US20040231622A1 - Valve train for internal combustion engine - Google Patents

Valve train for internal combustion engine Download PDF

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Publication number
US20040231622A1
US20040231622A1 US10/811,728 US81172804A US2004231622A1 US 20040231622 A1 US20040231622 A1 US 20040231622A1 US 81172804 A US81172804 A US 81172804A US 2004231622 A1 US2004231622 A1 US 2004231622A1
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United States
Prior art keywords
roller
cam lobe
outer circumferential
circumferential surface
surface roughness
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Abandoned
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US10/811,728
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English (en)
Inventor
Hiroyuki Takamura
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.)
Nippon Piston Ring Co Ltd
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Individual
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Filing date
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Assigned to NIPPON PISTON RING CO., LTD. reassignment NIPPON PISTON RING CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TAKAMURA, HIROYUKI
Publication of US20040231622A1 publication Critical patent/US20040231622A1/en
Abandoned legal-status Critical Current

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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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • 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
    • F01L1/181—Centre pivot rocking arms
    • 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
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values

Definitions

  • the present invention relates to a valve train for an internal combustion engine, comprising a cam lobe fixed on a cam shaft, and a roller follower provided with a roller to be contacted with the cam lobe while rotating.
  • Japanese Patent Application Laid Open No. 2002-70507 discloses a method for reducing the resistance due to the friction, in which the slide-contacting type cam follower is allowed to have a surface layer with a lowered coefficient of dynamic friction by forming at least the area of the surface layer sliding against the cam lobe is formed with a diamond and making the surface roughness Ra of this area be 0.3 ⁇ m or less.
  • the low friction has been achieved by changing from the can follower of the type of slide-contacting with the cam lobe (ex., flat tappet, or the like) to the roller follower of the type of rotation-contacting, such as a roller rocker arm and a roller tappet.
  • Japanese Patent Application Laid Open No. 3-78507 discloses that a minute ruggedness of Ra in the range of 0.08 to 0.25 ⁇ m is formed on an outer circumferential surface of the rotation-contacting part (roller rim) of the roller follower with respect to the cam lobe which is a part coming in rotation-contact with the cam lobe to improve a performance of retaining a lubricant oil on such outer circumferential surface, thus preventing the abnormal wear.
  • Japanese Patent Application Laid Open No. 2001-329807 discloses that a surface roughness Ra of an outer circumferential surface of the cam lobe in the valve train is made 0.5 ⁇ m or less, and a surface roughness Ra of an outer circumferential surface of the rotation-contacting part (roller rim) of the roller on the roller rocker arm with respect to the cam lobe is made 0.1 ⁇ m or less to achieve prevention of pitching in the outer circumferential surface of the cam lobe and prevention of peeling from the outer circumferential surface of the roller as well as reduction of wear on the outer circumferential surface of the cam lobe, and it also discloses that a surface roughness Ra of an outer circumferential surface of the cam lobe is made 0.5 ⁇ m or less to achieve reduction of aggressiveness (attacking) with respect to the outer circumferential surface of the rotation contacting part (roller rim) of the roller of the roller rocker arm with respect to the cam lobe.
  • the inventor of the present invention found the following fact. That is, in a rotation-contacting type combination of the cam lobe and the roller follower, the cam lobe and the roller follower are both abrasion products and accordingly low in the dynamic friction coefficient so that minute slippage is caused between the cam lobe and the roller follower and accordingly the efficient rotation is obstructed, thus leading a problem that the friction loss is caused.
