EP1561013A1 - Poussoir de commande a galet de desactivation et a deux etages comprenant un support et un ressort a perte de mouvement - Google Patents

Poussoir de commande a galet de desactivation et a deux etages comprenant un support et un ressort a perte de mouvement

Info

Publication number
EP1561013A1
EP1561013A1 EP02742117A EP02742117A EP1561013A1 EP 1561013 A1 EP1561013 A1 EP 1561013A1 EP 02742117 A EP02742117 A EP 02742117A EP 02742117 A EP02742117 A EP 02742117A EP 1561013 A1 EP1561013 A1 EP 1561013A1
Authority
EP
European Patent Office
Prior art keywords
shaft
bracket
roller
side member
finger follower
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.)
Withdrawn
Application number
EP02742117A
Other languages
German (de)
English (en)
Inventor
Nick John Hendriksma
Jongmin Lee
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.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
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 Delphi Technologies Inc filed Critical Delphi Technologies Inc
Priority claimed from PCT/US2002/019037 external-priority patent/WO2004027224A1/fr
Publication of EP1561013A1 publication Critical patent/EP1561013A1/fr
Withdrawn legal-status Critical Current

Links

Definitions

  • the present invention generally relates to cylinder and/or valve deactivation and two-step variable valve lift systems in internal combustion engines. More particularly, the present invention relates to a roller finger follower rocker arm device that accomplishes valve deactivation and/or cam profile mode switching in internal combustion engines.
  • Deactivation roller finger followers typically include a body and a roller carried by a shaft.
  • the roller is engaged by a cam of an engine camshaft that causes the RFF body to pivot, thereby actuating an associated engine valve.
  • the deactivation RFF is selectively switched between a coupled and a decoupled state.
  • the shaft In the coupled state the shaft is coupled to the body, and rotation of the output cam is transferred from the roller through the shaft to pivotal movement of the RFF body, which, in turn, reciprocates the associated valve.
  • the shaft In the decoupled state, the shaft is decoupled from the body.
  • the shaft does not transfer rotation of the output cam to pivotal movement of the RFF body, and the associated valve is not reciprocated. Rather, the shaft is reciprocated within grooves formed in the RFF body. The grooves retain and guide the reciprocation of the shaft.
  • a two-step RFF operates in a manner similar to a deactivation RFF, as described above.
  • the body of a deactivation RFF is typically engaged by zero-lift cam lobes. In the decoupled mode, the zero-lift cam lobes simply maintain the deactivation RFF body in a static position. Thus, the associated engine valve is not reciprocated.
  • the body of a two-step RFF is engaged by associated low-lift cam lobes. In the decoupled mode, the body of the two- step RFF is pivoted by the low-lift cam lobes. The pivoting of the body of the two-step RFF in the decoupled mode, in turn, reciprocates the associated engine valve according to the lift profile of the low-lift cam lobe.
  • Lost motion springs maintain contact between the roller and the output cam when either type (i.e., deactivation or two-step) of RFF is in the decoupled mode.
  • the lost motion springs engage the shaft and the body of the RFF.
  • the springs bias the shaft and roller against the output cam, and absorb the reciprocal motion of the shaft and roller.
  • lost motion springs add undesirable width to conventional RFF's.
  • movement of the lost motion springs causes wear and friction where the springs contact the body of the roller finger follower. Even further, the side load
  • RFF that reduces the potential for locking pin assembly misalignment, thereby improving the reliability of mode switching in the RFF.
  • RFF that reduces the likelihood of the shaft binding within the grooves, thereby improving the reliability of mode switching in the RFF.
  • the present invention provides a deactivation and/or two-step roller finger follower for use with an internal combustion engine.
  • the invention comprises, in one form thereof, an elongate body having a first side member and a second side member.
  • a bracket having first and second sides is associated with the body. The first side of the bracket is disposed adjacent an inside surface of the first side member of the body. The second side of the bracket is disposed adjacent an inside surface of the second side member of the body.
  • a roller is disposed between the first and second sides of the bracket. The roller defines a shaft orifice therethrough. An elongate hollow shaft extends through the shaft orifice and
  • a locking pin assembly is disposed at least partially within the hollow shaft.
  • the locking pin assembly has a first position wherein the shaft is decoupled from the body and a second position wherein the shaft is coupled to the body.
  • the locking pin assembly is switchable between the first and second positions.
  • An even further advantage of the present invention is a roller finger follower with a reduced likelihood of locking pin misalignment, and thus increased reliability in mode switching of the RFF.
