EP2305969A1 - Dispositif de commande temporelle d'ouverture/fermeture de soupape - Google Patents

Dispositif de commande temporelle d'ouverture/fermeture de soupape Download PDF

Info

Publication number
EP2305969A1
EP2305969A1 EP10002825A EP10002825A EP2305969A1 EP 2305969 A1 EP2305969 A1 EP 2305969A1 EP 10002825 A EP10002825 A EP 10002825A EP 10002825 A EP10002825 A EP 10002825A EP 2305969 A1 EP2305969 A1 EP 2305969A1
Authority
EP
European Patent Office
Prior art keywords
phase
rotational member
side rotational
spiral spring
closing timing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10002825A
Other languages
English (en)
French (fr)
Other versions
EP2305969B1 (de
Inventor
Masaki Kobayashi
Kenji Ikeda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Publication of EP2305969A1 publication Critical patent/EP2305969A1/de
Application granted granted Critical
Publication of EP2305969B1 publication Critical patent/EP2305969B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs

Definitions

  • This disclosure relates to a valve opening/closing timing control device capable of adjusting the opening/closing timing of the intake valves or exhaust valves of an internal combustion engine used in vehicles such as automobile, and more particularly to a valve opening/closing timing control device including a driving side rotational member synchronously rotatable with a crankshaft, a driven side rotational member arranged coaxially with the driving side rotational member in a relatively rotational manner and integrally rotatable with a camshaft that opens and closes valves of an internal combustion engine, a retarded angle chamber and an advanced angle chamber which are formed by the driving side rotational member and the driven side rotational member, in which the retarded angle chamber moves a relative rotational phase of the driven side rotational member to the driving side rotational member in a retarded angle direction, and the advanced angle chamber moves the relative rotational phase of both rotational members in an advanced angle direction, and a lock mechanism confining the relative rotational phase to a predetermined lock phase, specifically, a technique for
  • JP-A-2000-345816 discloses a valve opening/closing timing control device including a driving side rotational member (a shoe housing in Patent Document 1) and a driven side rotational member (a vane rotor in Patent Document 1), in which an accommodation chamber is divided into two parts, an advanced angle chamber and a retarded angle chamber, by a vane provided on the driven side rotational member.
  • the valve opening/closing timing control device further includes a fitting type restriction means for setting a phase difference between the driving side rotational member and the driven side rotational member to an optimum intermediate position, and a spring as an advanced angle means for rotating the driven side rotational member with respect to the driving side rotational member in the advanced angle direction.
  • a fitting type restriction means for setting a phase difference between the driving side rotational member and the driven side rotational member to an optimum intermediate position
  • a spring as an advanced angle means for rotating the driven side rotational member with respect to the driving side rotational member in the advanced angle direction.
  • One end portion of the spring is locked to a locking hole of the driving side rotational member, and the other end portion of the spring is locked to a locking hole of an elongated hole shape (second embodiment).
  • the driven side rotational member (camshaft side) is more to the retarded angle side than an intermediate position
  • the driven side rotational member is rotated in the direction of the intermediate position by the biasing force of the spring to fit the restriction means, and thus the engine starts up quickly.
  • operating oil is supplied to the restriction means to release the fitting, and the operating oil is supplied to any one of the advanced angle chamber and the retarded angle chamber to achieve a relative rotation between the driving side rotational member and the driven side rotational member.
  • Patent Document 1 when the driven side rotational member is relatively rotated toward the advanced angle side with respect to the driving side rotational member by releasing the fitting of the restriction means, the other end portion of the spring is moved in the engaging hole with the elongated hole shape, so that the biasing force of the spring does not act.
  • a valve opening/closing timing control device disclosed in JP-A-2009-074384 (Patent Document 2; paragraphs [0026] to [0028], and Figs. 3 to 7 ) includes a driving side rotational member and a driven side rotational member, in which an accommodation chamber is divided into two parts, an advanced angle chamber and a retarded angle chamber, by a vane provided on the driven side rotational member.
  • the valve opening/closing timing control device further includes a lock mechanism for fixing and maintaining the driving side rotational member and the driven side rotational member to an intermediate lock phase, and a torsion spring to bias the driving side rotational member and the driven side rotational member in the direction of the intermediate lock phase which generates an assisting force.
  • the torsion spring serves to suppress displacement of the retarded angle side in a region between an intermediate regulation phase which is placed in the direction of the retarded angle phase than the intermediate lock phase, and a most retarded angle phase, and has the role of a stopper at the displacement from the intermediate lock phase to the intermediate regulation phase after the engine starts up.
