WO2007069467A1 - 可変動弁装置ならびにそれを備えるエンジンシステムおよび乗り物 - Google Patents
可変動弁装置ならびにそれを備えるエンジンシステムおよび乗り物 Download PDFInfo
- Publication number
- WO2007069467A1 WO2007069467A1 PCT/JP2006/323982 JP2006323982W WO2007069467A1 WO 2007069467 A1 WO2007069467 A1 WO 2007069467A1 JP 2006323982 W JP2006323982 W JP 2006323982W WO 2007069467 A1 WO2007069467 A1 WO 2007069467A1
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- Prior art keywords
- state
- cam
- engine
- rotation
- valve
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/022—Chain drive
-
- 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
-
- 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
- F01L1/08—Shape of cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/181—Centre pivot rocking arms
- F01L1/182—Centre pivot rocking arms the rocking arm being pivoted about an individual fulcrum, i.e. not about a common shaft
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
- F01L2001/0535—Single overhead camshafts [SOHC]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2305/00—Valve arrangements comprising rollers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2800/00—Methods of operation using a variable valve timing mechanism
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/03—Auxiliary actuators
- F01L2820/035—Centrifugal forces
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/04—Sensors
- F01L2820/041—Camshafts position or phase sensors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D2041/001—Controlling intake air for engines with variable valve actuation
-
- 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
-
- 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
- F02D41/009—Electrical control of supply of combustible mixture or its constituents using means for generating position or synchronisation signals
-
- 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 relates to a variable valve operating apparatus, an engine system including the same, and a vehicle.
- variable valve timing mechanisms that control the opening and closing timing of intake valves or exhaust valves for the purpose of improving fuel efficiency, reducing harmful substances in exhaust gas, and increasing output in a specific rotation range.
- WT variable valve timing mechanisms
- variable variable timing mechanisms using, for example, an actuator such as a hydraulic cylinder or an electric motor.
- actuators are expensive.
- variable valve timing mechanism becomes large.
- Patent Document 1 Japanese Patent Laid-Open No. 9-324614
- valve timing is mechanically controlled at a predetermined rotational speed by the centrifugal force associated with the rotation of the engine rather than the ECU (Electronic Control Unit) switching the valve timing. Switch.
- the ECU determines the valve timing based on the engine speed, and controls the fuel injection amount, fuel injection timing, and spark ignition timing.
- the valve timing is switched. The engine speed varies.
- the ECU cannot accurately determine the actual nove timing during operation.
- the control of the fuel injection amount, fuel injection timing, and spark ignition timing by the ECU may be inappropriate for the actual valve timing.
- problems such as an increase in harmful substances in the exhaust gas occur.
- An object of the present invention is to provide a variable valve operating apparatus capable of accurately determining the switching of the state of the cam member while switching the valve timing by switching the state of the cam member with a mechanical structure. It is to provide an engine system and vehicle equipped with it.
- a variable valve operating apparatus is a variable valve operating apparatus that controls opening and closing of a valve in accordance with the rotational speed of the engine, and is configured to be rotatable in conjunction with the rotation of the engine. It is possible to shift to a first state having a first positional relationship with the rotary member and a second state having a second positional relationship.
- a movable member having a force member and a first detected portion, and moving the cam member to the first state force and the second state by moving with a centrifugal force accompanying the rotation of the rotating member;
- the member is at the first position corresponding to the first state or at the second position corresponding to the second state, the first detected part rotating with the rotation of the rotating member is arranged to be detectable. And a detector.
- the rotating member rotates in conjunction with the rotation of the engine, and the cam member rotates with the rotation of the rotating member.
- the valve that contacts the cam member opens and closes.
- the cam member can be shifted between a first state having a first positional relationship with respect to the rotating member and a second state having a second positional relationship. Thereby, the opening / closing timing of the valve driven by the cam member is switched.
- the movable member moves the first position force to the second position by the centrifugal force accompanying the rotation of the rotating member.
- the cam member shifts from the first state to the second state.
- the first detected portion of the movable member can be detected by the detector.
- the movable member when the movable member is in one of the first position and the second position, the first detected part is detected by the detector.
- the movable member it can be determined whether the movable member is in the first position or the second position based on whether or not the first detected part is detected by the detector, and the cam member is in the first position. It can be determined whether the current state or the second state. Therefore, it is possible to accurately determine the opening / closing timing of the valve by the cam member.
- variable valve operating apparatus further includes a second detected portion that rotates together with the rotating member, and the second detected portion is detected by the detector by rotating with the rotation of the rotating member. It may be provided at the position to be.
- the second detected portion rotates in accordance with the rotation of the rotating member regardless of whether the cam member is in the first state or the second state. It becomes more detectable. Since the detection period of the second detected part by the detector corresponds to the rotation period of the rotating member, the engine operation can be controlled based on the rotation period of the rotating member.
- the detection of the first detected part and the detection of the second detected part can be performed by a common detector. Therefore, since it is not necessary to provide a plurality of detectors separately, it is possible to reduce the size of the variable valve operating apparatus and to suppress an increase in production cost.
- the detector may be arranged at a position where the first detected portion and the second detected portion can be detected from a direction parallel to the rotation axis of the rotating member.
- the first detected object is detected by a common detector from a direction parallel to the rotation axis of the rotating member. And the second detected part are detected.
- the variable valve device can be miniaturized and the degree of freedom in design in the direction perpendicular to the rotating shaft of the rotating member can be improved.
- the detector may be arranged at a position where the first detected part and the second detected part can be detected from a direction perpendicular to the rotation axis of the rotating member.
- the first detected portion and the second detected portion are detected by a common detector from a direction perpendicular to the rotation axis of the rotating member.
- the variable valve device can be miniaturized and the degree of freedom in design in the direction parallel to the rotation axis of the rotating member can be improved.
- the length of the first detected portion in the rotational direction may be different from the length of the second detected portion in the rotational direction.
- the detection period of the first detected part by the detector is different from the detection period of the second detected part by the detector. Therefore, the first detected part and the second detected part can be easily identified based on the difference in the period during which the detector detects the object.
- An engine system includes an engine having a valve, a variable valve operating apparatus that controls opening and closing of the valve according to the rotational speed of the engine, and a control unit that controls the engine
- the variable valve operating apparatus includes a rotating member that is rotatably provided in conjunction with the rotation of the engine, and a first member that is provided so as to contact the valve and has a first positional relationship with the rotating member.
- a cam member capable of transitioning to the second state having the second positional relationship and a first detected portion, and moving the cam member by the centrifugal force accompanying the rotation of the rotating member.
- the rotating member Detector arranged so as to be able to detect the first detected part rotating with the rotation
- the control unit determines whether the cam member is in a deviation between the first state and the second state based on the output signal of the detector, and based on the determination result! This is to control the operation.
- valve of the engine is driven by the variable valve operating device.
- the rotating member rotates in conjunction with the rotation of the engine, and the cam member rotates with the rotation of the rotating member. This opens the valve that contacts the cam member. Close.
- the cam member can transition between a first state having a first positional relationship with respect to the rotating member and a second state having a second positional relationship. Thereby, the opening / closing timing of the valve driven by the cam member is switched.
- the first detected portion of the movable member can be detected by the detector.
- the detector gives the detection result of the first detected part to the control part as an output signal.
- the control unit determines whether the cam member is in the first state or the second state based on the output signal of the detector. Based on the determination result, the control unit controls the operation of the engine.
