EP2428656B1 - Vorrichtung zur Regelung der variablen Ventilsteuerzeit - Google Patents

Vorrichtung zur Regelung der variablen Ventilsteuerzeit Download PDF

Info

Publication number
EP2428656B1
EP2428656B1 EP11179376.6A EP11179376A EP2428656B1 EP 2428656 B1 EP2428656 B1 EP 2428656B1 EP 11179376 A EP11179376 A EP 11179376A EP 2428656 B1 EP2428656 B1 EP 2428656B1
Authority
EP
European Patent Office
Prior art keywords
inner rotor
cam shaft
intermediate member
control apparatus
variable valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP11179376.6A
Other languages
English (en)
French (fr)
Other versions
EP2428656A1 (de
Inventor
Kazunari Adachi
Yuji Noguchi
Takeo Asahi
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 EP2428656A1 publication Critical patent/EP2428656A1/de
Application granted granted Critical
Publication of EP2428656B1 publication Critical patent/EP2428656B1/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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location 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
    • F01L2001/34483—Phaser return springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2301/00—Using particular materials

Definitions

  • This disclosure generally relates to a variable valve timing control apparatus.
  • a known variable valve timing control apparatus (cam timing device for an internal combustion engine) is disclosed in JP3965051B (hereinafter referred to as Reference 1).
  • an inner rotor inner body in Reference 1
  • a shaft member such as a bolt (clamping screw in Reference 1).
  • Two passages are formed between the inner rotor and the cam shaft so as to be positioned away from each other in an axial direction (a rotational axis) of the cam shaft.
  • the inner rotor and the shaft member need to be made of materials having the approximately same linear expansion coefficients in order to inhibit oil supplied to the variable valve timing control apparatus form leaking therefrom to the outer side. Meanwhile, a threaded portion of the shaft member is required to have a sufficient strength. Therefore, the shaft member is generally made of a high-strength material. For example, in a case where the shaft member is being inserted into a central bore of the inner rotor so as to be screwed with the cam shaft, the inner rotor needs to be inhibited from being damaged by the high-strength material of the shaft member.
  • variable valve timing control apparatuses are known from DE 10 2008 057 492 A1 , DE 10 2008 050 134 A1 , DE 10 2008 030 057 A1 , DE 10 2007 020 526 A1 and US 2010/0175651 A1 .
  • the inner rotor does not need to be made of the high-strength material as long as the inner rotor is inhibited from being damaged by the shaft member. Utilization of the high-strength material to form the inner rotor makes further processing of the inner rotor difficult. In addition, the weight and cost of the inner rotor may increase.
  • variable valve timing control apparatus including an internal rotor, which does not need to be made of a high-strength material.
  • a variable valve timing control apparatus includes a housing rotating in synchronization with a drive shaft of an internal combustion engine and including an outer rotor, an inner rotor arranged coaxially with the housing and rotatable relative to the housing, a cam shaft to which the rotation of the inner rotor is transmitted, an intermediate member press-fitted to the cam shaft, arranged between the inner rotor and the cam shaft along a rotational axis of the cam shaft and rotating in synchronization with the inner rotor and the cam shaft, a first hydraulic fluid passage, an inner room formed between the cam shaft and the inner rotor, inhibiting the inner rotor from being in contact with the cam shaft, and constituting a portion of the first hydraulic fluid passage, a second hydraulic fluid passage, a passage formed in the intermediate member and constituting a portion of the second hydraulic fluid passage, and a contact portion at which an axial surface of the intermediate member is entirely in contact with the inner rotor between the first hydraulic fluid passage and the second hydraulic fluid passage along the rotational
  • variable valve timing control apparatus the inner room constituting a portion of the first hydraulic fluid passages is arranged between the inner rotor and the cam shaft, therefore inhibiting the inner rotor from being in contact with the cam shaft. Accordingly, even in a case where the cam shaft is made of a high-strength material, the inner rotor does not need to be made of a high-strength material in order to inhibit the inner rotor from being damaged by a contact with the cam shaft.
  • the variable valve timing control apparatus includes the contact portion at which the axial surface of the intermediate member is entirely in contact with the inner rotor between the first hydraulic fluid passage and the second hydraulic fluid passage along the rotational axis of the cam shaft.
  • the cam shaft may be a bolt for fixing the inner rotor to the cam shaft.
  • the cam shaft may be a different member instead of the bolt.
  • the intermediate member is made of a material having a linear expansion coefficient that is close to or equal to a linear expansion coefficient of a material of the cam shaft rather than a linear expansion coefficient of a material of the inner rotor.
  • a clearance defined between the intermediate member and the cam shaft in an assembled state is recommended to be maximally reduced while allowing the driven shaft to axially penetrate through the intermediate member, in order that the leakage of the hydraulic fluid from the clearance may be minimized.
  • the variable valve timing control apparatus is actually brought in operation and thereafter reaches a high temperature. In such case, the larger a difference between the linear expansion coefficient of the intermediate member and the linear expansion coefficient of the cam shaft, the further the clearance between the intermediate member and the cam shaft may be increased.
  • the material of the intermediate member has the linear expansion coefficient that is close to or equal to the linear expansion coefficient of the material of the cam shaft rather than the linear expansion coefficient of the material of the inner rotor. Therefore, the intermediate member and the cam shaft are equally swollen even under the high-temperature environment, thereby inhibiting the clearance between the intermediate member and the cam shaft from being increased.
