WO2013051111A1 - 動弁装置のロッカアーム - Google Patents
動弁装置のロッカアーム Download PDFInfo
- Publication number
- WO2013051111A1 WO2013051111A1 PCT/JP2011/072867 JP2011072867W WO2013051111A1 WO 2013051111 A1 WO2013051111 A1 WO 2013051111A1 JP 2011072867 W JP2011072867 W JP 2011072867W WO 2013051111 A1 WO2013051111 A1 WO 2013051111A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rocker arm
- cam
- sliding contact
- valve
- contact portion
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/185—Overhead end-pivot rocking arms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2810/00—Arrangements solving specific problems in relation with valve gears
- F01L2810/02—Lubrication
Definitions
- the present invention is a rocker arm technology that enables an improvement in fuel consumption and a reduction in the size of an automotive engine valve operating device that opens and closes an engine valve via a rocker arm that is swung by a camshaft cam.
- Patent Document 1 discloses a rocker arm of a valve gear that swings in conjunction with rotation of a cam integrated with an engine camshaft and moves an engine valve up and down.
- a rocker lever (rocker arm) 1 of the following Patent Document 1 is supported by a support member 3 in a swingable manner by engaging a spherically-shaped recess 2 with a spherical end 4 of the support member 3, and a valve (not shown). The other end is brought into contact with a base end portion (valve stem) of a gas exchange valve (engine valve) urged in a valve closing direction by a spring.
- a rotatable roller 6 is provided at the center of the rocker lever (rocker arm) 1, and a cam of a camshaft (not shown) is in contact with the roller 6.
- the rocker lever 1 opens the engine valve when a cam (not shown) pushes the roller 6 down, and closes the engine valve by a biasing force of a valve spring (not shown).
- the camshaft has a biasing force that the cam receives from the valve stem by the valve spring of the engine valve and the camshaft between the cam and the rocker arm when the cam pushes down the rocker arm against the biasing force when the valve is opened.
- Friction torque is generated in a direction that prevents rotation of the camshaft by the generated frictional force. Since the friction torque deteriorates the fuel consumption of the engine, the valve operating device of Patent Document 1 causes the cam that rotates together with the camshaft to roll and contact the roller 6 of the rocker lever 1, and is generated between the cam and the rocker arm. By reducing the frictional force, the frictional torque generated in the camshaft is reduced.
- the roller 6 of Patent Document 1 can reduce the frictional force generated between the cam and the rocker lever 1, but significantly increases the weight of the rocker lever 1 by using a needle bearing or the like. Since the increase in the weight of the rocker lever 1 increases the inertial force of the rocker lever 1, in the valve operating device, it is necessary to reinforce the spring load of the valve spring used for closing the valve. The urging force of the strengthened valve spring increases the friction torque generated in the camshaft by increasing the pressing force of the roller 6 against the cam.
- the present invention provides a valve operating device that opens and closes an engine valve by a rocker arm that swings in conjunction with a cam of a camshaft, and reduces the friction torque that hinders the rotation of the camshaft.
- This is a rocker arm technology that makes it possible to improve fuel economy and reduce the size of the valve gear.
- the rocker arm of the valve operating device is supported at one end by a support member that forms a swing center so as to be swingable, supports the valve stem by a pad surface provided at the other end, and slides the cam of the camshaft.
- a top plate portion having a cam sliding contact portion on the upper surface thereof, and at least one or more standing wall portions formed so as to be narrower than the top plate portion and extending substantially vertically from the top plate portion And it is comprised so that it may have.
- the rocker arm of the valve operating apparatus reinforces the strength of the top plate portion that receives the reaction force from the valve stem by the valve spring at the pad surface and receives the pressing force of the cam at the cam sliding contact portion. And at least one or more standing wall portions are integrated.
- the weight of the rocker arm is formed because the top plate portion is reinforced with a standing wall portion narrower than the top plate portion while being formed to be as thin as necessary. And the inertial force by a rocker arm is remarkably reduced.
- the spring load of the valve spring can be set to be extremely low, the friction torque generated in the camshaft based on the urging force of the valve spring, that is, the rotation of the camshaft is inhibited. Torque can be greatly reduced.
- the roller is omitted, and the friction torque can be reduced by reducing the biasing force of the valve spring as compared with the slight increase in the friction torque generated by sliding the cam on the rocker arm. Becomes more prominent.