  • one end portion of the torsion spring is fixed to the driving side rotational member, and the other end portion can abut against an opening formed diametrically in the driven side rotational member.
  • a spring receiving groove to which the other end portion is inserted is formed in the driving side rotational member.
  • the torsion spring is used between the driving side rotational member and the driven side rotational member as the biasing means for biasing the rotational members in the direction of the lock phase from the most retarded angle phase.
  • the number of turns in a coil portion of the torsion spring is required to some degree, thereby causing the whole valve opening/closing timing control device to become larger.
  • the number of turns in the coil portion is required to some degree. Therefore, there is a need for a space in the direction of a shaft core by a dimension corresponding to the number of turns, which causes the whole valve opening/closing timing control device to become larger.
  • a valve opening/closing timing control device including a driving side rotational member synchronously rotatable with a crankshaft of an internal combustion engine, a driven side rotational member arranged coaxially with the driving side rotational member in a relatively rotational manner and integrally rotatable with a camshaft that opens and closes valves of the internal combustion engine, a retarded angle chamber and an advanced angle chamber which are formed by the driving side rotational member and the driven side rotational member, in which the retarded angle chamber moves a relative rotational phase of the driven side rotational member to the driving side rotational member in a retarded angle direction in accordance with volume increase, and the advanced angle chamber moves the relative rotational phase in an advanced angle direction in accordance with volume increase, a lock mechanism confining the relative rotational phase to a predetermined lock phase, and a spiral spring providing a biasing force in a predetermined phase direction in a retarded angle region of the relative rotational phase from a most retard
  • the relative rotational phase of the driven side rotational member to the driving side rotational member is at the predetermined lock phase, but is not necessary at the predetermined lock phase.
  • it may be at the retarded angle region side near the predetermined lock phase or at the advanced angle region side near the predetermined lock phase, on the basis of the predetermined lock phase. That is, at the time of starting of the internal combustion engine, if the relative rotational phase of the driven side rotational member to the driving side rotational member is in a predetermined region including the predetermined lock phase, proper starting is achieved.
  • the relative rotational phase acts in the predetermined phase direction by the biasing force of the spiral spring, so that the relative rotational phase is early moved in the predetermined phase direction to enhance the starting ability of the internal combustion engine. Further, in a case in which the relative rotational phase is more towards the advanced angle region than the predetermined phase, the biasing force of the spiral spring does not act. In particular, since no space corresponding to the coil portion of the torsion spring is required by using the spiral spring, it is possible to suppress the device from becoming larger. As a result, the valve opening/closing timing control device can be compactly configured without impairing the function of biasing the driving side rotational member and the driven side rotational member in the predetermined phase direction from the most retarded angle phase.
  • the aspect this disclosure may include the spiral spring providing the biasing force in the predetermined lock phase direction in the retarded angle region of the relative rotational phase from the most retarded angle phase to the predetermined lock phase, and not providing the biasing force to the most advanced angle phase from the predetermined lock phase.
  • the relative rotational phase acts in the predetermined lock phase direction as the predetermined phase by the biasing force of the spiral spring, so that the relative rotational phase is maintained early to the predetermined lock phase to enhance the starting ability of the internal combustion engine. Further, in a case in which the relative rotational phase is in the advanced angle region than the predetermined lock phase, the biasing force of the spiral spring does not act.
  • the outer circumference of a shaft-shaped body which rotates integrally with the driven side rotational member is provided with an engaging concave portion having a region distance corresponding to the advanced angle region from the predetermined lock phase to the most advanced angle phase.
  • An engaging portion formed by bending an inner end portion of the spiral spring is engaged to the engaging concave portion, and a support portion of an outer end portion of the spiral spring is supported by a support body which rotates integrally with the driving side rotational member.
  • the engaging portion is biased in a direction of engaging the engaging concave portion by the spiral spring.
  • the biasing force can act to rotate the driven side rotational member in the predetermined lock phase direction in a case in which the relative rotational phase of the driven side rotational member to the driving side rotational member is in the retarded angle region. Further, in a case in which the relative rotational phase of the driven side rotational member to the driving side rotational member is in the advanced angle phase, the free rotation of the driven side rotational member is allowed.
