US20160169061A1 - Valve opening and closing timing control device - Google Patents

Valve opening and closing timing control device Download PDF

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Publication number
US20160169061A1
US20160169061A1 US14/910,112 US201414910112A US2016169061A1 US 20160169061 A1 US20160169061 A1 US 20160169061A1 US 201414910112 A US201414910112 A US 201414910112A US 2016169061 A1 US2016169061 A1 US 2016169061A1
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United States
Prior art keywords
phase
fluid
chamber
control
relative rotational
Prior art date
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Abandoned
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US14/910,112
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English (en)
Inventor
Takashi IWAYA
Koji Nunami
Hiroyuki Amano
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Aisin Corp
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Aisin Seiki Co Ltd
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Assigned to AISIN SEIKI KABUSHIKI KAISHA reassignment AISIN SEIKI KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IWAYA, TAKASHI, AMANO, HIROYUKI, NUNAMI, KOJI
Publication of US20160169061A1 publication Critical patent/US20160169061A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/0532—Camshafts overhead type the cams being directly in contact with the driven valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/3443—Solenoid driven oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34463—Locking position intermediate between most retarded and most advanced positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34466—Locking means between driving and driven members with multiple locking devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34473—Lock movement perpendicular to camshaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2800/00—Methods of operation using a variable valve timing mechanism

Definitions

  • the present invention relates to a valve opening and closing timing control device that controls a relative rotational phase of a driven-side rotary member rotating integrally with a camshaft of an internal combustion engine relative to a driving-side rotary member rotating synchronously with a crankshaft of the internal combustion engine.
  • valve opening and closing timing control device controlling the opening and closing timing of one of or both of an intake valve and an exhaust valve has been used in order to enhance a fuel consumption of an internal combustion engine (hereinafter referred to as an engine).
  • This kind of valve opening and closing timing control device controls the opening and closing timing by changing a relative rotational phase between a driving-side rotary member rotating synchronously with a crankshaft and a driven-side rotary member rotating integrally with a camshaft.
  • an optimum opening and closing timing of each of the intake valve and the exhaust valve differs in accordance with an operation condition of the engine, for example, when the engine starts and when a vehicle runs.
  • the optimum opening and closing timing of each of the intake valve and the exhaust valve for starting the engine is realized by locking the relative rotational phase of the driven-side rotary member relative to the rotation of the driving-side rotary member (hereinafter referred to as a relative rotational phase) at a predetermined phase that is provided between a most retard phase and a most advance phase.
  • variable valve timing control device of an internal combustion engine including a feature that locks a rotational phase of a camshaft relative to a crankshaft of the internal combustion engine at an intermediate locked phase being positioned at a substantially middle of an adjustable range of the rotational phase.
  • the variable timing control device of the internal combustion engine includes a lock control portion that controls an oil-pressure control device in order to lock the rotational phase of the camshaft at the intermediate locked phase by a lock pin when a lock request is generated.
  • the lock control portion controls the oil-pressure control device so that the rotational phase of the camshaft passes through the intermediate locked phase while biasing the lock pin in a lock direction when the lock request is generated.
  • a control amount of the oil-pressure control device is changed further by a predetermined amount in a moving direction of the rotational phase of the camshaft. In this case, it is determined that the locking is completed in a case where the rotational phase of the camshaft does not move.
  • Patent document 1 JP2010-138699A
  • Patent document 1 controls the rotational phase of the camshaft to pass through the intermediate locked phase when the lock request is generated.
  • the control amount of the oil-pressure control device is further changed to the predetermined amount in the moving direction of the rotational phase of the camshaft when the rotational phase of the camshaft does not move at vicinity of the intermediate locked phase.
  • the rotational phase of the camshaft may pass through the intermediate locked phase, and in such a case, it takes some time to complete the locking.
  • the object of the present invention is, in a view of an aforementioned problem, to provide a valve opening and closing timing control device that can promptly move a relative rotational phase of a driven-side rotary member relative to a driving-side rotary member to an intermediate locked phase.
  • a valve opening and closing timing control device of this invention for achieving the above-mentioned purpose includes a driving-side rotary member rotating synchronously with a crankshaft of an internal combustion engine, a driven-side rotary member rotating integrally with a camshaft of the internal combustion engine, the driven-side rotary member being relatively rotatable with the driving-side rotary member, a fluid pressure chamber being formed with the driving-side rotary member and the driven-side rotary member, a vane being positioned within the fluid pressure chamber, the vane dividing the fluid pressure chamber into a retard chamber and an advance chamber that each allows an inflow and an outflow of a fluid, the vane selectively moving a relative rotational phase of the driven-side rotary member relative to the driving-side rotary member between a retarded direction and an advance direction, the retarded direction where a volume within the retard chamber increases by the inflow of the fluid, the advance direction where a volume within the advance chamber increases by the inflow of the fluid, an intermediate lock mechanism being provided at one of
  • the relative rotational phase of the driven-side rotary member relative to the driving-side rotary member can be in a lock state securely while promptly moving to the reference phase without jumping over the intermediate locked phase.
  • the relative rotational phase can promptly move to the intermediate locked phase.