  • the hydraulic fluid is supplied to an outer circumferential side of the cam shaft and is supplied via the intermediate member through the second hydraulic fluid passage to the inner rotor.
  • the hydraulic fluid may be supplied via the second hydraulic fluid passage to the inner rotor without any modification or processing relative to an existing cam shaft of a known variable valve control apparatus. Consequently, even in a case where the intermediate member is additionally arranged at the known variable valve timing control apparatus, the existing cam shaft may be utilized, resulting in a cost reduction.
  • the cam shaft and the intermediate member are made of iron materials and the inner rotor is made of an aluminum material.
  • both the cam shaft and the intermediate member have high strengths and the substantially equal linear expansion coefficients from each other. Therefore, when the cam shaft is being inserted into the intermediate member, the intermediate member is inhibited from being damaged by the cam shaft. In addition, the clearance between the cam shaft and the intermediate member may be inhibited from being increased even under the high-temperature environment.
  • the inner rotor is made of the aluminum material; thereby, the inner rotor may be easily processed and the weight and cost of the inner rotor are effectively minimized.
  • a timing sprocket is arranged at the outer rotor and a bearing portion supporting the timing sprocket is arranged at the intermediate member.
  • the bearing portion arranged at the intermediate member for supporting the timing sprocket requires strength.
  • the bearing portion of the intermediate member is not made of the aluminum material forming the inner rotor but is made of the iron material. Accordingly, abrasion of the bearing portion is appropriately inhibited, therefore improving durability of the variable valve timing control apparatus.
  • the clearance between the intermediate member and the cam shaft that serves as the driven shaft is inhibited from being increased, thereby minimizing the leakage of the hydraulic fluid from the clearance.
  • variable valve timing control apparatus is arranged at a suction valve in an engine E for a vehicle.
  • the engine E for the vehicle in each of the first and second embodiments corresponds to an internal combustion engine.
  • the variable valve timing control apparatus includes a housing 1 rotating in synchronization with a crank shaft C serving as a drive shaft of the engine E, and an inner rotor 2 arranged coaxially with the housing 1 and rotatable relative thereto.
  • An intermediate member 6 is arranged between the inner rotor 2 and a bolt 5 serving as a driven shaft to which a rotation of the inner rotor 2 is transmitted (the bolt 5 will be hereinafter referred to as an OCV bolt 5). Then, the rotation of the inner rotor 2 transmitted from the driven shaft is transmitted to a rotary shaft of a cam.
  • a cam shaft 101 corresponds to the rotary shaft of the cam controlling opening and closing operations of the suction valve of the engine E.
  • the cam shaft 101 rotates in synchronization with the inner rotor 2, the OCV bolt 5, and the intermediate member 6. Further, the cam shaft 101 is rotatably attached to a cylinder head of the engine E.
  • the housing 1 integrally includes a front plate 11, an outer rotor 12 arranged around a circumferential outer side of the inner rotor 2, and a rear plate 13 integrated with a timing sprocket 15.
  • the front plate 11 is arranged at a first side of the housing 1 in an opposite direction from a second side of the housing 1 along a rotational axis of the cam shaft 101 connected to the second side of the housing 1.
  • the inner rotor 2 is accommodated in the housing 1; thereby, fluid pressure chambers 4 are formed between the inner rotor 2 and the outer rotor 12 as will be described below.
  • crank shaft C is rotationally driven and a driving force of the crank shaft C is transmitted via a driving force transmission member 102 to the timing sprocket 15. Then, the housing 1 rotates in a rotating direction indicated by an arrow S in Fig. 2 , thereby rotating the cam shaft 101 and allowing the cam arranged at the cam shaft 101 to move the suction valve downwardly to open the suction valve.
  • the outer rotor 12 includes plural protruding portions 14 protruding radially inwardly and positioned at intervals from one another along the rotating direction S; thereby, the fluid pressure chambers 4 are formed between the inner rotor 2 and the outer rotor 12.
  • Each of the protruding portions 14 serves as a shoe slidably contacting an outer circumferential surface of the inner rotor 2.
  • the inner rotor 2 includes protruding portions 21 protruding radially outwardly. Each of the protruding portions 21 is arranged at a portion of the outer circumferential surface, which faces each of the fluid pressure chambers 4.
  • the fluid pressure chamber 4 is partitioned by the protruding portion 21 into an advanced angle chamber 41 and a retarded angle chamber 42 along the rotating direction S.
  • the four fluid pressure chambers 4 are provided in the first embodiment; however, less than or more than the four fluid pressure chambers 4 may be formed in the variable valve timing control apparatus of the first embodiment.
  • Oil (hydraulic fluid) is supplied to and discharged from the advanced angle chambers 41 and the retarded angle chambers 42, or the supply/discharge of the oil to/from the advanced angle chambers 41 and the retarded angle chambers 42 is stopped. Therefore, a hydraulic pressure of the oil is applied to the protruding portions 21. Thus, a relative rotational phase between the housing 1 and the inner rotor 2 is shifted in an advanced angle direction or a retarded angle direction, or is maintained in any desired phase.
  • the advanced angle direction indicated by an arrow S1 in Fig. 2 is a direction in which a capacity of the advanced angle chamber 41 increases. Meanwhile, the retarded angle direction indicated by an arrow S2 in Fig.
  • FIG 2 is a direction in which a capacity of the retarded angle chamber 42 increases.
