WO2013129110A1 - 内燃機関の可変バルブタイミング制御装置 - Google Patents
内燃機関の可変バルブタイミング制御装置 Download PDFInfo
- Publication number
- WO2013129110A1 WO2013129110A1 PCT/JP2013/053393 JP2013053393W WO2013129110A1 WO 2013129110 A1 WO2013129110 A1 WO 2013129110A1 JP 2013053393 W JP2013053393 W JP 2013053393W WO 2013129110 A1 WO2013129110 A1 WO 2013129110A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve timing
- intermediate lock
- lock
- rotor
- controlled
- Prior art date
Links
Images
Classifications
-
- 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
- F01L1/34—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
-
- 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
-
- 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
-
- 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
- F01L2001/34459—Locking in multiple 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
- F01L2001/34463—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
- 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
- F01L2250/00—Camshaft drives characterised by their transmission means
- F01L2250/04—Camshaft drives characterised by their transmission means the camshaft being driven by belts
-
- 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 variable valve timing control device for an internal combustion engine.
- variable valve timing device for an internal combustion engine having an intermediate lock mechanism capable of locking a camshaft phase with respect to a crankshaft at an intermediate phase is conventionally known.
- variable valve timing device for an internal combustion engine disclosed in Patent Document 1
- a housing that rotates in synchronization with a crankshaft, a rotor that is provided in the housing and rotates with a camshaft, and can be engaged with both the housing and the rotor.
- the two lock pins are inserted into the two lock grooves formed in the rotor from the housing side to restrict the relative rotation of the camshaft with respect to the crankshaft.
- An intermediate lock mechanism for holding the valve timing at a predetermined intermediate lock position is disclosed.
- the variable valve timing device in Patent Document 1 can change the valve timing by supplying hydraulic oil to an advance side hydraulic chamber or a retard side hydraulic chamber formed between the housing and the rotor.
- hydraulic oil is alternately and repeatedly supplied to the advance side hydraulic chamber and the retard side hydraulic chamber, and then the lock pin is pushed back to the housing side by hydraulic pressure.
- the valve timing is stabilized at the intermediate lock position, and the relative rotation of the housing and the rotor from the intermediate lock position is suppressed, so that the lock pin is pressed against the housing and the rotor.
- the frictional force between the lock pin and the housing and the rotor generated by this can be reduced, and the two lock pins can be easily pulled out from the two lock grooves.
- the intermediate lock mechanism has two lock pins, unless the hydraulic pressure in the advance side hydraulic chamber and the hydraulic pressure in the retard side hydraulic chamber are made strictly uniform, one of the two lock pins is Since it will always be pressed with respect to a housing and a rotor, possibility that cancellation
- a variable valve timing control device for an internal combustion engine of the present invention includes a variable valve timing mechanism that varies a valve timing of an engine valve, and an intermediate lock mechanism that can perform an intermediate lock that holds the valve timing at a predetermined intermediate lock position. ing.
- the intermediate lock mechanism includes an advance side intermediate position holding member and a retard side intermediate position holding member that engage with the first rotor and the second rotor of the variable valve timing mechanism.
- the advance side intermediate position holding member restricts the valve timing from moving from the intermediate lock position to the advance side, and the retard side intermediate position holding member is used to retard the valve timing from the intermediate lock position. The movement to the side is restricted.
- the valve timing When releasing the intermediate lock by the intermediate lock mechanism, the valve timing is controlled to the advance side or the retard side from the intermediate lock position, and the direction opposite to the direction in which the valve timing of the engine valve is controlled
- the valve timing of the engine valve is adjusted by the first intermediate lock release.
- the valve timing of the engine valve is controlled in the direction opposite to the controlled direction, and the second intermediate lock release for releasing the engagement of the other intermediate position holding member with respect to the first rotor and the second rotor is performed. It is a feature.
- the intermediate lock by the intermediate lock mechanism can be released without generating a friction force between the intermediate position holding member and the housing and the rotor, and the intermediate lock mechanism can be released. It is possible to suppress the failure of release.
- FIG. 1 is an explanatory diagram showing a schematic configuration of a variable valve timing control device for an internal combustion engine according to the present invention.
- This variable valve timing mechanism 2 receives the supply of hydraulic oil and continuously variably controls the rotational phase difference between a crankshaft (not shown) and a camshaft (not shown) to provide an engine valve (intake valve) (not shown).
- intake valve an engine valve
- the valve timing (the phase of the lift center angle) of the exhaust valve can be varied within a predetermined range.
- the variable valve timing mechanism 2 is applied to the intake valve side.