  • the phase control portion performs one of the control of the supply of the fluid to the retard chamber and the discharge of the fluid from the advance chamber, and the control of the discharge of the fluid from the retard chamber and the supply of the fluid to the advance chamber, in order for the travelling speed of the relative rotational phase from the present phase to the intermediate locked phase to be reduced by a predetermined amount of change.
  • the phase control portion performs one of the control of the supply of the fluid to the retard chamber and the discharge of the fluid from the advance chamber, and the control of the discharge of the fluid from the retard chamber and the supply of the fluid to the advance chamber, based on a map defined by a relationship between the travelling speed of the relative rotational phase from the present phase to the intermediate locked phase and a quantity of state showing a state of the fluid flowed to the retard chamber and to the advance chamber.
  • the easiness of the flow of the fluid in a case where the fluid passes through the flow passage changes in accordance with, for example, the pressure level and the temperature level of the fluid.
  • a map defining the quantity of state and the travelling speed is memorized while the pressure level and the temperature level of the fluid serves as the amount of the state showing the state of the fluid.
  • valve opening and closing timing control device further includes a determination portion determining whether the lock member reaches a determination phase, the determination phase being provided between the intermediate locked phase and the reference phase, and the determination portion determines whether the lock member reaches the determination phase when the phase control portion controls the lock member to move to the determination phase after performing one of the control of the supply of the fluid to the retard chamber and the discharge of the fluid from the advance chamber, and the control of the discharge of the fluid from the retard chamber and the supply of the fluid to the advance chamber.
  • the determination portion securely determines whether the lock member reaches the intermediate locked phase.
  • the relative rotational phase moves from the present phase to the reference phase based on a first travelling speed
  • the relative rotational phase moves from the reference phase to the intermediate locked phase based on a second travelling speed that is slower than the first travelling speed
  • the relative rotational phase because the travelling speed of the relative rotational phase is reduced in a case where the relative rotational phase moves from the reference phase to the intermediate locked phase after moving from the present phase to the reference phase, the relative rotational phase can be prevented from passing through the intermediate locked phase. Accordingly, the relative rotational phase can move promptly and securely from the present phase to the intermediate locked phase without passing through the intermediate locked phase.
  • FIG. 1 is a cross sectional view of a valve opening and closing timing control device.
  • FIG. 2 is a cross sectional view illustrating a lock state taken along line II-II in FIG. 1 .
  • FIG. 3 is a cross sectional view illustrating an unlock state taken along line II-II in FIG. 1 .
  • FIG. 4 is a cross sectional view illustrating a most retard phase state taken along line II-II in FIG. 1 .
  • FIG. 5 is a view schematically illustrating a reference phase in a case where a relative rotational phase moves from a present position to an intermediate locked phase along an advance direction.
  • FIG. 6 is a view schematically illustrating a reference phase in a case where the relative rotational phase moves from the present position to the intermediate locked phase along a retarded direction.
  • FIG. 7 is a view illustrating an example of a travelling speed in a case where an inner rotor relative to an outer rotor relatively rotates from the present phase to the intermediate locked phase.
  • FIG. 8 is a view illustrating another example of a travelling speed in a case where the inner rotor relative to an outer rotor relatively rotates from the present phase to the intermediate locked phase.
  • FIG. 1 is a side cross sectional view illustrating a whole configuration of the valve opening and closing timing control device 1 according to the present embodiment.
  • FIGS. 2 to 4 are cross sectional views illustrating respective states taken along line II-II in FIG. 1 .
  • the valve opening and closing timing control device 1 is mounted on a vehicle including an engine as an internal combustion engine as a drive source and on a hybrid vehicle including a drive source including the engine and an electric motor.
  • the valve opening and closing timing control device 1 includes an outer rotor 12 serving as a driving-side rotary member and an inner rotor 2 serving as a driven-side rotary member.
  • the outer rotor 12 rotates synchronously relative to a crankshaft 110 of an internal combustion engine E.
  • the inner rotor 12 is relatively rotatable and is coaxially positioned relative to the outer rotor 12 while rotating integrally with a camshaft 101 of the internal combustion engine E.
  • the valve opening and closing timing control device 1 controls an opening and closing timing of an intake valve 115 by setting a relative rotational phase (a relative rotational angle) of the outer rotor 12 and the inner rotor 2 about an axis X.
  • the inner rotor 2 is mounted integrally on a distal end portion of the camshaft 101 . Specifically, the inner rotor 2 is fitted in and fixed to the distal end portion of the camshaft 10 with a fastening bolt 20 .
  • the valve opening and closing timing control device 1 includes a front plate 11 , the outer rotor 12 and a rear plate 13 .
  • the front plate 11 is provided opposite to a side where the camshaft 101 is connected.
  • the rear plate 13 is integrally formed with a timing sprocket 15 and is provided at the side where the camshaft 101 is connected.
  • the inner rotor 2 is covered by the outer rotor 2 .
  • the outer rotor 12 is sandwiched by the front plate 11 and the rear plate 13 from opposing ends in an axial direction. In this state, the front plate 11 , the outer rotor 12 and the rear plate 13 are fitted in and fixed to one another with the aforementioned fastening bolt 20 .