  • a most advanced angle phase is obtained when the capacity of the advanced angle chamber 41 is largest.
  • a most retarded angle phase is obtained when the capacity of the retarded angle chamber 42 is largest.
  • the variable valve timing control apparatus includes a lock mechanism 8 that may lock the relative rotational phase of the inner rotor 2 to the housing 1 at a predetermined phase between the most advanced angle phase and the most retarded angle phase (the predetermined phase will be hereinafter referred to as a lock phase).
  • the lock mechanism 8 locks the relative rotational phase at the lock phase, thereby appropriately maintaining a rotational phase of the cam shaft 101 relative to a rotational phase of the crank shaft C. As a result, a stable rotating speed of the engine E may be obtained.
  • the lock mechanism 8 includes a lock member 81 movable along the rotational axis of the cam shaft 101 and a lock passage 82 formed in the inner rotor 2.
  • the lock member 8 is biased by a biasing member and is maintained in an engaged state with a lock groove formed at the front plate 11 or the rear plate 13, thereby being maintained in a locked state.
  • the lock passage 82 connects to advanced angle passages 43.
  • the oil is supplied to the lock passage 82 to thereby apply the hydraulic pressure to the lock mechanism 8.
  • the lock member 81 is released from the lock groove against a biasing force of the biasing member, therefore being released from the locked state.
  • OCV oil control valve
  • a control valve serving as a control valve
  • the OCV 51 includes a spool 52, a spring 53 biasing the spool 52, and an electromagnetic solenoid 54 driving the spool 52.
  • the electromagnetic solenoid 54 is a known electromagnetic solenoid; therefore, a detailed explanation of the electromagnetic solenoid 54 will be omitted herein.
  • the spool 52 is accommodated in an accommodating portion 5a formed in a first end portion of the OCV bolt 5, which is located at the housing 1.
  • the spool 52 is slidably movable within the accommodating portion 5a along the rotational axis of the cam shaft 101.
  • An external threaded portion 5b is formed at a second end portion of the OCV bolt 5 (the second end portion is axially opposite from the first end portion).
  • the external threaded portion 5b of the OCV bolt 5 is screwed with an internal threaded portion 101 a of the cam shaft 101, thereby fixing the OCV bolt 5 to the cam shaft 101.
  • the spring 53 is arranged in the accommodating portion 5a so as to be in the vicinity of the cam shaft 101, thereby consistently biasing the spool 52 toward an opposite side of the cam shaft 101 along the rotational axis.
  • the electromagnetic solenoid 54 is powered and a push pin 54a arranged at the electromagnetic solenoid 54 axially presses against a rod portion 52a formed at the spool 52. As a result, the spool 52 axially slides toward the cam shaft 101 against a biasing force of the spring 53.
  • a duty ratio of electric power supplied to the electromagnetic solenoid 54 is adjusted, thereby axially adjusting a position of the spool 52 of the OCV 51.
  • a feed amount of the electric power supplied to the electromagnetic solenoid 54 is controlled by an electric control unit (ECU).
  • ECU electric control unit
  • the intermediate member 6 formed in a hollow cylindrical shape is arranged in the inner rotor 2 so as to be axially positioned close to the cam shaft 101 (to the right side seen in Fig. 5 ).
  • a bearing portion for the timing sprocket 15 is arranged at the intermediate member 6.
  • a washer 7 is arranged in the inner rotor 2 so as to be axially positioned at the opposite side of the cam shaft 101 (to the left side seen in Fig. 5 ).
  • the OCV bolt 5 is inserted through central bores of the housing 1, the washer 7, the inner rotor 2, and the intermediate member 6 under a state where the intermediate member 6 and the washer 7 are arranged in the inner rotor 2 and the housing 1 is arranged around the circumferential outer side of the inner rotor 2.
  • an axial surface of the intermediate member 6, which axially faces the front plate 11, and an axial surface of the washer 7, which axially faces the rear plate 13, are entirely in contact with the inner rotor 2 along the rotational axis of the cam shaft 101; therefore, a contact portion A between the inner rotor 2 and the intermediate member 6 is formed.
  • the washer 7 functions to increase a connecting force of the OCV bolt 5 relative to the cam shaft 101; however, the washer 7 is not an essential component for the variable valve timing control apparatus according to the first embodiment.
  • a component having the same function as the washer 7 and formed into a different shape from the shape of the washer 7 may be utilized in the variable valve timing control apparatus of the first embodiment.
  • the component may be arranged at a different position from the position of the washer 7 in the first embodiment.
  • the oil is stored in an oil pan 61.
  • the driving force of the crank shaft C is transmitted to a mechanical oil pump 62; thereby, the oil in the oil pan 61 is pumped by the oil pump 62 and is supplied to a supply passage 45 that will be described below.
  • the OCV 51 controls the supply/discharge of the oil from/ to advanced angle passages 43 and retarded angle passages 44 and controls to stop the supply/discharge of the oil from/ to the advanced angle passage 43 and the retarded angle passages 44.
  • a portion (the spool 52) of the OCV 51 switches connection and disconnection between the advanced angle passages 43 and the retarded angle passages 44.
  • the advanced angle passages 43 connecting to the advanced angle chambers 41, respectively and serving as first hydraulic fluid passages are formed by through-holes 43a formed in the OCV bolt 5, an inner room 43b formed between the OCV bolt 5 and the inner rotor 2, and through-holes 43c formed in the inner rotor 2.
  • the retarded angle passages 44 connecting to the retarded angle chambers 42, respectively and serving as second hydraulic fluid passages are formed by through-holes 44a formed in the OCV bolt 5, through-holes 44b formed in the intermediate member 6 and serving as passages constituting portions of the second hydraulic fluid passages, and through-holes 44c formed in the inner rotor 2.
