US20130036992A1 - Hydraulic valve timing controller - Google Patents

Hydraulic valve timing controller Download PDF

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Publication number
US20130036992A1
US20130036992A1 US13/553,918 US201213553918A US2013036992A1 US 20130036992 A1 US20130036992 A1 US 20130036992A1 US 201213553918 A US201213553918 A US 201213553918A US 2013036992 A1 US2013036992 A1 US 2013036992A1
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US
United States
Prior art keywords
coil spring
valve timing
angle position
rotor
timing controller
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.)
Abandoned
Application number
US13/553,918
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English (en)
Inventor
Kazuhiro Iwai
Toshiki Fujiyoshi
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.)
Denso Corp
Original Assignee
Denso Corp
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 Denso Corp filed Critical Denso Corp
Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IWAI, KAZUHIRO, FUJIYOSHI, TOSHIKI
Publication of US20130036992A1 publication Critical patent/US20130036992A1/en
Abandoned legal-status Critical Current

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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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • 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
    • F01L2001/34453—Locking means between driving and driven members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs

Definitions

  • the present disclosure relates to a hydraulic valve timing controller which adjusts valve timing of a valve that is opened/closed by a camshaft driven by a torque transmitted from a crankshaft of an internal combustion engine.
  • a hydraulic valve timing controller has an outer rotor rotating with a crankshaft and an inner rotor accommodated in the outer rotor in such a manner as to rotate with a camshaft.
  • a plurality of working chambers are defined in the outer rotor by the inner rotor.
  • Working fluid is introduced into or discharged from the working chamber, whereby the inner rotor rotates relative to the outer rotor in one rotational direction or the other rotational direction. According to a differential phase between these rotors, a valve timing of a valve is adjusted.
  • JP-2011-69316A (US-2011-0073056A1) shows a hydraulic valve timing controller provided with a coil spring of which outer end and inner end are respectively engaged with the outer rotor and the inner rotor.
  • a deforming direction the other rotational direction of the inner rotor is referred to as a biasing direction
  • the coil spring is twisted and deformed along with a relative rotation of the inner rotor in the deforming direction, whereby the inner rotor is biased relative to the outer rotor in the biasing direction.
  • the inner rotor is compulsorily rotated in the biasing direction relative to the outer rotor, so that a valve timing is appropriately adjusted for starting the engine.
  • adjacent windings of wire of the coil spring are contact with each other at a single point between the outer end and the inner end.
  • the contacting adjacent windings are easily moved apart from each other.
  • the primary natural frequency of the coil spring is decreased. It is likely that the engine vibration frequency agrees with a primary natural frequency of the coil spring and the resonance will occur in the coil spring, which may cause mechanical damages.
  • the primary natural frequency of the coil spring is larger than the engine vibration, whereby the resonance can be avoided with high reliability.
  • FIG. 1 is a longitudinal sectional view showing a valve timing controller according to a first embodiment of the present invention, taken along a line I-I in FIG. 2 .
  • FIG. 2 is a cross-sectional view taken along a line II-II in FIG. 1 ;
  • FIG. 3 is a cross-sectional view of a valve timing controller in an operational state different from FIG. 2 ;
  • FIG. 4 is a cross-sectional view a valve timing controller in an operational state different from FIGS. 2 and 3 ;
  • FIG. 6 is a front view of a valve timing controller in an operational state different from FIG. 5 ;
  • FIG. 7 is a front view of a valve timing controller in an operational state different from FIGS. 5 and 6 ;
  • FIG. 8 is a cross-sectional view of a valve timing controller taken along a line VIII-VIII in FIG. 1 ;
  • FIG. 9A is a front view showing a coil spring in a set condition
  • FIG. 11 is a cross sectional view showing a valve timing controller according to a second embodiment
  • FIG. 12 is a schematic chart for explaining a characteristic of a biasing mechanism shown in FIG. 11 ;
  • FIG. 13 is a cross sectional view showing a valve timing controller according to a modification of the first embodiment
  • FIG. 14 is a cross sectional view showing a valve timing controller according to another modification of the first embodiment
  • FIG. 15 is a cross sectional view showing a valve timing controller according to another modification of the second embodiment.
  • FIG. 16 is a cross sectional view showing a valve timing controller according to the other modification of the first embodiment.