  • crankshaft 110 When the crankshaft 110 is rotationally driven, a rotational driving force is transmitted to the timing sprocket 15 via a power transmission member 102 .
  • the outer rotor 12 is rotationally driven in a rotational direction S shown in FIG. 2 .
  • the inner rotor 2 is rotationally driven in the rotational direction S in accordance with the rotational drive of the outer rotor 12 to rotate the camshaft 101 .
  • a cam 116 being provided at the camshaft 101 opens a valve by pressing down the intake valve 115 of the internal combustion engine E.
  • the outer rotor 12 is formed with plural protrusions 14 protruding inwardly in a radial direction so as to be separated from one another along the rotational direction S.
  • a fluid pressure chamber 4 is formed by the outer rotor 12 and the inner rotor 2 .
  • the protrusion 4 serves as a shoe relative to an outer peripheral surface 2 a of the inner rotor 2 . According to the present embodiment, an example in which four of the fluid pressure chambers 4 are formed is explained, however, is not intended to limit the scope of the invention.
  • a portion of the outer peripheral surface 2 a is formed with a vane groove 21 of which a depth direction corresponds to the radial direction of the inner rotor 2 .
  • a portion of a vane 22 is inserted into the vane groove 21 and is standingly positioned outwardly in the radial direction. Thus, the vane 22 is positioned within the fluid pressure chamber 4 .
  • the fluid pressure chamber 4 is divided into an advance chamber 41 and a retard chamber 42 with the vane 22 .
  • the advance chamber 41 and the retard chamber 42 allow an inflow and an outflow of an oil along the rotational direction S.
  • the relative rotational phase of the inner rotor 2 relative to the outer rotor 12 moves (is displaced) in the retarded direction of the relative rotational direction.
  • the retarded direction corresponds to a direction in which a volume of the retard chamber 42 increases by the inflow of the oil, the direction that is shown with a reference numeral S 2 in FIG. 2 .
  • the relative rotational phase moves (is displaced) in the advance direction of the relative rotational direction.
  • the advance direction corresponds to a direction in which the vane 22 relatively rotationally moves relative to the outer rotor 12 and corresponds to a direction in which a volume of the advance chamber 41 increases by the inflow of the oil, the direction shown with a reference numeral S 1 in FIG. 2 .
  • a spring 23 is positioned between the vane groove 21 and the vane 22 , and biases the vane 22 outwardly in the radial direction. Accordingly, the oil is prevented from leaking at a position between the advance chamber 41 and the retard chamber 42 .
  • the vane 22 selectively moves the relative rotational phase between the retarded direction and the advance direction.
  • an advance passage 43 is formed at the inner rotor 2 and at the camshaft 101 so as to be communicated with each of the advance chambers 41 .
  • a retard passage 44 is formed at the inner rotor 2 and at the camshaft 101 so as to be communicated with each of the retard chambers 42 .
  • the advance passage 43 and the retard passage 44 are connected to respective predetermined ports of a first control valve 174 .
  • the oil is maintained to be supplied, to be discharged, or to be supplied and discharged relative to the advance chamber 41 and the retard chamber 42 , and the fluid pressure of the oil is applied to the vane 22 .
  • the relative rotational phase is displaced either in the advance direction S 1 or in the retarded direction S 2 .
  • the relative rotational phase is maintained at a desired phase.
  • a torsion spring 3 is provided to be extended from the inner rotor 2 to the front plate 11 .
  • the torsion spring 3 biases the inner rotor 2 to a retard side in order to resist an averaged displacing force in the retarded direction S 2 based on a torque variation of the camshaft 101 .
  • the relative rotational phase can be displaced in the advance direction S 1 smoothly and promptly.
  • the inner rotor 2 is smoothly and relatively rotationally movable relative to the outer rotor 12 about the axis X within a predetermined range.
  • the predetermined range in which the outer rotor 12 and the inner rotor 2 are relatively rotationally movable that is, a phase difference between a most advance phase and a most retard phase, corresponds to a displaceable range of the vane 22 within the fluid pressure chamber 4 .
  • the most retard phase corresponds to a phase where the volume of the retard chamber 42 comes to be at a maximum.
  • the most advance phase corresponds to a phase where the volume of the advance chamber 41 comes to be at a maximum.
  • an intermediate lock mechanism 6 holds the outer rotor 12 and the inner rotor 2 at respective predetermined relative positions. Accordingly, the relative rotational phase of the outer rotor 12 and the inner rotor 2 is locked at the intermediate locked phase that is positioned between the most retard phase and the most advance phase. As such, because the relative rotational phase is held at the intermediate locked phase, the rotational phase of the camshaft 101 relative to the rotational phase of the crankshaft 110 is appropriately maintained. Thus, the stable rotation of the internal combustion engine E is realized.
  • the intermediate locked phase corresponds to a phase in which the respective opening timings of the intake valve 115 and of the exhaust valve are partially duplicated (overlapped) with each other, or corresponds to a phase in which the closing timing of the exhaust valve and the opening timing of the intake valve 115 are substantially the same (zero lap).