- variable valve timing mechanism 2 includes an inner rotor 21 (first rotor) and an outer rotor 22 (second rotor) that is fitted to the inner rotor 21 so as to be relatively rotatable.
- the inner rotor 21 is fixed to the tip of an intake camshaft (not shown) rotatably supported by a cylinder block (not shown) of the internal combustion engine, and rotates integrally with the intake camshaft.
- an intake camshaft (not shown) rotatably supported by a cylinder block (not shown) of the internal combustion engine, and rotates integrally with the intake camshaft.
- the intake camshaft rotates together with the inner rotor 21, the intake valve is driven to open and close by a cam (not shown) provided on the intake camshaft.
- Four vanes 23 are provided radially on the outer periphery of the inner rotor 21.
- the outer rotor 22 is coaxially disposed on the outer peripheral side of the inner rotor 21.
- the outer rotor 22 is fixed to an intake cam sprocket (not shown) by a plurality of mounting bolts 24.
- the intake cam sprocket is linked to the crankshaft via a timing chain (or timing belt) (not shown).
- the tip of the vane 23 is in sliding contact with the inner periphery of the recess 26, and the tip of the protrusion 25 is in sliding contact with the outer periphery of the inner rotor 21.
- the inner rotor 21 and the intake camshaft 4, and the intake cam sprocket and the outer rotor 22 can be relatively rotated around the same axis.
- two spaces 27 and 28 are defined in a liquid-tight manner by being partitioned by the vane 23.
- the space 28 on the intake camshaft rotation direction (arrow P1 direction) side with respect to the vane 23 is the retard side hydraulic chamber, and the space 27 on the opposite side (arrow P2 direction) advances. It is a corner side hydraulic chamber.
- an oil passage 32 communicating with the advance angle side oil passage 30 and an oil passage 33 communicating with the retard angle side oil passage 31 are formed.
- the vane 23 is
- the valve timing of the intake valve is most retarded when it hits against the other end surface 26b of the recess 26 or a stopper (not shown) on the end surface 26b side.
- the valve timing position of the intake valve at this time is set as the most retarded position.
- valve timing of the intake valve is a predetermined intermediate lock position between the most advanced angle position and the most retarded angle position
- an intermediate lock mechanism provided between the inner rotor 21 and the outer rotor 22 is used.
- the relative rotational phases of the inner rotor 21 and the outer rotor 22 are maintained by 34a and 34b.
- the intermediate lock mechanism 34a is an advance side intermediate lock mechanism that restricts the movement of the inner rotor 21 in the advance direction (arrow P1 direction), and the intermediate lock mechanism 34b is in the retard direction (arrow P2 direction) of the inner rotor 21.
- This is a retard-side intermediate locking mechanism that restricts movement.
- the advance side intermediate lock mechanism 34a and the retard side intermediate lock mechanism 34b in this embodiment have substantially the same configuration.
- the advance side intermediate locking mechanism 34 a is a lock key 35 a as an elongated intermediate position holding member that can advance and retreat in a direction orthogonal to the rotation axes of the inner rotor 21 and the outer rotor 22, and a lock formed on the convex portion 25 of the outer rotor 22.
- the length of the engagement recess 38a along the circumferential direction of the inner rotor 21 is formed to be longer than the length of the lock key 35a at the tip along the circumferential direction of the inner rotor 21.
- the tip of the lock key 35a engages with the advance side wall surface 46a of the engagement recess 38a, so that the relative rotational phase of the inner rotor 21 and the outer rotor 22 is advanced from the predetermined intermediate phase. Is restricted from moving to.
- the retard side wall surface 47a of the engaging recess 38a is separated from the tip of the lock key 35a in the engaging recess 38a by a predetermined distance along the circumferential direction of the inner rotor 21 at the intermediate lock position.
- hydraulic oil can be supplied to the engaging recess 38 a from an oil passage 40 a formed in the inner rotor 21. Further, the hydraulic oil in the engagement recess 38a can be drained (discharged) through the oil passage 40a.
- the retard-side intermediate lock mechanism 34b has substantially the same configuration as the advance-side intermediate lock mechanism 34a, and serves as an elongated intermediate position holding member that can advance and retract in a direction perpendicular to the rotation axes of the inner rotor 21 and the outer rotor 22.
- An engagement recess 38b formed on the outer periphery of the inner rotor 21 and engageable with the tip of the lock key 35b is roughly constituted.
- the length of the engaging recess 38b along the circumferential direction of the inner rotor 21 is formed to be longer than the length along the circumferential direction of the inner rotor 21 at the tip of the lock key 35b.