- control unit determines whether the cam member is in the first state or the second state based on the output signal of the detector, whereby the opening / closing timing of the noble by the cam member is determined. Can be accurately determined. Therefore, the control unit can control the engine operation so as to be optimized according to the opening / closing timing of the valve.
- variable valve apparatus further includes a second detected portion that rotates together with the rotating member, and the second detected portion is detected by the detector by rotating with the rotation of the rotating member. It may be provided at the position to be.
- the second detected portion rotates in accordance with the rotation of the rotating member regardless of whether the cam member is in the first state or the second state. It becomes more detectable. Since the detection period of the second detected part by the detector corresponds to the rotation period of the rotating member, the control unit can control the engine based on the rotation period of the rotating member.
- the detection of the first detected part and the detection of the second detected part can be performed by a common detector. Therefore, since it is not necessary to provide a plurality of detectors separately, it is possible to reduce the size of the variable valve operating apparatus and to suppress an increase in production cost. As a result, it is possible to reduce the size and cost of the engine.
- the length of the first detected portion in the rotational direction may be different from the length of the second detected portion in the rotational direction.
- the detection period of the first detected part by the detector is different from the detection period of the second detected part by the detector. Therefore, the first detected part and the second detected part can be easily identified based on the difference in the period during which the detector detects the object.
- the control unit may determine whether or not the first detected unit is detected based on a detection period of the first or second detected unit by the detector.
- the control unit can easily identify the detection of the first detected part and the detection of the second detected part by the detector.
- the control unit may determine whether or not the first detected unit is detected based on the number of detections by the detector during one rotation period of the rotating member.
- the second detected portion is detected every rotation of the rotating member.
- the first detected part is detected when the movable member is in either the first position or the second position.
- control unit can determine whether or not the force has detected the first detected portion based on the number of detections by the detector during one rotation period of the rotating member. Thereby, the control unit can determine whether the cam member is in the first state or the second state.
- the control unit determines whether the cam member is shifted between the first state and the second state based on the output signal of the detector, and based on the determination result, the fuel in the engine Control at least one of injection quantity, fuel injection timing and spark ignition timing.
- a vehicle includes an engine system and a driving member driven by power generated by the engine system, and the engine system includes an engine having a valve,
- the variable valve device is equipped with a variable valve device that controls opening and closing of the valve according to the rotational speed of the engine and a control unit that controls the engine.
- a member a cam member provided in contact with the valve, and capable of transitioning between a first state having a first positional relationship with the rotating member and a second state having a second positional relationship;
- a movable member that has one detected part and moves the cam member to the first state force and the second state by moving with the centrifugal force accompanying the rotation of the rotating member, and the movable member corresponds to the first state To first position or second
- a detector arranged to detect the first detected part that rotates with the rotation of the rotating member when in the second position corresponding to the state, and the control unit outputs an output signal of the detector Based on this, it is determined whether the cam member is in the first state or the second state, and the operation of the engine is controlled based on the determination result.
- the drive member is driven by the power generated by the engine system.
- the control unit determines whether the cam member is in the first state or the second state based on the output signal of the detector. Thereby, the opening / closing timing of the valve by the cam member can be accurately determined.
- control unit can control the operation of the engine to be optimized according to the opening / closing timing of the valve.
- the first detected portion is detected by the detector when the movable member is in one of the first position and the second position.
- FIG. 1 is a schematic diagram of a motorcycle according to an embodiment of the present invention.
- FIG. 2 is a schematic diagram for explaining the outline of the variable valve operating apparatus according to the embodiment of the present invention.
- FIG. 3 is an assembled perspective view for explaining the structure of the valve timing control device.
- FIG. 4 is a cutaway perspective view for explaining the operation of the valve timing control device.
- FIG. 5 is a cutaway perspective view for explaining the operation of the valve timing control device.
- FIG. 6 is a diagram for explaining the switching between the high rotation state and the low rotation state of the valve timing control device.
- FIG. 7 is a detailed sectional view of the cylinder head.
- FIG. 8 is a diagram showing lift amounts of the intake valve and the exhaust valve by the valve timing control device.
- FIG. 9 is a cross-sectional view showing details of the inside of the cylinder head.
- FIG. 10 is a cross-sectional view showing a nove timing control device and a cam sensor in a low rotation state.
- FIG. 11 is a cross-sectional view showing a valve timing control device and a cam sensor in a high rotation state.
- FIG. 12 is a timing chart for explaining an example of ECU processing performed based on a cam signal and a crank signal.
- FIG. 13 is a timing chart for explaining an example of ECU processing performed based on a cam signal and a crank signal.
- FIG. 14 is a flowchart showing valve timing control processing by the ECU.
- FIG. 15 is a flowchart showing valve timing control processing by the ECU.
- FIG. 16 is a flowchart showing valve timing control processing by the ECU.
- FIG. 17 is a flowchart showing valve timing control processing by the ECU.
- FIG. 18 is a view showing another arrangement example of the cam sensor.
- variable valve operating apparatus an engine system including the same, and a vehicle will be described.
- a small motorcycle will be described as a vehicle.
- FIG. 1 is a schematic diagram of a motorcycle according to an embodiment of the present invention.
- the head pipe 3 is provided at the front end of the main body frame 6.
- a front fork 2 is provided on the head pipe 3 so as to be swingable in the left-right direction.
- the front wheel 1 is rotatably supported at the lower end of the front fork 2.
- a handle 4 is attached to the upper end of the head pipe 3.
- An engine 7 is held at the center of the main body frame 6.
- a fuel tank 8 is provided above the engine 7, and a seat 9 is provided behind the fuel tank 8.
- a rear arm 10 is connected to the main body frame 6 so as to extend to the rear of the engine 7.
- the rear arm 10 holds the rear wheel 11 and the rear wheel driven sprocket 12 rotatably.
- a muffler 14 is attached to the rear end of the exhaust pipe 13 connected to the engine 7.
- the rear wheel drive sprocket 15 is attached to the drive shaft 26 of the engine 7.
- the rear-wheel drive sprocket 15 is connected to the rear-wheel drive socket 12 of the rear wheel 11 via a chain 16.
- the engine 7 includes a variable valve gear.
- the variable valve operating apparatus according to the present embodiment will be described.
- FIG. 2 is a schematic diagram for explaining the outline of the variable valve operating apparatus according to the embodiment of the present invention.
- the variable valve apparatus 50 includes a valve timing control device 200 and a force sensor 250.
- the valve timing control device 200 is provided in the cylinder head 7S and includes a cam driven sprocket 221, an intake cam 231 and an exhaust cam 241.
- crankshaft 23 rotates, and the cam drive sprocket 24 provided on the crankshaft 23 rotates.
- the rotational force of the cam drive sprocket 24 is controlled via the chain 25 by valve timing control. It is transmitted to the cam driven sprocket 221 of the control device 200. As a result, the valve timing control device 200 rotates.
- the phase relationship between the intake cam 231 and the exhaust cam 241 changes in accordance with the rotational speed of the engine 7 and changes in the rotational speed (increase and decrease in rotational speed). As a result, the valve timing changes.
- crank sensor 260 In the vicinity of the crankshaft 23, a crank sensor 260 is provided.
- the crank sensor 260 gives information related to the rotation of the crankshaft 23 to the ECU (Electronic Control Unit) 500 as a crank signal CR. Details of the crank sensor 260 and the crank signal CR will be described later.
- a cam sensor 250 is provided in the vicinity of the valve timing control device 200 in the cylinder head 7S.
- the cam sensor 250 provides information regarding the operation of the valve timing control device 200 to the ECU 500 as a cam signal CA.