- the rocker arm of the valve operating device according to the first or second aspect, wherein at least one hole is provided at a position excluding the cam sliding contact portion of the top plate portion.
- the rocker arm is further reduced in weight by forming the hole.
- the urging force transmitted from the valve spring to the cam is further reduced, and the friction torque generated on the camshaft is further reduced.
- claim 4 is the rocker arm of the valve operating device according to any one of claims 1 to 3, wherein at least one hole is provided in the standing wall.
- the rocker arm of the valve operating device according to the fourth aspect, wherein the hole provided in the standing wall portion swings the cam sliding contact portion swinging around the swing center. It was set up on the orbit.
- the hole portion is formed on the swinging track of the cam sliding contact portion, so that the pressing portion of the rocker arm cam is reduced in weight. Accordingly, in the rocker arm according to the fifth aspect, the rotational moment required for the cam to push down the cam sliding contact portion of the rocker arm is reduced.
- claim 6 is the rocker arm of the valve operating device according to any one of claims 1 to 5, wherein an oil groove is provided in the cam sliding contact portion.
- the lubricating oil flowed between the cam and the cam sliding contact portion is fixed to the oil groove, and when the cam slides on the cam sliding contact portion, an oil film is formed between them. It is formed. As a result, the frictional force generated between the cam and the cam sliding contact portion is reduced, and the wear resistance between the cam and the cam sliding contact portion is improved.
- a seventh aspect of the present invention is the rocker arm of the valve operating device according to any one of the first to sixth aspects, wherein at least one of the cam sliding contact portion and the pad surface has a convex curved surface. It was made to have.
- the cam sliding contact portion When the cross sections in the width direction of both the cam sliding contact portion and the pad surface are formed flat, the cam sliding contact portion is inclined with respect to the cam due to rattling of the rocker arm, and the pad surface is valved due to rattling of the rocker arm. Inclined with respect to the stem. In that case, the cam sliding contact portion generates an unexpected frictional force with the cam when the corner contacts the cam, and the pad surface is between the valve stem by contacting the corner of the valve stem. An unexpected frictional force is generated. The frictional force inhibits the rotation of the camshaft.
- An eighth aspect of the present invention is the rocker arm of the valve operating device according to any one of the first to seventh aspects, wherein the standing wall portion has a pair of inner wall surfaces, and the outer peripheral surfaces of the pair of inner wall surfaces and the valve stem. A gap of approximately 0.1 mm to 1 mm in total is provided between the two.
- the rocker arm of the valve operating apparatus of the first aspect since the friction torque generated in the cam shout is reduced as compared with the conventional one due to the remarkable weight reduction of the rocker arm, the fuel efficiency of the engine is improved. Further, by omitting the roller, it is possible to reduce the size of the valve operating device, reduce the cost of parts, and solve problems caused by abnormal wear of the needle bearing and shaft.
- the rocker arm of the seventh aspect at least one of the frictional force generated between the cam sliding contact portion and the cam or the frictional force generated between the pad surface and the valve stem is reduced. Since the generated friction torque is further reduced, the fuel efficiency of the engine is further improved, and a stable opening / closing operation of the engine valve is realized.
- a stable valve opening / closing operation is realized by reducing the frictional force between the valve and the standing wall.
- FIG. 1 is a perspective view showing the 1st Example of the rocker arm of a valve operating apparatus.
- B is a top view of the rocker arm of the first embodiment.
- FIG. 2A is a cross-sectional view taken along the line AA in FIG. 1B, in which the rocker arm is cut in the longitudinal direction.
- B is a bottom view of the rocker arm of the first embodiment.
- FIG. 3C is a cross-sectional view taken along the line BB in FIG.
- (A) is a figure which shows the modification which made the cam and cam sliding contact part the convex-shaped curved surface, Comprising: It is sectional drawing equivalent to FIG.2 (c).
- FIG. 2 (B) is a view showing a modified example in which the pad surface and the valve stem are convex curved surfaces, and the support portion of the valve stem is cut in the width direction at a position corresponding to EE in FIG. 2 (a). It is sectional drawing. It is operation
- (A) is a perspective view showing the 2nd Example of the rocker arm of a valve operating apparatus.