- the distal end of the lock key 35b engages with the retard side wall surface 47b of the engagement recess 38b, so that the relative rotational phase of the inner rotor 21 and the outer rotor 22 is retarded from the predetermined intermediate phase. Is restricted from moving to.
- the advance side wall surface 46b of the engagement recess 38b is separated from the tip of the lock key 35b in the engagement recess 38b by a predetermined distance along the circumferential direction of the inner rotor 21 at the intermediate lock position.
- hydraulic oil can be supplied to the engaging recess 38b from an oil passage 40b formed in the inner rotor 21.
- the hydraulic oil in the engagement recess 38b can be drained (discharged) through the oil passage 40b.
- the valve timing of the intake valve can be held at the intermediate lock position. ing.
- the variable valve timing mechanism 2 is driven by hydraulic oil from the oil pump 41.
- the oil pump 41 is mechanically driven based on the rotational force of the crankshaft and sucks the hydraulic oil in the oil pan 42.
- the oil pump 41 supplies hydraulic oil to an oil control valve (OCV) 43 and an oil switching valve (OSV) 44.
- OCV oil control valve
- OSV oil switching valve
- the oil control valve 43 and the oil switching valve 44 are control valves that are duty-controlled based on commands from an ECM (engine control module) 11.
- the oil control valve 43 can supply hydraulic oil to the advance side hydraulic chamber 27 via the advance side oil passage 30 and supply hydraulic oil to the retard side hydraulic chamber 28 via the retard side oil passage 31. It is possible.
- the oil switching valve 44 can supply hydraulic oil from the intermediate position holding oil passage 45 to the engagement recesses 38a and 38b of the intermediate lock mechanisms 34a and 34b via the oil passages 40a and 40b.
- the oil switching valve 44 has substantially the same configuration as that in which the port communicating with the advance side oil passage 30 is sealed when the oil control valve 43 is advanced.
- the ECM 11 receives detection signals from various sensors.
- the target value of the valve timing of the intake valve is sequentially updated and calculated based on the engine operating state grasped from the result. Then, the ECM 11 outputs a command signal to the oil control valve 43 according to the engine operating state, and performs switching control of the oil control valve 43.
- the oil control valve 43 is switched so that hydraulic oil is supplied to the advance side hydraulic chamber 27, and when the valve timing of the intake valve is retarded, the retard side
- the oil control valve 43 is switched so that the hydraulic oil is supplied to the hydraulic chamber 28.
- the valve timing of the intake valve variably controlled by the variable valve timing mechanism 2 can be detected by the ECM 11 based on the output signals of the crank angle sensor 12 and the cam angle sensor 13.
- FIG. 2 is an explanatory diagram schematically showing the operating state of the oil control valve 43 and the oil switching valve 44 with respect to the duty ratio which is a control command value.
- the operation state of the oil control valve 43 includes an advance operation that advances the valve timing of the intake valve and a neutral operation that does not supply hydraulic oil to both the advance side hydraulic chamber 27 and the retard side hydraulic chamber 28 (dead zone). ) And a retarding operation that retards the valve timing of the intake valve.
- the advance operation the hydraulic oil is supplied to the advance hydraulic chamber 27 while the hydraulic oil in the retard hydraulic chamber 28 is drained (discharged), so the valve timing of the intake valve is advanced. Change to the side.
- the retard operation the hydraulic oil is supplied to the retard hydraulic chamber 28 while the hydraulic fluid in the advance hydraulic chamber 27 is drained (discharged), so the valve timing of the intake valve is retarded. To change.
- the operating state of the oil switching valve 44 includes a lock state in which the valve timing of the intake valve can be held at the intermediate lock position, a lock release state in which the valve timing of the intake valve is not held at the intermediate lock position, It is roughly classified into a lock indefinite state in which it is not certain whether it is in the locked state or the unlocked state.
- the lock indefinite state In the lock indefinite state, the supply of hydraulic oil to the engagement recesses 38a and 38b and the drain (discharge) of the hydraulic oil are prohibited, and immediately before the engagement recesses 38a and 38b enter the lock indefinite state.
- the distal ends of the lock keys 35a and 35b engage with the corresponding engaging recesses 38a and 38b, and the distal ends of the lock keys 35a and 35b correspond to the corresponding engaging recesses 38a and 38b. In some cases, they do not engage.
- variable valve timing mechanism 2 when the valve timing of the intake valve is held at the intermediate lock position by the intermediate lock mechanisms 34a and 34b, the hydraulic pressure in the advance side hydraulic chamber 27 is increased. If there is a pressure difference between the hydraulic pressure in the retard side hydraulic chamber 28, one of the lock keys 35 a and 35 b is pressed against the corresponding engagement recess 38 and the side wall of the lock key storage chamber 36.
