the exhaust cam 230 (the state of Fig. 22(a) ), the recess 232 is positioned on an extending line of the through hole 210b. In this state, when the fitting portion 332 of the fitting member 330 is fitted into the recess 232, the rotation of the exhaust cam 230 with respect to the shaft member 210 is blocked.
  • the switching mechanism 300 ( Fig. 16 ) is kept in the rotation blocked state during the forward rotation of the crankshaft 13.
  • the fitting portion 332 of the fitting member 330 is fitted into the recess 232 while the fitting pin 217 abuts against the one end DA of the groove 231 of the exhaust cam 230, and the rotation of the exhaust cam 230 with respect to the shaft member 210 is blocked.
  • the switching mechanism 300 ( Fig. 12 ) is kept in the rotatable state.
  • the exhaust cam 230 is rotatable with respect to the shaft member 210 in a predetermined range.
  • the exhaust cam 230 is energized in the second direction Q2 by the twisted coil spring 225 of Fig. 12 .
  • the energizing force in the second direction Q2 applied from the twisted coil spring 225 to the exhaust cam 230 is smaller than the force in the first direction Q1 applied from the exhaust rocker arm 520 of Fig. 10 to the exhaust cam 230 as the counterforce during the rotation of the valve driver 17. Therefore, when the force in the first direction Q1 is applied from the exhaust rocker arm 520 to the exhaust cam 230 during the rotation of the valve driver 17, the exhaust cam 230 is rotated in the first direction Q1 with respect to the shaft member 210 in a rotatable range.
  • Figs. 23(a) to 23(d) are diagrams for explaining the function of the exhaust cam 230 during the forward rotation of the crankshaft 13
  • Figs. 24(a) to 24(d) are diagrams for explaining the function of the exhaust cam 230 during the reverse rotation of the crankshaft 13.
  • the exhaust cam 230 is integrally rotated with the shaft member 210 in the first direction Q1 while the fitting pin 217 abuts against the one end DA of the groove 231 of the exhaust cam 230.
  • the cam nose 230T of the exhaust cam 230 pushes up the roller 522.
  • the exhaust valve 16 of Fig. 10 is lifted and the exhaust port 23 is opened in the range from the angle A15 to the angle A16 of Fig. 3 .
  • Fig. 24(a) shows the state of the exhaust cam 230 when the crank angle is the angle A30 of Fig. 4
  • Fig. 24(d) shows the state of the exhaust cam 230 when the crank angle is the angle A31 of Fig. 4
  • Figs. 24(b) and 24(c) show the states of the exhaust cam 230 between the states of Fig. 24(a) and Fig. 24(d) .
  • the reverse rotation of the crankshaft 13 is performed in the range from the angle A30 to the angle A31 of Fig. 4 .
  • the exhaust cam 230 can be rotated with respect to the shaft member 210. Further, the exhaust cam 230 is energized in the second direction Q2 by the twisted coil spring 225 of Fig. 12 .
  • the crank angle is at the angle A30 of Fig. 4
  • the cam nose 230T of the exhaust cam 230 does not abut against the roller 522 as shown in Fig. 24(a) . Therefore, the force in the first direction Q1 is not applied from the roller 522 to the exhaust cam 230, and the fitting pin 217 is kept in a state of abutting against the one end DA of the groove 231 by the energizing force of the twisted coil spring 225.
  • Figs. 25(a) and 25(b) are diagrams showing the operation of the exhaust cam 230 immediately after the rotation direction of the crankshaft 13 is switched from the reverse direction to the forward direction.
  • the rise portion of the cam nose 230T abuts against the roller 522 and the fitting pin 217 is between the one end DA and the other end DB of the groove 231 immediately after the rotation direction of the crankshaft 13 is switched from the reverse direction to the forward direction.
  • the shaft member 210 is rotated in the first direction Q1 while the rise portion of the cam nose 230T is kept in the state of abutting against the roller 522 by the energizing force of the twisted coil spring 225 of Fig. 12 .
  • Figs. 26(a) and 26(b) are diagrams for explaining the operation of the switching mechanism 300.
  • Fig. 26(a) shows the switching mechanism 300 in the rotatable state
  • Fig. 26(b) shows the switching mechanism 300 in the rotation blocked state.
  • one direction in the axial direction is a third direction Q3, and the other direction is a fourth direction Q4.