  • FIG. 1 is an isometric view of one embodiment of a roller finger follower of the present invention operably installed in an engine;
  • FIG. 2 is an isometric view of the RFF of Fig. 1 ;
  • FIG. 3 is an isometric view of the lost motion bracket of Fig. 2;
  • FIG. 4 is a side view of the RFF of Fig. 1 ;
  • FIG. 5 is an isometric view of a second embodiment of the lost motion bracket of the present invention as installed in a RFF;
  • FIG. 6 is a side view of the lost motion bracket of Fig. 5;
  • FIG. 7 is a perspective view of the lost motion spring of Fig. 5.
  • FIG 8 is an opposite side view of the lost motion bracket of Fig. 5.
  • roller finger Generally, and as will be described more particularly hereinafter, the roller finger
  • the follower of the present invention includes a lost motion bracket and lost motion springs.
  • the bracket is coupled to a hollow shaft, and coil springs connect the bracket to the body of the roller finger follower.
  • the roller finger follower assembly operates as a conventional roller finger follower.
  • the bracket and coil springs replace the lost motion springs of conventional two-step and deactivation roller finger followers.
  • the bracket and coil springs maintain contact between the roller and the cam when the roller is decoupled from the body of the roller finger follower.
  • roller finger follower (RFF) 10 is installed in internal combustion engine 12.
  • a first end of RFF 10 engages valve stem 14 of engine 12, a second end engages a stem 16 of lash adjuster 18.
  • RFF 10 includes body 20, locking pin assembly 22, roller
  • Body 20 includes first end 32, second end 34, elongate first side member 36, and elongate second side member 38.
  • First end 32 includes valve stem seat 40, which receives valve stem 14 of engine 12.
  • Second end 34 defines a semi-spherical lash adjuster socket 42 (not shown), which receives lash adjuster stem 16 of engine 12.
  • Each of first side member 36 and second side member 38 includes a respective outside surface 36a and 38a.
  • Outer rollers 44, 46 are rotatably disposed, such as, for example, on bosses or studs (not shown), adjacent outside surfaces 36a, 38a, respectively. Outer rollers 44,
  • outer roller 46 rotate freely about axis A.
  • the outer surface (not referenced) of outer roller 44 engages low- or zero-lift cam lobe 48a (Fig. 1) and the outer surface (not referenced) of outer roller 46 engages low- or zero-lift cam lobe 48b (Fig. 1 ).
  • Low- or zero-lift cam lobes 48a, 48b are configured with one of a low lift relative to high-lift cam lobe 48 or substantially zero lift.
  • High-lift cam lobe 48 (Fig. 1 ) is disposed between cam lobes 48a, 48b on camshaft 30, and has high lift profile relative to cam lobes 48a, 48b.
  • First side member 36 and second side member 38 each include an inside surface 36b, 38b, respectively. Inside surface 36b defines groove 50 and inside surface
  • Roller 24 is a substantially cylindrical hollow member. Roller 24 is rotatably disposed upon and carried by engages elongate hollow shaft 54. A plurality of needle bearings (not shown) is disposed between an inside surface of roller 24 and an outside surface of shaft 54. Thus, roller 24 is free to rotate about shaft 54 and relative to axis A in an essentially friction free manner.
  • the outer surface (not referenced) of roller 24 is configured to engage high-lift cam lobe 48 of camshaft 30 of internal combustion engine 12.
  • Locking pin assembly 22 extends through shaft 54, and selectively couples and decouples shaft 54 to and from body 20, and is more particularly described in commonly-assigned U.S. Patent Application Serial No. 09/664,668, the disclosure of which is incorporated herein by reference.
  • Bracket 26 includes, as best shown in Figs. 2 and 3, first bracket end 70, second bracket end 72, first bracket side 74, second bracket side 76, and protrusions 78, 80.
  • Each of first bracket end 70 and second bracket end 72 is somewhat arch-like or parabolic in shape.
  • the bottom surface of first bracket end 70 defines first spring seat 82 and, similarly, the bottom surface of second bracket end 72 defines second spring seat 84.
  • Each of first bracket side 74 and second bracket side 76 is somewhat arch-like or parabolic in shape, and extends longitudinally between first bracket end 70 and second bracket end 72.
  • the top surfaces (not referenced) of first bracket side 74 and second bracket side 76 are substantially planar with the top surfaces (not referenced) of first bracket end 70 and second bracket end 72.
  • first bracket side 74 and second bracket side 76 defines a respective shaft orifice 86, 88 therethrough.