- the valve timing of the intake valve tends to move further toward the advance side than the intermediate lock position. A part on the front end side is pressed against the engaging recess 38 a and a part on the rear end side of the lock key 35 a is pressed against the lock key accommodation chamber 36.
- the lock key 35a is pulled out of the engagement recess 38a by the frictional force of the portion pressed against the engagement recess 38a and the lock key storage chamber 36a (perpendicular to the rotation axes of the inner rotor 21 and the outer rotor 22). Movement in the direction of movement) is restricted. That is, if it is attempted to release the intermediate lock by the intermediate lock mechanisms 34a and 34b in such a state, the lock key 35a may not be successfully pulled out from the engagement recess 38a.
- valve timing of the intake valve can be held at the intermediate lock position in a state where there is no pressure difference between the hydraulic pressure in the advance side hydraulic chamber 27 and the hydraulic pressure in the retard side hydraulic chamber 28, both the lock keys 35a and 35b Although it is not pressed against the corresponding engaging recess 38 and the side wall of the lock key accommodating chamber 36, it is difficult to make the advance side hydraulic chamber 27 and the retard side hydraulic chamber 28 to have exactly the same oil pressure. .
- the valve timing of the intake valve when releasing the state in which the valve timing of the intake valve is held at the intermediate lock position by the intermediate lock mechanisms 34a, 34b (when releasing the intermediate lock), first, the valve timing of the intake valve Is controlled to the advance side or the retard side from the intermediate lock position, and the tip of one lock key 35 that restricts the movement opposite to the direction in which the valve timing of the intake valve is controlled is Pull out the first intermediate unlock. Then, after the first intermediate lock is released, the valve timing of the intake valve is controlled in the direction opposite to the first intermediate lock release, and the tip of the other lock key 35 is pulled out from the engagement recess 38, and the second intermediate lock release is pulled out. To implement.
- FIG. 3 schematically shows the case where the intermediate lock of the retard side intermediate lock mechanism 34b is released as the first intermediate lock release, and the intermediate lock of the advance side intermediate lock mechanism 34a is released as the second intermediate lock release. It is explanatory drawing shown.
- the valve timing of the intake valve is controlled to be advanced from the intermediate lock position, and a part of the front end side of the lock key 35a of the advance side intermediate lock mechanism 34a is engaged.
- the tip of the lock key 35b of the retard side intermediate lock mechanism 34b is pulled out from the engagement recess 38b, and the retard side intermediate lock mechanism 34b The intermediate lock is released.
- the timing for pulling the tip of the lock key 35b from the engagement recess 38b by releasing the first intermediate lock is after the tip of the lock key 35a is pressed against the advance side wall surface 46a of the engagement recess 38a. Therefore, the oil switching valve 44 is in the unlocked state from the locked state when the tip of the lock key 35a is pressed against the advance side wall surface 46a of the engaging recess 38a by the first intermediate unlocking. It is controlled to switch to.
- the valve timing of the intake valve is controlled to be retarded from the intermediate lock position, and a part of the front end side of the lock key 35a is on the advance side of the engagement recess 38.
- the tip of the lock key 35a of the advance side intermediate lock mechanism 34a is pulled out from the engagement recess 38a, and the intermediate lock of the advance side intermediate lock mechanism 34a is released. To do.
- valve timing of the intake valve is controlled to be retarded from the intermediate lock position, the vane 23 will move in the direction indicated by the arrow in FIG. 3b, and the relative rotational phase of the inner rotor 21 and the out rotor 22 will change. And As a result, the advance side wall surface 46a of the engagement recess 38a tends to move away from the lock key 35a, so that a part of the front end side of the lock key 35a is advanced side wall surface 46a of the engagement recess 38a. Separate from.
- the intermediate lock mechanisms 34a and 34b prevent the intermediate friction mechanisms 34a and 34b from generating a friction force between the lock key 35a and the lock key 35b that are generated by pressing the lock key 35a and the lock key 35b against the inner rotor 21 and the outer rotor 22.
- the lock can be released. Therefore, the intermediate lock mechanism 34a, 34b can release the intermediate lock with high accuracy, and the failure to release the intermediate lock can be suppressed.
- FIG. 4 is a timing chart showing an example of an operation when the variable valve timing mechanism 2 in the present embodiment releases the intermediate lock of the intermediate lock mechanisms 34a and 34b.
- the intermediate lock release sequence permission flag becomes “1”
- the oil control valve 43 causes the hydraulic pressure in the advance hydraulic chamber 27 to In order to balance the hydraulic pressure in the retarded-side hydraulic chamber 28 and the retarded-side hydraulic chamber 28, an unlocking preparation operation is performed in which the hydraulic pressure is alternately supplied to the advanced-side hydraulic chamber 27 and the retarded-side hydraulic chamber 28 multiple times.