- (B) is a top view of the rocker arm of the second embodiment.
- (A) is CC sectional drawing of FIG.4 (b).
- (B) is a bottom view of the rocker arm of the second embodiment.
- (C) is a DD cross-sectional view of FIG. 5 (a). It is a perspective view showing the 3rd Example of the rocker arm of a valve operating apparatus.
- the rocker arm 10 of the valve gear of the first embodiment is formed by a metal top plate portion 11 and a pair of standing wall portions 12 and 12.
- the top plate portion 11 includes a protruding portion 13 that protrudes upward, an engaging portion 14 of a support member 16 (end pivot type lash adjuster) provided continuously to the left end of the protruding portion 13, and a right end of the protruding portion 13. It is provided by a support portion 15 that is provided continuously and supports the valve stem 17a of the engine valve 17.
- the protruding portion 13 includes a cam sliding contact portion 18 (a portion surrounded by lines L1 and L2 in FIG. 1A and FIG. 3) where a cam of a camshaft (not shown) slides, and a flat plate portion 19.
- the cam sliding contact portion 18 is formed as an arc-shaped convex portion protruding upward, and the flat plate portion 19 is continuous with the left end of the cam sliding contact portion 18 and is inclined downward.
- the engaging portion 14 of the support member 16 is formed continuously with the left end of the flat plate portion 19 and has a substantially hemispherical shape protruding upward.
- An engagement portion 20 of the support member 16 that is a substantially hemispherical concave portion is formed inside the engagement portion 14, and the engagement portion 20 engages with the spherical head 21 of the support member 16.
- the support portion 15 is formed as an arc-shaped convex portion that is continuous with the right end portion of the cam sliding contact portion 18 and protrudes downward.
- a pad surface 22 which is a portion that comes into contact with the valve stem 17 a, is formed.
- At least one of the cam sliding contact portion 18 and the pad surface 22 is subjected to DLC coating or the like as a surface treatment for realizing a reduction in friction coefficient, an improvement in wear resistance, or an increase in hardness. Is more desirable.
- the surface treatment reduces the frictional force generated between the cam (not shown) and the cam sliding contact portion 18 or the pad surface 22 and the valve stem 17a, and reduces the friction torque generated in the direction of preventing the rotation of the camshaft. To improve fuel economy.
- the cam sliding contact portion 18 may be a simple smooth surface, but it is more desirable to provide a plurality of oil grooves 25 as shown in FIG.
- a plurality of linear oil grooves 25 parallel to the longitudinal direction of the rocker arm are formed.
- a pair of standing wall portions 12 and 12 projecting in a direction substantially perpendicularly downward from these front and rear ends are integrally provided on the lower surfaces of the projecting portion 13 and the support portion 15.
- the total of the width W2 in the front-rear direction of the pair of standing wall portions 12 and 12 is formed to be narrower than the width W1 of the top plate portion 11.
- the rocker arm 10 is formed in a shape approximating an inverted U shape in the cross section in the front-rear direction, and has a hollow portion 24 on the inside, so that the weight is reduced.
- the pair of standing wall portions 12 and 12 are provided with holes 23 and 23 penetrating in the front-rear direction.
- the hole portion may be formed in the top plate portion 11 as long as it is a portion excluding the cam sliding contact portion 18 and the pad surface 22 such as the flat plate portion 19.
- the rocker arm 10 is reduced in weight by the holes 23 and 23.
- the weight reduction of the rocker arm 10 reduces the frictional force generated between the cam and the cam sliding contact portion 18 and reduces the friction torque acting in the direction of inhibiting the rotation of the camshaft in the camshaft. To improve.
- FIG. 2A shows a modification of the cam sliding contact portion and the pad surface of the first embodiment.
- the rocker arm 10 'in FIG. 2A has the same configuration as the rocker arm 10 in FIG. 1, except for the cam sliding contact portion 18' and the pad surface 22 '.
- 2A (a) is formed so that the cross section in the width direction has a convex curved surface that is convex toward the cam 9, and the pad surface 22 of the support portion 15 'in FIG. 2A (b).
- the cross section in the width direction is formed to have a convex curved surface that is convex toward the upper end portion 17e' of the valve stem 17a 'of the engine valve 17'.