  • the supply passage 45 supplying the oil to the advanced angle chambers 41 or the retarded angle chambers 42 is formed by a passage 45a formed in the cam shaft 101, a passage 45b formed in the intermediate member 6, and through-holes 45c formed in the OCV bolt 5.
  • the oil flowing through the supply passage 45 firstly flows into an annular groove 52b formed at an outer circumferential surface of the spool 52.
  • the annular groove 52b is not in connection with the through-holes 43a and 44a formed in the OCV bolt 5
  • the oil is not supplied to the advanced angle chambers 41 and the retarded angle chambers 42.
  • the through-holes 43a are not in connection with through-holes 52c formed in the spool; therefore, the oil in the advanced angle chambers 41 is not discharged therefrom through the through-holes 52c, the accommodating portion 5a, and a discharge hole 52d to an outer side of the variable valve timing control apparatus.
  • the through-holes 44a are not in connection with the accommodating portion 5a. Accordingly, the oil in the retarded angle chambers 42 is not discharged therefrom through the retarded angle passages 44, the accommodating portion 5a, and the discharge hole 52d to the outer side of the variable valve timing control apparatus. That is, a predetermined feed amount of the electric power is supplied to the electromagnetic solenoid 54 so that the OCV 51 controls the spool 52 to be maintained in a position shown in Fig. 1 . As a result, the supply/discharge of the oil to/from the advanced angle chambers 41 and the retarded angel chambers 42 is stopped and the relative rotational phase between the housing 1 and the inner rotor 2 is maintained.
  • the spool 52 In a case where the electromagnetic solenoid 54 is not powered, the spool 52 is maintained in a position shown in Fig. 3 , by means of the biasing force of the spring 53. In such condition in Fig. 3 , the annular groove 52b of the spool 52 is in connection with the through-holes 43a of the OCV bolt 5 and is not in connection with the through-holes 44a of the OCV bolt 5. In addition, the through-holes 44a are simultaneously in connection with the accommodating portion 5a. Accordingly, the oil supplied to the supply passage 45 is supplied through the advanced angle passages 43 to the advanced angle chambers 41.
  • the oil in the retarded angle chambers 42 is discharged therefrom through the retarded angle passages 44, the accommodating portion 5a, and the discharge hole 52d to the outer side of the variable valve timing control apparatus.
  • the relative rotational phase between the housing 1 and the inner rotor 2 is shifted in the advanced angle direction S1 by the hydraulic pressure applied to the advanced angle chambers 41.
  • the spool 52 In a case where the electromagnetic solenoid 54 is maximally powered, the spool 52 is maintained in a position shown in Fig. 4 against the biasing force of the spring 53. In such condition in Fig. 4 , the annular groove 52b of the spool 52 is in connection with the through-holes 44a of the OCV bolt 5 and is not in connection with the through-holes 43a of the OCV bolt 5. In addition, the through-holes 43a are simultaneously in connection with the through-holes 52c of the spool 52. Accordingly, the oil supplied to the supply passage 45 is supplied through the retarded angle passages 44 to the retarded angle chambers 42.
  • the oil is supplied from the supply passage 45 to an outer circumferential side of the OCV bolt 5 and is thereafter supplied via the intermediate member 6 through the retarded angle passages 44 to the inner rotor 2.
  • the oil in the advanced angle chambers 41 is discharged therefrom through the advanced angle passages 43, the through-holes 52c, the accommodating portion 5a, and the discharge hole 52d to the outer side of the variable valve timing control apparatus.
  • the relative rotational phase between the housing 1 and the inner rotor 2 is shifted in the retarded angle direction S2 by the hydraulic pressure applied to the retarded angle chambers 42.
  • the intermediate member 6 and the inner room 43b are axially arranged between the OCV bolt 5 and the inner rotor 2. Accordingly, the OCV bolt 5 is not in contact with the inner rotor 2. Consequently, even in a case where the OCV bolt 5 is made of a high-strength material, the inner rotor 2 does not need to be made of a high-strength material in order to inhibit the inner rotor 2 from being damaged by a contact with the OCV volt 5.
  • the inner rotor 2 may be easily processed.
  • the weight and cost of the inner rotor 2 are effectively minimized.
  • variable valve timing control apparatus includes the contact portion A at which the axial surface of the intermediate member 6, axially facing the front plate 11 is entirely in contact with the inner rotor 2 between the advanced angle passages 43 and the retarded angle passages 44 along the rotational axis of the cam shaft 101. Accordingly, the oil in the advanced angle passages 43 and the oil in the retarded angle passages 44 are not mixed together with one another in a clearance between the inner rotor 2 and the intermediate member 6. Consequently, controllability of the variable valve timing control apparatus may not deteriorate.
  • the intermediate member 6 is made of a material having a linear expansion coefficient that is substantially equal to or close to a linear expansion coefficient of the material of the OCV bolt 5.
  • the OCV bolt 5 and the intermediate member 6 are substantially equally swollen under a high-temperature environment, thereby inhibiting the clearance between the OCV bolt 5 and the intermediate member 6 from being increased.
  • leakage of the oil from the clearance is inhibited and the controllability of the variable valve timing control apparatus may be maintained.
  • the OCV bolt 5 and the intermediate member 6 are made of iron materials, strength requirements for the OCV bolt 5 and the intermediate member 6 are satisfied.
  • the OCV bolt 5 and the intermediate member 6 appropriately have the substantially same linear expansion coefficients.
  • the housing 1, the washer 7, the inner rotor 2, the intermediate member 6, and the like are axially fixed to one another by the OCV bolt 5. Accordingly, even in a case where the housing 1, the washer 7, the inner rotor 2, the intermediate member 6, and the like are swollen under the high-temperature environment, a clearance may not be easily generated at the contact portion A between the inner rotor 2 and the intermediate member 6.