  • Each of shaft orifices 86, 88, is substantially concentric with center axis A when bracket 26 is positioned in RFF 10 and locking pin assembly 22 is selectively positioned in the default/coupled position.
  • Each of first bracket side 74 and second bracket side 76 further defines a respective protrusion 78, 80.
  • Each of protrusions 78, 80 extend from a respective top surface (not referenced) of first bracket side 74 and second bracket side 76 to a respective bottom surface of first bracket side 74 and second bracket side 76.
  • Shaft orifice 86 in first bracket side 74 extends through protrusion 78 and shaft orifice 88 in second bracket side 76 extends through protrusion 80.
  • the side and top edges of each of protrusions 78, 80 are
  • each of the top edges of protrusions 78, 80 is substantially planar with a respective top surface (not referenced) of first bracket side 74 and second bracket side 76.
  • the side edges of protrusions 78,80 are substantially perpendicular to the top edge of protrusions 78, 80.
  • the widths of protrusions 78, 80 are specified such that protrusion 78 slidingly engages groove 50 and protrusion 80 slidingly engages groove 52 with relatively close tolerances.
  • the bottom edges of protrusions 78, 80 are somewhat arch-like or parabolic in shape.
  • bracket 26 is disposed within body 20.
  • first shaft orifice 86 a second end of shaft 54 (not shown) is disposed within second shaft orifice 88.
  • Roller 24 is therefore disposed between first bracket side 74 and second bracket side 76.
  • Bracket 26 extends from first end 32 to second end 34 of body 20.
  • First coil spring 90 is
  • first coil spring seat 82 disposed at least partially within first coil spring seat 82, and is in abutting engagement
  • second coil spring 92 is disposed at least partially within second coil spring seat 84, and is in abutting engagement with second end 34 of body 20.
  • RFF 10 is disposed such that roller 24 engages high-lift cam lobe 48, valve stem seat 40 receives valve stem 14, and lash adjuster socket 42 engages lash adjuster stem 16.
  • Outer rollers 44, 46 each engage a respective low- or zero-lift cam lobes 48a, 48b of camshaft 30, which prevents any undesirable pump up of lash adjuster 18 due to oil pressure.
  • locking pin assembly 22 couples shaft 54, and thus roller 24, to body 20 to thereby transfer rotary motion of high- lift cam lobe 48 to vertical motion of valve stem 14. More particularly, rotary motion of high-lift cam lobe 48 is transferred by roller 24 to shaft 54 and, in turn, to body 20.
  • the coupling of shaft 54, and thus roller 24, to each of first and second side members 36, 38, respectively, by locking pin assembly 22 transfers the rotary motion of high-lift cam lobe 48 via roller 24 to pivoting movement of body 20 about lash adjuster 8, thereby reciprocating valve stem 14 and actuating a corresponding valve of engine 12. Since shaft 54 is coupled by locking pin assembly 22 to body 20, roller 24 and bracket 26 do not move relative to body 20.
  • valve springs 90, 92 are not compressed with locking pin assembly 22 in the default or coupled position.
  • a valve spring biases valve stem 14 towards the closed position.
  • Valve stem 14 biases RFF 10 toward camshaft 30. Therefore, the force due to valve spring 94 maintains the contact between roller 24 and high-lift cam lobe 48.
  • locking pin assembly 22 does not couple shaft 54 to body 20.
  • shaft 54 and roller 24 are not coupled to either of first side member 36 or second side member 38 of body 20.
  • rotary motion of high-lift cam lobe 48 is transferred by roller 24 via shaft 54 to bracket 26.
  • shaft 54, roller 24 and bracket 26 are correspondingly reciprocated relative to body 20.
  • shaft 54 is reciprocated toward and away from camshaft 30.
  • Shaft 54 as described above, carries roller 24, and has a first end (not referenced) disposed within first shaft orifice 86 of bracket 26 and a second end disposed within second shaft orifice 88 of bracket 26.
  • shaft 54 couples roller 24 to bracket 26. Therefore, reciprocation of shaft 54, in turn, is transferred to reciprocation of bracket 26 toward and away from camshaft 30.
  • ⁇ Bracket 26 reciprocates within each of grooves 50 and 52 in a direction toward and away from camshaft 30. In contrast to the default position, rotary motion of high-lift cam lobe 48 is not transferred by roller 24 via shaft 54 and locking pin assembly 22 to
  • valve stem 14 is not reciprocated nor is a corresponding valve of engine 12 actuated.