- the intermediate lock request is generated when, for example, the water temperature or the oil temperature is equal to or lower than a predetermined temperature, or the engine rotational speed is equal to or lower than the predetermined rotational speed R. It may occur depending on the operating conditions even when it is not stopped.
- the oil control valve 43 has the valve timing of the intake valve advanced from the intermediate locking position. Is controlled at a predetermined constant duty ratio.
- the second intermediate unlocking is performed for a predetermined time T2, and during that time, the oil control valve 43 has a valve timing of the intake valve that is higher than the intermediate lock position. Control is performed at a predetermined constant duty ratio so as to be on the retard side.
- the predetermined time T1 and the predetermined time T2 are set to the same length.
- the oil switching valve 44 is not at the start of the first intermediate lock release, but the tip of the lock key 35a is brought into contact with the advance side wall surface 46a of the engagement recess 38a by the first intermediate lock release. Since it is controlled to switch from the locked state to the unlocked state after being pressed, the OSV drive permission flag sets the oil switching valve 44 to the locked state between time t2 and time t3. Is switched to “0” to bring the oil switching valve 44 into the unlocked state. Therefore, after time t3, the hydraulic pressure is always applied to the lock keys 35a and 35b in the direction in which the intermediate lock is released, and the intermediate lock of the intermediate lock mechanisms 34a and 34b can be quickly released. it can.
- the response speed of the variable valve timing mechanism 2 by the oil control valve 43 changes as shown in FIG. 5 in accordance with the value of the current applied to the oil control valve 43.
- the control command value to the oil control valve 43 is on the horizontal axis as a current value instead of the duty ratio, and the duty ratio increases in the direction in which the current value increases.
- the response speed of the variable valve timing mechanism 2 is, in other words, the change speed of the valve timing of the intake valve.
- the variable valve timing decreases as the OCV applied current value decreases until the OCV applied current value decreases by a predetermined amount or more as viewed from the central dead band (region where the OCV applied current value is A2 or more and A3 or less).
- the delay side velocity linear region (the region where the OCV applied current value is greater than or equal to A1 and less than A2) where the response speed to the retard side of mechanism 2 increases is variable, and is variable when the current value becomes smaller than a predetermined amount as seen from the center dead band.
- the response speed to the retard side of the valve timing mechanism 2 becomes a maximum value and becomes a retard angle speed saturation region (region where the OCV applied current value is less than A1).
- the retarded side of the variable valve timing mechanism 2 until the OC current value increases by a predetermined amount or more as viewed from the central dead band region where the OCV applied current value is A2 or more and A3 or less.
- the advance side velocity linear range region where the OCV applied current value is larger than A3 and A4 or less
- the response speed to becomes larger becomes larger. It is an advance side velocity saturation region (region where the OCV applied current value is larger than A4) where the response speed to the advance side becomes the maximum value and becomes constant.
- variable valve timing mechanism 2 does not move to the advance side or the retard side.
- the response speed of the variable valve timing mechanism 2 is reliably advanced or retarded.
- the duty ratio corresponding to the OCV applied current value in the retard side velocity linear region or the advance side velocity linear region is used.
- the OCV applied current value in the retard side velocity linear region or the advance side velocity linear region is used, considering the product variation of the oil control valve 43, the retard side velocity linear region or the advance side velocity linear region. Among these, it is preferable to use an OCV applied current value that is somewhat distant from the central dead zone.
- the lock key 35a of the advance side intermediate lock mechanism 34 is in contact with the retard side wall surface 47a of the engagement recess 38a. Time is faster. Therefore, there is a possibility that the front end of the lock key 35a hits the retarded side wall surface 47a before it comes out of the engaging recess 38a.
- the second intermediate unlocking is performed. It is advantageous that the response speed of the variable valve timing mechanism 2 in FIG. 2 is slow, and the retarded-side speed linear range or the advanced-side speed linearity is greater than the OCV applied current value in the retarded-side speed saturated region or the advanced-side speed saturated region. It is advantageous to use the OCV applied current value in the region.
- the second intermediate If the response speed of the variable valve timing mechanism 2 at the time of unlocking is made slower than the response speed of the variable valve timing mechanism 2 at the time of releasing the first intermediate lock, the lock key 35b is quickly engaged when the first intermediate lock is released.
- the engagement of the recess 38b can be released, and when the second intermediate lock is released, the engagement of the lock key 35a and the engagement recess 38 can be more reliably released.