  • variable valve timing control apparatus will be explained as follows with reference to Fig. 6 .
  • a basic configuration of the variable valve timing control apparatus according to the second embodiment is the same as that of the variable valve timing control apparatus according to the first embodiment. Therefore, differences in the variable valve timing control apparatus between the first and second embodiments will be described below.
  • the same reference numbers are assigned to the same components in the first and second embodiments.
  • the cam shaft 101 penetrates through the central bore of the inner rotor 2 along the rotational axis.
  • the cam shaft 101 serves as the driven shaft.
  • An inner room 101 b into which a bolt 91 is inserted is formed in an end portion of the cam shaft 101.
  • An external threaded portion 91 a formed at the bolt 91 is screwed with the internal threaded portion 101 a of the cam shaft 101; thereby, the inner rotor 2 arranged in the housing 1 is fixed to the cam shaft 101.
  • the OCV 51 is arranged at the variable valve timing control apparatus in the first embodiment.
  • the OCV 51 is arranged at the oil pump 62 in the second embodiment.
  • the OCV 51 controls the oil to be supplied to any of the advanced angle chambers 41 and the retarded angle chambers 42 that will be described below; thereafter, the oil flows into the variable valve timing control apparatus.
  • the supply passage 45 described in the first embodiment is not provided at the variable valve timing control apparatus according to the second embodiment.
  • the advanced angle passages 73 connecting to the advanced angle chambers 41, respectively and serving as the first hydraulic fluid passages are formed by a passage 73a formed in the cam shaft 101, an inner room 73b formed between the cam shaft 101 and the inner rotor 2, and through-holes 73c formed in the inner rotor 2.
  • the retarded angle passages 74 connecting to the retarded angle chambers 42, respectively and serving as the second hydraulic fluid passages are formed by passages 74a formed in the cam shaft 101, passages 74b formed in the intermediate member 6, and through-holes 74c formed in the inner rotor 2.
  • the passages 74b serve as passages constituting portions of the retarded angle passages 74.
  • the intermediate member 6 and the inner room 73b constituting a portion of the advanced angle passages 73 are arranged between the cam shaft 101 and the inner rotor 2. Accordingly, the cam shaft 101 is not in contact with the inner rotor 2. Consequently, even in a case where the cam shaft 101 is made of a high-strength material, the inner rotor 2 does not need to be made of a high-strength material in order to inhibit the inner rotor 2 from being damaged by a contact with the cam shaft 101.
  • the intermediate member 6 includes the axial surface axially facing the front plate 11 and defined at the contact portion A relative to the inner rotor 2. Therefore, the oil in the advanced angle passages 73 is not mixed together with the oil in the retarded angle passages 74, thereby inhibiting the deterioration of the controllability of the variable valve timing control apparatus.
  • the intermediate member 6 includes the axial surface axially facing the front plate 11 and defined at the contact portion A relative to the inner rotor 2, and an axial surface axially facing the rear plate 13 and defined at a contact portion B relative to the inner rotor 2.
  • the contact portion B is arranged between the advanced angle passages 73 and the retarded angle passages 74.
  • the intermediate member 6 is configured so that not only the axial surface defined at the contact portion A but also the axial surface defined at the contact portion B may be entirely in contact with the inner rotor 2 along the rotational axis of the cam shaft 101. As illustrated in Fig.
  • the passages 74b formed in the intermediate member 6 are configured so as to be axially in connection with the passages 74a formed in the cam shaft 101.
  • the intermediate member 6 does not need to be made of the material having the linear expansion coefficient that is substantially equal to or close to a linear expansion coefficient of the material of the cam shaft 101, therefore offering a wide selection of materials for forming the intermediate member 6.
  • the intermediate member 6 and the cam shaft 101 are press-fitted to each other; thereafter, the inner rotor 2 may be attached to a circumferential outer side of the intermediate member 6. Accordingly, a clearance is inhibited from being axially generated between the intermediate member 6 and the cam shaft 101.
  • a variable valve timing control apparatus includes an oil passage configuration where a clearance is axially generated between the intermediate member 6 and the cam shaft 101
  • the oil in the advanced angle passages 73 may be mixed together with the oil in the retarded angle passages 74.
  • press-fitting the intermediate member 6 to the cam shaft 101 as described in the first embodiment inhibits the clearance from being axially generated between the intermediate member 6 and the cam shaft, therefore not deteriorating the controllability of the variable valve timing control apparatus.
  • variable valve timing control apparatus may be adapted to be arranged at an exhaust valve in the engine E.
  • the variable valve timing control apparatus according to each of the first and second embodiments may not include the lock mechanism 8.
  • the oil passage configuration in each of the first and second embodiments may be modified as long as the modified oil passage configuration does not affect the operational function of the variable valve timing control apparatus.
  • each of the OCV bolt 5 and the cam shaft 101 serves as the driven shaft.
  • a different member may be adapted as the driven shaft instead of the OCV bolt 5 or the cam shaft 101.
  • the arrangement and shape of the intermediate member 6 described in each of the first and second embodiments may be modified.
  • variable valve timing control apparatus may be utilized in the internal combustion engine E for the vehicle and the like.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (5)