  • the phase is such that the respective opening timings of the intake valve 115 and of the exhaust valve are partially duplicated with each other, the carbon hydride (HC) is reduced at the start-up of the internal combustion engine E. Accordingly, the low-emission internal combustion engine E is available.
  • the combustion engine E that has a great start-up performance at a cold area and that has a great idling stability is available.
  • the intermediate lock mechanism 6 includes an intermediate lock passage 61 , two of intermediate lock grooves 62 , a housing portion 63 , two plate-shaped intermediate lock members 64 , and a spring 65 .
  • the intermediate lock groove 62 corresponds to a recess of the present invention
  • the intermediate lock member 64 corresponds to a lock member of the present invention.
  • the intermediate lock passage 61 is formed at the inner rotor 2 and at the camshaft 101 , and connects the intermediate lock groove 62 to a second control valve 175 . Because the second control valve 175 is controlled, the supply/discharge of the oil to/from the intermediate lock groove 62 can be switched independently.
  • the intermediate lock groove 62 is formed to be extended on the outer peripheral surface 2 a of the inner rotor 2 in a circumferential direction and has a predetermined width in the relative rotational direction.
  • the housing portion 63 is formed at two positions of the outer rotor 12 . Two of the intermediate lock members 64 are positioned at the respective housing portions 63 , and are able to be in and out of the housing portions 63 in the radial direction.
  • the intermediate lock member 64 is formed at the outer rotor 12 and is movable relative to the inner rotor 2 .
  • the spring 65 is positioned at the housing portion 63 and biases each of the intermediate lock members 64 inwardly in the radial direction, that is, biases each of the intermediate lock members 64 to a side where the intermediate lock groove 62 is provided.
  • each of the two of the intermediate lock members 64 protrudes to be fitted into each of the intermediate lock grooves 62 . Accordingly, each of the intermediate lock members 64 is retained simultaneously at a predetermined position of each of the intermediate lock grooves 62 . As a result, as shown in FIG. 2 , the relative rotational phase of the inner rotor 2 relative to the outer rotor 12 is locked at the aforementioned intermediate locked phase. In a case where the second control valve 175 is controlled to supply the oil to the intermediate lock groove 62 , as shown in FIG. 3 , both of the intermediate lock members 64 are retracted from the respective intermediate lock grooves 62 to the respective housing portions 63 .
  • the inner rotor 2 comes to be relatively rotationally movable.
  • a state where the intermediate lock mechanism 6 locks the relative rotational phase at the intermediate phase is referred to as a lock state.
  • a state where the lock state is released is referred to as an unlock state.
  • the intermediate lock mechanism 6 is switchable between the lock state and the unlock state.
  • a pin shape can be appropriately adapted as the shape of the intermediate lock member 64 other than the plate shape that is shown in the present embodiment.
  • each of the two of the intermediate lock grooves 62 has a ratchet structure so that the groove depth comes to be gradually deeper along the retarded direction S 2 of the inner rotor 2 . Accordingly, the intermediate lock member 64 is gradually restricted and comes to be easily entered into the intermediate lock groove 62 . Meanwhile, the intermediate lock passage 61 is divided into two on the way of the inner rotor 2 and is connected to each of the intermediate lock grooves 62 .
  • the present valve opening and closing timing control device 1 is provided with a most retarded angle lock mechanism 7 in addition to the aforementioned intermediate lock mechanism 6 .
  • the most retarded angle lock mechanism 7 locks the relative rotational phase to the most retard phase by holding the outer rotor 12 and the inner rotor 2 at the predetermined relative positions at the time of low-speed rotation, for example, at the time of an idling operation. That is, irrespective of the displacing force in the retarded direction S 2 and in the advance direction S 1 based on the torque variation of the camshaft 101 , because the inner rotor 2 does not relatively rotationally move, the stable idling operation state can be realized.
  • the most retard phase corresponds to a phase where the valve is opened at a later timing than the closing timing of the exhaust valve, the phase in which the start-up performance of the internal combustion engine E is secured while preventing a pre-ignition at a warm area of the internal combustion engine E.
  • the most retarded angle lock mechanism 7 is provided with a most retarded angle lock passage 71 , a most retarded angle lock groove 72 , a housing portion 73 , a plate-shaped most retarded angle lock member 74 , and a spring 75 .
  • the most retarded angle lock passage 71 is used in parallel with one of the plural advance passages 43 .
  • the most retarded angle lock member 74 serves as a same member as the intermediate lock member 64 being provided at one of the two of the intermediate lock members 64 , the one being positioned in the advance direction S 1 .
  • the housing portion 73 serves as a same member as the housing portion 63 being provided at one of the two of the housing portions 63 , the one being positioned in the advance direction S 1 .
  • the spring 75 serves as a same member as the spring 65 being positioned at the housing portion 63 .
  • the most retarded angle lock member 74 protrudes to the most retarded angle lock groove 72 .
  • the relative rotational movement of the inner rotor 2 relative to the outer rotor 12 is locked and the relative rotational phase is held at the most retard phase.