  • valve stem 14 is reciprocated a relatively small amount due to the engagement of low-lift cam lobes 48a, 48b with outer rollers 44, 46,
  • protrusions 78, 80 of bracket 26 reciprocate or slide within each of grooves 50, 52 in a direction toward and away from camshaft 30.
  • the widths of protrusions 78, 80 are specified such that protrusion 78 slidingly engages groove 50 and protrusion 80 slidingly engages groove 52 with relatively close tolerances.
  • Bracket 26 is substantially precluded from moving in a transverse direction, i.e., in a direction toward and/or away from first end 32 of body 20, by the engagement of protrusions 78, 80 within grooves 50, 52, respectively.
  • Bracket 26 carries shaft 54 which, in turn, carries roller 24.
  • roller 24 and bracket 26 are also substantially precluded from moving in a transverse direction toward and/or away from first end 32 of body 20. Therefore, play of shaft 54 and roller 24 in a transverse direction is substantially reduced, and generally smoother and more controlled displacement thereof occurs due to the engagement of protrusions 78, 80 of bracket 26 within grooves 50, 52, respectively.
  • first coil spring 90 and second coil spring 92 control the motion of bracket 26 toward and away from camshaft 30 and roller 24 toward and away from camshaft 30, and ensure that roller 24 remains in contact with high-lift cam lobe 48.
  • Grooves 50, 52 retain and guide the movement of bracket 26 as high-lift cam lobe 48 rotates and displaces roller 24 and, thus, bracket 26.
  • bracket 26 is disposed upon shaft 54 proximate to first and second side members 36, 38 of body 20.
  • First coil spring 90 engages first coil spring seat 82 and the top surface
  • first and second coil spring 92 engages second coil spring seat 84 and the top surface (not referenced) of second end 34 of body 20.
  • First and second coil springs 90 and 92 apply a spring force or load upon first and second bracket end 70, 72, respectively, to thereby bias bracket 26 and, thus, roller 24 in the direction towards camshaft 30.
  • high-lift cam lobe 48 is rotated from a low-lift to a higher lift profile, a downward force is exerted upon roller 24 and, thus, bracket 26. In the decoupled position, this force is transmitted to first and second coil springs 90, 92 by bracket 26.
  • first and second coil springs 90, 92 upon bracket 26 and, thus, roller 24 is overcome by the force exerted by high-lift cam lobe 48 through roller 24 upon bracket 26, thereby resulting in bracket 26 being slidingly displaced within grooves 50, 52 in a direction away from camshaft 30.
  • the spring constants of first and second coil springs 90, 92 are selected such that the resultant spring force of coil springs 90, 92 on end 32 of body 20 is less than the spring force of the valve spring 94 (not shown) attached to valve stem 14.
  • first and second coil springs 90, 92 bias bracket 26 within grooves 50, 52 in the direction of camshaft 30 and into a position which enables the return of locking pin assembly 22 to the default position.
  • RFF 110 is installed in internal combustion engine 12.
  • RFF 110 includes body 120, locking pin assembly 22, roller 24, and bracket 126.
  • Body 120 includes first side 122 with inner surface 122a and second side 124 with inner surface 124a.
  • First side 122 and second side 124 respectively correspond to first side 36 and second side 38 of body 20.
  • First side 122 and second side 124 respectively differ from first side 36 and second side 38 in that inner surface 122a of first side 122 and inner surface 124a of second side 124 are substantially fiat and do not define grooves such as groove 50 of inner surface 36b and groove 52 of inner surface 38b of RFF 10.
  • Bracket 126 includes first arm 130, second arm 132, spacer 134, spring rod 136, and torsion spring 138.
  • Each of first arm 130 and second arm 132 has a respective first arm end 130a, 132a as well as a respective second arm end 130b, 132b.
  • Each of first arm 130 and second arm 132 are pivotally coupled to body 120 and in close proximity to a corresponding one of first side 122 and second side 124. More particularly, first arm 130 is disposed in close proximity to inside surface 122a of first side 122, and second arm 132 is disposed in close proximity to inside surface 124a of second side 124.
  • the cumulative clearance between first arm 130 and inner surface 122a, and between second arm 132 and inside surface 124a, is a predetermined small distance, such as, for example, between 0.1 to 0.3 millimeters (mm), to allow for lubrication of each respective arm/inner surface interface.
  • a predetermined small distance such as, for example, between 0.1 to 0.3 millimeters (mm)
  • First arm 130 and second arm 132 each define a bend, such as, for example, an angle of approximately 40 degrees, between a respective first end 130a, 132a and a respective second end 130b, 132b thereof.