  • the present invention has been achieved, and an object thereof is to provide a valve train for an internal combustion engine, capable of eliminating the minute slippage between the cam lobe and the roller follower, and reducing the friction loss in the valve train system.
  • the present inventor has found out that the friction loss in the valve train system having a combination of a cam lobe and a roller follower can be reduced by increasing the dynamic friction coefficient between the cam lobe and the roller follower so as to eliminate the minute slippage at the time of rotation-contact.
  • a first aspect of the present invention provides a valve train for an internal combustion engine, which comprises a cam lobe fixed on a cam shaft, and a roller follower provided with a roller to come in rotation-contact with the cam lobe, wherein the cam lobe is made of an iron based sintered material, and the surface roughness Ra of the outer circumferential surface thereof is in a range of 0.4 to 2.2 ⁇ m.
  • the surface roughness Ra of the outer circumferential surface of the roller is in a range of 0.4 to 2.2 ⁇ m.
  • a second aspect of the present invention provides a valve train for an internal combustion engine, which comprises a cam lobe fixed on a cam shaft, and a roller follower provided with a roller to come in rotation-contact with the cam lobe, wherein the surface roughness Ra of the outer circumferential surface of the roller is in a range of 0.4 to 2.2 ⁇ m.
  • the surface roughness Ra of the outer circumferential surface of the cam lobe is in a range of 0.4 to 2.2 ⁇ m.
  • valve train of the present invention allows smooth rotation of the roller follower, the minute slippage between the cam lobe and the roller follower can be eliminated, thus reducing the friction loss in the valve train system.
  • FIG. 1 is a view showing a configuration example of a valve train for an internal combustion engine according to the present invention
  • FIG. 2 is a view showing an example of a cam lobe.
  • FIG. 3 is an enlarged front view of an example of a contact part of a rocker arm with respect to a cam lobe
  • FIG. 4 is a graph showing the transition of the friction characteristic (1,500 rpm) according to the combination between the cam lobe outer circumferential surface roughness and the roller outer circumferential surface roughness;
  • FIG. 5 is a graph showing the transition of the friction characteristic (2,000 rpm) according to the combination between the cam lobe outer circumferential surface roughness and the roller outer circumferential surface roughness:
  • FIG. 6 is a graph showing the transition of the friction characteristic (2,500 rpm) according to the combination between the cam lobe outer circumferential surface roughness and the roller outer circumferential surface roughness;
  • FIG. 7 is a graph showing the transition of the pitching characteristic according to the combination between the cam lobe outer circumferential surface roughness and the roller outer circumferential surface roughness;
  • FIG. 8 is a view showing the configuration of a friction torque measuring device.
  • FIG. 9 is a view showing the configuration of a roller on roller rolling-and sliding wear tester device for measuring the number of pitching.
  • a valve train for an internal combustion engine comprises a cam lobe fixed on a cam shaft to be rotated synchronously with a crank shaft of an engine, and a roller follower provided with a roller to come in rotation-contact with the cam lobe.
  • rotation-contact means that the roller is in contact with the cam shaft while the roller is rotating.
  • the roller follower is a member provided with a roller to be in rotation-contact with a cam lobe at its part contacting with the cam lobe for converting the rotating motion of the cam shaft to the valve reciprocal motion, and it can be designed in a suitable form according to the structure of the valve operating mechanism.
  • roller follower examples include, a rocker arm (roller rocker arm) or a tappet (roller tappet) both of which are of the type provided with a roller at its contacting part with respect to the cam lobe, or another type in which a roller to be in rotation-contact with the cam lobe is directly mounted on the top end at the base part of the valve member, or the like.
  • FIG. 1 shows an embodiment of a valve train according to the present invention.