- Cam sensor 250 and cam signal C are provided in the vicinity of the valve timing control device 200 in the cylinder head 7S.
- the cam sensor 250 provides information regarding the operation of the valve timing control device 200 to the ECU 500 as a cam signal CA.
- the throttle valve sensor 270 detects the opening of a throttle valve (not shown) provided in the engine 7 (hereinafter referred to as throttle opening TR).
- the throttle opening TR detected by the throttle valve sensor 270 is given to the ECU 500.
- the spark ignition signal SI is given from the ECU 500 to the spark plug 280 provided at the upper part of the cylinder head 7S, and the fuel injection signal FI is given to the injector 290 provided in the engine 7.
- the fuel injection amount and fuel injection timing from 290 are controlled.
- FIG. 3 is an assembled perspective view for explaining the structure of the valve timing control device 200.
- X, ⁇ , and Z three directions orthogonal to each other are defined as an X direction, a Y direction, and a Z direction.
- the valve timing control device 200 is roughly composed of a cam driven sprocket unit 220, an intake camshaft 230, and an exhaust camshaft 240.
- the cam driven sprocket section 220 is formed of a cam driven sprocket 22 parallel to the XZ plane. Have one. A through hole 220a is formed in the center of the cam driven sprocket 221. Plate-like support members 211 and 212 are attached to one surface of the cam driven sprocket 221 with two screws 219, respectively, at a predetermined interval. A protrusion 219a extending in the Y direction is provided on the head of one screw 219 attached to the support member 211. Details of the protrusion 219a will be described later.
- the support member 211 has protrusions 211B and 211D extending in the Y direction at the top and bottom
- the support member 212 has protrusions 212B and 212D extending in the Y direction at the top and bottom.
- a spring holding piece 211C extending in the Y direction is formed between the protruding piece 211B and the protruding piece 211D
- a spring holding piece 212C extending in the Y direction is formed between the protruding piece 212B and the protruding piece 212D.
- Through-holes are formed in the protrusion pieces 211B, 211D, 212B, 212D and the thread holding pieces 211C, 212C.
- a substantially rectangular parallelepiped weight 213 is disposed between the protruding piece 211B and the protruding piece 212B.
- the weight 213 is rotatably held by a rotating shaft 215 inserted in the through hole of the protruding piece 211B and the protruding piece 212B.
- Two hook portions 213f are formed so that the end force on the upper surface of the weight 213 also extends obliquely downward.
- the tip of the hook portion 213f is formed in a semi-cylindrical shape.
- a substantially rectangular parallelepiped protrusion 213a is formed on the upper surface of the weight 213 along the X direction so as to be inclined in the Y direction. Details of the protrusion 213a will be described later.
- a substantially rectangular parallelepiped weight 216 is disposed between the protruding piece 211D and the protruding piece 212D.
- the weight 216 is rotatably held by a rotating shaft 218 inserted in the through hole of the protruding piece 211D and the protruding piece 212D.
- the weight 216 has substantially the same shape as the weight 213, and has a hook portion 216f corresponding to the hook portion 213f. However, the weight 216 is not formed with a portion corresponding to the protruding portion 213a.
- the weights 213 and 216 are arranged so as to be symmetrical with respect to an axis parallel to the X direction.
- a high-speed lock pin 214 is disposed below the weight 213 so as to penetrate the cam driven sprocket 221.
- the lock pin 214 is held by a hook portion 213 f formed on the weight 213.
- a low-speed lock pin 217 is disposed above the weight 216.
- the low-speed lock pin 217 is held by a hook portion 216f formed on the weight 216.
- the high-speed lock pin 214 and the low-speed lock pin 217 are slidable in the Y direction with respect to the cam driven sprocket 222. In the state shown in FIG. 3, the tip of the low-speed lock pin 217 protrudes in the Y direction from the tip of the high-speed lock pin 214 on the other surface side of the cam dribbon socket portion 220.
- One end of the spring S1 is locked in the through hole of the protruding portion (not shown) of the weight 213, and the other end is locked in the through hole of the spring holding piece 211C. Further, one end of the spring S2 is locked in the through hole of the protruding portion (not shown) of the weight 216, and the other end is locked in the through hole of the spring holding piece 212C.
- a protrusion 220 T is formed at a portion between the cam driven sprocket 221 and the weight 216.
- Two fixing pins 230A and 230B are provided so as to extend in the Y direction from the other surface side of the cam driven sprocket 221.
- the fixing pins 230A and 230B are respectively connected to the cam driven sprocket 221 on both sides of the through-hole 220a.
- an intake camshaft 230 and an exhaust camshaft 240 are both arranged such that their axis J is parallel to the Y direction.
- the intake camshaft 230 is formed of an intake cam 231, a step 232, and a rotating shaft 233.
- the intake camshaft 230 has a cylindrical rotating shaft 233 on one end side, a step portion 232 having a diameter slightly larger than the diameter of the rotating shaft 233 at the center, and the other end side. It has a suction power mu 231.
- a rotation through hole 230H extending in the Y direction from the center of the end surface of the rotation shaft 233 to the center of the end surface of the intake cam 231 is formed. That is, the rotation through hole 230H is formed so that the one end force of the intake camshaft 230 in the Y direction also extends to the other end.
- a high-speed pin introduction hole 233c, a low-speed pin introduction hole 233d, and two pin floating grooves 233a and 233b are formed on the end surface of the rotating shaft 233 on a circle centered on the axis J! .
- the high-speed pin introduction hole 233c and the low-speed pin introduction hole 233d are formed so as to be substantially opposed to each other via the rotation through hole 230H. That is, the high-speed lock pin 214 and the low-speed lock pin 217 are arranged at a position that makes an angle of 180 ° with respect to the axis J.
- the high-speed pin introduction hole 233c and the low-speed pin introduction hole 233d also have a positional force that forms an angle of 180 ° with the axis J as the center, and the circumferential force is shifted by a predetermined angle.
- the pin floating grooves 233a and 233b are formed so as to extend along the circumferential direction around the axis J and to face each other via the rotation through hole 230H.
- the exhaust camshaft 240 has a cam fixing shaft 243 extending in the Y direction on one end side, a stepped portion 242 and an exhaust cam 241 in the central portion, and a protruding shaft 244 extending in the Y direction on the other end side. Yes.
- a sprocket screw hole 240H is formed at the end of the cam fixing shaft 243.
- the cam fixing shaft 243 of the exhaust camshaft 240 is inserted into the rotation through hole 230H of the intake camshaft 230.
- the exhaust camshaft 240 holds the intake camshaft 230 rotatably.
- one end of the cam fixing shaft 243 of the exhaust camshaft 240 is inserted into the through hole 220a from the other surface side of the cam driven sprocket 221.
- exhaust cam 241, the stepped portion 242, the cam fixing shaft 243, and the protruding shaft 244 of the exhaust camshaft 240 may be integrally formed! Also good.
- intake cam 231, the stepped portion 232, and the rotating shaft 233 of the intake camshaft 230 may be integrally formed! / May be formed individually!
- FIG. 4 and 5 are cutaway perspective views for explaining the operation of the nozzle timing control device 200.
- the direction indicated by the arrow Z is defined as the Z direction.
- the direction in which the arrow is directed is the + direction, and the opposite direction is the one direction.
- the one-dot chain line in the figure indicates the axis J of the valve timing control device 200.
- FIG. 4 shows a state when the assembly of the valve timing control device 200 is completed.