  • the third direction Q3 is a direction in which the moving member 320 comes closer to the spring engaging member 310
  • the fourth direction Q4 is a direction in which the moving member 320 moves away from the spring engaging member 310.
  • the flange portion 422 of the rotation member 420 abuts against the step 412 of the cover member 410, and the bar-shaped member 450 is stored in the holding member 440.
  • the pressure receiving portion 326 of the moving member 320 abuts against one end of the holding member 440, and the first abutment portion 323 of the moving member 320 is positioned on the extending line of the through hole 210b of the shaft member 210.
  • the abutment portion 331 of the fitting member 330 abuts against the first abutment portion 323 of the moving member 320, and the fitting portion 332 is stored in the through hole 210b.
  • the position of the fitting member 330 of Fig. 26(a) is an example of a rotatable position.
  • the flange portion 422 of the rotation member 420 abuts against the annular member 30, and the bar-shaped member 450 projects from the one end of the holding member 440 in the third direction Q3.
  • the second abutment portion 325 of the moving member 320 is positioned on the extending line of the through hole 210b of the shaft member 210.
  • the fitting portion 331 of the fitting member 330 abuts against the second abutment portion 325 of the moving member 320, and the fitting portion 332 of the fitting member 330 objects from the outer peripheral surface of the cam attachment portion 212 of the shaft member 210.
  • the fitting portion 332 of the fitting member 330 is fitted into the recess 232 of the exhaust cam 230 ( Figs. 22(a) and 22(b) ).
  • the position of the fitting member 330 of Fig. 26(b) is an example of the rotation blocked position.
  • the switching mechanism 300 is in the rotation blocked state of Fig. 26(b) before the start-up of the engine 10.
  • the crankshaft 13 is rotated in the reverse direction, and the shaft member 210 is rotated in the second direction Q2.
  • Each portion of the switching mechanism 300 except for the sliding mechanism 350 is rotated in the second direction Q2 together with the shaft member 210.
  • the friction force in the first direction Q1 is exerted from the sliding member 352 of the sliding mechanism 350 onto the sliding portion 423 of the rotation member 420. Therefore, the rotation member 420 is rotated in the first direction Q1 with respect to the shaft member 210 and is moved in the fourth direction Q4 in the axial direction.
  • the flange portion 422 of the rotation member 420 abuts against the step 412 of the cover member 410 such that the rotation in the first direction Q1 and the movement in the fourth direction Q4 of the rotation member 420 are blocked.
  • the moving member 320 and the bar-shaped member 450 are moved in the fourth direction Q4 by the energizing force of the spring 315.
  • the bar-shaped member 450 is stored in the holding member 440, and the pressure receiving portion 326 of the moving member 320 abuts against the one end of the holding member 440.
  • the abutment portion 331 of the fitting member 330 abuts against the first abutment portion 323 of the moving member 320 by the energizing force of the spring 335.
  • the fitting portion 332 of the fitting member 330 is stored in the through hole 210b of the shaft member 210. In such a way, the switching mechanism 300 switches from the rotation blocked state of Fig. 26(b) to the rotatable state of Fig. 26(a) .
  • the rotation direction of the crankshaft 13 switches from the reverse direction to the forward direction, and the shaft member 210 is rotated in the first direction Q1.
  • the fitting pin 217 does not abut against the one end DA of the groove 231 of the exhaust cam 230 and the recess 232 of the exhaust cam 230 is not positioned on the extending line of the through hole 210b of the shaft member 210 immediately after the rotation direction of the crankshaft 13 switches from the reverse direction to the forward direction. Therefore, the fitting portion 332 of the fitting member 330 is kept in the state of being stored in the through hole 210b of the shaft member 210.
  • the switching mechanism 300 switches from the rotatable state of Fig. 26(a) to the rotation blocked state of Fig. 26(b) .
  • the shaft member 210 is rotated in the first direction Q1 such that friction force in the second direction Q2 is exerted from the sliding member 352 of the sliding mechanism 350 onto the sliding portion 423 of the rotation member 420. Therefore, the rotation member 420 is rotated in the second direction Q2 with respect to the shaft member 210 and is moved in the third direction Q3 of the axial direction.
  • the flange portion 422 of the rotation member 420 abuts against the annular member 430 such that the rotation in the second direction Q2 and the movement in the third direction Q3 of the rotation member 420 are blocked.