- the cam 9, the cam sliding contact portion 18 ', the pad surface 22', and the valve stem 17a ' may be tilted back and forth with respect to the axis L5 extending in the vertical direction of the rocker arm due to the rattling.
- the corner (18a ', 18b') of the cam sliding contact portion 18 ' contacts the sliding contact surface 9a of the cam 9, or the width direction corner (17b) of the upper end portion 17e' of the valve stem 17a '.
- ', 17c' contacts the pad surface 22 ', a frictional force that prevents the rotation of the camshaft is generated, which causes a problem in that the engine valve can be opened and closed stably.
- the rocker arm 10 ' shown in FIG. 2A has an advantage that a frictional force that hinders the rotation of the camshaft is unlikely to occur at the cam sliding contact portion 18' and the pad surface 22 '.
- the sliding contact surface 9a of the cam 9 and the upper end portion 17e 'of the valve stem 17a' are both formed so that the cross section in the width direction is a convex curved surface.
- the corners (9b, 9c) of the cam 9 and the corners (18a ′, 18b ′) of the cam sliding contact portion 18 ′ are less likely to contact the cam sliding contact portion 18 ′ and the sliding contact surface 9a, respectively.
- the corners (17b ′, 17c ′) of the upper end portion 17e ′ of the valve stem 17a ′ are further less likely to contact the pad surface 22 ′.
- the rocker arm 10 is supported by the support member 16 so as to be swingable about the swing center L ⁇ b> 0 of the ball head 21 by the engagement portion 20 engaging the ball head 21. .
- the rocker arm 10 is a cross-sectional view, but the cut surface of the top plate portion 11 is omitted from the hatching.
- the pad surface 22 is biased upward by a valve stem 17a that receives a biasing force in a valve closing direction from a valve spring (not shown).
- the cam sliding contact portion 18 is pressed against a cam of a cam shaft (not shown) disposed above the cam surface, and the cam shaft always slides with the cam sliding contact portion 18. Rotates in contact.
- the rocker arm 10 swings in the direction (D1 direction in FIG. 3) to open the engine valve 17 by being pushed down by the rotating cam, and according to the rotational position of the cam and the biasing force of the valve spring received from the engine valve 17. And swings in the direction in which the engine valve 17 is closed (direction D2 in FIG. 3).
- the cam sliding contact portion 18 (the portion surrounded by the lines L1 and L2 in FIG. 3) swings around the swing center L0.
- fluctuation of the lines L1 and L2 is represented by the dashed-dotted lines L3 and L4
- the hole parts 23 and 23 are formed in the area
- the pressing part by the cam which is not illustrated is reduced in weight.
- the rocker arm 10 the rotational torque required for the cam to push down the cam sliding contact portion is reduced, and the friction torque acting in the direction of inhibiting the rotation of the camshaft in the camshaft is reduced. Improved fuel economy.
- the rocker arm 29 according to the second embodiment is different from the standing wall portions 12 and 12 according to the first embodiment in the shape of the standing wall portion 31 and includes ribs 32 and 32 for reinforcement, and is common to the rocker arm 10 according to the first embodiment. It has a configuration.
- the rocker arm 29 of the second embodiment is formed by a metal top plate portion 30 and a standing wall portion 31.
- the top plate portion 30 having the same shape as the top plate portion 11 of the first embodiment is constituted by a projecting portion 33, a support member engaging portion 34 (not shown), and a valve stem support portion 35.
- the protruding portion 33 includes a cam sliding contact portion 36 and a flat plate portion 37.
- the engaging portion 34 is formed continuously from the left end of the flat plate portion 37 and has a substantially hemispherical shape protruding upward. Inside the engaging portion 34, a substantially hemispherical recessed engaging portion 38 that engages with a spherical head of a support member (not shown) is formed.
- a pad surface 39 which is a portion that abuts on a valve stem (not shown) biased upward, is formed.
- at least one of the cam sliding contact portion 36 and the pad surface 39 is more preferably subjected to DLC coating or the like as a surface treatment for realizing a reduction in friction coefficient.
- the cam sliding contact portion 36 is provided with a plurality of oil grooves 42 as in the first embodiment to fix the lubricating oil.
- the top plate portion 30 is provided with a pair of ribs 32 and 32 that are integrated with the flat plate portion 37 and the engaging portion 34 and that extend above these.