  • the valve train of this embodiment is composed of a cam lobe 2 fixed on a cam shaft 1 , and a rocker arm 3 provided with a roller 4 to be in rotation-contact with the cam lobe.
  • the rocker arm 3 has a rocker arm main body 5 , at one end part of which it supports the roller 4 rotatably by a pin 6 , and the rocker arm 3 itself is supported swayably at a middle part of the main body 5 by a rocker shaft 7 , and furthermore, an adjusting screw 8 which is screwed on the other end part of the rocker arm 3 butts against an end face of a base part of a valve body 9 by its top end part.
  • a compression spring 10 applies an elastic force to the valve body 9 in the direction of closing an intake port or an exhaust port.
  • FIG. 2 includes a front view ( 2 A) and a side view ( 2 B) respectively showing an example of the shape of the cam lobe 2 .
  • FIG. 3 is an enlarged front view of an example of the contact part of the rocker arm 3 at which it comes in contact with the cam lobe 2 .
  • the rocker arm 3 supports the roller 4 rotatably in the following manner: a pair of supporting wall parts 5 a each having a bearing hole 5 b and positioning with an interval therebetween is formed on one end part of the rocker arm main body 5 , at which the rocker arm main body 5 comes into contact with the cam lobe 2 , the roller 4 having a bearing hole 4 a is disposed between the pair of the supporting wall parts 5 a , and the pin 6 is inserting through one bearing hole 5 b of the supporting wall parts, the bearing hole 4 a of the roller 4 , and then the other bearing hole 5 b of the supporting wall parts.
  • the material of the roller 4 is not particularly limited, and for example, a bearing steel such as the bearing steel SUJ2, or the like is preferable.
  • At least one of the measures described below is applied to the valve train in order to rotate the roller smoothly without causing the minute slippage at the time of bringing the cam lobe 2 of the cam shaft into rotation-contact with the roller 4 of the roller follower.
  • Measure 1 A cam lobe made of an iron sintered material is used, and the surface roughness Ra of the outer circumferential surface thereof is made to be in a range of 0.4 to 2.2 ⁇ m, preferably 0.4 to 1.2 ⁇ m, and particularly preferably 0.85 to 1.2 ⁇ m.
  • the surface roughness Ra of the outer circumferential surface of the roller of the roller follower (the contacting surface with respect to the cam lobe) is made to be in a range of 0.4 to 2.2 ⁇ m, and preferably 0.4 to 1.2 ⁇ m
  • the dynamic friction coefficient of the contact surface between the cam lobe and the roller is increased by using an iron based sintered material for forming the cam lobe and further setting the surface roughness Ra of the outer circumferential surface to 0.4 ⁇ m or more.
  • Such increase of the dynamic friction coefficient can prevent the minute slippage therebetween, thus alleviating the friction loss of the valve train system.
  • the surface roughness Ra of the outer circumferential surface on the cam lobe is set to 2.2 ⁇ m or less.
  • the sintered cam lobe for the first measure one made of any iron based sintered alloy such as a Mo—Ni—Fe based ones and a Mo—Ni—Cr—Fe based one can be used.
  • iron based sintered alloy those having a porosity about 2 to 10% can be used from the view point of the strength, the wear resistance or the like of the cam lobe.
  • the friction loss can further be alleviated while restraining the increase of the pitching wear, and thereby the minute slippage between the cam lobe and the roller can further be restrained to the lower degree, thus being preferable.
  • the material of the roller 4 is not particularly limited, for example, a bearing steel, such as the bearing steel SUJ2 is preferable.
  • the dynamic friction coefficient of the contact surface between the cam lobe and the roller is increased by setting the surface roughness Ra of the outer circumferential surface on the roller to 0.4 ⁇ m or more.
  • Such increase of the dynamic friction coefficient can prevent the minute slippage therebetween, thus alleviating the friction loss of the valve train system.
  • the surface roughness Ra of the outer circumferential surface on the roller is set to 2.2 ⁇ m or less.
  • the material of the cam lobe 2 is not particularly limited, any material known for the conventional cam lobe may be used, and examples thereof include an iron based sintered alloy, a carbon steel S50C (it may be subjected to high frequency quenching), or the like.