  1. Vorrichtung zur Steuerung einer variablen Ventilsteuerzeit mit:
    einem mit einer Antriebswelle (C) eines Verbrennungsmotors (E) synchron drehenden und einen äußeren Rotor (12) beinhaltenden Gehäuse (1);
    einem zu dem Gehäuse (1) koaxial angeordneten und relativ zum Gehäuse (1) drehbaren inneren Rotor (2);
    einer Nockenwelle (101), auf welche die Drehung des inneren Rotors (2) übertragen wird;
    einem zwischen dem inneren Rotor (2) und der Nockenwelle (101) entlang der Rotationsachse der Nockenwelle (101) angeordneten und mit dem inneren Rotor (2) sowie der Nockenwelle (101) synchron drehenden Zwischenglied (6);
    einem ersten Hydraulikfluiddurchgang (73);
    einem zwischen der Nockenwelle (101) und dem inneren Rotor (2) gebildeten, den Kontakt zwischen dem inneren Rotor (2) und der Nockenwelle (101) verhindernden und einen Abschnitt des ersten Hydraulikfluiddurchgangs (73) bildenden inneren Raum (73b);
    einem zweiten Hydraulikfluiddurchgang (74);
    einem in dem Zwischenglied (6) ausgebildeten und einen Teil des zweiten Hydraulikfluiddurchgangs (74) bildenden Durchgang (74b); und
    einem Kontaktabschnitt (A, B), an dem eine axiale Fläche des Zwischenglieds (6) vollständig in Kontakt mit dem inneren Rotor (2) zwischen dem ersten Hydraulikfluiddurchgang (73) und dem zweiten Hydraulikfluiddurchgang (74) entlang der Rotationsachse ist,
    dadurch gekennzeichnet, dass
    das Zwischenglied (6) mittels Presspassung mit der Nockenwelle (101) verbunden ist.
  2. Vorrichtung zur Steuerung der variablen Ventilsteuerzeit gemäß Anspruch 1, wobei
    das Zwischenglied (6) aus einen Material hergestellt ist, dessen linearer Ausdehnungskoeffizient vielmehr einem linearen Ausdehnungskoeffizienten des Materials der Nockenwelle (101) als dem linearen Ausdehnungskoeffizienten des Materials des inneren Rotors (2) nahe kommt oder gleicht.
  3. Vorrichtung zur Steuerung der variablen Ventilsteuerzeit gemäß Anspruch 1 oder 2, wobei
    eine Hydraulikflüssigkeit einer Außenumfangsseite der Nockenwelle (101) zugeführt wird und über das Zwischenglied (6) durch den zweiten Hydraulikfluiddurchgang (74) dem inneren Rotor (2) zugeführt wird.
  4. Vorrichtung zur Steuerung der variablen Ventilsteuerzeit gemäß einem der Ansprüche 1 bis 3, wobei
    die Nockenwelle (101) und das Zwischenglied (6) aus Eisenmaterialien bestehen und der innere Rotor (2) aus Aluminiummaterial besteht.
  5. Vorrichtung zur Steuerung der variablen Ventilsteuerzeit gemäß Anspruch 4, wobei
    ein Steuerzahnrad (15) am äußeren Rotor (12) angeordnet ist und ein das Steuerzahnrad (15) unterstützender Lagerabschnitt am Zwischenglied (6) angeordnet ist.
EP11179376.6A 2010-09-10 2011-08-30 Vorrichtung zur Regelung der variablen Ventilsteuerzeit Not-in-force EP2428656B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2010203234A JP5585832B2 (ja) 2010-09-10 2010-09-10 弁開閉時期制御装置