  • the engaging portion since the engaging portion is biased in a direction of a shaft core, it does not lead to problems in which the engaging portion becomes released from the engaging concave portion.
  • the aspect of this disclosure may include a regulation piece to restrict displacement of the engaging portion in the direction of the advanced angle region by abutment of the engaging portion.
  • the aspect of this disclosure may include a suppression piece to suppress displacement of the engaging portion in the direction in which the spiral spring bulges.
  • the suppression piece suppresses displacement of the engaging portion of the spiral spring in a releasing direction from the engaging concave portion, it does not lead to problems of the engaging portion releasing from the engaging concave portion.
  • the support portion is formed in a concave surface which is concave in the center direction of the spiral spring, and the support body is formed in a protruding surface which fits into the concave surface.
  • the concave surface and the engaging portion may be disposed at a position in which a spring body is sandwiched in a radial direction.
  • Fig. 1 is a cross-sectional view illustrating a valve opening/closing timing control device including an electromagnetic control valve
  • Figs. 2A and 2B are cross-sectional views taken along the line IIa-IIa and the line IIb-IIb in Fig. 1 in a most retarded angle phase;
  • Figs. 3A and 3B are cross-sectional views illustrating an outer rotor and an inner rotor at a lock phase, and a spiral spring at the lock phase;
  • Figs. 4A and 4B are cross-sectional views illustrating the outer rotor and the inner rotor at a most advanced angle phase, and the spiral spring at the most advanced angle phase;
  • Fig. 5 is a perspective view illustrating the shape of the spiral spring.
  • a valve opening/closing timing control device includes an outer rotor 1 serving as a driving side rotational member and synchronously rotatable with a crankshaft (not shown) of an engine (an internal combustion engine), an inner rotor 2 serving as a driven side rotational member and coaxially and synchronously rotatable with a camshaft 3 which opens and closes an intake valve or an exhaust valve in a combustion chamber of the engine, and an electromagnetic control valve V.
  • the valve opening/closing timing control device includes a configuration in which the inner rotor 2 (driven side rotational member) is inserted in the outer rotor 1 (driving rotational member). Consequently, the outer rotor 1 and the inner rotor 2 can be relatively freely rotated around a core X of a rotational shaft in the range of a predetermined relative rotational phase.
  • a fluid pressure chamber is formed between the outer rotor 1 and the inner rotor 2, the fluid pressure chamber is partitioned into a retarded angle chamber 11 and an advanced angle chamber 12 by a vane 5 installed therein.
  • the vane 5 is inserted into a vane groove formed in the outer circumference of the inner rotor 2, and is biased in a protruding direction by a leaf spring. Consequently, at the time of relative rotation of the outer rotor 1 and the inner rotor 2, an outer end portion of the vane 5 is slidable on an inner surface of the outer rotor in the fluid pressure chamber.
  • the camshaft 3 is coaxially arranged with the core X of the rotational shaft.
  • the camshaft 3 is connected to the inner rotor 2 by a connecting bolt 4.
  • a front plate 6 is placed on one surface of the outer rotor 1, and a rear plate 7 is placed on the other surface of the outer rotor 1.
  • the front plate 6 and the rear plate 7 are fixed to the outer rotor 1 by a plurality of fixing bolts 8. With the configuration, the inner rotor 2 is interposed between the front plate 6 and the rear plate 7.
  • the front plate 6 includes a spiral spring S to provide a biasing force on the outer rotor 1 (driving side rotational member) and the inner rotor 2 (driven side rotational member), and a cover 9 to cover the spiral spring.
  • the detailed configuration of the spiral spring S will be described below.
  • a timing sprocket 7S is integrally installed on the outer circumference of the rear plate 7. Between the timing sprocket 7S and a gear attached to the crankshaft of the engine, there is provided a power transmission member (not shown) such as a timing chain or a timing belt.
  • a rotational driving force of the crankshaft is transmitted to the timing sprocket 7S through the power transmission member, and the outer rotor 1 rotates in a rotational direction T shown in Fig. 2A or the like.
  • the camshaft 3 rotates, and the intake valve or the exhaust valve of the engine is opened or closed by the driving rotation of a cam (not shown) provided on the camshaft 3.
  • valve opening/closing timing control device when the engine operates, if the advanced angle chamber 12 is supplied with operating oil, the volume of the advanced angle chamber 12 is enlarged by the pressure acting on the vane 5, and thus the inner rotor 2 is moved in a direction denoted by an arrow T1 with respect to the outer rotor 1. Consequently, the relative rotational phase of the outer rotor 1 and the inner rotor 2 is shifted in the advanced angle direction.
  • the retarded angle chamber 11 is supplied with the operating oil, the volume of the retarded angle chamber 11 is enlarged by the pressure acting on the vane 5 in an adverse direction, and thus the inner rotor 2 is moved in a direction denoted by an arrow T2 with respect to the outer rotor 1.