  • the first control valve 174 is controlled to try to displace the relative rotational phase to the advance side, the oil is supplied to the most retarded angle lock groove 72 . Accordingly, the most retarded angle lock member 74 is retracted from the most retarded angle lock groove 72 to the housing portion 73 . That is, the relative rotational phase is unlocked.
  • the pin shape can be appropriately adapted other than the plate shape shown in the present embodiment.
  • the most retarded angle lock member 74 ( 64 ) is entered into the most retarded angle lock groove 72 to be established in the most retarded angle lock state.
  • the number of components can be reduced while the configuration is simplified.
  • a manufacturing cost can be reduced.
  • the outer rotor 12 has an additional space in the circumferential direction, and as shown in FIG. 2 , four of the fluid pressure chambers 4 can be provided.
  • the displaceable range of the relative rotational phase can be increased by increasing the width of the fluid pressure chamber 4 in the circumferential direction.
  • the oil-pressure passage is provided with a pump 171 , a first control valve 174 and a second control valve 175 .
  • the pump 171 is driven by the internal combustion engine E and supplies the oil.
  • the first control valve 174 controls the supply of the oil to the fluid pressure chamber 4 .
  • the second control valve 175 controls the supply of the oil to the intermediate lock mechanism 6 .
  • a phase control portion 180 controls respective operations of the first control valve 174 and of the second control valve 175 in order to control the aforementioned relative rotational phase. For example, in a case where the intermediate lock mechanism 6 shifts from the unlock state to the lock state, the phase control portion 180 controls the supply of the fluid to the retard chamber 42 and the discharge of the fluid from the advance chamber 41 , or the discharge of the fluid from the retard chamber 42 and the supply of the fluid to the advance angle chamber 41 in order for the intermediate lock member 64 to reach the intermediate locked phase.
  • An arithmetic processing unit is used for the phase control portion 180 .
  • the phase control portion 180 is configured by a single control device or by plural control devices.
  • the pump 171 serves as a mechanical oil-pressure pump that is driven by a rotational force transmitted from the crankshaft 110 of the intermediate combustion engine E.
  • the pump 171 pumps the stored oil stored in an oil pan 176 from an inlet port and discharges the oil from an outlet port to a downstream.
  • the outlet port of the pump 171 is communicated with respective predetermined ports of the first control valve 174 and of the second control valve 175 .
  • a variable electromagnetic spool valve can be used for the first control valve 174 .
  • the variable electromagnetic spool valve displaces a spool being positioned within a sleeve so as to be slidable against a spring by the energization from the phase control portion 180 to a solenoid.
  • the first control valve 174 includes an advance port, a retard port, a supply port, and a drain port.
  • the advance port is communicated with the advance passage 43 .
  • the retard port is communicated with the retard passage 44 .
  • the supply port is communicated with a flow passage of the downstream of the pump 171 .
  • the drain port is communicated with the oil pan 176 .
  • the first control valve 174 is configured by a three-position control valve that is able to perform three-state controls that are, an advanced angle control, a retarded angle control, and a hold control.
  • the advanced angle control communicates the advance port to the supply port and communicates the retard port to the drain port.
  • the retarded angle control communicates the retard port to the supply port and communicates the advance port to the drain port.
  • the hold control closes the advance port and the retard port. Because the advanced angle control is performed, the vane 22 relatively rotationally moves in the advance direction S 1 relative to the outer rotor 12 .
  • the relative rotational phase is displaced to the advance side. Because the retarded angle control is performed, the vane 22 relatively rotationally moves in the retarded direction S 2 relative to the outer rotor 12 .
  • the relative rotational phase is displaced to the retarded angle. Because the hold control is performed, the vane 22 does not relatively rotationally move.
  • the relative rotational phase can be held at a desired phase.
  • the oil is supplied to the advance passage 43 and to the most retarded angle lock passage 71 .
  • the most retarded angle lock passage 71 is closed by the most retarded angle lock member 74 .
  • the oil is supplied to the advance chamber 41 via the advance passage 43 .
  • the inner rotor 2 relatively rotationally moves to the advanced angle.
  • the phase control portion 180 controls the first control valve 174 to control the supply or the discharge of the oil relative to the advance chamber 41 and the most retarded angle lock passage 71 , or the retard chamber 42 . Accordingly, the first control valve 174 performs a switching control of the intermediate lock mechanism 6 between the lock state and the unlock state, and performs the control of the relative rotational phase of the inner rotor 2 relative to the outer rotor 12 . According to the present embodiment, when the first control valve 174 is energized, the retarded angle control comes to be available. When the energization of the first control valve 174 is stopped, the advanced angle control comes to be available. In addition, the first control valve 174 sets the opening by the adjustment of the duty ratio of the electric power being supplied to an electromagnetic solenoid. Accordingly, the fine adjustment of the supply/discharge amount of the oil is available.
  • the second control valve 175 includes a restriction port, a supply port and a drain port.
  • the restriction port is communicated with the intermediate lock passage 61 .
  • the supply port is communicated with the flow passage of the downstream of the pump 171 .
  • the drain port is communicated with the oil pan 176 .
  • the second control valve 175 is configured as a two-position control valve being able to control two-state controls that are a release control and a restriction control.
  • the release control communicates the restriction port to the supply port.