  • the rotation member 420 is moved in the third direction Q3 such that the one end of the bar-shaped member 450 projects from the holding member 440 in the third direction Q3.
  • This causes the moving member 320 to be moved in the third direction Q3 and the movement blocking portion 321 of the moving member 320 to abut against the spring engaging member 310.
  • the abutment portion 331 of the fitting member 330 is pressed in the direction away from the axis of the shaft member 210 by the tapered portion 324 of the moving member 320.
  • the fitting member 330 is moved against the energizing force of the spring 335 in the direction away from the axis of the shaft member 210, and the fitting portion 332 of the fitting member 330 projects outside of the through hole 210b.
  • Figs. 27(a) and 27(b) are diagrams for explaining another example of the switching mechanism 300.
  • the switching mechanism 300 of Figs. 27(a) and 27(b) difference from the examples of Figs. 26(a) and 26(b) will be described.
  • an outer diameter of the first abutment portion 323 of the moving member 320 is larger than an outer diameter of the second abutment portion 325.
  • the tapered portion 324 is formed such that an outer diameter gradually becomes smaller from the first abutment portion 323 towards the second abutment portion 325.
  • the outer peripheral surface of the first abutment portion 323 and the outer peripheral surface of the second abutment portion 325 are connected via the outer peripheral surface of the tapered portion 324.
  • the switching mechanism 300 enters the rotation blocked state.
  • the fitting portion 331 of the fitting member 330 abuts against the second abutment portion 325 of the moving member 320
  • the fitting portion 332 of the fitting member 330 is stored in the through hole 210b of the shaft member 210.
  • the switching mechanism 300 enters the rotatable state.
  • Spiral grooves 424c, 424d are formed at the outer peripheral surface of the ball receiving portion 421 of the rotation member 420 instead of the grooves 424a, 424b of Figs. 26(a) and 26(b) .
  • a direction of the spiral of the groove 424c is opposite to a direction of the spiral of the groove 424a
  • a direction of the spiral of the groove 424d is opposite to a direction of the spiral of the groove 424b.
  • the ball member 431a is fitted into the groove 424c
  • the ball member 431b is fitted into the groove 424d.
  • the rotation member 420 is rotated in the first direction Q1 with respect to the shaft member 210 such that the rotation member 420 is moved in the third direction Q3.
  • the rotation member 420 is rotated in the second direction Q2 with respect to the shaft member 210 such that the rotation member 420 is moved in the fourth direction Q4.
  • the switching mechanism 300 is in the rotation blocked state of Fig. 27(a) before the start-up of the engine 10.
  • the crankshaft 13 is rotated in the reverse direction, and the shaft member 210 is rotated in the second direction Q2.
  • This causes the friction force in the first direction Q1 to be exerted from the sliding member 352 of the sliding mechanism 350 onto the sliding portion 423 of the rotation member 420. Therefore, the rotation member 420 is rotated in the first direction Q1 with respect to the shaft member 210 and is moved in the third direction Q3 of the axial direction.
  • the rotation member 420 is moved in the third direction Q3 such that the one end of the bar-shaped member 450 projects from the holding member 440 in the third direction Q3.
  • This causes the moving member 320 to be moved in the third direction Q3 and the movement blocking portion 321 of the moving member 320 to abut against the spring engaging member 310.
  • the abutment portion 331 of the fitting member 330 abuts against the second abutment portion 325 of the moving member 320 by the energizing force of the spring 335.
  • This causes the fitting member 330 to be stored in the through hole 210b of the shaft member 210. In such a way, the switching mechanism 300 switches from the rotation blocked state of Fig. 27(a) to the rotatable state of Fig. 27(b) .
  • the moving member 320 and the bar-shaped member 450 are moved in the fourth direction Q4 by the energizing force of the spring 315.
  • This causes the bar-shaped member 450 to be stored in the holding member 440 and the pressure receiving portion 326 of the moving member 320 to abut against the one end of the holding member 440.
  • the abutment portion 331 of the fitting member 330 is pressed by the tapered portion 324 of the moving member 320 in a direction away from the axis of the shaft member 210.
  • the fitting member 330 is moved against the energizing force of the spring 335 in the direction away from the axis of the shaft member 210 and the fitting portion 332 of the fitting member 330 projects outside of the through hole 210b.
  • the fitting portion 332 of the fitting member 330 is fitted into the recess 232 of the exhaust cam 230 ( Figs. 22(a) and 22(b) ).