  • the opening and closing timing of the intake vale or exhaust valve is controlled by changing a rotational phase of the camshaft 3 with respect to the rotational phase of the crankshaft.
  • the valve opening/closing timing control device includes a lock mechanism L to maintain the relative rotational phase between the outer rotor 1 and the inner rotor 2 at a lock phase suitable for the start-up of the engine.
  • the lock mechanism L restricts the relative rotation between the outer rotor 1 and the inner rotor 2 when the relative rotational phase between the outer rotor 1 and the inner rotor 2 becomes the predetermined phase, i.e., the predetermined lock phase.
  • the lock mechanism L confines (locks) the outer rotor 1 and the inner rotor 2 at a set relative rotational phase in circumstances in which the pressure of the operating oil is an unstable state immediately after the start-up of the engine. Therefore, the rotational phase of the camshaft 3 with respect to the rotational phase of the crankshaft is maintained at a phase suitable for the start-up of the engine, thereby providing the stable start-up of the engine.
  • the lock mechanism L is constituted of a pair of lock pieces 14 of a plate shape extendable and withdrawing freely to and from the outer rotor 1, a spring 15 biasing each of the lock pieces 14 in a protruding direction (direction of the inner rotor 2), and a pair of lock concave portions 16 formed on the outer circumferential portion of the inner rotor 2 in a concave shape so as to be engaged to each of the lock pieces 14.
  • a pin shape may be employed, as well as the plate shape shown in this embodiment.
  • the inner rotor 2 is provided with a retarded angle chamber side oil passage 11a through which the operating oil is distributed to a plurality of retarded angle chambers 11, an advanced angle chamber side oil passage 12a through which the operating oil is distributed to a plurality of advanced angle chambers 12, and a lock release oil passage 16a through which the operating oil is distributed to the lock concave portion 16.
  • the cam shaft 3 is fitted with a bush 18, and the bush 18 is relatively rotated with respect to the camshaft 3.
  • the operating oil supplied from a hydraulic pump P to the supply oil passage 18a is supplied to a cylindrical space 2S of the inner rotor 2 by the oil passage system.
  • the operating oil supplied to the inner rotor 2 is supplied to the retarded angle chamber side oil passage 11a, the advanced angle chamber side oil passage 12a, and the lock release oil passage 16a by the electromagnetic control valve V, and is discharged from the retarded angle chamber side oil passage 11a, the advanced angle chamber side oil passage 12a and the lock release oil passage 16a by the electromagnetic control valve V.
  • the electromagnetic control valve V includes an operating oil control portion Va having a spool valve 22 which is operated by an electromagnetic solenoid 21, and an operating oil supply/discharge portion Vb of a cylindrical shape to perform distribution of the operating oil, in which the operating oil control portion and the operating oil supply/discharge portion are integrally formed.
  • the operating oil supply/discharge portion Vb includes a check valve C provided in a main oil passage 23 to receive the operating oil from the above-described inner oil passage 2a.
  • three ports 24, 25 and 26 are formed in a groove shape, in which the distribution of the operating oil is controlled by the spool valve 22.
  • An oil seal 27 is fitted from outside on the outer circumference of the operating oil supply/discharge portion Vb to suppress leakage of the operating oil from each of the ports 24, 25 and 26.
  • the above-described cylindrical space 2S is formed in the inner rotor 2 so as to form a cylindrical shape around the core X of the rotational shaft, and the above-described operating oil supplying/discharging portion Vb of the electromagnetic control valve V is relatively rotatably fitted in the cylindrical space 2S.
  • the retarded angle chamber side oil passage 11a, the advanced angle chamber side oil passage 12a and the lock release oil passage 16a are in communication with the ports 24, 25 and 26 in the figure, but the relative disposition of the oil passages is not limited thereto.
  • a gap is formed between the inner rotor 2 and the front plate 6 and between the inner rotor 2 and the rear plate 7, in which the operating oil slightly leaks there through.
  • the operating oil slightly leaks through the other movable portion.
  • the leaked operating oil is collected by an oil pan (not shown).
  • control system of the valve opening/closing timing control device includes a crank angle sensor detecting the rotational angle of the crankshaft of the engine, a camshaft angle sensor detecting the rotational angle of the camshaft 3, and an ECU (not shown) controlling the electromagnetic control valve V
  • the ECU is provided with a signal system acquiring ON/OFF information of an ignition key, information from an oil temperature sensor detecting the temperature of the engine oil, or the like, and control information of the optimum relative rotational phase according to the driving state of the engine is stored in a nonvolatile memory.
  • the ECU detects the relative phase of the outer rotor 1 and the inner rotor 2 based on information of the driving state (e.g., revolutions of engine, temperature of cooling water or the like) and the detected result of the above-described crank angle sensor and camshaft angle sensor.