- the ribs 32, 32 reinforce the rocker arm 29 via the top plate portion 30 and improve the rigidity of the rocker arm 29, thereby improving the responsiveness of the valve gear.
- the ribs 32 may be provided between the flat plate portion 19 and the engaging portion 14 of the first embodiment.
- the standing wall portion 31 is formed to extend downward from the lower surface of the top plate portion 30.
- the standing wall portion 31 in FIG. 5B includes one standing wall portion 40 projecting downward from the center in the longitudinal direction of the projecting portion 33, a pair of standing wall portions 41 projecting downward from the front and rear ends of the support portion 35, and a U-shape. Formed by the portion 43.
- One standing wall portion 40 is integrated with the pair of standing wall portions 41 by a U-shaped portion 43.
- the total of the width W3 in the front-rear direction of one standing wall 40 and the width W4 of the pair of standing walls 41, 41 is formed to be narrower than the width W1 of the top plate 30.
- the rocker arm 29 has a substantially T-shaped cross section at a position where one standing wall portion 40 is formed, as shown in FIG. 5C, and a cross section at the position where a pair of standing wall portions 41 are formed.
- the one standing wall 40 is provided with a hole 44 penetrating in the front-rear direction.
- the hole portion may be formed in the top plate portion 30 as long as it is a portion excluding the cam sliding contact portion 36 and the pad surface 39.
- the rocker arm 29 is reduced in weight by the hole 44.
- the hole 44 is on the track on which the cam sliding contact portion 36 swings in the standing wall portion 31 in order to reduce the weight of the portion pressed by the cam in the same manner as the holes 23 and 23 of the first embodiment. It is desirable to be provided.
- FIG. 6 shows the rocker arm 50 of the third embodiment.
- the rocker arm 50 has the same configuration as the rocker arm 10 of the first embodiment, except that the shape of the oil groove 51 is different from the oil groove 25 of FIG.
- a large number of dimple-shaped oil grooves 51 are formed in the cam sliding contact portion 18 ′′ of the rocker arm 50.
- the large number of oil grooves 51 form a strong oil film between a cam (not shown) and the cam sliding contact portion 18 '' by holding a large amount of lubricating oil, and therefore, between the cam and the cam sliding contact portion 18 ''. Abrasion resistance is further improved.
- Camshaft cam 10 Rocker arm of valve gear 11 Top plate portion 12, 12 'Standing wall portion 12a', 12b 'Inner wall surface 16 Support member (end pivot type lash adjuster) 17a, 17a ′ Valve stem of engine valve 17d ′ Outer peripheral surface of valve stem 18, 18 ′, 18 ′′ Cam sliding contact portion 22, 22 ′ Pad surface 23 Hole portion 25 Oil groove 29 Rocker arm of valve operating device 30 Top plate portion 31 Standing wall portion 36 Cam sliding contact portion 39 Pad surface 42 Oil groove 44 Hole portion 50 Rocker arm of valve gear 51 Oil groove L0 Center of swing
Abstract
Description
10 動弁装置のロッカアーム
11 天板部
12,12’ 立壁部
12a’,12b’ 内壁面
16 支持部材(エンドピボット型ラッシュアジャスタ)
17a,17a’ エンジンバルブのバルブステム
17d’ バルブステムの外周面
18,18’,18’’ カム摺接部
22、22’ パッド面
23 孔部
25 油溝
29 動弁装置のロッカアーム
30 天板部
31 立壁部
36 カム摺接部
39 パッド面
42 油溝