  • the switching mechanism 300 switches from the rotatable state of Fig. 27(b) to the rotation blocked state Fig. 27(a) .
  • the crankshaft 13 is rotated in reverse by the starter/generator 14 at the start-up of the engine 10.
  • the intake valve 15 is driven by the valve driver 17 such that the fuel injected by the injector 19 is led to the combustion chamber 31a.
  • the fuel-air mixture in the combustion chamber 31a is ignited by the ignition plug 18 while the piston 11 is close to the compression top dead center.
  • the piston 11 is driven such that the crankshaft 13 is rotated in the forward direction. Therefore, an enough torque in the forward direction can be obtained, and the piston 11 can easily go over the compression top dead center. Therefore, the engine 10 can be stably started. Further, because an enough torque for the start-up of the engine 10 can be obtained by the ignition of the fuel-air mixture without using the large-size starter/generator 14, a size of the engine 10 can be reduced. Further, because it is not necessary to use the large-size starter/generator 14, generation of the excess power can be suppressed.
  • the intake valve 15 is driven by the valve driver 17 such that the intake port 21 is opened in the range from the angle A21 to the angle A22 only during the reverse rotation of the crankshaft 13.
  • the fuel-air mixture can be reliably led to the combustion chamber 31a during the reverse rotation of the crankshaft 13 while a backflow of the combusted gas to the intake passage 22 is prevented during the forward rotation of the crankshaft 13.
  • the exhaust valve 16 is driven by the valve driver 17 such that the exhaust port 23 is not opened during the reverse rotation of the crankshaft 13.
  • the fuel-air mixture can be efficiently led to the combustion chamber 31a in the range from the angle A21 to the angle A22.
  • the fuel is injected by the injector 19 at the angle A11 positioned between the angle A0 and the angle A3 during the forward rotation of the crankshaft 13, and the fuel is injected by the injector 19 at the angle A23 positioned between the angle A0 and the angle A1 during the reverse rotation of the crankshaft 13.
  • the fuel is injected into the intake passage 22 before the intake port 21 is opened.
  • the fuel can be appropriately led to the combustion chamber 31a.
  • the fuel-air mixture in the combustion chamber 31a is ignited by the ignition plug 18 after the rotation of the crankshaft 13 in the reverse direction is stopped at the angle A31.
  • the crankshaft 13 can be reliably rotated in the forward direction after the ignition of the fuel-air mixture.
  • crankshaft 13 is driven in the forward direction by the starter/generator 14 after the ignition of the fuel-air mixture at the angle A31. This enables an even larger torque in the forward direction to be obtained. Therefore, the piston 11 can reliably go over the compression top dead center.
  • the invention is not limited to this.
  • the fuel may be directly injected into the combustion chamber 31a by the injector 19 through the intake port 21 with the intake port 21 opened.
  • the invention is not limited to this. During the reverse rotation of the crankshaft 13, the intake port 21 does not have to be opened in the range from the angle A12 to the angle A13.
  • the reverse rotation of the crankshaft 13 is started after the crank angle is adjusted to the angle A30 in the embodiment described above, the invention is not limited to this. If the fuel-air mixture can be introduced into the combustion chamber 31a during the reverse rotation of the crankshaft 13, the reverse rotation of the crankshaft 13 may be started at any position.
  • valve driver 17 While the camshaft is used as the valve driver 17 in the embodiment described above, the invention is not limited to this.
  • a hydraulic valve driving mechanism, an electromagnetic valve driving mechanism or the like may be used as the valve driver 17.
  • the invention is not limited to this.
  • the cam angle sensor that detects the rotation angle of the valve driver 17 (hereinafter referred to as a cam angle) may be provided, and the rotation angle in the range of the two rotations of the crankshaft 13 may be obtained based on the detection result of the cam angle sensor.
  • the rotation angle in the range of two rotations of the crankshaft 13 may be obtained based on the crank angle detected by the crank angle sensor 43 and the cam angle detected by the cam angle sensor. In this case, more accurate rotation angle in the range of two rotations of the crankshaft 13 can be obtained.
  • the invention is not limited to this. If the starter/generator 14 can be appropriately controlled, the current sensor 44 does not have to be provided.