- FIG. 5 shows the state of the nozzle timing control device 200 when the engine 7 is rotating at high speed (when the rotational speed of the engine 7 is high).
- FIG. 4 the cam driven sprocket portion 220 is cut out along the central force Z direction. As shown in FIG. 3, the fixing pin 230B is actually connected to the cam dribbling socket 221.
- the weight 213 is biased in the ⁇ Z direction by the spring S1.
- the weight 213 holds the high-speed lock pin 214 inserted into the through hole 220b of the cam driven sprocket 221. Thereby, the rotation operation of the weight 213 around the rotation shaft 215 is limited.
- the weight 216 is urged in the + Z direction by a spring S2 (not shown) (see FIG. 3).
- the weight 216 holds the low-speed lock pin 217 inserted into the through hole 220c of the cam driven sprocket 221. Thereby, the rotation operation of the weight 216 around the rotation shaft 218 is limited.
- One end of 14 is substantially in contact with a contact surface 230M perpendicular to the axis J of the intake camshaft 230.
- the low speed lock pin 217 is inserted into the low speed pin introduction hole 233d of the intake camshaft 230.
- One end of the low-speed lock pin 217 inserted into the low-speed pin introduction hole 233d is substantially in contact with the bottom surface of the low-speed pin introduction hole 233d.
- the pin floating groove 233b extends along the circumferential direction around the axis J.
- one end in the circumferential direction of the pin floating groove 233b is referred to as a low speed groove end LP, and the other end in the circumferential direction of the pin floating groove 233b is referred to as a high speed groove end HP.
- the fixed pin 230B inserted into the pin floating groove 233b is positioned at the low speed groove end LP. Since the fixed pin 230B is fixed to the cam driven sprocket 221, the intake camshaft 230 is restricted from rotating in the direction of the arrow Ml relative to the cam driven sprocket 221 and the exhaust camshaft 240. [0101] However, in the state of FIG. 4, the low speed lock pin 217 is inserted into the low speed pin introduction hole 233d, so that the intake camshaft 230 has an arrow Ml and an arrow with respect to the cam driven sprocket 221 and the exhaust camshaft 240. Cannot rotate in any of the M2 directions.
- the spring S2 urges the weight 216 in the + Z direction, so that the elastic force of the spring S2 and the force acting in the direction of the thick arrow M4 are not. balance. As a result, the low-speed lock pin 217 does not completely come out of the low-speed pin introduction hole 233d.
- the force in the direction of the thick arrow M4 generated in the weight 216 is larger than the elastic force of the spring S2 in FIG. 4, and the low-speed lock pin 217 is pulled out of the low-speed pin introduction hole 233d in the direction of the arrow M6. Power also increases.
- intake camshaft 230 can rotate in the direction of arrow M2.
- a reaction force from an intake rocker arm described later is applied to the intake camshaft 230.
- a force is generated to rotate the intake camshaft 230 in the direction of arrow M2. Details will be described later.
- intake camshaft 230 rotates in the direction of arrow M2 with respect to cam driven sprocket portion 220.
- the position of the high-speed pin introduction hole 233c matches the position of one end of the high-speed lock pin 214. Since the force due to the centrifugal force of the weight 213 is generated in the high-speed lock pin 214 in the direction of the arrow M5, one end of the high-speed lock pin 214 is inserted into the high-speed pin introduction hole 233c.
- the fixed pin 230B inserted into the pin floating groove 233b is positioned at the high speed groove end HP.
- the intake camshaft 230 cannot rotate in either the direction of the arrow Ml or the arrow M2. Therefore, when the engine 7 is rotating at a high speed, the phase relationship between the intake cam 231 and the exhaust cam 241 is fixed in a state different from that when the engine 7 is rotating at a low speed.
- the low speed lock pin 217 is inserted into the zero low speed pin introduction hole 233d. Thereby, the intake camshaft 230 is fixed in the state shown in FIG. [0117] Although the function of the pin floating groove 233a (see FIG. 4) not shown in FIGS. 4 and 5 is not described, the function of the pin floating groove 233a is the same as that of the pin floating groove 233b.
- the protrusion 220T is indicated by a broken line.
- the protrusion 220T is provided to limit the rotation operation of the weight 216 about the rotation shaft 218. For example, when the weight 216 rotates a predetermined amount, one surface of the weight 216 comes into contact with the protrusion 220T. Accordingly, the weight 216 is largely rotated in the direction of the arrow M4, and the low speed lock pin 217 is prevented from coming out of the through hole 220c.
- the phase relationship between the intake cam 231 and the exhaust cam 241 is switched between when the engine 7 is rotating at a low speed and when the engine 7 is rotating at a high speed.
- the state of the valve timing control device 200 when the engine 7 is at a low speed (FIG. 4) is referred to as a low speed state
- the state of the valve timing control device 200 when the engine 7 is at a high speed (FIG. 5) is high. This is called a rotating state.
- FIG. 6 is a diagram for explaining switching of the valve timing control device 200 between a high rotation state and a low rotation state.
- the first rotation speed R1 and the second rotation speed R2 are realized by setting the constituent members of the valve timing control device 200.
- the elastic forces of the spring S1 and the spring S2 are set to be different from each other.
- the force acting on the high speed lock pin 214 held by the weight 213 is different from the force acting on the low speed lock pin 217 held by the weight 216.
- the (second rotation speed R2) is different from the rotation speed (first rotation speed R1) at which the low-speed lock pin 217 is extracted from the low-speed pin introduction hole 233d.
- the centrifugal force applied to the weights 213 and 216 and the biasing force of the springs SI and S2 are balanced.
- the rotational speed for example, the rotational speed between the rotational speed R3 and the rotational speed R4 shown in FIG. 6
- hunting in which the valve behavior becomes unstable is sufficiently prevented.
- cam profile changes due to hunting are prevented, and deterioration in engine performance and durability is prevented.
- FIG. 7 (a) is a detailed sectional view of the cylinder head 7S shown in FIG. FIG. 7 (a) shows the cylinder head 7S viewed from the direction of arrow P in FIG.
- FIG. 7B is a diagram for explaining the phase relationship between the intake cam 231 and the exhaust cam 241.
- the exhaust cam 241 is shown by a thick solid line in FIG. 7 (b).
- the intake cam 231 is indicated by a thin solid line and a two-dot chain line.
- the valve timing control device 200 rotates in the direction of the arrow Q2.
- the three directions orthogonal to each other are defined as the X direction, the Y direction, and the Z direction.
- the intake rocker arm 330 extending in the X direction from one side of the upper part of the valve timing control device 200, and the exhaust gas extending in the X direction on the other side of the valve timing control device 200.
- Rocker arm 340 force Cylinder head is installed in 7S.
- the intake rocker arm 330 is rotatably held by a shaft 331 at the center thereof. Further, a roller 330T provided at one end of the intake rocker arm 330 abuts on the intake force drum 231. At the other end of the intake rocker arm 330, an adjuster 332 is provided. Below the adjuster 332, the upper end of the intake valve 334 is located. The intake valve 334 is provided with a valve spring 335, and the valve spring 335 biases the intake valve 334 upward.
- the exhaust rocker arm 340 is rotatably held by a shaft 341 at the center thereof. Also, the roller 340T force exhaust force provided at one end of the exhaust rocker arm 340 Abuts against 241. On the other end of the exhaust rocker arm 340, an adjuster 342 is provided. Below the adjuster 342, the upper end of the exhaust valve 344 is located. The exhaust valve 344 is provided with a valve spring 345. The valve spring 345 urges the intake valve 344 upward!