  • the surface roughness Ra of the outer circumferential surface (the contacting surface with the roller) on the cam lobe 2 is also set within a range of 0.4 to 2.2 ⁇ m, in particular, 0.
  • the friction loss can further be alleviated while restraining the increase of the pitching wear, and thereby the minute slippage between the cam lobe and the roller can further be restrained to the lower degree, thus being preferable.
  • the method for controlling the surface roughness of each contact surface on the roller and the cam lobe in the above-mentioned range is not particularly limited, and various surface works can be applied, for example, the grinding work such as cross hatching, and blasting work such as shot blasting which is a method of blowing the hard particles such as the metal particles and the ceramic particles at the high speed and high pressure.
  • blasting work such as shot blasting which is a method of blowing the hard particles such as the metal particles and the ceramic particles at the high speed and high pressure.
  • shot blasting is suitable, and particularly suitable condition for the shot blasting is to jet the steel grids having a 44 ⁇ m average particle size by 0.44 to 0.55 MPa.
  • the cam lobe after sintering process may be subjected to a refining process as needed, and the cam lobe subjected to such process may be used as it is without applying the blast work.
  • the sintering powder were prepared such that the element composition after secondary sintering was adjusted to C: 0.8% by mass, Mo: 0.5% by mass, Ni: 2.5% by mass, and Fe: remainder. Furthermore, as the lubricating agent, a zinc stearate was added and mixed.
  • a temporary sintered compact was obtained by executing first press molding (primary molding) the prepared sintering particles by a 500 to 800 Mpa (5 to 8 ton/cm 2 ) surface pressure so as to form a green compact, and by executing temporary sintering (primary sintering) the green compact at 600° C. to 900° C. in a vacuum sintering furnace. Then, a secondary sintered compact was obtained by executing second press molding (secondary molding) the temporary sintered compact by a 700 to 1200 Mpa (7to 12ton/cm 2 ) surface pressure, and by executing main sintering (secondary sintering) the secondary compact at 1,100° C. to 1,200° C.
  • This secondary sintered compact was further subjected to the quench and temper process, and then grinding finish process of the outer circumferential surface, thereby obtaining a cam lobe made of an iron based sintered material which had an outer circumferential hardness at 52 HRC, a density at 7.46 Ngm ⁇ 3 , and a surface roughness Ra of the outer circumferential surface in the range of 0.2 to 2.2 ⁇ m.
  • a bearing steel SUJ2 shaped in a roller was subjected to the quench and temper process, and then grinding finish process of the outer circumferential surface, thereby obtaining a roller having an outer circumferential hardness at 61 HRC, and a surface roughness Ra of the outer circumferential surface in the range of 0.2 to 2.2 ⁇ m.
  • the force Fz in the horizontal direction (the direction perpendicular to the cam shaft) of the roller circumference, the friction force Fy with respect to the guide part 12 , and the force Fx in the cam shaft direction were measured by a three component force sensor 13 , and the load Fp of the push rod 11 was measured by a force sensor 14 .
  • the friction torque Ff was calculated from the measurement results and the contact angle ⁇ and the contact load Fc between the cam lobe and the roller, and using the below-mentioned formula.
  • roller size the contact part with the cam lobe of the roller rocker arm having a 34 mm cylinder size provided with the roller part having a 28 mm outer diameter and a 17 mm width
  • Cam lobe size basic circle radius 23 mm, lifting amount 7.9 mm
  • Lubricant oil SAE10W-30
  • oil temperature 90° C.
  • Cam rotation speed 1,500 rpm, 2,000 rpm, 2,500 rpm
  • the cycle times of the rotation at which the pitching was caused was measured in the following manner: the outer circumferential surface on the cam lobe iron based sintered material (test piece 15 ) of the cam shaft and that on the roller (counterpart cylindrical test piece 16 ) of the roller rocker arm were brought into contact with each other under 3,000 N of the applied lord (load 18 ); the rotation of the cam lobe iron based sintered material (test piece 15 ) was started at a constant rotation frequency (rotation speed) while a lubricant oil 17 was dropped to the contact surface between the test pieces; and then the cycle times of rotation was counted till occurrence of the pitching.