  • the engine system 200 is an example of an engine system
  • the engine 10 is an example of a single-cylinder engine
  • the ECU 6 is an example of a controller
  • the intake passage 22 is an example of an intake passage
  • the injector 19 is an example of a fuel injection device
  • the intake port 21 is an example of an intake port
  • the exhaust port 23 is an example of an exhaust port
  • the intake valve 15 is an example of an intake valve
  • the exhaust valve 16 is an example of an exhaust valve
  • the valve driver 17 is an example of a valve driver.
  • combustion chamber 31a is an example of a combustion chamber
  • ignition plug 18 is an example of an ignition device
  • crankshaft 13 is an example of a crankshaft
  • starter/generator 14 is an example of a starter/generator
  • piston 11 is an example of a piston.
  • the shaft member 210 is an example of a shaft
  • the main-intake cam 240 is an example of a first intake cam
  • the sub-intake cam 245 is an example of a second intake cam
  • the opening 246 and the fitting pin 241 are examples of a first restriction mechanism
  • the twisted coil spring 255 is an example of a first energize member
  • the first direction Q1 is an example of a first direction
  • the second direction Q2 is an example of a second direction.
  • the cam nose 240T is an example of a first cam nose
  • the cam nose 245T is an example of a second cam nose
  • the exhaust cam 230 is an example of an exhaust cam
  • the fitting member 330 is an example of a blocker
  • the moving member 320 is an example of a mover
  • the groove 231 and the fitting pin 217 are examples of a second restriction mechanism
  • the twisted coil spring 225 is an example of a second energize member.
  • the motorcycle 100 is an example of a saddle-straddling type motor vehicle
  • the rear wheel 7 is an example of a drive wheel
  • the vehicle body 1 is an example of a main body.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Control Of Vehicle Engines Or Engines For Specific Uses (AREA)

Claims (15)

  1. Système de moteur, comprenant:
    un moteur monocylindre (10); et
    un dispositif de commande (6) configuré de manière à commander le moteur monocylindre (10), dans lequel le moteur monocylindre (10) comporte
    un dispositif d'injection de carburant (19) disposé dans un passage d'admission (22),
    un pilote de soupape (17) configuré de manière à entraîner respectivement une soupape d'admission (15) configurée pour ouvrir et fermer un orifice d'admission et une soupape d'échappement (16) configurée pour ouvrir et fermer un orifice d'échappement,
    un dispositif d'allumage (18) configuré de manière à allumer un mélange air-carburant dans une chambre de combustion (31a), et
    un démarreur/générateur (14) prévu sur un vilebrequin (13) et configuré de manière à faire tourner le vilebrequin (13) dans des directions en avant et en arrière et générer de l'énergie électrique par une rotation du vilebrequin (13),
    caractérisé par le fait que
    le dispositif de commande (6) est configuré de manière à commander le démarreur/générateur (14) pour faire tourner le vilebrequin (13) dans la direction inverse pendant le démarrage,
    le pilote de soupape (17) est configuré de manière à piloter la soupape d'admission (15) de sorte que le carburant injecté par le dispositif d'injection de carburant (19) soit amené vers la chambre de combustion (31a) depuis le passage d'admission (22) à travers l'orifice d'admission à un premier moment dans un laps de temps au cours duquel le vilebrequin (13) est entraîné en rotation dans la direction inverse, et
    le dispositif de commande (6) est configuré de manière à commander le dispositif d'allumage (18) de sorte que le mélange carburant-air soit allumé à un deuxième moment auquel le mélange combustible-air est comprimé dans la chambre de combustion (31a) par la rotation du vilebrequin (13) dans la direction inverse et un piston n'atteint pas un centre mort supérieur de compression après que le carburant soit amené à la chambre de combustion (31a) au premier moment.
  2. Système de moteur selon la revendication 1, dans lequel
    le premier moment est compris dans un laps de temps pendant lequel le piston tombe d'un centre mort supérieur d'échappement pendant la rotation du vilebrequin (13) dans la direction inverse.