  • the restriction control communicates the restriction port to the drain port.
  • the phase control portion 180 controls the second control valve 175 to control the supply/discharge of the oil to/from the intermediate lock groove 62 of the intermediate lock mechanism 6 .
  • the second control valve 175 performs the switching control of the intermediate lock mechanism 6 between a restricted state or a released state.
  • the second control valve 175 can switch between the supply of the oil to the intermediate lock groove 62 and the discharge of the oil from the intermediate lock groove 62 .
  • the second control valve 175 is configured such that when the second control valve 175 is energized, the oil can be discharged from the intermediate lock groove 62 , and the energization of the second control valve 175 is stopped, the oil can be supplied to the intermediate lock groove 62 .
  • a crank angle sensor detecting a rotational angle of the crankshaft 11 is provided in the vicinity of the crankshaft 110 of the internal combustion engine E.
  • a camshaft angle sensor detecting a rotational angle of the camshaft 101 is provided in the vicinity of the camshaft 101 .
  • the phase control portion 180 detects the relative rotational phase from detection results of the crank angle sensor and of the camshaft angle sensor and determines which phase the relative rotational phase is positioned.
  • the on/off information of an ignition key is transmitted to the phase control portion 180 .
  • the control information of an optimum relative rotational phase in accordance with an operation state of the internal combustion engine E is memorized within a memory of the phase control portion 180 .
  • the phase control portion 180 controls the relative rotational phase in accordance with the operation state of the internal combustion engine E.
  • the phase control portion 180 performs one of a control of the supply of the fluid to the retard chamber 42 and the discharge of the fluid from the advance chamber 41 , and a control of the discharge of the fluid from the retard chamber 42 and the supply of the fluid to the advance chamber 41 by reducing the travelling speed of the relative rotational phase from a reference phase to the intermediate locked phase to be slower than the travelling speed of the relative rotational phase to the reference phase that is provided between a present phase and the intermediate locked phase.
  • the phase control portion 180 detects the relative rotational phase from the detection results of the crank angle sensor and of the camshaft angle sensor, and determines which phase the relative rotational phase is positioned.
  • the reference phase is provided between the present phase and the intermediate locked phase.
  • the reference phase can be provided to be changeable to an intermediate position each time between the present phase and the intermediate locked phase. Alternatively, the reference phase can be pre-provided in the vicinity of the intermediate locked phase.
  • FIGS. 5 and 6 schematically illustrate the reference phase and the intermediate locked phase.
  • FIG. 5 shows an example of a case where two of the intermediate lock members 64 move to the intermediate locked phase from a state where the intermediate lock members 64 are not positioned within the intermediate lock grooves 62 , respectively, by the rotation of the inner rotor 2 in the advance direction S 1 .
  • FIG. 6 shows an example of a case where two of the intermediate lock members 64 move to the intermediate locked phase from a state where the intermediate lock members 64 are not positioned within the intermediate lock grooves 62 , respectively, by the rotation of the inner rotor 2 in the retarded direction S 2 .
  • FIGS. 5 shows an example of a case where two of the intermediate lock members 64 move to the intermediate locked phase from a state where the intermediate lock members 64 are not positioned within the intermediate lock grooves 62 , respectively, by the rotation of the inner rotor 2 in the retarded direction S 2 .
  • a reference phase P is provided therebetween.
  • the reference phase P is provided within the intermediate lock groove 62 in FIG. 5 .
  • the reference phase P can be provided at an out of the intermediate lock groove 62 .
  • the reference phase P is provided at the out of the intermediate lock groove 62 in FIG. 6 .
  • the reference phase P can be provided within the intermediate lock groove 62 .
  • the phase control portion 180 performs one of the control of the supply of the fluid to the retard chamber 42 and the discharge of the fluid from the advance chamber 41 , and the control of the discharge of the fluid from the retard chamber 42 and the supply of the fluid to the advance chamber 41 so as to reduce the traveling speed of the relative rotational phase by a predetermined amount of change from a position O of the present phase to a position A of the intermediate locked phase via a position P of the reference phase.
  • the reduction of the speed by the predetermined amount of change indicates that the travelling speed is reduced by a predetermined negative acceleration and indicates that the travelling speed is reduced gradually as shown in FIG. 7 . Accordingly, the relative rotational phase can be promptly and securely moved from the present phase to the intermediate locked phase.
  • a change of the travelling speed shown in FIG. 7 corresponds to an example.
  • the relative rotational phase moves from the position O of the present phase to the position P of the reference phase based on a predetermined first travelling speed.
  • the relative rotational phase can move from the position P of the reference phase to the position A of the intermediate locked phase based on a second travelling speed that is slower than the first travelling speed. While the relative rotational phase travels from the position O of the present phase to the position A of the intermediate locked phase, the travelling speed of the relative rotational phase can be naturally changed by equal to or more than three steps.
  • a determination portion 181 determines whether the intermediate lock member 64 reaches the reference phase when the phase control portion 180 controls the intermediate lock member 64 to travel to a side where the reference phase is positioned after controlling the supply and discharge.