- the predetermined time T1 is compared with the predetermined time T1.
- the predetermined times T1 and T2 can be changed according to the operation state. For example, when the water temperature or the oil temperature increases, the response speed of the variable valve timing mechanism 2 becomes relatively fast. In this case, the predetermined times T1 and T2 may be set to be relatively short. .
- the direction of changing the valve timing of the intake valve when the first intermediate lock is released is such that the target value of the valve timing of the intake valve after the release of the intermediate lock in the intermediate lock mechanisms 34a, 34b is relative to the intermediate lock position. Depending on whether it is on the advance side or the retard side, it may be set.
- the setting of the valve timing of the intake valve is set as shown in FIG. 6 according to the operating state, the engine rotation speed becomes higher than the predetermined rotation speed R, and the valve timing of the intake valve is set to the intermediate position.
- the first intermediate lock is performed.
- the valve timing of the intake valve is controlled to be on the more advanced side than the intermediate lock position.
- the valve timing of the intake valve may be controlled so as to be retarded from the intermediate lock position.
- the valve timing of the intake valve is retarded from the intermediate lock position. This can be surely prevented.
- the intermediate lock position of the valve timing of the intake valve Switching from can be performed smoothly.
- the valve timing of the intake valve is set.
- the deviation between the detected value of the intake valve and the target value of the valve timing of the intake valve is large, it is determined that the intermediate lock mechanism 34a, 34b has failed to release the intermediate lock, and the first intermediate lock release is performed.
- the second intermediate lock release may be performed. In this way, even if the intermediate lock mechanism 34a, 34b fails to release the intermediate lock, the intermediate lock can be released again, and the intermediate lock can be reliably released.
- FIG. 7 is a flowchart showing the flow of control in this embodiment described above.
- S15 the oil control valve 43 is controlled for the predetermined time T1 with a duty ratio such that the valve timing of the intake valve is surely advanced from the intermediate lock position.
- S16 the oil control valve 43 is controlled for the predetermined time T2 with a duty ratio such that the valve timing of the intake valve is surely retarded from the intermediate lock position. That is, S15 corresponds to the first intermediate lock release, and S16 corresponds to the second intermediate lock release.
- S17 it is determined whether or not the intermediate lock of the intermediate lock mechanisms 34a and 34b has been released. If it is determined that the intermediate lock has been released, the process proceeds to S18, and the control is switched to normal control in which the valve timing of the intake valve is variably controlled to the valve timing corresponding to the operating state.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
Claims (7)
- カムシャフトと連動して回転する第1ロータと、当該第1ロータと同軸上に配置され、クランクシャフトに連動して回転する第2ロータと、を有し、前記第1ロータ及び前記第2ロータの相対回転位相を運転状態に応じて変更することで機関弁のバルブタイミングを可変する可変バルブタイミング機構と、
所定の中間ロック位置にバルブタイミングを保持する中間ロックが可能な中間ロック機構と、を備えた内燃機関の可変バルブタイミング制御装置において、
前記中間ロック機構は、前記第1ロータ及び前記第2ロータに係合し、バルブタイミングが前記中間ロック位置から進角側に移動することを規制する進角側中間位置保持部材と、バルブタイミングが前記中間ロック位置から遅角側に移動することを規制する遅角側中間位置保持部材と、を有し、