  3. Système de moteur selon la revendication 1 ou 2, dans lequel
    le pilote de soupape (17) est configuré de manière à
    piloter la soupape d'échappement (16) de sorte que l'orifice d'échappement soit ouvert pendant un laps de temps pendant lequel un angle de rotation du vilebrequin (13) se situe dans une première plage, et de manière à piloter la soupape d'admission (15) de sorte que l'orifice d'admission soit ouvert pendant un laps de temps pendant lequel l'angle de rotation du vilebrequin (13) se situe dans une deuxième plage pendant la rotation du vilebrequin (13) dans la direction en avant, et
    piloter la soupape d'admission (15) de sorte que l'orifice d'admission soit ouvert pendant un laps de temps pendant lequel l'angle de rotation du vilebrequin (13) se situe dans une troisième plage dans la première plage pendant la rotation du vilebrequin (13) dans la direction inverse, et
    la troisième plage est plus grande qu'une plage dans laquelle la première plage et la deuxième plage viennent en recouvrement.
  4. Système de moteur selon la revendication 3, dans lequel
    la deuxième plage et la troisième plage sont séparées l'une de l'autre.
  5. Système de moteur selon la revendication 3 ou 4, dans lequel
    le pilote de soupape (17) est configuré de manière à piloter la soupape d'échappement (16) de sorte que l'orifice d'échappement ne soit pas ouvert pendant un laps de temps pendant lequel l'angle de rotation de vilebrequin (13) se situe au moins dans la troisième plage pendant la rotation du vilebrequin (13) dans la direction inverse.
  6. Système de moteur selon l'une quelconque des revendications 3 à 5, dans lequel
    le dispositif de commande (6) est configuré de manière à commander le dispositif d'injection de carburant (19) de sorte que le carburant soit injecté lorsque l'angle de rotation du vilebrequin (13) se situe dans une quatrième plage pendant la rotation du vilebrequin (13) dans la direction en avant et que le carburant soit injecté lorsque l'angle de rotation du vilebrequin (13) se situe dans une cinquième plage différente de la quatrième plage pendant la rotation du vilebrequin (13) dans la direction inverse.
  7. Système de moteur selon la revendication 6, dans lequel
    la cinquième plage est réglée de manière à être positionnée à un angle plus avancé que la quatrième plage pendant la rotation du vilebrequin (13) dans la direction inverse.
  8. Système de moteur selon la revendication 6 ou 7, dans lequel
    la cinquième plage se situe dans la deuxième plage.
  9. Système de moteur selon l'une quelconque des revendications 3 à 8, dans lequel
    le pilote de soupape (17) comporte
    un arbre (210) prévu pour être mis en rotation ensemble avec la rotation du vilebrequin (13),
    une première came d'admission (240) prévue pour être mise en rotation de manière solidaire avec l'arbre (210) et configurée de manière à actionner la soupape d'admission (15),
    une deuxième came d'admission (245) prévue de manière à pouvoir tourner par rapport à l'arbre (210) et configurée de manière à faire fonctionner la soupape d'admission (15),
    un premier mécanisme de limitation (241, 246) configuré de manière à limiter un mouvement de la deuxième came d'admission (245) par rapport à l'arbre (210), et
    un premier élément d'activation (255) configuré de manière à activer la deuxième came d'admission (245), où
    le premier mécanisme d'activation (241, 246) est prévu de sorte que la rotation de la deuxième came d'admission (245) dans une première direction soit bloquée dans une première position de l'arbre (210) et que la rotation de la deuxième came d'admission (245) dans un deuxième direction, opposée à la première direction, soit bloquée dans une deuxième position de l'arbre (210),
    la deuxième came d'admission (245) est configurée pour actionner la soupape d'admission (15) dans la première position et ne pas actionner la soupape d'admission (15) dans la deuxième position,
    le premier élément d'activation (255) est configuré de manière à actionner la deuxième came d'admission (245) dans la première direction,
    une contre-force supérieure à la force d'actionnement du premier élément d'actionnement (255) est appliquée à la deuxième came d'admission (245) de la soupape d'admission (15) de sorte que la deuxième came d'admission (245) soit déplacée dans la deuxième direction pendant la rotation du vilebrequin (13) dans la direction en avant, et
    la deuxième came d'admission (245) est configurée pour être déplacée vers la première position par la force d'actionnement du premier élément d'actionnement (255) de sorte que la deuxième came d'admission (245) actionne la soupape d'admission (15) pendant la rotation du vilebrequin, (13) dans la direction inverse.
  10. Système de moteur selon la revendication 9, dans lequel
    la première came d'admission (240) présente un premier nez de came (240T),
    la deuxième came d'admission (245) présente un deuxième nez de came (245T), et
    l'ensemble du deuxième nez de came (245T) vient en recouvrement avec le premier nez de came (240T) lorsque la deuxième came d'admission (245) se trouve dans la deuxième position, et au moins une partie du deuxième de nez came (245T) ne vient pas en recouvrement avec le premier nez de came (240T) lorsque la deuxième came d'admission (245) se trouve dans la première position.