  • FIG. 1 shows a first embodiment of a hydraulic valve timing controller 1 which is applied to an internal combustion engine for a vehicle.
  • the valve timing controller 1 is provided in a torque transmitting system where an engine torque is transmitted from a crankshaft (not shown) to a camshaft 2 .
  • the valve timing controller 1 adjusts a valve timing of an intake valve which is driven by a camshaft 2 with hydraulic oil as “hydraulic fluid”.
  • valve timing controller 1 has an outer rotor 10 and an inner rotor 20 .
  • a rotational phase of the inner rotor 20 is varied relative to the outer rotor 20 , whereby a valve timing is adjusted.
  • a circumferential direction, a radial direction and an axial direction of the outer rotor 10 is the same as those of the inner rotor 20 .
  • a rotational phase of the inner rotor 20 relative to the outer rotor 10 is referred to as a differential phase of rotors.
  • the outer rotor 10 is a sprocket housing including a shoe housing 12 , a sprocket plate 13 and a lock plate 14 .
  • the shoe housing 12 has a main body 120 and a plurality of shoes 122 .
  • Each of the shoes 122 is circumferentially arranged one after another at generally equal intervals on an inner surface of the main body 120 and radially inwardly projects therefrom.
  • an accommodation chamber 30 is defined between the adjacent shoes 122 in the circumferential direction.
  • the sprocket plate 13 has a sprocket 130 which is linked with a crankshaft through a timing chain (not shown). During an operation of the internal combustion engine, a driving torque is transmitted from the crankshaft to the sprocket 130 such that the outer rotor 10 rotates in a clockwise direction in FIGS. 2 to 4 together with the crankshaft.
  • the inner rotor 20 is a vane rotor which is arranged between the plates 13 and 14 in the outer rotor 10 .
  • the inner rotor 20 has a shaft 200 and a plurality of vanes 202 .
  • the shaft 200 is shaped cylindrically and is comprised of a shaft body 200 a and a rotational bush 200 b . Both ends of the shaft body 200 a are slidably in contact with the plates 13 and 14 , and its outer circumferential surface is slidably in contact with the end of each shoe 122 .
  • the shaft body 200 a is coaxially connected to the camshaft 2 which penetrates a center hole 132 of the sprocket plate 13 .
  • the inner rotor 20 rotates in the clockwise direction in FIGS. 2 to 4 together with the camshaft 2 relative to the housing 11 .
  • the rotational bush (axial portion) 200 b penetrates a center hole 142 of the lock plate 14 .
  • Each of the vanes 202 protrudes radially outwardly from the shaft 200 at regular intervals and is accommodated in the corresponding accommodation chamber 30 .
  • Axial both ends of the vane 202 are slidably in contact with the plates 13 and 14 , and a radial top end of the vane 202 is slidably in contact with an inner surface of the shoe housing 12 .
  • Each of the vanes 202 divides the corresponding accommodating chamber 30 in circumferential direction into working chambers 32 and 33 . The working oil is introduced into working chambers 32 and 33 or is discharged therefrom.
  • a specified vane 202 a has a lock member 22 and a lock spring 24 .
  • a column-shaped lock member 22 is biased by a lock spring 24 to be inserted into a lock hole 140 .
  • the inner rotor 20 can not rotate relative to the outer rotor 10 .
  • the lock member 22 is disengaged from the lock hole 140 by receiving hydraulic pressure from at least one of the chambers 32 and 33 , the inner rotor 20 can rotate relative to the outer rotor 10 .
  • the inner rotor rotates in the advance direction “Da” relative to the outer rotor 10 .
  • the differential phase between rotors 10 and 20 is varied in the advance direction, so that the valve timing is advanced.
  • the inner rotor rotates in the retard direction “Dr” relative to the outer rotor 10 .
  • the differential phase between rotors 10 and 20 is varied in the retard direction, so that the valve timing is retarded.
  • FIG. 3 shows a situation where the differential phase is most retarded
  • FIG. 4 shows a situation where the differential phase is most advanced
  • FIG. 2 shows a situation where the differential phase is fixed at an intermediate lock phase between the most retarded phase and the most advanced phase. This intermediate phase is realized when the engine is off, and this intermediate lock phase is a most appropriate phase for optimizing a startability of the engine.
  • a biasing mechanism 5 for biasing the inner rotor 20 toward the intermediate phase will be described, hereinafter.
  • the outer rotor 10 has an outer stopper 18 which protrudes from the lock plate 14 in an axial direction opposite to the shoe housing 12 .
  • This outer stopper 18 is a column pin which is eccentrically located with respect to a rotation center “Cr” of the rotors 10 and 20 .
  • the rotational bush 200 b has a heptagonal profile as shown in FIGS. 5 to 8 .
  • One corner portion of the rotational bush 200 b radially outwardly protrudes more than the other corner portions. This protruding corner portion forms a support portion 204 .