  • the control of the supply and discharge by the phase control portion 180 serves as a control performing one of the control of the supply of the fluid to the retard chamber 42 and the discharge of the fluid from the advance chamber 41 , and the control of the discharge of the fluid from the retard chamber 42 and the supply of the fluid to the advance chamber 41 so that the intermediate lock member 64 comes to be positioned at the intermediate locked phase.
  • Controlling the intermediate lock member 64 to travel to a side where the reference phase is positioned (a side of a position of the present phase in a case where the intermediate lock member 64 travels to the intermediate locked phase) will hereunder be explained as a determination control.
  • the determination control in a case where the determination portion 181 determines that the intermediate lock member 64 reaches the position P of the reference phase, the result is transmitted to the phase control portion 180 .
  • the phase control portion 180 recognizes that the relative rotational phase of the inner rotor 2 relative to the outer rotor 12 does not correspond to the intermediate locked phase.
  • the phase control portion 180 controls the first control valve 174 to travel to the intermediate locked phase.
  • the phase control portion 180 recognizes that the relative rotational phase of the inner rotor 2 relative to the outer rotor 12 corresponds to the intermediate locked phase.
  • the phase control portion 180 stops the control of the first control valve 174 .
  • the phase control portion 180 alternately supplies the fluid to the retard chamber 42 and to the advance chamber 41 .
  • the case where the determination portion 181 determines that the intermediate lock member 64 is not provided at the position P of the reference phase after the control of the supply and discharge by the first control valve 174 corresponds to a case where the intermediate lock member 64 is positioned at the intermediate locked phase.
  • the vane 22 swings in the advance direction S 1 and in the retarded direction S 2 in a state where the relative rotation is restricted by the supply of the fluid alternately to the retard chamber 42 and to the advance chamber 41 by the phase control portion 180 .
  • the intermediate lock member 64 does not reach the reference phase, it can be determined that the intermediate lock member 64 is securely fitted in the intermediate lock groove 62 . Accordingly, according to this configuration, the fitted-in state of the intermediate lock member 64 can be confirmed.
  • the respective oil pressure levels of the retard chamber 42 and of the advance chamber 41 increase and decrease
  • the respective oil pressure levels of passages being connected to the retard chamber 42 and to the advance chamber 41 increase and decrease in accordance with the oil pressure levels of the retard chamber 42 and of the advance chamber 41 . Accordingly, extraneous materials within the passages can be circulated and removed (cleaned).
  • each of two of the intermediate lock grooves 62 has the ratchet structure so that the groove depth comes to be gradually deeper along the retarded direction S 2 of the inner rotor 2 .
  • the intermediate lock groove 62 can be naturally configured to have a constant groove depth.
  • the single intermediate lock groove 62 and the single intermediate lock member 64 are provided and the intermediate lock groove 62 has the ratchet structure so that the groove depth comes to be gradually deeper along the retarded direction S 2 of the inner rotor 2 .
  • the length of the intermediate lock groove 62 in the circumferential direction, the length of a position having a deeper groove is set at a degree where the outer rotor 12 and the inner rotor 2 do not relatively rotate with each other in a case where the intermediate lock member 64 is fitted into the deeper groove.
  • the intermediate lock groove 62 can be configured to have a constant groove depth. In such a case, it is favorable that the length of the intermediate lock groove 62 in the circumferential direction is set at a degree where the outer rotor 12 and the inner rotor 2 allow relative rotation with each other in a case where the intermediate lock member 64 is fitted into the intermediate lock groove 62 .
  • the intermediate lock member 64 is explained to be provided at the outer rotor 12 and the intermediate lock groove 62 is explained to be provided at the inner rotor 2 .
  • the intermediate lock member 64 can be naturally provided at the inner rotor 2 and the intermediate lock groove 62 can be configured to be naturally provided at the outer rotor 12 .
  • the phase control portion 180 is explained to alternately supply the fluid to the retard chamber 42 and to the advance chamber 41 .
  • the applicability of this invention is not limited to this.
  • the phase control portion 180 can be naturally configured so as not to alternately supply the fluid to the retard chamber 42 and to the advance chamber 4 .
  • the phase control portion 180 can be configured so as to supply the fluid to the retard chamber 42 and to the advance chamber 41 alternately in a case where the determination portion 181 performs the determination.
  • valve opening and closing timing control device 1 controls the opening and closing timing of the intake valve 115 .
  • the valve opening/control timing control device 1 can be configured to naturally control the opening and closing timing of the exhaust valve.
  • the determination portion 181 is explained to determine whether the intermediate lock member 64 reaches the reference phase when the intermediate lock member 64 is controlled to move to the reference phase after the control of the supply and discharge by the phase control portion 180 .
  • a position of a determination phase is provided between the position A of the intermediate locked phase and the position P of the reference phase.
  • the phase control portion 180 performs one of the control of the supply of the fluid to the retard chamber 42 and the discharge of the fluid from the advance chamber 41 , and the control of the discharge of the fluid from the retard chamber 42 and the supply of the fluid to the advance chamber 41 .