前記中間ロック機構による前記中間ロックを解除する場合、
バルブタイミングを前記中間ロック位置よりも進角側もしくは遅角側に制御して、バルブタイミングを制御した方向とは逆側の移動を規制する一方の中間位置保持部材の前記第1ロータ及び前記第2ロータに対する係合を解除する第1中間ロック解除を行った後、
前記第1中間ロック解除でバルブタイミングを制御した方向とは逆方向にバルブタイミングを制御し、他方の中間位置保持部材の前記第1ロータ及び前記第2ロータに対する係合を解除する第2中間ロック解除を実施する内燃機関の可変バルブタイミング制御装置。 - 前記中間ロックを解除する際には、前記各中間位置保持部材に対して、前記中間ロックを解除する方向に付勢力を作用させる請求項1に記載の内燃機関の可変バルブタイミング制御装置。
- 前記第2中間ロック解除時のバルブタイミングの変化速度を、前記第1中間ロック解除時のバルブタイミングの変化速度よりも遅くする請求項1または2に記載の内燃機関の可変バルブタイミング制御装置。
- 運転状態に変化によりバルブタイミングが前記中間ロック位置から切り替えられる際に、切り替え後のバルブタイミングが前記中間ロック位置よりも遅角側のバルブタイミングとなる場合には、
前記第1中間ロック解除にて、バルブタイミングを前記中間ロック位置よりも進角側に制御し、
前記第2中間ロック解除にて、バルブタイミングを前記中間ロック位置よりも遅角側に制御する請求項1~3のいずれかに記載の内燃機関の可変バルブタイミング制御装置。 - 運転状態に変化によりバルブタイミングが前記中間ロック位置から切り替えられる際に、切り替え後の機関弁のバルブタイミングが前記中間ロック位置よりも進角側にバルブタイミングとなる場合には、
前記第1中間ロック解除にて、バルブタイミングを前記中間ロック位置よりも遅角側に制御し、
前記第2中間ロック解除にて、バルブタイミングを前記中間ロック位置よりも進角側に制御する請求項1~3のいずれかに記載の内燃機関の可変バルブタイミング制御装置。 - 前記中間ロックの解除後に、バルブタイミングの目標値を前記中間ロック位置よりも進角側もしくは遅角側の値とした際に、バルブタイミングの検出値と、バルブタイミングの目標値との偏差が大きい場合には、
前記中間ロックの解除を再度実施する請求項1~5のいずれかに記載の内燃機関の可変バルブタイミング制御装置。 - 前記第2中間ロック解除時にバルブタイミングを進角側もしくは遅角側に制御する期間は、前記第1中間ロック解除時にバルブタイミングを進角側もしくは遅角側に制御する期間よりも長くなるよう設定されている請求項1~6のいずれかに記載の内燃機関の可変バルブタイミング制御装置。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/374,319 US9267398B2 (en) | 2012-02-29 | 2013-02-13 | Variable valve timing control device of internal combustion engine |
CN201380011222.7A CN104136745A (zh) | 2012-02-29 | 2013-02-13 | 内燃机的可变阀定时控制装置 |
EP13755604.9A EP2821623A4 (en) | 2012-02-29 | 2013-02-13 | DEVICE FOR CONTROLLING VARIABLE VALVE SYNCHRONIZATION IN AN INTERNAL COMBUSTION ENGINE |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012042671 | 2012-02-29 | ||
JP2012-042671 | 2012-02-29 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2013129110A1 true WO2013129110A1 (ja) | 2013-09-06 |
Family
ID=49082312
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/053393 WO2013129110A1 (ja) | 2012-02-29 | 2013-02-13 | 内燃機関の可変バルブタイミング制御装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US9267398B2 (ja) |
EP (1) | EP2821623A4 (ja) |
JP (1) | JPWO2013129110A1 (ja) |
CN (1) | CN104136745A (ja) |
WO (1) | WO2013129110A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019069593A1 (ja) * | 2017-10-06 | 2019-04-11 | ボッシュ株式会社 | バルブタイミング制御装置及びバルブタイミング制御方法 |
JP2019105167A (ja) * | 2017-12-08 | 2019-06-27 | アイシン精機株式会社 | 弁開閉時期制御装置 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5978080B2 (ja) * | 2012-09-19 | 2016-08-24 | 日立オートモティブシステムズ株式会社 | 内燃機関のバルブタイミング制御装置及び該バルブタイミング制御装置のコントローラ |
JP6201842B2 (ja) * | 2014-03-19 | 2017-09-27 | アイシン精機株式会社 | 弁開閉時期制御システム |
JP2019199870A (ja) * | 2018-05-18 | 2019-11-21 | アイシン精機株式会社 | 弁開閉時期制御装置 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001055935A (ja) * | 1999-08-17 | 2001-02-27 | Denso Corp | 内燃機関の可変バルブタイミング制御装置 |
JP2002349220A (ja) | 2001-05-21 | 2002-12-04 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
JP2010138732A (ja) * | 2008-12-09 | 2010-06-24 | Denso Corp | 内燃機関の可変バルブタイミング制御装置 |
JP2011179385A (ja) * | 2010-02-26 | 2011-09-15 | Toyota Motor Corp | 流量制御弁及びこれを具備する内燃機関のバルブタイミング制御装置 |
JP2012026271A (ja) * | 2010-07-20 | 2012-02-09 | Mikuni Corp | バルブタイミング変更装置 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100406777B1 (ko) * | 1999-08-17 | 2003-11-21 | 가부시키가이샤 덴소 | 가변밸브 타이밍 제어장치 |
JP4465846B2 (ja) | 2000-09-27 | 2010-05-26 | アイシン精機株式会社 | 弁開閉時期制御装置 |
JP2009133263A (ja) | 2007-11-30 | 2009-06-18 | Toyota Motor Corp | 内燃機関のバルブタイミング制御装置 |
JP5013323B2 (ja) * | 2008-12-09 | 2012-08-29 | 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 |