  • an angle position of the support portion 204 is denoted by “SA”.
  • the inner rotor 20 includes a plate-shaped rotational arm 206 which radially outwardly extends from the rotational bush 200 b and an inner stopper 208 which axially extends from the rotational arm 206 toward the lock plate 14 .
  • the inner stopper 208 is a column-shaped pin which eccentrically locates with respect to the center “Cr” of the rotors 10 and 20 .
  • An eccentric amount of the inner stopper 208 is the same as that of the outer stopper 18 .
  • a rotational locus of the inner stopper 208 does not overlap with the outer stopper 18 .
  • a coil spring 50 is disposed around the rotational bush 200 b .
  • the coil spring 50 is formed by winding a metallic wire 52 spirally.
  • the coil spring 50 is disposed in a clearance 500 between the lock plate 14 and the rotational arm 206 in such a manner that a winding center “Cs” of the coil spring 50 agrees with a rotation center “Cr” of the rotors 10 and 20 .
  • the wire 52 surrounding the rotational bush 200 b forms a most inner winding portion 520 having five bent portions in the circumferential direction.
  • the most inner winding portion 520 is wound around the rotational bush 200 b in such a manner that the five bent portions 520 a respectively confront the corner portions of the bush 200 b .
  • the corner portion 520 a which is most apart from the inner end 520 b in the advance direction “Da” is engaged with the support portion 204 .
  • the most inner winding portion 520 supported by the support portion 204 is always engaged with the inner rotor 20 at a supporting point “Pi”.
  • the most inner winding portion 520 which further extends from the support portion 204 in the advance direction “Da” is apart from the rotational bush 200 b radially outwardly, whereby a space 56 is formed between the portion 520 and the bush 200 b.
  • a most outer winding portion 522 of the coil spring 50 has an outer end portion 522 a which is bent in U-shape. Since the outer end portion 522 a is arranged on a rotational locus of the outer stopper 18 and the inner stopper 208 , the outer end portion 522 a is engaged with at least one of the stoppers 18 and 208 according to the differential phase between rotors 10 and 20 . In the present embodiment, as shown in FIG. 8 , an engaging point “Po” between the outer end portion 522 a and the stopper 18 , 208 is located in an angle range AA which is defined between the angle position “SA” and an angle position which is advanced by 90°.
  • the condition of the coil spring 50 is referred to as a set condition.
  • the condition of the coil spring 50 is referred to as a free condition.
  • the coil spring 50 is configured in such a manner as to satisfy a following formula:
  • T represents a thickness of the wire 52 in a radial direction
  • N represents a number of turn of the wire 52 at the specified angle position “SA”.
  • N is “3”.
  • Rsi represents a radial distance between the supporting point “Pi” and the center “Cs” of the coil spring 50 that is in the set condition.
  • Ro represents a radial distance between a point “Pa” and the center “Cs” of the coil spring 50 that is in the free condition.
  • the point “Pa” corresponds to the angle position “SA” of the coil spring 50 that is in the set condition. Specifically, as shown by a solid line in FIG. 8 , when the coil spring 50 is released in the set condition, the point “Pa” is on the angle position “SA”.
  • the outer end portion 522 a of the coil spring 50 is brought into engagement with the outer stopper 18 , as shown in FIG. 6 .
  • the inner stopper 208 is apart from the outer end portion 522 a in the retard direction “Dr”
  • a twist deformation is generated in the coil spring 50 according to the relative rotation.
  • the inner rotor 20 receives a biasing force in the advance direction “Da” from the coil spring 50 . That is, when the inner rotor 20 is retarded more than the intermediate lock phase, the coil spring 50 is twisted and deformed according to a rotation of the inner rotor 20 in the retard direction “Dr”.
  • the coil spring 50 biases the inner rotor 20 in the advance direction “Da”.
  • the most outer winding portion 522 is engaged with both the outer stopper 18 and the inner stopper 208 in order to correctly switch between the biasing and non-biasing of the inner rotor 20 .
  • the biasing mechanism 5 According to the differential phase between the rotors 10 and 20 , the most outer winding portion 522 is engaged with the outer stopper 18 or the inner stopper 208 . With respect to the intermediate lock phase, the coil spring 50 biases the inner rotor 20 or the coil spring 50 is prohibited to bias the inner rotor 20 . While performing a lost motion, the windings of the wire 52 which are adjacent in the radial direction is shown in FIG. 8 .
  • the windings of the wire 52 of between the engaging point “Po” and the supporting point “Pi” is in contact with each other at a plurality of points “Pc 1 ” and “Pc 2 ” which are adjacent in the radial direction on the specified angle position “SA”.
  • the most inner winding portion 520 is directly supported by the support portion 204 at the specified angle position “SA”.