  11. Système de moteur selon la revendication 9 ou 10, dans lequel
    le pilote de soupape (17) comporte par ailleurs
    une came d'échappement (230) prévue de manière à pouvoir tourner par rapport à l'arbre (210) et configurée de manière à actionner la soupape d'échappement,
    un bloqueur (330) prévu de manière à pouvoir se déplacer entre une position de blocage de rotation dans laquelle la rotation de la came d'échappement (230) par rapport à l'arbre (210) est bloquée dans une position prédéterminée de l'arbre (210) et une position de rotation dans laquelle la came d'échappement (230) peut tourner par rapport à l'arbre (210), et
    un déplaceur (320) configuré pour déplacer le bloqueur (330) vers la position de blocage de rotation pendant la rotation du vilebrequin (13) dans la direction en avant et vers la position de rotation lors de la rotation du vilebrequin (13) dans la direction inverse.
  12. Système de moteur selon la revendication 11, dans lequel
    le pilote de soupape (17) comporte par ailleurs un deuxième mécanisme de limitation (217, 231) configuré pour limiter un mouvement de la came d'échappement (230) par rapport à l'arbre (210),
    le deuxième mécanisme de limitation (217, 231) est prévu de manière à bloquer la rotation de la came d'échappement (230) dans la première direction dans une troisième position de l'arbre (210) et la rotation de la came d'échappement (230) dans la deuxième direction dans une quatrième position de l'arbre (210),
    une contre-force est appliquée par la soupape d'échappement (16) sur la came d'échappement (230) de sorte que la came d'échappement (230) soit déplacée dans la première direction pendant la rotation du vilebrequin (13) dans la direction inverse, et
    le bloqueur (330) est configuré de manière à bloquer la came d'échappement (230) dans la quatrième position dans la position de rotation bloquée.
  13. Système de moteur selon la revendication 12, dans lequel
    le pilote de soupape (17) comporte par ailleurs un deuxième élément d'actionnement (225) configuré de manière à actionner la came d'échappement (230) dans la deuxième direction, et
    une force d'actionnement du deuxième élément d'actionnement (225) est inférieure à la contre-force dans la première direction appliquée par la soupape d'échappement (16) sur la came d'échappement (230) pendant la rotation du vilebrequin (13) dans la direction inverse.
  14. Système de moteur selon l'une quelconque des revendications 1 à 13, dans lequel
    le dispositif de commande (6) est configuré de manière à commander de sorte que le mélange air-carburant soit allumé par le dispositif d'allumage (18) tandis que le vilebrequin (13) est entraîné en rotation dans la direction en avant au deuxième moment.
  15. Système de moteur selon la revendication 14, dans lequel
    le dispositif de commande (6) est configuré de manière à commander de sorte que le vilebrequin (13) soit entraîné dans la direction en avant par le démarreur/générateur (14) après le deuxième moment.
EP13188298.7A 2012-10-11 2013-10-11 Système motorisé Not-in-force EP2719883B1 (fr)

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EP2719883B1 true EP2719883B1 (fr) 2014-11-05

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JP4665818B2 (ja) * 2006-03-31 2011-04-06 マツダ株式会社 エンジンの始動装置
US20100000492A1 (en) * 2006-08-24 2010-01-07 Vishvas Prabhakar Ambardekar Modified revolving piston internal combustion engine
EP2240683A1 (fr) * 2008-01-08 2010-10-20 Continental Automotive GmbH Procédé pour démarrer un moteur à combustion interne, dispositif et appareil de commande
JP2010059959A (ja) * 2008-08-08 2010-03-18 Yamaha Motor Co Ltd エンジンの点火制御装置、内燃機関及びそれらを備えた自動二輪車
TWI467088B (zh) * 2011-02-11 2015-01-01 Kwang Yang Motor Co The Starting Method of Single - cylinder and Four - stroke Engine

Also Published As

Publication number Publication date
EP2719883A1 (fr) 2014-04-16
JP2014077405A (ja) 2014-05-01
TW201414918A (zh) 2014-04-16
ES2527207T3 (es) 2015-01-21
TWI487834B (zh) 2015-06-11

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