  • the distribution of the operating oil to the retarded angle chamber side oil passage 11a, the advanced angle chamber side oil passage 12a and the lock release oil passage 16a is performed by operating the electromagnetic control valve V based on the information, thereby controlling the relative rotational phase of the outer rotor 1 and the inner rotor 2.
  • the phase control is achieved between the most retarded angle phase (relative rotational phase in which the volume of the retarded angle chamber 11 is maximized) and the most advanced angle phase (relative rotational phase in which the volume of the advanced angle chamber 12 is maximized), and the lock state and the unlock state by the lock mechanism L are achieved.
  • the ECU moves the relative phase of the outer rotor 1 and the inner rotor 2 in the lock phase direction by supplying the operating oil to the retarded angle chamber 11 or the advanced angle chamber 12 in a state in which the operating oil is discharged from the lock release oil passage 16a. Consequently, the engine stops in a state in which the pair of lock pieces 14 is engaged to the pair of the corresponding lock concave portions 16.
  • the engine starts up reliably by confining (restricting) the outer rotor 1 and the inner rotor 2 with the lock mechanism L to hold the relative rotation (to the predetermined lock phase).
  • the ECU After the start-up of the engine, the ECU supplies the operating oil to the lock release oil passage 16a to lift the lock pieces 14 up from the lock concave portions 16 to thereby release the lock.
  • the ECU changes the relative phase of the outer rotor 1 and the inner rotor 2 in a state in which the pressure of the operating oil acts on the lock release oil passage 16a, so that the control of the opening and closing timing of the intake valve and the exhaust valve is performed by the ECU.
  • the above-described spiral spring S has a function of providing the biasing force in the lock phase direction (direction of the predetermined phase) with respect to the inner rotor 2. Therefore, a problem in which the relative phase of the inner rotor 2 integrally rotating with the camshaft 3 is retarded with respect to the rotation of the outer rotor 1 since the camshaft 3 receives resistance from the valve spring is solved.
  • the inner rotor 2 may reach the most retarded angle phase with respect to the outer rotor 1.
  • the ECU controls the phase of the inner rotor 2 with respect to the outer rotor 1 to move to the lock phase early and thus set the phase in a lock state so as to perform reliable start-up of the engine.
  • the electromagnetic control valve V discharges the operating oil from the lock release oil passage 16a, discharges the operating oil from the retarded angle side oil passage 11a and supplies the operating oil to the advanced angle chamber side oil passage 12a by the control of the ECU, so that the inner rotor 2 with respect to the outer rotor 1 is moved in the lock phase direction.
  • the lock pieces 14 are engaged to the lock concave portions 16 at the timing in which the outer rotor 1 and the inner rotor 2 reach the lock phase, so that the lock mechanism L is in the lock state.
  • the rotational phase of the most retarded angle phase in which the inner rotor 2 is disposed at the most retarded angle side, is referred to as a super-retarded angle phase.
  • the time is needed until the relative rotational phase reaches the lock phase, so that the start-up of the engine is not smoothly performed.
  • the operating oil is cold at the time of stopping the engine in cold climates, the viscosity of the operating oil is high, and thus the distribution of the operating oil to each of the retarded angle chamber 11 and the advanced angle chamber 12 is not smoothly performed. For this reason, the start-up of the engine is not smoothly performed.
  • it is aimed to shorten the time required to reach the lock phase by assisting the relative movement of the outer rotor 1 and the inner rotor 2 in the direction of the lock phase by the above-described spiral spring S.
  • the spiral spring S operates to bias the relative rotational phase of the inner rotor 2 (driven side rotational member) with respect to the outer rotor 1 (driving side rotational member) in the direction of the lock phase in a retarded angle region A from the most retarded angle phase to the lock phase.
  • the spiral spring S operates so as not to provide the biasing force in an advanced angle region B from the lock phase to the most advanced angle phase. In this instance, it is not necessary for the spiral spring S to provide the biasing force in the direction of the lock phase in the whole area of the retarded angle region A.
  • the biasing force may act from the super-retarded angle phase to near the lock phase, or the biasing force may act in the advanced angle side on the basis of the lock phase to the advanced angle region A near the lock phase.
  • the phase on which the biasing force of the spiral spring S acts is the predetermined phase of the embodiment disclosed here and thus becomes a proper phase (region) suitable for the start-up of the engine (internal combustion engine).
  • the spiral spring S is formed in a spiral shape from a strap of spring material, the thickness (dimension of the rotational shaft in the direction of core X) can be thinned as compared with one including a coil portion such as a torsion spring. In a case where the spiral spring S is installed, since a large space is not required in the direction of the core X of the rotational shaft, it is possible to downsize the valve opening/closing timing control device.