Publications (2)

Publication Number Publication Date
EP2428656A1 EP2428656A1 (de) 2012-03-14
EP2428656B1 true EP2428656B1 (de) 2015-08-05

Family

ID=44509062

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11179376.6A Not-in-force EP2428656B1 (de) 2010-09-10 2011-08-30 Vorrichtung zur Regelung der variablen Ventilsteuerzeit

Country Status (4)

Country Link
US (1) US20120060779A1 (de)
EP (1) EP2428656B1 (de)
JP (1) JP5585832B2 (de)
CN (1) CN102400728B (de)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5321926B2 (ja) * 2011-02-18 2013-10-23 アイシン精機株式会社 弁開閉時期制御装置
JP5626243B2 (ja) * 2012-02-29 2014-11-19 株式会社デンソー 液圧式バルブタイミング調整装置
JP5831335B2 (ja) * 2012-04-03 2015-12-09 株式会社日本自動車部品総合研究所 バルブタイミング調整装置
JP5811358B2 (ja) * 2012-05-24 2015-11-11 株式会社デンソー バルブタイミング調整装置
DE102012214757A1 (de) * 2012-08-20 2014-02-20 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
JP5991091B2 (ja) 2012-09-04 2016-09-14 アイシン精機株式会社 弁開閉時期制御装置
CN103174490B (zh) * 2013-04-01 2014-10-22 天津大学 基于转子控制的液压可变气门装置
DE102013209520A1 (de) * 2013-05-23 2014-12-11 Schaeffler Technologies Gmbh & Co. Kg Rotor für einen Flügelzellenversteller einer Nockenwellenverstelleinrichtung
JP5817784B2 (ja) * 2013-05-24 2015-11-18 株式会社デンソー 液圧式バルブタイミング調整装置
JP2015045281A (ja) * 2013-08-28 2015-03-12 アイシン精機株式会社 弁開閉時期制御装置
JP5979102B2 (ja) * 2013-08-28 2016-08-24 アイシン精機株式会社 弁開閉時期制御装置
JP2015045282A (ja) 2013-08-28 2015-03-12 アイシン精機株式会社 弁開閉時期制御装置
DE102013015675A1 (de) * 2013-09-23 2015-03-26 Gkn Sinter Metals Holding Gmbh Rotor für einen Nockenwellenversteller, Teileset zur Herstellung eines Rotors für einen Nockenwellenversteller sowie Verfahren zur Herstellung eines gefügten Bauteils, bevorzugt eines Rotors für einen Nockenwellenversteller
JP6273801B2 (ja) * 2013-11-29 2018-02-07 アイシン精機株式会社 弁開閉時期制御装置
JP6187203B2 (ja) * 2013-11-29 2017-08-30 アイシン精機株式会社 弁開閉時期制御装置
DE102013226449B4 (de) 2013-12-18 2020-11-26 Schaeffler Technologies AG & Co. KG Spanlos gefertigte Ölkanäle in einem geteilten Rotor für einen hydraulischen Nockenwellenversteller
JP6217438B2 (ja) * 2014-02-14 2017-10-25 アイシン精機株式会社 弁開閉時期制御装置
JP6295720B2 (ja) * 2014-02-27 2018-03-20 アイシン精機株式会社 弁開閉時期制御装置
JP6225750B2 (ja) * 2014-02-27 2017-11-08 アイシン精機株式会社 弁開閉時期制御装置
JP6292083B2 (ja) * 2014-08-27 2018-03-14 アイシン精機株式会社 弁開閉時期制御装置
CN104712387B (zh) * 2015-01-28 2017-02-01 宁波太平洋电控系统有限公司 带中间锁止功能的可变气门正时机构
JP6721334B2 (ja) * 2015-12-28 2020-07-15 株式会社ミクニ バルブタイミング変更装置
JP6666715B2 (ja) * 2015-12-28 2020-03-18 株式会社ミクニ バルブタイミング変更装置
JP6410742B2 (ja) * 2016-01-08 2018-10-24 アイシン精機株式会社 弁開閉時期制御装置
US10151222B2 (en) * 2016-09-28 2018-12-11 Schaeffler Technologies AG & Co. KG Electric cam phasing system including an activatable lock
JP2018135842A (ja) * 2017-02-23 2018-08-30 アイシン精機株式会社 弁開閉時期制御装置
JP6954764B2 (ja) * 2017-05-12 2021-10-27 株式会社デンソー バルブタイミング調整装置
JP6497430B2 (ja) * 2017-11-30 2019-04-10 アイシン精機株式会社 弁開閉時期制御装置

Family Cites Families (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4091776A (en) * 1974-04-04 1978-05-30 Rockwell International Corporation Fluid actuated timing mechanism
DE19509845C2 (de) * 1994-03-18 1998-01-15 Unisia Jecs Corp Nockenwellen-Verstellantrieb
JP3744594B2 (ja) * 1996-05-15 2006-02-15 アイシン精機株式会社 弁開閉時期制御装置
US5836276A (en) * 1996-08-09 1998-11-17 Denso Corporation Rotational phase adjusting apparatus having fluid reservoir
DE19708661B4 (de) * 1997-03-04 2005-06-16 Ina-Schaeffler Kg Vorrichtung zur Variierung der Ventilsteuerzeiten einer Brennkraftmaschine, insbesondere Nockenwellen-Verstelleinrichtung nach dem Flügelzellenprinzip
DE19817319C2 (de) * 1998-04-18 2001-12-06 Daimler Chrysler Ag Nockenwellenversteller für Brennkraftmaschinen
JP4013364B2 (ja) * 1998-10-30 2007-11-28 アイシン精機株式会社 弁開閉時期制御装置
DE19944535C1 (de) * 1999-09-17 2001-01-04 Daimler Chrysler Ag Nockenwellenversteller für Brennkraftmaschinen
JP4350861B2 (ja) * 2000-02-15 2009-10-21 株式会社日立製作所 内燃機関のバルブタイミング制御装置
JP2002047906A (ja) * 2000-07-31 2002-02-15 Daihatsu Motor Co Ltd 内燃機関におけるバルブタイミング可変装置
DE10134320A1 (de) * 2001-07-14 2003-01-23 Ina Schaeffler Kg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Rotationskolben-Verstelleinrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
JP2004060591A (ja) * 2002-07-31 2004-02-26 Mikuni Corp バルブタイミング変更装置
DE102004035035B4 (de) * 2003-07-24 2022-04-14 Daimler Ag Nockenwellenversteller für Brennkraftmaschinen
US20050045130A1 (en) * 2003-08-27 2005-03-03 Borgwarner Inc. Camshaft incorporating variable camshaft timing phaser rotor
EP1596040B1 (de) * 2004-05-14 2010-10-13 Schaeffler KG Nockenwellenversteller
JP3974139B2 (ja) * 2005-04-26 2007-09-12 株式会社日立製作所 内燃機関のバルブタイミング制御装置
DE102006033425A1 (de) * 2006-07-19 2008-02-21 Schaeffler Kg Gruppe mehrerer Nockenwellen mit Nockenwellenverstellern
DE102007020526A1 (de) * 2007-05-02 2008-11-06 Schaeffler Kg Nockenwellenversteller für eine Brennkraftmaschine mit verbesserter Ausführung der Druckräume
DE102008029692B4 (de) * 2008-06-24 2016-02-11 Hilite Germany Gmbh Gebaute Nockenwelle mit einem Flügelzellenversteller und Herstellungsverfahren
DE102008030057B4 (de) * 2008-06-27 2018-01-25 Hilite Germany Gmbh Nockenwellenverstelleinrichtung
DE102008050134B4 (de) * 2008-10-04 2017-06-29 Schaeffler Technologies AG & Co. KG Einrichtung zur Nockenwellenverstellung für eine Verbrennungskraftmaschine
DE102008057492A1 (de) * 2008-11-15 2010-05-20 Daimler Ag Nockenwellenverstellvorrichtung
JP4640510B2 (ja) * 2009-01-14 2011-03-02 株式会社デンソー バルブタイミング調整装置
JP2010059979A (ja) * 2009-12-18 2010-03-18 Aisin Seiki Co Ltd 弁開閉時期制御装置
JP5146550B2 (ja) * 2011-01-14 2013-02-20 株式会社デンソー バルブタイミング調整装置