  • the most inner winding portion 520 is wound around the rotational bush 200 b from the support portion 204 in the retard direction “Dr” and is apart from the support portion 204 in the advance direction “Da” from the support portion 204 .
  • the support portion 204 biases the wire 52 radially outwardly, the inner wire 52 is biased to the outer wire 52 radially at the points “Pc 1 ” and “Pc 2 ”.
  • the wire 52 is supported by the support portion 204 at the points “Pc 1 ” and “Pc 2 ”, it is restricted that the winding of the wire 52 moves apart radially from the adjacent winding of the wire 52 at the points “Pc 1 ” and “Pc 2 ”.
  • the wire 52 Since the coil spring 50 is formed to satisfy the above formula (1) in the set condition, the wire 52 is biased radially inwardly.
  • the most outer winding portion 522 When assembling the coil spring 50 in the set condition, the most outer winding portion 522 is engaged with the engaging point “Po”, so that the wire 52 is easily biased radially inwardly.
  • SA At the specified angle position “SA”, this radial inward biasing force and the radial outward biasing force at the support portion 204 are surely applied to the wire 52 of between the engaging point “Po” and the supporting point “Pi”.
  • the wire lengths “L 1 ” and “L 2 ” are ensured between the points “Pi”, “Pc 1 ” and “Pc 2 ”, which are shorter enough than the wire length between the point “Po” and the point “Pi”. Therefore, in a case that the primary mode vibration propagating between the points “Pi”, “Pc 1 ” and “Pc 2 ” is assumed as shown in FIG. 10 , its primary natural frequency can be increased. Even if the engine vibration is increased according to an increase in engine speed, the primary natural frequency of the coil spring 50 is larger than the engine vibration, whereby the resonance can be avoided with high reliability.
  • the space 58 allows the coil spring 50 to twist and deform. Also, the space 56 allows the coil spring 50 to twist and deform.
  • the twisted coil spring 50 surely biases the inner rotor 20 .
  • the resonance can be avoided with high reliability without deteriorating a biasing operation of the coil spring 50 to the inner rotor 20 .
  • a biasing mechanism 2005 has a first support portion 204 and a second support portion 2204 which support the wire 52 of the coil spring 50 .
  • the second support portion 2204 is a columnar pin which projects form the rotational arm 206 toward the lock plate 14 .
  • the second support portion 2204 is apart from the specified angle position “SA” in the circumferential direction on a specified radial line “SL” which passes through the first support portion 204 on the angle position “SA”. That is, the second support portion 2204 deviates from the angle position “SA” by about 90 ° in a circumferential direction.
  • the second support portion 2204 is located at a space 58 which is defined between the most outer winding portion 522 and a next outer winding portion 2524 .
  • the second support portion 2204 forms direct-support portions “Ps 1 ” and “Ps 2 ” which directly support the most outer winding portion 522 and the next outer winding portion 2524 .
  • the wire lengths “L 1 ” to “L 4 ” which defines the primary natural frequency are ensured between the points “Ps 1 ” and “Ps 2 ” and the points “Pi”, “Pc 1 ” and “Pc 2 ”.
  • antinode portions of the primary mode vibration illustrated by two-dots-dash line in FIG. 12 can be restricted by the second support portion 2204 .
  • the primary natural frequency can be established greater than the supposed maximum engine vibration. Further, a space 58 is defined between the most inner winding portion 520 and the adjacent wire 2524 so that the coil spring 50 is allowed to twist and deform. Thus, the resonance can be avoided with high reliability without deteriorating a biasing operation of the coil spring 50 to the inner rotor 20 .
  • the number of the direct contact portions of the windings of the wire 52 at the position “SA” can be increased according to an increase in turn number of the coil spring 50 .
  • a contact point “Pc 3 ” is formed in addition to the contact points “Pc 1 ” and “Pc 2 ”.
  • FIG. 14 shows another modification in which the support portion 204 is formed by a columnar pin which projects from the rotational arm 206 of the inner rotor 20 .
  • FIG. 15 shows another modification in which the second support portion 2204 is located in a space 58 between the most inner winding portion 520 and its adjacent wire 2524 .
  • the wire 52 can be directly supported by the second support portion 2204 at the point “Ps 1 ” on the line “SL”.
  • FIG. 16 shows the other modification in which the coil spring 50 biases the inner rotor 20 without providing the inner stopper 208 .
  • the valve timing controller 1 may adjusts a valve timing of an exhaust valve, while the advance direction and the retard direction are reversed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
US13/553,918 2011-08-08 2012-07-20 Hydraulic valve timing controller Abandoned US20130036992A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011173211A JP5333544B2 (ja) 2011-08-08 2011-08-08 液圧式バルブタイミング調整装置
JP2011-173211 2011-08-08