  • the results are shown in the Table 7 and FIG. 7.
  • the combinations shown in the Table 7 are encoded as shown in the Table 8.
  • Test machine roller on roller rolling-and sliding wear tester
  • Lubricant oil SAE10W-30
  • Oil temperature 100° C.
  • Amount of lubricant oil supplied 2 ⁇ 10 ⁇ 4 m 3 /min
  • Judgment method The occurrence of cracks due to the pitching was detected by the AE (acoustic emission), and the cycle times when the occurrence of cracks was detected was defined as the cycle time leading to the pitching.
  • the friction torque (Ff (0.2/0.2)) of the combination with the surface roughness Ra of the outer circumferential surface of the cam lobe of 0.2 ⁇ m and the surface roughness Ra of the outer circumferential surface of the roller of 0.2 ⁇ m that is, the combination with the surface roughness Ra of the outer circumferential surface of the cam lobe of less than 0.4 ⁇ m and the surface roughness Ra of the outer circumferential surface of the roller of less than 0.4 ⁇ m was 0.28 N ⁇ m, 0.19 N ⁇ m, and 0.15 N ⁇ m, respectively at the 1,500 rpm, 2,000 rpm and 2,500 rpm.
  • the friction torque (Ff (2.2/2.2)) of the combination with the surface roughness Ra of the outer circumferential surface of the cam lobe of 2.2 ⁇ m and the surface roughness Ra of the outer circumferential surface of the roller of 2.2 ⁇ m was 0.12 N ⁇ m, 0.08 N ⁇ m, and 0.07 N ⁇ m, respectively at the 1,500 rpm, 2,000 rpm and 2,500 rpm.
  • the friction torque in this case tends to be reduced with the rise of the rotational frequency.
  • the improvement ratio (Ff(2.2/2.2)/Ff(0.2/0.2)) of the friction torque (Ff (2.2/2.2)) in the combination of the surface roughnesses Ra of the cam lobe and the outer circumferential surface of the roller of both 2.2 ⁇ m with respect to the friction torque (Ff (0.2/0.2)) in the combination of the surface roughnesses Ra of the cam lobe and the outer circumferential surface of the roller of both 0.2 ⁇ m was each about 4.3/10, 4.2/10 and 4.7/10, respectively at the 1,500 rpm, 2,000 rpm and 2,500 rpm.
  • Friction torque (Cam rotation speed: 2,000 rpm) Outer circumferential surface roughness Ra of Roller part of Roller follower ( ⁇ m) Friction torque Material: quenched SUJ2 (Nm) 0.2 0.4 0.8 1.2 1.6 2.0 2.2 Outer 0.2 0.19 0.18 0.18 0.17 0.16 0.16 0.15 circumferential 0.4 0.17 0.15 0.15 0.14 0.13 0.13 0.12 surface 0.8 0.14 0.14 0.13 0.13 0.11 0.10 0.10 roughness Ra of 1.0 0.13 0.13 0.12 0.12 0.11 0.10 0.09 Cam lobe ( ⁇ m) 1.4 0.11 0.11 0.10 0.10 0.09 0.09 0.09 Material: iron 1.8 0.11 0.11 0.10 0.10 0.09 0.09 0.09 based sintered 2.0 0.11 0.10 0.10 0.09 0.09 0.09 0.09 0.09 0.08
  • Friction torque (Cam rotation speed: 2,500 rpm) Outer circumferential surface roughness Ra of Roller part of Roller follower ( ⁇ m) Friction torque Material: quenched SUJ2 (Nm) 0.2 0.4 0.8 1.2 1.6 2.0 2.2 Outer 0.2 0.15 0.15 0.15 0.14 0.13 0.13 0.13 circumferential 0.4 0.14 0.13 0.12 0.12 0.12 0.11 surface 0.8 0.11 0.10 0.10 0.10 0.10 0.10 0.10 0.10 roughness Ra of 1.0 0.11 0.10 0.10 0.10 0.10 0.10 0.10 0.10 0.10 0.10 Cam lobe ( ⁇ M) 1.4 0.10 0.10 0.10 0.10 0.09 0.09 0.09 Material: iron 1.8 0.09 0.09 0.09 0.09 0.09 0.08 0.08 based sintered 2.0 0.09 0.09 0.09 0.08 0.08 0.08 0.08 0.08 0.07 0.07 0.07
  • the number of pitching occurrence was 5.0 ⁇ 10 5 , and it was smallest.
  • the number of the pitching occurrence can be improved by about 4 times compared with the case of using the chilled cast iron cam shaft in combination with the roller follower. Furthermore, according to the combination of having the surface roughness Ra of the outer circumferential surface of the iron based sintered material cam lobe and the roller of less than 2.2 ⁇ m, the number of the pitching occurrence is improved over 4 times.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Gears, Cams (AREA)
US10/811,728 2003-03-31 2004-03-29 Valve train for internal combustion engine Abandoned US20040231622A1 (en)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP2003095649 2003-03-31
JP2003097478 2003-03-31
JP2003-097478 2003-03-31
JP2003-095649 2003-03-31
JP2003-120256 2003-04-24
JP2003120256 2003-04-24
JP2004052364A JP2004340128A (ja) 2003-03-31 2004-02-26 内燃機関の動弁装置
JP2004-052364 2004-02-26