Also Published As

Publication number Publication date
JP5585832B2 (ja) 2014-09-10
CN102400728B (zh) 2015-05-13
CN102400728A (zh) 2012-04-04
US20120060779A1 (en) 2012-03-15
JP2012057578A (ja) 2012-03-22
EP2428656A1 (de) 2012-03-14

Similar Documents

Publication Publication Date Title
EP2428656B1 (de) Vorrichtung zur Regelung der variablen Ventilsteuerzeit
US8418664B2 (en) Variable valve timing control apparatus
JP6373464B2 (ja) 内燃機関のバルブタイミング制御装置
US6758178B2 (en) Valve timing control device
EP2216518B1 (de) Nockenwellenversteller
EP2343438B1 (de) Nockenwellenversteller
EP2233705B1 (de) Vorrichtung zur Regelung der Ventilsteuerzeit
EP2843202B1 (de) Variable Ventilsteuerzeit-Steuervorrichtung
EP2405107B1 (de) Vorrichtung zur Regelung der variablen Ventilsteuerzeit
JP2015072011A (ja) カムシャフトフェーザ
US10066520B2 (en) Valve opening and closing timing control apparatus
EP2708706B1 (de) Vorrichtung zur Regelung der Ventilsteuerzeit
US7415952B2 (en) Valve timing control device
US8800516B2 (en) Variable valve timing control apparatus
EP2843201A1 (de) Variable Ventilsteuerzeit-Steuervorrichtung
JP6273801B2 (ja) 弁開閉時期制御装置
US20030029400A1 (en) Variable valve timing control device
US9995185B2 (en) Valve timing control device for internal combustion engine
US20210172347A1 (en) Valve opening and closing timing control device
US20210172346A1 (en) Valve opening and closing timing control device
JP4453222B2 (ja) 弁開閉時期制御装置

Legal Events

Date Code Title Description
AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL 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 RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

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

17P Request for examination filed

Effective date: 20120907

17Q First examination report despatched

Effective date: 20130531

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150216

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): AL 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 RS 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: 740840

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150815

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

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: 602011018410

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 740840

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150805

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20150805

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

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: 20150805

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: 20151106

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: 20150805

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: 20150805

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: 20151105

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: 20151205

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: 20151207

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: 20150805

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: 20150805

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: 20150805

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: 20150805

Ref country code: RS

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: 20150805

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: 20150805

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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: 20150805

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

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: 20150805

Ref country code: CH

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

Effective date: 20150831

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: 20150805

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: 20150805

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: 20150805

Ref country code: LI

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

Effective date: 20150831

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: 20150805

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602011018410

Country of ref document: DE

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

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: 20150805

Ref country code: MC

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: 20150805

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

26N No opposition filed

Effective date: 20160509

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

Effective date: 20151105

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: 20150830

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: 20150805

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

Ref country code: GB

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

Effective date: 20151105

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 602011018410

Country of ref document: DE

Representative=s name: WINTER, BRANDL - PARTNERSCHAFT MBB, PATENTANWA, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 602011018410

Country of ref document: DE

Representative=s name: WINTER, BRANDL, FUERNISS, HUEBNER, ROESS, KAIS, DE

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: 20150805

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

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: 20110830

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: 20150805

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: 20150805

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

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: 20150805

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

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

Ref country code: BE

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

Effective date: 20150831

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: 20150805

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

Ref country code: LU

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

Effective date: 20150830

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: 20150805

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

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

Ref country code: AL

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: 20150805

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

Ref country code: DE

Payment date: 20190820

Year of fee payment: 9

Ref country code: FR

Payment date: 20190711

Year of fee payment: 9

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602011018410

Country of ref document: DE

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

Ref country code: DE

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

Effective date: 20210302

Ref country code: FR

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

Effective date: 20200831