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130036993A1 (en) * 2011-08-08 2013-02-14 Denso Corporation Valve timing controller
US20150292585A1 (en) * 2012-12-13 2015-10-15 Suncall Corporation Spiral spring
US20160167106A1 (en) * 2012-12-14 2016-06-16 Suncall Corporation Spiral spring manufacturing method
CN106032759A (zh) * 2014-09-10 2016-10-19 日立汽车系统株式会社 内燃机的气门正时控制装置
US20220220869A1 (en) * 2019-06-21 2022-07-14 Mitsubishi Electric Corporation Valve timing adjustment device
US20240052764A1 (en) * 2021-03-16 2024-02-15 Mitsubishi Electric Corporation Valve timing adjustment device and method for manufacturing valve timing adjustment device

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KR101354800B1 (ko) 2010-01-25 2014-01-22 가부시끼가이샤 도시바 액정/고분자 복합체, 그것을 사용한 액정 표시 장치, 액정/고분자 복합체의 제조 방법

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US20110073056A1 (en) * 2009-09-28 2011-03-31 Aisin Seiki Kabushiki Kaisha Valve opening/closing timing control device
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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
US20100075765A1 (en) * 2008-09-22 2010-03-25 Hydraulik-Ring Gmbh Vane-type camshaft adjuster
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US20100313835A1 (en) * 2009-06-10 2010-12-16 Denso Corporation Valve timing control apparatus
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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130036993A1 (en) * 2011-08-08 2013-02-14 Denso Corporation Valve timing controller
US9062573B2 (en) * 2011-08-08 2015-06-23 Denso Corporation Valve timing controller
US20150292585A1 (en) * 2012-12-13 2015-10-15 Suncall Corporation Spiral spring
US9400026B2 (en) * 2012-12-13 2016-07-26 Suncall Corporation Spiral spring
US20160167106A1 (en) * 2012-12-14 2016-06-16 Suncall Corporation Spiral spring manufacturing method
US9782819B2 (en) * 2012-12-14 2017-10-10 Suncall Corporation Spiral spring manufacturing method
CN106032759A (zh) * 2014-09-10 2016-10-19 日立汽车系统株式会社 内燃机的气门正时控制装置
US9506378B2 (en) 2014-09-10 2016-11-29 Hitachi Automotive Systems, Ltd. Variable valve timing control apparatus of internal combustion engine
US20220220869A1 (en) * 2019-06-21 2022-07-14 Mitsubishi Electric Corporation Valve timing adjustment device
US20240052764A1 (en) * 2021-03-16 2024-02-15 Mitsubishi Electric Corporation Valve timing adjustment device and method for manufacturing valve timing adjustment device
US11933201B2 (en) * 2021-03-16 2024-03-19 Mitsubishi Electric Corporation Valve timing adjustment device and method for manufacturing valve timing adjustment device

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JP5333544B2 (ja) 2013-11-06
JP2013036390A (ja) 2013-02-21

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