  • the outer circumference of an axial portion 10 (one example of the axial body) of the inner rotor 2 is provided with an engaging concave portion 10G having an opening width (opening width in a circumferential direction) of a region distance corresponding the advanced angle region B.
  • the front plate 6 connected to the outer rotor 1 is provided with a protruding surface 6T protruding in the direction of the core X of the rotational shaft.
  • the spiral spring S has a spring body 30 of a spiral shape.
  • An engaging portion 31 is formed by bending the inner end portion of the spiral spring and is engaged to the engaging concave portion 10G, and a concave surface 32 (one example of the support portion) is formed on an outer end portion of the spiral spring in a concaved shape in a center direction (core X of the rotational shaft) of the spiral spring S so that the protruding surface 6T (one example of the support body) is inserted into the concave surface.
  • the front plate 6 is provided with a suppression piece 33 constituted of a pin which abuts against the engaging portion 31 to suppress a displacement of the engaging portion 31 in the direction of the advanced angle region B.
  • the front plate 6 is provided with a suppression piece 34 constituted of a pin which abuts against an adjacent portion of the engaging portion 31 of the spiral spring S to suppress a displacement of the engaging portion 31 in a direction in which the diameter of the spiral spring S is bulged.
  • the engaging portion 31 and the concave surface 32 described above are positioned in a position to which the spring body 30 is sandwiched.
  • the spiral spring S is set in such a manner that the distance from the engaging portion 31 to the concave surface 32 is slightly longer than that from the engaging concave portion 10G to the protruding surface 6T in a no-load free state.
  • spacers 35 are inserted into a gap of the spring body 30 in the vicinity of the outer circumference of the spiral spring S.
  • the above-described biasing force is obtained by compressing the spring body 30 in a radial direction so as to shorten the distance of the engaging portion 31 and the concave surface 32 slightly when the spiral spring S is set. Consequently, the engaging portion 31 is biased in a direction (direction of the core X of the rotational shaft) of fitting it into the engaging concave portion 10G by the resilient force of the spring body 30. Simultaneously, the concave surface 32 is biased in a direction of pressing it against the protruding surface 6T. Further, the appropriate gap is formed in the spring body 30 by the spacers 35. Therefore, both ends of the spiral spring S can be supported reliably and the biasing force can provide between the outer rotor 1 and the inner rotor 2 reliably.
  • the biasing force of the spiral spring S is provided on the outer rotor 1 and the inner rotor 2 continuously through the protruding surface 6T and the axial portion 10 until reaching the lock phase.
  • the engaging portion 31 abuts against the regulation piece 33, as shown in Fig. 3B .
  • the region, on which the biasing force of the spiral spring S acts, corresponds to the retarded angle region A.
  • the relative rotational phase reaches the lock phase and the engaging portion 31 abuts against the regulation piece 33, the biasing force of the spiral spring S does not act on the axial portion 10. Further, the lock pieces 14 of the lock mechanism L fit into the lock concave portions 16 to reach the lock state, the stable start-up of the engine is achieved. Since the engaging portion 31 of the spiral spring S abuts against the suppression piece 34, it is possible to suppress the displacement of the spiral spring S in the bulging direction, so that the engaging portion 31 is not released from the engaging concave portion 10G.
  • the outer end portion of the spiral spring S may be formed to have a support structure in such a manner that the front plate 6 is provided with a concave portion or a hole for engagement, and the outer end portion of the spiral spring S is bent to be engaged to the concave portion or the hole.
  • the configuration may be formed in such a manner that a pin or the like serving as the engaging portion 31 protrudes from the inner end portion of the spiral spring S to be engaged to the engaging concave portion 10G.
  • valve opening/closing timing control device includes the spiral spring S to bias the relative rotational phase of the outer rotor 1 and the inner rotor 2 in the lock phase direction, the space corresponding to the coil portion such as the torsion spring is not required, thereby suppressing the device from becoming larger.
  • the spiral spring S applies the biasing force in the lock phase direction at the relative rotational phase only in a case where the relative rotational phase of the inner rotor 2 (driven side rotational member) to the outer rotor 1 (driving side rotational member) is in the retarded angle region A from the most retarded angle phase to near the lock phase. Consequently, if the engine starts up in the state in which the relative rotational phase of the inner rotor 2 to the outer rotor 1 is at the most retarded angle phase, the movement of the inner rotor 2 with respect to the outer rotor 1 is assisted until reaching the lock phase.
  • the embodiment disclosed here can be used in the whole valve opening/closing timing control devices capable of setting opening and closing timing of any one of an intake valve and an exhaust valve of an engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP10002825A 2009-09-28 2010-03-17 Dispositif de commande temporelle d'ouverture/fermeture de soupape Not-in-force EP2305969B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2009222386A JP5516937B2 (ja) 2009-09-28 2009-09-28 弁開閉時期制御装置