  • the determination portion 181 determines whether the intermediate lock member 64 reaches the position of the determination phase when the phase control portion 180 controls the intermediate lock member 64 to move to the determination phase side. In such a case, because a position between the intermediate locked phase and the position for determination (the position of the determination phase) can be shallow, the determination portion 181 can determine whether the intermediate lock member 64 reaches the intermediate locked phase more securely.
  • the phase control portion 180 is explained to perform one of the control of the supply of the fluid to the retard chamber 42 and the discharge of the fluid from the advance chamber 41 , and the control of the discharge of the fluid from the retard chamber 42 and the supply of the fluid to the advance chamber 41 so that the travelling speed of the relative rotational phase from the present phase to the intermediate locked phase is reduced by the predetermined amount of change.
  • the applicability of this invention is not limited to this.
  • the phase control portion 180 performs one of the control of the supply of the fluid to the retard chamber 42 and the discharge of the fluid from the advance chamber 41 , and the control of the discharge of the fluid from the retard chamber 42 and the supply of the fluid to the advance chamber 41 based on a map that is defined by a relationship between the travelling speed of the relative rotational phase from the present phase to the intermediate locked phase and the quantity of state showing a state of the fluid that is flowed to the retard chamber 42 and to the advance chamber 41 .
  • the quantity of state showing the state of the fluid corresponds to a temperature level and a pressure level of the fluid, for example.
  • the map that defines the traveling speed with the relationship of the temperature level and the pressure level of the fluid is pre-memorized, and the phase control portion 180 can be configured to control the oil pressure levels of the retard chamber 42 and of the advance chamber 41 based on the map.
  • the phase control portion 180 controls the travelling speed from the reference phase to the intermediate locked phase to be slower than the travelling speed from the present phase to the reference phase, the relative rotational phase can be promptly travelled to the intermediate locked phase.
  • the present invention is applicable to a valve opening and closing timing control device that controls the relative rotational phase of a driven-side rotary member rotating integrally with a camshaft of an internal combustion engine relative to a driving-side rotary member rotating synchronously with a crankshaft of the internal combustion engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
US14/910,112 2013-08-08 2014-06-25 Valve opening and closing timing control device Abandoned US20160169061A1 (en)

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JP2013-165408 2013-08-08
JP2013165408A JP6036600B2 (ja) 2013-08-08 2013-08-08 弁開閉時期制御装置
PCT/JP2014/066855 WO2015019735A1 (ja) 2013-08-08 2014-06-25 弁開閉時期制御装置

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JP (1) JP6036600B2 (ja)
CN (1) CN105392971B (ja)
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US20170114728A1 (en) * 2014-07-11 2017-04-27 Honda Motor Co., Ltd. Control apparatus for internal combustion engine
US10450905B2 (en) * 2017-03-23 2019-10-22 Aisin Seiki Kabushiki Kaisha Variable valve timing control device

Families Citing this family (2)

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Publication number Priority date Publication date Assignee Title
WO2019210510A1 (zh) * 2018-05-04 2019-11-07 舍弗勒技术股份两合公司 凸轮轴相位器
CN112211691B (zh) * 2019-07-09 2024-06-25 舍弗勒投资(中国)有限公司 凸轮轴相位器组件

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JP3775031B2 (ja) * 1997-12-12 2006-05-17 トヨタ自動車株式会社 内燃機関のバルブタイミング制御方法及びバルブタイミング制御装置
JP4159241B2 (ja) * 2000-11-30 2008-10-01 株式会社デンソー 内燃機関用バルブタイミング調整装置
JP4160408B2 (ja) * 2003-01-17 2008-10-01 株式会社日立製作所 内燃機関のバルブタイミング制御装置
JP4640616B2 (ja) * 2006-08-23 2011-03-02 アイシン精機株式会社 弁開閉時期制御装置
JP2008280933A (ja) * 2007-05-11 2008-11-20 Denso Corp 内燃機関制御装置及び内燃機関制御システム
JP5126157B2 (ja) * 2009-04-23 2013-01-23 株式会社デンソー 内燃機関の可変バルブタイミング制御装置
JP5003789B2 (ja) * 2010-04-28 2012-08-15 トヨタ自動車株式会社 内燃機関の可変動弁装置
JP5773195B2 (ja) * 2011-07-12 2015-09-02 アイシン精機株式会社 弁開閉時期調整システム

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US20100139592A1 (en) * 2008-12-09 2010-06-10 Denso Corporation Variable valve timing control apparatus for internal combustion engine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170114728A1 (en) * 2014-07-11 2017-04-27 Honda Motor Co., Ltd. Control apparatus for internal combustion engine
US10113490B2 (en) * 2014-07-11 2018-10-30 Honda Motor Co., Ltd. Control apparatus for internal combustion engine
US10450905B2 (en) * 2017-03-23 2019-10-22 Aisin Seiki Kabushiki Kaisha Variable valve timing control device

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JP6036600B2 (ja) 2016-11-30
EP3032050A4 (en) 2016-09-07
WO2015019735A1 (ja) 2015-02-12
EP3032050A1 (en) 2016-06-15
EP3032050B1 (en) 2019-01-16
JP2015034501A (ja) 2015-02-19
CN105392971B (zh) 2017-12-22
CN105392971A (zh) 2016-03-09

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