- valve timing control device 200 rotates, the rollers 330T and 340T move up and down.
- the intake rocker arm 330 rotates about the shaft 331 and the exhaust rocker arm 340 rotates about the shaft 341.
- the adjuster 332 of the intake rocker arm 330 drives the intake valve 334 up and down
- the adjuster 342 of the exhaust rocker arm 340 drives the exhaust valve 344 up and down.
- lift the vertical movement of the intake valve 334 and the exhaust valve 344 by the intake rocker arm 330 and the exhaust rocker arm 340
- lift amount the movement distance
- FIG. 7 (b) when the valve timing control device 200 is in a low rotation state, the tip of the cam nose of the intake cam 231 is at a position T1 indicated by a solid line in FIG. 7 (b). .
- the rotational speed of the engine 7 increases to the first rotational speed R1 (Fig. 6), as shown in Figs. 4 and 5, the low-speed lock pin 217 (Figs. 4 and 5) is connected to the intake camshaft 230 ( (Fig. 4 and Fig. 5)
- the force is also pulled out and the intake camshaft 230 can rotate in the direction of the arrow Q2 with respect to the cam driven sprocket section 220 (Figs. 4 and 5).
- valve timing control device 200 the phase of the intake cam 231 with respect to the exhaust force 241 is switched between the low rotation state and the high rotation state. As a result, the lift timing of the intake valve 334 and the exhaust valve 344 changes. Details are described below.
- FIG. 8 shows an intake valve 334 and an exhaust valve by the valve timing control device 200.
- a change in lift amount of 344 is shown.
- the horizontal axis indicates the crank angle (the rotation angle of the crankshaft 23), and the vertical axis indicates the suction angle.
- the lift amount of the air valve 334 and the exhaust valve 344 is shown.
- the intake valve 334 and the exhaust valve 344 are open when the lift amount is greater than 0, and are closed when the lift amount force is ⁇ .
- crank angle is shown from one 360 ° to + 360 °.
- Crank angle is 0 °, 360
- the piston 21 When the angle is 360 °, the piston 21 is located at the top dead center TDC in the cylinder 20, and when the crank angle is 180 ° and 180 °, the piston 21 is located at the bottom dead center BDC in the cylinder 20.
- a thick line 241L in FIG. 8 indicates that an exhaust cam is generated when the valve timing control device 200 rotates.
- the change in the lift amount of the exhaust valve 344 driven by 241 is shown. According to the thick line 241L, the lift amount of the exhaust valve 344 increases from about 240 ° to about 120 °, and the crank angle decreases from about 120 ° to about 30 °.
- a solid line TL1 in FIG. 8 shows a change in the lift amount of the intake valve 334 driven by the intake cam 231 of the valve timing control device 200 in the low rotation state.
- the lift amount of the intake valve 334 increases when the crank angle increases by about 40 ° to about 170 ° and the crank angle decreases by about 4 ° from about 170 ° force to about 300 °! / ⁇
- the amount of overlap between the period during which the intake valve 334 is open and the period during which the exhaust valve 344 is open is small.
- the amount of overlap is 0.
- a two-dot chain line TL2 in FIG. 8 shows a change in the lift amount of the intake valve 334 driven by the intake cam 231 of the valve timing control device 200 in the high rotation state.
- the lift amount of the intake valve 334 increases from about 30 ° to about 100 °, and decreases from about 100 ° to about 230 °.
- the phase of the intake cam 231 changes with respect to the exhaust cam 241 between the case where the valve timing control device 200 is in the low rotation state and the case where the valve timing control device 200 is in the high rotation state.
- the exhaust valve 344 is open and the intake valve 334 is open.
- the amount of burlap changes.
- valve timing control device 200 When the valve timing control device 200 is in a low rotation state, the intake valve 334 is opened and the exhaust valve 344 is opened and the overlap is reduced. Therefore, harmful substances in the exhaust gas are reduced and fuel efficiency is improved. In addition, when the valve timing control device 200 is in a high rotation state, the overlap between the period during which the intake valve 334 is open and the period during which the air valve 344 is open increases, so high output is efficiently achieved. Obtainable.
- FIG. 9 to 11 are sectional views showing in detail the inside of the cylinder head 7S of FIG.
- FIG. 10 shows the valve timing control device 200 and the cam sensor 250 in a low rotation state.
- FIG. 11 shows the valve timing control device 200 and the cam sensor 250 in a high rotation state.
- the directions indicated by arrows ⁇ and Z are defined as the Y direction and the Z direction.
- the direction in which the arrow points is the + direction, and the opposite direction is the one direction.
- the thick dashed line in the figure indicates the axis J of the valve timing control device 200.
- the protrusion 219a is located in the + Z direction of the axis J.
- one end surface of the bearing B1 is in contact with the inner contact surface BH1 of the cylinder head 7S.
- One end surface of the bearing B2 is in contact with the internal contact surface BH2 of the cylinder head 7S.
- a side cover SC is attached to the cylinder head 7S so as to cover the cam driven sprocket portion 220 side of the nozzle timing control device 200.
- a force sensor 250 is fixed to the side cover SC.
- the cam sensor 250 for example, a magnetic pickup sensor is used.
- a detection unit 250a is provided at the center of the front end surface of the cam sensor 250.
- the distance D1 between the detection unit 250a and the shaft center J of the valve timing control device 200 is equal to the distance D2 between the projection 219a of the valve timing control device 200 and the shaft center J, and the detection unit 250a
- the distance E1 between the valve timing control device 200 and the cam driven sprocket 221 of the valve timing control device 200 is slightly smaller than the distance E2 between the tip of the protrusion 219a of the valve timing control device 200 and the cam drib ness pocket 221 (for example, about 3 mm). ) It is arranged to be larger.
- the protrusion 219a passes through a detectable position that is separated from the detection unit 250a of the cam sensor 250 by a slight distance.
- FIG. 10 and FIG. 11 show a state where the weight 213 exists at a position facing the cam sensor 250.
- the valve timing control device 200 is in a high rotation state.
- the weight 213 rotates in the direction of the arrow M3 due to the centrifugal force associated with the rotation.
- the protrusion 213 a provided on the weight 213 is parallel to the axis J of the valve timing control device 200.
- the distance between the protrusion 213a and the axis J of the valve timing control device 200 is the protrusion of FIG. It is equal to the distance D2 between 21 9a and the axis J of the valve timing control device 200. Further, in this state, the distance between the tip end surface of the projection 213a and the cam driven sprocket 222 of the valve timing control device 200 is equal to the distance E2 between the tip end of the projection 219a and the cam driven sprocket 221 in FIG. equal.
- the protrusion 213a of the weight 213 passes through the detectable position of the cam sensor 250 every time the valve timing control device 200 makes one rotation, like the protrusion 219a.
- valve timing control device 200 when the valve timing control device 200 is in the high rotation state, both when the protrusion 219a passes the detectable position of the cam sensor 250 and when the protrusion 213a passes the detectable position. , A pulse is generated in the cam signal CA.
- the length of the protrusion 213a is formed to be about three times larger than the length of the protrusion 219a.
- the pulse width of the pulse generated by the protrusion 213a is different from the pulse width of the pulse generated by the protrusion 219a. Therefore, it is possible to distinguish between the pulse generated by the protrusion 213a and the pulse generated by the protrusion 219a.
- the length of the protrusion 213a is formed larger than the length of the protrusion 219a.
- the length of the protrusion 219a is not limited to this, and the length of the protrusion 213a is not limited thereto. It may be formed larger than this.