Publications (2)

Publication Number Publication Date
EP2305969A1 true EP2305969A1 (de) 2011-04-06
EP2305969B1 EP2305969B1 (de) 2012-06-20

Family

ID=43303982

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10002825A Not-in-force EP2305969B1 (de) 2009-09-28 2010-03-17 Dispositif de commande temporelle d'ouverture/fermeture de soupape

Country Status (4)

Country Link
US (1) US20110073056A1 (de)
EP (1) EP2305969B1 (de)
JP (1) JP5516937B2 (de)
CN (1) CN102032011B (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013046474A1 (en) * 2011-09-26 2013-04-04 Aisin Seiki Kabushiki Kaisha Valve timing controller
EP2666979A3 (de) * 2012-05-25 2016-01-20 Aisin Seiki Kabushiki Kaisha Vorrichtung zur Steuerung der Ventilsteuerzeiteinstellung
GB2530123A (en) * 2014-09-10 2016-03-16 Hitachi Automotive Systems Ltd Variable valve timing control apparatus of internal combustion engine
EP3109422A3 (de) * 2015-06-26 2017-01-11 Hyundai Motor Company Drehrichtungssteuerungsvorrichtung von cvvt

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5447436B2 (ja) * 2011-05-20 2014-03-19 株式会社デンソー バルブタイミング調整装置
JP5738076B2 (ja) * 2011-05-31 2015-06-17 株式会社ミクニ バルブタイミング変更装置
JP5500393B2 (ja) * 2011-08-08 2014-05-21 株式会社デンソー バルブタイミング調整装置
JP5333544B2 (ja) * 2011-08-08 2013-11-06 株式会社デンソー 液圧式バルブタイミング調整装置
JP5382086B2 (ja) 2011-10-25 2014-01-08 株式会社デンソー 液圧式バルブタイミング調整装置
DE102012200683B4 (de) * 2012-01-18 2017-01-26 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102012206567B4 (de) * 2012-04-20 2024-09-26 Schaeffler Technologies AG & Co. KG Federaufhängung eines hydraulischen Nockenwellenverstellers
JP6040601B2 (ja) * 2012-07-12 2016-12-07 アイシン精機株式会社 弁開閉時期制御装置
JP5966781B2 (ja) * 2012-09-06 2016-08-10 アイシン精機株式会社 弁開閉時期制御システム
JP6091115B2 (ja) * 2012-09-07 2017-03-08 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その製造方法
JP5661725B2 (ja) * 2012-12-13 2015-01-28 サンコール株式会社 ぜんまいばね
JP5946781B2 (ja) * 2013-02-06 2016-07-06 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
JP5920632B2 (ja) * 2013-02-07 2016-05-18 株式会社デンソー バルブタイミング調整装置
DE102014216119A1 (de) * 2013-08-22 2015-02-26 Schaeffler Technologies Gmbh & Co. Kg Verfahren und Vorrichtung zum Wickeln einer Rückstellfeder mit einem zweiteiligen Rotor für einen Nockenversteller
DE102017111385A1 (de) 2017-05-24 2018-04-05 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit Druckentlastungsschaltstellung
CN110662888B (zh) * 2017-06-01 2021-07-27 三菱电机株式会社 配气正时调节装置
JP6779423B2 (ja) * 2018-09-05 2020-11-04 三菱電機株式会社 バルブタイミング調整装置
CN112901304B (zh) * 2021-02-04 2022-05-13 浙江吉利控股集团有限公司 控制机油控制阀系统流量的方法及机油控制阀系统
US11560816B1 (en) 2021-07-16 2023-01-24 Schaeffler Technologies AG & Co. KG Spring retainer retention tab for bias spring
US11946395B2 (en) 2022-02-11 2024-04-02 Borgwarner Inc. Variable cam timing phaser

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19854891A1 (de) * 1997-11-28 1999-06-10 Aisin Seiki Ventilzeitsteuervorrichtung
DE19903624A1 (de) * 1998-01-30 1999-08-12 Aisin Seiki Variabler Ventilsteuerzeitenregler
WO2005049976A1 (de) 2003-11-21 2005-06-02 Schaeffler Kg Hydraulischer nockenwellenversteller und verfahren zum betreiben desselben
US20070277757A1 (en) 2006-06-06 2007-12-06 Fischer Thomas H Vane-type cam phaser having bias spring system to assist intermediate position pin locking
US20090188456A1 (en) 2008-01-30 2009-07-30 Schaeffler Kg Camshaft adjusting device
US20090211549A1 (en) 2008-02-21 2009-08-27 Schaeffler Kg Cam phase adjuster with a plurality of springs