44 孔部
50 動弁装置のロッカアーム
51 油溝
L0 揺動中心
Claims (8)
- 揺動中心を形成する支持部材によって一端を揺動可能に支持され、他端に設けられたパッド面によってバルブステムを支持し、カムシャフトのカムを摺接させるカム摺接部をその上面に有する天板部と、
前記天板部よりも幅を狭く形成され、前記天板部から略垂直方向に延出するよう設けられた少なくとも一以上の立壁部と、
を有することを特徴とする、動弁装置のロッカアーム。 - 前記カム摺接部または前記パッド面のうち少なくとも一方には、摩擦係数低減用の表面処理がなされたことを特徴とする、請求項1に記載の動弁装置のロッカアーム。
- 前記天板部の前記カム摺接部を除く位置に少なくとも一以上の孔部が設けられたことを特徴とする請求項1または2に記載の動弁装置のロッカアーム。
- 前記立壁部に少なくとも一以上の孔部が設けられたことを特徴とする、請求項1から3のうちいずれかに記載の動弁装置のロッカアーム。
- 前記立壁部に設けられた孔部は、前記揺動中心の周りを揺動するカム摺接部の揺動軌道上に設けられたことを特徴とする、請求項4に記載の動弁装置のロッカアーム。
- 前記カム摺接部に油溝が設けられたことを特徴とする、請求項1から5のうちいずれかに記載の動弁装置のロッカアーム。
- 前記カム摺接部または前記パッド面のうち少なくとも一方の幅方向断面が、凸曲面形状を有することを特徴とする、請求項1から6のうちいずれかに記載の動弁装置のロッカアーム。
- 前記立壁部が一対の内壁面を有し、前記一対の内壁面と前記バルブステムの外周面との間には、合計で略0.1mm~1mmとなる隙間が設けられたことを特徴とする、請求項1から7のうちいずれかに記載の動弁装置のロッカアーム。
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012531149A JP5936001B2 (ja) | 2011-10-04 | 2011-10-04 | 動弁装置のロッカアーム |
KR1020137023208A KR20140066971A (ko) | 2011-10-04 | 2011-10-04 | 동밸브 장치의 로커 암 |
EP11873550.5A EP2765284A4 (en) | 2011-10-04 | 2011-10-04 | ROCKER LEVER FOR VALVE TRANSMISSION |
US14/006,883 US20140007832A1 (en) | 2011-10-04 | 2011-10-04 | Rocker arm for valve control apparatus |
CN2011800701576A CN103477036A (zh) | 2011-10-04 | 2011-10-04 | 动阀装置的摇臂 |
PCT/JP2011/072867 WO2013051111A1 (ja) | 2011-10-04 | 2011-10-04 | 動弁装置のロッカアーム |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2011/072867 WO2013051111A1 (ja) | 2011-10-04 | 2011-10-04 | 動弁装置のロッカアーム |
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WO2013051111A1 true WO2013051111A1 (ja) | 2013-04-11 |
Family
ID=48043303
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PCT/JP2011/072867 WO2013051111A1 (ja) | 2011-10-04 | 2011-10-04 | 動弁装置のロッカアーム |
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US (1) | US20140007832A1 (ja) |
EP (1) | EP2765284A4 (ja) |
JP (1) | JP5936001B2 (ja) |
KR (1) | KR20140066971A (ja) |
CN (1) | CN103477036A (ja) |
WO (1) | WO2013051111A1 (ja) |
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CN104481622A (zh) * | 2014-11-20 | 2015-04-01 | 绵阳富临精工机械股份有限公司 | 一种无滚子气门摇臂及其加工方法 |
FR3031137B1 (fr) * | 2014-12-29 | 2016-12-23 | Renault Sa | Linguets de distribution arretes axialement par l'axe d'articulation et par la culasse |
DE102016206837A1 (de) * | 2016-04-22 | 2017-10-26 | Schaeffler Technologies AG & Co. KG | Schlepphebel für eine Brennkraftmaschine |
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- 2011-10-04 WO PCT/JP2011/072867 patent/WO2013051111A1/ja active Application Filing
- 2011-10-04 EP EP11873550.5A patent/EP2765284A4/en not_active Withdrawn
- 2011-10-04 US US14/006,883 patent/US20140007832A1/en not_active Abandoned
- 2011-10-04 KR KR1020137023208A patent/KR20140066971A/ko not_active Application Discontinuation
- 2011-10-04 JP JP2012531149A patent/JP5936001B2/ja active Active
- 2011-10-04 CN CN2011800701576A patent/CN103477036A/zh active Pending
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See also references of EP2765284A4 |
Also Published As
Publication number | Publication date |
---|---|
EP2765284A4 (en) | 2016-03-09 |
JPWO2013051111A1 (ja) | 2015-03-30 |
CN103477036A (zh) | 2013-12-25 |
JP5936001B2 (ja) | 2016-06-15 |
US20140007832A1 (en) | 2014-01-09 |
EP2765284A1 (en) | 2014-08-13 |
KR20140066971A (ko) | 2014-06-03 |
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