- crank signal CR the crank signal
- the crankshaft 23 is provided with a plurality of protrusions, and the protrusions pass through the detectable position of the crank sensor 260 as the crankshaft 23 rotates.
- a plurality of pulses are generated in the crank signal CR given from the crankshaft 23 to the ECU 500.
- the outer peripheral surface of the crankshaft 23 is equally spaced every 30 °. Is provided with a protrusion. As a result, 12 pulses are generated in the crank signal CR during one rotation of the crankshaft 23.
- FIGS. 12 and 13 are timing charts for explaining an example of the processing of the ECU 500 performed based on the cam signal CA and the crank signal CR.
- FIG. 12 shows the processing of the ECU 500 when the valve timing control device 200 is in a low rotation state
- FIG. 13 shows the processing of the ECU 500 when the valve timing control device 200 is in a high rotation state. It is.
- the horizontal axis represents the crank angle. The crank angle is shown in a range from an arbitrary angle to an angle advanced by 720 ° (for one engine 7 cycle).
- the plurality of protrusions formed on the crankshaft 23 pass through the detectable position of the crank sensor 260, so that a plurality of pulses P2 are generated at equal intervals in the crank signal CR.
- a plurality of pulses P2 are generated at equal intervals in the crank signal CR.
- the ECU 500 In response to the pulses PI and P2 of the cam signal C A and the crank signal CR, the ECU 500 generates multiple interrupts.
- Cam signal interrupt D11 is generated in response to the rising edge of pulse P1 of cam signal CA, and cam signal interrupt D12 is generated in response to the falling edge of pulse P1.
- Interrupt interval TD1 between the input signal interrupt D11 and the cam signal interrupt D12 is equal to the pulse width TC1.
- crank signal interrupt D21 is generated in response to the rising edge of the pulse P2 of the crank signal CR.
- the interrupt interval between each crank signal interrupt D21 is equal to the pulse interval of the pulse P2 (cycle of the crank signal CR), etc.
- the ECU 500 sets the crank angle numbers of ', (T ⁇ -, 23'.
- the ECU 500 sets ', 0-, ⁇ ',
- the crank angle in one cycle of engine 7 is recognized in 24 stages based on the crank angle number of 23 ', for example, the crank signal interrupt that occurs first after the compression top dead center (top dead center in the compression process) D21
- the crank angle number ', 0' is set, in this case, based on the fuel injection or spark ignition control force crank angle number ', CT acquisition timing.
- ECU 500 corrects the crank angle number based on cam signal interrupt D12.
- the ECU 500 sets the crank angle number to a predetermined value (in the example shown in FIGS. 12 and 13, the crank angle number is set to “15” when the cam signal interrupt D12 is generated). This is set). In this case, even if the crank angle number is set incorrectly due to the noise described above, the crank angle number is corrected to an accurate value every cycle. As a result, it is possible to prevent a large deviation from occurring between the crank angle recognized by the ECU 500 based on the crank angle number and the actual crank angle.
- the ECU 500 sets the WT signal number.
- the WT signal number is maintained in the state of ', 0'.
- the pulse force S cam signal CA and crank signal CR may be generated due to other factors such as noise.
- the cam signal Other interrupts are generated in addition to interrupts Dl 1 to D14 and crank signal interrupt D21.
- interrupts that occur at the rising edge of a pulse are collectively referred to as rising interrupts
- interrupts that occur at the falling edge of a pulse are collectively referred to as falling interrupts.
- the rising force interrupts include cam signal interrupts Dl and D13, crank signal interrupts D21, and interrupts generated at the rise of the pulse due to other factors such as noise.
- Falling interrupts include cam signal interrupts D12 and D14 and interrupts generated at the falling edge of a pulse due to other factors such as noise.
- ECU 500 increments the WT signal number by 1 when cam signal interrupt D14 occurs. In this case, it is possible to determine whether or not the cam signal interrupt D14 is generated by determining whether or not the WT signal number is added for each cycle of the engine 7.
- the ECU 500 determines whether or not the VVT signal number has increased from the previous time.
- the timing of spark ignition by spark plug 280, the fuel injection amount from injector 290, and the fuel injection timing are controlled based on these pieces of information.
- the control operation of the ignition plug 280 and the injector 290 by the ECU 500 will be described with reference to FIGS.
- FIG. 14 is a flowchart showing valve timing control processing by the ECU 500.
- ECU 500 initializes the WT signal number (Fig. 13) and sets the initial value (step Sl). Next, ECU 500 acquires the operating state of engine 7 including cam signal CA, crank signal CR, and throttle opening degree TR (step S2).
- step S3 the ECU 500 performs a valve timing determination process based on the operating state acquired in step S2 (step S3).
- the valve timing control device 200 it is determined whether the valve timing control device 200 is in a low rotation state or a high rotation state.
- step S3 the rotational speed of the engine 7 (hereinafter referred to as the engine rotational speed) is calculated based on the crank signal CR. Details of the valve timing determination processing in step S3 will be described later.
- step S3 As a result of the valve timing determination process in step S3, if the valve timing control device 200 is in a high rotation state, the ECU 500 calculates the throttle opening TR obtained in step S2 and the engine rotation speed in step S3. Based on the result, the fuel injection amount and fuel injection timing from the injector 290 (FIG. 2) and the spark ignition timing by the spark plug 280 (FIG. 2) are calculated (steps S4 and S5).
- the fuel injection amount, the fuel injection timing, and the ignition timing are calculated by map calculation using a map set in advance corresponding to the high rotation state.
- the ECU 500 determines whether or not the calculation result of the engine speed in step S3 is lower than a preset speed RL (step S6).
- the rotational speed RL is set to a value lower than the second rotational speed R2 (FIG. 6) described above.
- step S6 If it is determined in step S6 that the engine rotation speed is lower than the rotation speed RL, the reveal timing control device 200 is not functioning normally, and the warning process for the user is not performed. Done (step S7). Warning processing includes warning buzzer or warning lamp.
- step S3 As a result of the valve timing determination process in step S3, if the valve timing control device 200 is in a low rotation state, the ECU 500 calculates the throttle opening TR obtained in step S2 and the engine rotation speed in step S3. Based on the result, the fuel injection amount and fuel injection timing from the injector 290 (FIG. 2) and the spark ignition timing by the spark plug 280 (FIG. 2) are calculated (steps S4 and S8). Here, for example, the fuel injection amount, fuel injection timing and And the ignition timing is calculated.
- ECU 500 determines whether or not the engine rotation speed calculation result force in step S3 is higher than a predetermined rotation speed RH set in advance (step S9).
- the rotational speed RH is set to a value higher than the first rotational speed R1 (FIG. 6) described above.
- step S6 it is determined whether or not the valve timing control device 200 is functioning normally.
- step S9 If it is determined in step S9 that the engine rotational speed is higher than the rotational speed RH, the noreb timing control device 200 is not functioning properly, and the warning process for the user is not performed. Is performed (step S7).
- step S6 or step S9 if the valve timing control device 200 functions normally, the fuel injection amount and fuel that are set in advance so as to reduce the load on the engine 7 are reduced. You may switch to the injection timing and the spark ignition timing.
- step S6 If it is determined in step S6 that the engine rotational speed is equal to or higher than the rotational speed RL, or if it is determined in step S9 that the engine rotational speed is equal to or lower than the rotational speed RH, the valve It is determined that the timing control device 200 is functioning normally.