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JP (1) JP2004340128A (ja)
KR (1) KR100632883B1 (ja)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090266324A1 (en) * 2005-12-27 2009-10-29 Ntn Corporation Rocker Arm, Rocker Shaft, Valve Cap, Adjust Screw, Pivot Receiving Member, and Valve of Arm Type Valve Operating Device
WO2010127731A1 (de) * 2009-05-02 2010-11-11 Thyssenkrupp Presta Teccenter Ag System zur steuerung eines gaswechselventils einer brennkraftmaschine
EP2682230A2 (de) 2012-07-06 2014-01-08 MAHLE International GmbH Verfahren zur Herstellung/Bearbeitung eines Nockens

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Publication number Priority date Publication date Assignee Title
JP2007255277A (ja) * 2006-03-23 2007-10-04 Jtekt Corp カムフォロア
JP2007309392A (ja) * 2006-05-17 2007-11-29 Komatsu Ltd 軸受装置
JP4724083B2 (ja) * 2006-09-27 2011-07-13 株式会社オティックス 内燃機関用カムシャフト
KR101902711B1 (ko) 2017-08-24 2018-11-07 최병영 내연기관의 마찰저감을 위한 밸브트레인 장치

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US4485770A (en) * 1980-12-24 1984-12-04 Honda Giken Kogyo Kabushiki Kaisha Material for valve-actuating mechanism of internal combustion engine
US5456136A (en) * 1991-04-24 1995-10-10 Ntn Corporation Cam follower with roller for use with engine
US5997988A (en) * 1995-11-21 1999-12-07 Koyo Seiko Co., Ltd. Machine part
US6367439B1 (en) * 1998-03-31 2002-04-09 Sumitomo Electric Industries, Ltd. Combination body of shim and cam

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JPS6124818A (ja) * 1984-07-14 1986-02-03 Ntn Toyo Bearing Co Ltd 軸受転動体
JPH07243308A (ja) * 1994-03-01 1995-09-19 Toyota Motor Corp 金属部材同士の摺動装置及び内燃機関の動弁装置
JP3777079B2 (ja) * 2000-02-17 2006-05-24 日本ピストンリング株式会社 カムシャフト
JP2001329807A (ja) * 2000-05-18 2001-11-30 Nsk Ltd エンジンの動弁機構用カムフォロア装置
JP3869192B2 (ja) * 2000-07-17 2007-01-17 株式会社ジェイテクト 転がり摺動部品

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4485770A (en) * 1980-12-24 1984-12-04 Honda Giken Kogyo Kabushiki Kaisha Material for valve-actuating mechanism of internal combustion engine
US5456136A (en) * 1991-04-24 1995-10-10 Ntn Corporation Cam follower with roller for use with engine
US5997988A (en) * 1995-11-21 1999-12-07 Koyo Seiko Co., Ltd. Machine part
US6367439B1 (en) * 1998-03-31 2002-04-09 Sumitomo Electric Industries, Ltd. Combination body of shim and cam

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090266324A1 (en) * 2005-12-27 2009-10-29 Ntn Corporation Rocker Arm, Rocker Shaft, Valve Cap, Adjust Screw, Pivot Receiving Member, and Valve of Arm Type Valve Operating Device
US8118004B2 (en) * 2005-12-27 2012-02-21 Ntn Corporation Rocker arm, rocker shaft, valve cap, adjust screw, pivot receiving member, and valve of arm type valve operating device
WO2010127731A1 (de) * 2009-05-02 2010-11-11 Thyssenkrupp Presta Teccenter Ag System zur steuerung eines gaswechselventils einer brennkraftmaschine
DE102009019788B4 (de) * 2009-05-02 2020-06-18 Thyssenkrupp Presta Teccenter Ag System zur Steuerung eines Gaswechselventils einer Brennkraftmaschine
EP2682230A2 (de) 2012-07-06 2014-01-08 MAHLE International GmbH Verfahren zur Herstellung/Bearbeitung eines Nockens
DE102012211864A1 (de) 2012-07-06 2014-05-22 Mahle International Gmbh Verfahren zur Herstellung/Bearbeitung eines Nockens

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JP2004340128A (ja) 2004-12-02
KR100632883B1 (ko) 2006-10-16
KR20040085074A (ko) 2004-10-07

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