CN102365428B (zh) * | 2009-04-10 | 2014-04-02 | 丰田自动车株式会社 | 附带中间锁止机构的可变气门正时机构 |
JP5376227B2 (ja) * | 2009-05-25 | 2013-12-25 | アイシン精機株式会社 | 弁開閉時期制御装置 |
JP2011038446A (ja) | 2009-08-07 | 2011-02-24 | Denso Corp | バルブタイミング調整装置 |
JP5534320B2 (ja) | 2010-03-26 | 2014-06-25 | アイシン精機株式会社 | 弁開閉時期制御装置 |
JP2011236781A (ja) * | 2010-05-07 | 2011-11-24 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
-
2013
- 2013-02-13 US US14/374,319 patent/US9267398B2/en not_active Expired - Fee Related
- 2013-02-13 WO PCT/JP2013/053393 patent/WO2013129110A1/ja active Application Filing
- 2013-02-13 CN CN201380011222.7A patent/CN104136745A/zh active Pending
- 2013-02-13 JP JP2014502120A patent/JPWO2013129110A1/ja active Pending
- 2013-02-13 EP EP13755604.9A patent/EP2821623A4/en not_active Withdrawn
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001055935A (ja) * | 1999-08-17 | 2001-02-27 | Denso Corp | 内燃機関の可変バルブタイミング制御装置 |
JP2002349220A (ja) | 2001-05-21 | 2002-12-04 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
JP2010138732A (ja) * | 2008-12-09 | 2010-06-24 | Denso Corp | 内燃機関の可変バルブタイミング制御装置 |
JP2011179385A (ja) * | 2010-02-26 | 2011-09-15 | Toyota Motor Corp | 流量制御弁及びこれを具備する内燃機関のバルブタイミング制御装置 |
JP2012026271A (ja) * | 2010-07-20 | 2012-02-09 | Mikuni Corp | バルブタイミング変更装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2821623A4 * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019069593A1 (ja) * | 2017-10-06 | 2019-04-11 | ボッシュ株式会社 | バルブタイミング制御装置及びバルブタイミング制御方法 |
JPWO2019069593A1 (ja) * | 2017-10-06 | 2020-10-01 | ボッシュ株式会社 | バルブタイミング制御装置及びバルブタイミング制御方法 |
JP2019105167A (ja) * | 2017-12-08 | 2019-06-27 | アイシン精機株式会社 | 弁開閉時期制御装置 |
Also Published As
Publication number | Publication date |
---|---|
US9267398B2 (en) | 2016-02-23 |
JPWO2013129110A1 (ja) | 2015-07-30 |
US20140366825A1 (en) | 2014-12-18 |
EP2821623A4 (en) | 2015-03-25 |
CN104136745A (zh) | 2014-11-05 |
EP2821623A1 (en) | 2015-01-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CA2755884C (en) | Control device for hydraulic variable valve timing mechanism | |
WO2013129110A1 (ja) | 内燃機関の可変バルブタイミング制御装置 | |
JP5929300B2 (ja) | エンジンのバルブタイミング制御装置 | |
JP5916441B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
JP2010270740A (ja) | 弁開閉時期制御装置 | |
JP2019105167A (ja) | 弁開閉時期制御装置 | |
JP5692459B2 (ja) | 内燃機関の可変バルブタイミング制御装置 | |
JP2011001888A (ja) | 内燃機関の制御装置 | |
JP4950949B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
JP4997182B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
WO2015019735A1 (ja) | 弁開閉時期制御装置 | |
WO2015015960A1 (ja) | 弁開閉時期制御装置 | |
JP6254711B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
JP5267263B2 (ja) | 弁開閉時期制御装置 | |
JP6141435B2 (ja) | バルブタイミング調整装置の制御装置 | |
JP6258828B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
WO2013115174A1 (ja) | 内燃機関の可変バルブタイミング制御装置 | |
JP6797342B2 (ja) | バルブタイミング調整装置 | |
JP2018044529A (ja) | 弁開閉時期制御装置 | |
WO2017208312A1 (ja) | 可変動弁装置の制御方法及び可変動弁装置 | |
JP6104392B2 (ja) | バルブタイミング調整装置 | |
JP6201842B2 (ja) | 弁開閉時期制御システム | |
JP6589342B2 (ja) | 弁開閉時期制御装置 | |
JP2018053734A (ja) | 弁開閉時期制御装置 | |
JP2010071165A (ja) | 内燃機関の可変バルブタイミング機構 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 13755604 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2014502120 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14374319 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
REEP | Request for entry into the european phase |
Ref document number: 2013755604 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2013755604 Country of ref document: EP |