- ECU 500 instructs fuel injection to injector 290 from fuel injection signal FI based on the calculation result of fuel injection amount and fuel injection timing in step S5 or step S8, and spark ignition in step S5 or step S8. Based on the timing calculation result, ignition is commanded to the spark plug 280 by the spark ignition signal SI (step S10).
- the injector 290 can perform fuel injection with an appropriate amount and timing based on the valve timing of the intake valve 334 and the exhaust valve 344 (FIG. 8). Further, the spark plug 280 can perform spark ignition at an appropriate timing based on the valve timings of the intake valve 334 and the exhaust valve 344. Thereafter, the ECU 500 repeats the processes of steps S2 to S10.
- FIG. 15 is a flowchart for explaining the details of the valve timing determination process (step S3) of FIG.
- ECU 500 determines whether or not an interrupt based on cam signal CA has occurred (step S11).
- step S11 When an interrupt based on the cam signal CA occurs, the ECU 500 performs cam signal processing described later (step S12). After that, the ECU 500 proceeds to the process of step S2 or step S4 in FIG.
- the ECU 500 receives the crank signal.
- step S13 It is determined whether or not an interrupt based on CR has occurred.
- step S13 if an interrupt based on the crank signal CR occurs, ECU5
- step S14 the ECU 500 performs the crank signal processing described later. Thereafter, the ECU 500 returns to the process of step S2 in FIG.
- FIG. 16 is a flowchart for explaining details of the cam signal processing (step S12) of FIG.
- ECU 500 determines whether or not the interrupt generated in step S11 of Fig. 15 is a falling interrupt (step S31).
- step S11 of Fig. 15 If the interrupt generated in step S11 of Fig. 15 is not a falling interrupt, that is, if it is a rising interrupt, ECU 500 measures the time of occurrence of the rising interrupt (step S32). Thereafter, the ECU 500 returns to the process of step S2 in FIG.
- step S31 if the interrupt generated in step S11 of Fig. 15 is a falling interrupt, ECU 500 measures the time of occurrence of the falling interrupt (step S31).
- ECU 500 calculates an interrupt interval between the rising interrupt measured in step S32 and the falling interrupt measured in step S33 (step S34).
- ECU 500 determines whether or not the interrupt interval measured in step S34 is greater than a predetermined value A1 set in advance (step S35).
- the predetermined value A1 is set to a value that is greater than or equal to the interrupt interval TD1 of the cam signal interrupts Dll and D12 and smaller than the interrupt interval TD2 of the cam signal interrupts D13 and D14.
- the ECU 500 determines whether or not the interrupt interval is smaller than a predetermined value A2 set in advance (step S36).
- the predetermined value A2 is set to a value smaller than the interrupt interval TD1 of the cam signal interrupts Dl l and D12.
- the ECU 500 processes the rising interrupt generated in step S11 as noise (step S37). That is, ECU 500 returns to the process of step S2 without performing any process.
- step S36 If it is determined in step S36 that the interrupt interval is equal to or greater than the predetermined value A2, it is determined that the interrupt generated in step S11 is the cam signal interrupt D12. Thereby, the ECU 500 corrects the crank angle number by setting the crank angle number to a predetermined value (step S38).
- step S39 ECU 500 determines whether or not the WT signal number is the same as the previous time.
- step S40 the ECU 500 determines that the valve timing control device 200 is in a low rotation state (step S40), and clears the WT signal number to the initial value 0 (step S41). Thereafter, the ECU 500 proceeds to the process of step S4 in FIG.
- step S42 determines that the valve timing control device 200 is in a high rotation state (step S42), and increments the WT signal number by 1 (step S43). ). Thereafter, the ECU 500 proceeds to the process of step S4 in FIG.
- FIG. 17 is a flowchart for explaining details of the crank signal processing (step S14) of FIG.
- ECU 500 increments the current crank angle number by 1 (step S51).
- step S52 determines whether or not the crank angle number has exceeded 23.
- step S53 clears the crank angle number to 0.
- ECU 500 calculates an interrupt interval between the interrupt that occurred in step S13 and the interrupt that occurred last time (step S54). ECU 500 calculates the engine rotation speed based on the calculated interrupt interval (step S55). Thereafter, the ECU 500 returns to the process of step S2 in FIG.
- the phase correlation between the intake cam 231 and the exhaust cam 241 of the valve timing control device 200 is the phase relationship at the time of high rotation. It is accurately determined by the force 3 ⁇ 4 CU500 whether the force is in the phase relationship at the time of low rotation. Thereby, ECU 500 can accurately determine the valve timings of intake valve 334 and exhaust valve 344.
- ECU 500 can optimally control the fuel injection amount, the fuel injection timing, and the spark ignition timing based on the valve timings of intake valve 334 and exhaust valve 344.
- crank angle number is always corrected to an accurate value by detecting the protrusion 219a by the cam sensor 250.
- ECU 500 can accurately control the fuel injection amount, the fuel injection timing, and the spark ignition timing based on the crank angle number.
- valve timing control device 200 and the cam sensor 250 are examples of variable valve operating devices
- the cam driven sprocket 221 is an example of a rotating member
- the intake camshaft 230 is an example of a cam member.
- the intake camshaft 230 when the valve timing control device 200 is in the low rotation state is an example of the first state
- the intake camshaft when the normalizing control device 200 is in the high rotation state 230 state is second
- the protrusion 213a is an example of a first detected part
- the weights 213 and 216 are examples of a movable member
- the cam sensor 250 is an example of a detector
- the protrusion 219a is a second part. This is an example of the detected part.
- engine 7 and ECU 500 are examples of an engine system
- intake valve 334 and exhaust valve 344 are examples of valves
- ECU 500 is an example of a control unit
- cam signal CA is an output signal of a detector. This is an example of the detection period
- the detection width TCI and TC2 are examples of the detection period.
- the motorcycle 100 is an example of a vehicle
- the rear wheel 11 is an example of a driving member.
- cam sensor 250 is arranged in a direction parallel to the axis J of the valve timing control device 200 so as to face one surface of the cam driven sprocket 221 (FIG. 9 to FIG. 9). (Fig. 11) Cam sensor 250 may be placed in other positions!
- FIG. 18 is a diagram showing another arrangement example of the cam sensor 250. As shown in FIG. 18 (a) is a cross-sectional view showing the arrangement of the valve timing control device 200 and the cam sensor 250. FIG. 18 (b) shows the cam sensor 250 and the valve timing control device 200 of FIG. It is a side view seen from the direction. FIG. 18 shows a valve timing control device 200 in a high rotation state.
- the weight 213 of the valve timing control device 200 is provided with a protrusion 213e.
- the protrusion 213e is parallel to one surface of the cam driven sprocket 221.
- the protruding portion 211D of the support member 211 is formed with a protruding portion 21la.
- the protrusion 21 la is parallel to one surface of the cam driven sprocket 221. [0238] Note that, in the circumferential direction around the axis J, the protrusion 213e has a length approximately three times that of the protrusion 21la.
- ECU 500 Based on these pulses generated in cam signal CA, ECU 500 performs the control operation shown in FIGS.
- the cam sensor 250 can be arranged at an arbitrary position. As a result, the design freedom of the cylinder head 7S of the engine 7 is increased.
- any portion such as the weights 213, 216 or the screw 219 may be directly detected by the cam sensor 250 without providing the protrusions 213a, 219a, 213e, 21la.
- the arrangement or shape of the weights 213 and 216 or the screws 219 and the like are appropriately set so that the cam sensor 250 can detect them.