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5165150U (de) * 1974-11-15 1976-05-22
DE10007200A1 (de) * 2000-02-17 2001-08-23 Schaeffler Waelzlager Ohg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
JP2003120229A (ja) * 2001-10-05 2003-04-23 Hitachi Unisia Automotive Ltd 内燃機関のバルブタイミング制御装置
DE10351223B4 (de) * 2003-10-28 2010-02-18 Hydraulik-Ring Gmbh Nockenwellenverstelleinrichtung für Fahrzeuge, vorzugsweise für Kraftfahrzeuge
US7363897B2 (en) * 2006-06-06 2008-04-29 Delphi Technologies, Inc. Vane-type cam phaser having bias spring system to assist intermediate position pin locking
JP4238903B2 (ja) * 2006-09-13 2009-03-18 株式会社日立製作所 内燃機関用カム軸位相可変装置および位相可変装置
JP5046015B2 (ja) * 2007-09-19 2012-10-10 アイシン精機株式会社 弁開閉時期制御装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19854891A1 (de) * 1997-11-28 1999-06-10 Aisin Seiki Ventilzeitsteuervorrichtung
DE19903624A1 (de) * 1998-01-30 1999-08-12 Aisin Seiki Variabler Ventilsteuerzeitenregler
WO2005049976A1 (de) 2003-11-21 2005-06-02 Schaeffler Kg Hydraulischer nockenwellenversteller und verfahren zum betreiben desselben
US20070277757A1 (en) 2006-06-06 2007-12-06 Fischer Thomas H Vane-type cam phaser having bias spring system to assist intermediate position pin locking
US20090188456A1 (en) 2008-01-30 2009-07-30 Schaeffler Kg Camshaft adjusting device
US20090211549A1 (en) 2008-02-21 2009-08-27 Schaeffler Kg Cam phase adjuster with a plurality of springs

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013046474A1 (en) * 2011-09-26 2013-04-04 Aisin Seiki Kabushiki Kaisha Valve timing controller
US9151190B2 (en) 2011-09-26 2015-10-06 Aisin Seiki Kabushiki Kaisha Valve timing controller
EP2666979A3 (de) * 2012-05-25 2016-01-20 Aisin Seiki Kabushiki Kaisha Vorrichtung zur Steuerung der Ventilsteuerzeiteinstellung
GB2530123A (en) * 2014-09-10 2016-03-16 Hitachi Automotive Systems Ltd Variable valve timing control apparatus of internal combustion engine
US9506378B2 (en) 2014-09-10 2016-11-29 Hitachi Automotive Systems, Ltd. Variable valve timing control apparatus of internal combustion engine
EP3109422A3 (de) * 2015-06-26 2017-01-11 Hyundai Motor Company Drehrichtungssteuerungsvorrichtung von cvvt

Also Published As

Publication number Publication date
CN102032011A (zh) 2011-04-27
US20110073056A1 (en) 2011-03-31
EP2305969B1 (de) 2012-06-20
JP5516937B2 (ja) 2014-06-11
CN102032011B (zh) 2014-01-29
JP2011069316A (ja) 2011-04-07

Similar Documents

Publication Publication Date Title
EP2305969B1 (de) Dispositif de commande temporelle d'ouverture/fermeture de soupape
EP2302177B1 (de) Vorrichtung zur variablen Steuerung der Ventilöffnungs-/Schließungszeit
US8418664B2 (en) Variable valve timing control apparatus
JP5582363B2 (ja) 弁開閉時期制御装置
US8522734B2 (en) Valve timing control device
EP2343438B1 (de) Nockenwellenversteller
US6263843B1 (en) Valve timing control device of internal combustion engine
US9708939B2 (en) Valve open/close timing control device
US9447710B2 (en) Variable valve timing control device
US6994062B2 (en) Variable valve timing control device
US9423011B2 (en) Variable valve timing control apparatus
US10422254B2 (en) Variable valve timing control device
US6701878B2 (en) Variable valve timing device
US11255227B2 (en) Valve opening and closing timing control device
US11408309B2 (en) Valve opening and closing timing control device
JP6102188B2 (ja) 弁開閉時期制御装置
US20210172346A1 (en) Valve opening and closing timing control device
JP4371186B2 (ja) 弁開閉時期制御装置
JP5022327B2 (ja) 内燃機関の可変バルブタイミング機構
JP4573127B2 (ja) 弁開閉時期制御装置
JP6102189B2 (ja) 弁開閉時期制御装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

AX Request for extension of the european patent

Extension state: AL BA ME RS

17P Request for examination filed

Effective date: 20110830

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: AISIN SEIKI KABUSHIKI KAISHA

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KOBAYASHI, MASAKI

Inventor name: IKEDA, KENJI

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 563194

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120715

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602010001866

Country of ref document: DE

Effective date: 20120816

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120920

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20120620

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 563194

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120620

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

Effective date: 20120620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120921

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121020

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121022

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121001

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

26N No opposition filed

Effective date: 20130321

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602010001866

Country of ref document: DE

Effective date: 20130321

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120920

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130331

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20140317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140331

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140331

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120620

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20100317

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130317

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20200303

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20200214

Year of fee payment: 11

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602010001866

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210331

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20211001