- valve timing control device 200 that switches the valve timing of the intake valve 334 and the exhaust valve 344 in accordance with the change in centrifugal force accompanying the rotation of the engine 7 as a variable valve operating device 200.
- the present invention is not limited to this, and can also be applied to a variable valve gear that switches the lift amount of the intake valve 334 or the exhaust valve 344 by a change in centrifugal force accompanying the rotation of the engine 7. is there.
- the valve timing control device 200 in which the weights 213 and 216 are rotated as a variable valve operating device by the change in centrifugal force accompanying the rotation of the engine 7 has been described.
- the present invention is not limited to this, and can also be applied to a variable valve apparatus in which a weight moves in a linear direction due to a change in centrifugal force accompanying the rotation of the engine 7.
- the force is set so that the width of the protrusion 213a of the weight 213 is different from the width of the protrusion 219a of the screw 219.
- the width of the protrusion 213a of the weight 213 and the screw The width of the two 19 protrusions 219a may be set equal.
- ECU 500 determines whether the number of pulses generated in cam signal CA is two forces that are one in one cycle of engine 7. If the number of pulses generated in the force signal CA in one cycle of the engine 7 is one, the valve timing control device 200 is determined to be in a low rotation state, and the number of pulses generated in one cycle of the engine 7 is determined. When the number is two, it is determined that the noble timing controller 200 is in a high rotation state.
- the ECU 500 after determining whether the valve timing control device 200 is in the low rotation state or the high rotation state, the ECU 500 causes the throttle valve sensor 270 to Based on the detected throttle opening TR and the engine speed, the fuel injection amount, fuel injection timing, and spark ignition timing are calculated (Fig. 14). It may be calculated based on conditions. For example, the ECU 500 determines whether the fuel injection amount, the fuel injection timing, and the fuel injection amount are based on one or more conditions of throttle opening TR, engine speed, oil temperature, water temperature, engine temperature, or fuel type. The spark ignition timing may be calculated.
- the present invention can be used for various vehicles and ships equipped with engines such as motorcycles and four-wheeled automobiles.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06833785A EP1961926B1 (en) | 2005-12-13 | 2006-11-30 | Variable valve gear, and engine system and vehicle that have the same |
BRPI0619812-0A BRPI0619812A2 (pt) | 2005-12-13 | 2006-11-30 | mecanismo de válvula variável, e sistema de motor e veìculo que tem o mesmo |
US12/094,008 US7684922B2 (en) | 2005-12-13 | 2006-11-30 | Variable valve system, and engine system and vehicle including the same |
CN200680046778XA CN101331296B (zh) | 2005-12-13 | 2006-11-30 | 可变气门传动装置、具备它的发动机系统以及车辆 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005359363A JP4948831B2 (ja) | 2005-12-13 | 2005-12-13 | 可変動弁装置ならびにそれを備えるエンジンシステムおよび乗り物 |
JP2005-359363 | 2005-12-13 |
Publications (1)
Publication Number | Publication Date |
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WO2007069467A1 true WO2007069467A1 (ja) | 2007-06-21 |
Family
ID=38162778
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/323982 WO2007069467A1 (ja) | 2005-12-13 | 2006-11-30 | 可変動弁装置ならびにそれを備えるエンジンシステムおよび乗り物 |
Country Status (9)
Country | Link |
---|---|
US (1) | US7684922B2 (ja) |
EP (1) | EP1961926B1 (ja) |
JP (1) | JP4948831B2 (ja) |
CN (1) | CN101331296B (ja) |
AT (1) | ATE523664T1 (ja) |
BR (1) | BRPI0619812A2 (ja) |
ES (1) | ES2368945T3 (ja) |
MY (1) | MY143673A (ja) |
WO (1) | WO2007069467A1 (ja) |
Cited By (1)
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WO2017146002A1 (ja) * | 2016-02-26 | 2017-08-31 | 武蔵精密工業株式会社 | 内燃機関用動弁装置におけるカム位相可変機構 |
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JP2010096083A (ja) * | 2008-10-16 | 2010-04-30 | Fujitsu Ten Ltd | 制御装置及びその制御方法 |
US8942908B2 (en) * | 2010-04-30 | 2015-01-27 | GM Global Technology Operations LLC | Primary torque actuator control systems and methods |
DE102011003507A1 (de) | 2011-02-02 | 2012-08-02 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellen- oder Nockenwellenverstellmechanismus mit einem fliehkraftabhängig verstellbarem Einlassnocken, der über einen Mitnehmerstift bewegt wird |
DE102011003558A1 (de) | 2011-02-03 | 2012-08-09 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellen- oder Nockenverstellmechanismus mit Schlingfedern |
JP5916092B2 (ja) * | 2011-03-30 | 2016-05-11 | 本田技研工業株式会社 | 車両用火花点火4サイクルエンジン |
DE102011075158A1 (de) | 2011-05-03 | 2012-11-08 | Schaeffler Technologies AG & Co. KG | Nockenwellen- oder Nockenverstellmechanismus mit kraftschlüssig in einen Freilauf eingebundenen Schlingfedern |
DE102011080486A1 (de) | 2011-08-05 | 2013-02-07 | Schaeffler Technologies AG & Co. KG | Nockenverstellmechanismus, Verbrennungskraftmaschine und Leichtkraftrad |
JP5817845B2 (ja) * | 2012-01-12 | 2015-11-18 | トヨタ自動車株式会社 | バルブタイミング制御装置 |
JP6071568B2 (ja) * | 2013-01-16 | 2017-02-01 | 本田技研工業株式会社 | 車両用制御装置 |
DE102015201254A1 (de) * | 2015-01-26 | 2016-07-28 | Schaeffler Technologies AG & Co. KG | Fliehkraftaktuierter Dualflügelversteller |
EP3354888B1 (en) | 2015-10-13 | 2020-01-15 | Denso Corporation | Cam angle sensor fault diagnosis apparatus for straddled vehicle, engine system, and straddled vehicle |
JP6702038B2 (ja) * | 2016-07-05 | 2020-05-27 | スズキ株式会社 | 可変動弁機構、エンジン及び自動二輪車 |
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- 2006-11-30 BR BRPI0619812-0A patent/BRPI0619812A2/pt not_active Application Discontinuation
- 2006-11-30 EP EP06833785A patent/EP1961926B1/en active Active
- 2006-11-30 MY MYPI20081679A patent/MY143673A/en unknown
- 2006-11-30 AT AT06833785T patent/ATE523664T1/de not_active IP Right Cessation
- 2006-11-30 WO PCT/JP2006/323982 patent/WO2007069467A1/ja active Application Filing
- 2006-11-30 US US12/094,008 patent/US7684922B2/en not_active Expired - Fee Related
- 2006-11-30 CN CN200680046778XA patent/CN101331296B/zh active Active
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Also Published As
Publication number | Publication date |
---|---|
US7684922B2 (en) | 2010-03-23 |
ATE523664T1 (de) | 2011-09-15 |
EP1961926B1 (en) | 2011-09-07 |
ES2368945T3 (es) | 2011-11-23 |
CN101331296A (zh) | 2008-12-24 |
EP1961926A1 (en) | 2008-08-27 |
CN101331296B (zh) | 2012-01-11 |
JP4948831B2 (ja) | 2012-06-06 |
JP2007162563A (ja) | 2007-06-28 |
EP1961926A4 (en) | 2009-12-30 |
US20090240420A1 (en) | 2009-09-24 |
BRPI0619812A2 (pt) | 2011-10-18 |
MY143673A (en) | 2011-06-30 |
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