  • First end 130a of first arm 130 defines first shaft orifice 144 and first end 132a of second arm 132 defines second shaft orifice 146 (not shown).
  • Each of first shaft orifice 144 and second shaft orifice 146 is elongated and/or elliptical in shape.
  • a respective end of shaft 54 is disposed in each of first shaft orifice 144 and second shaft orifice 146.
  • Roller 24 is rotatably disposed upon and carried by shaft 54.
  • Second end 130b of first arm 130 defines first spring rod orifice 148 and second end 132b of second arm 132 defines
  • First spring rod orifice 50 (not shown).
  • First spring rod orifice 148 and second rod orifice 150 are substantially concentric about axis B.
  • First arm 130 further includes first notch 152 and second arm 132 includes second notch 154 (not shown).
  • First notch 152 is proximate second arm end 130b of first arm 130 and second notch 154 is proximate second arm end 132b of second arm 132.
  • Spacer 134 is a hollow cylindrical member interconnecting second arm end 130b of first arm 130 and second arm end 132b of second arm 132. Spacer 134 is substantially concentric about axis B.
  • Spring rod 136 is an elongate cylinder disposed within and extending through spacer 134 into first spring rod orifice 148 and into second spring rod orifice 150. A first end (not referenced) of spring rod 136 defines first shoulder 156 and a second end (not referenced) of spring rod 136 defines second shoulder 158.
  • torsion spring 138 is a double bodied torsion spring and includes spring seating 160, coils 162, 164, and spring arms 166, 168.
  • Spring seating 160 is received within and abuttingly engages a top surface of each of first notch 152 and second notch 154.
  • Spring coil 162 is disposed on spring rod 136 between first shoulder 156 and first arm 130. Spring coil 162 surrounds at (east a portion of spring rod 136 between first shoulder 156 and first arm 130.
  • Spring arm 166 is in abutting engagement with the top surface (not referenced) of first side member 122 of body 120.
  • spring coil 164 is disposed on spring rod 136 between second shoulder 158 and second arm 132. Spring coil 164 surrounds at least a portion of spring rod 136 between second shoulder 158 and second arm 132.
  • Spring arm 168 is in abutting engagement with the top surface (not referenced) of second side member 124 of body
  • RFF 110 works in generally the same manner as RFF 10, and bracket 126 performs the same general function as described above in regard to bracket 26, i.e., limiting movement of roller 24 and shaft 54 in a direction transverse to body 120 to improve switching reliability.
  • bracket 126 performs this function by pivoting rather than reciprocating as does bracket 26.
  • RFF 110 and RFF 10 works in a substantially similar manner to a conventional RFF.
  • locking pin assembly 22 is selectively switched to the decoupled position such that shaft 54, and thus roller 24, are no longer coupled to body 120.
  • rotation of high-lift cam lobe 48 to a higher lift position causes bracket 126 to pivot about axis B of spring rod 136 in a direction away from camshaft 30. More particularly, as high-lift cam lobe 48 rotates to a higher lift position, high-lift cam lobe 48 places a force on roller 24 and, thus, shaft 54 in the direction away from camshaft 30.
  • Torsion spring 138 applies a load to body 120 as bracket 126 pivots away from cam shaft 30.
  • the spring constant of torsion spring 138 is specified such that the load applied to first side 122 and second side 124 of body 120 is smaller than the load that would be required to create a moment about end 34 of body 120 large enough to cause
  • torsion spring 138 maintains contact between roller 24 and high-lift cam lobe 48. More particularly, as high-lift cam lobe 48 rotates or pivots toward a lower lift position, spring seating 160 of torsion spring 138 applies a load to first arm 130 and second arm 132 which, in turn, pivots bracket 126 about spring rod 136 and toward camshaft 30. Thus, torsion spring 138 biases bracket 126 in a direction towards camshaft 30, thereby maintaining roller 24 in contact with high-lift cam lobe 26.
  • roller 24 is disposed within bracket 26 or bracket 126.
  • needle bearings that are disposed between roller 24 and shaft 52 are retained within roller 24 by bracket 26 in the first embodiment.
  • the needle bearings are thereby protected from damage.
  • the elongation of shaft orifices 144, 146 in the second embodiment are small for two-step applications, and bracket 126 retains the needle bearings.
  • side members 36, 38 of RFF 10 each define grooves 50, 52, respectively, within which are received protrusions 78, 80 of bracket 26.
  • RFF 10 and bracket 26 can be alternately configured, such as, for example, as fitting together with relatively tight tolerances to thereby substantially reduce any play in the shaft in a direction generally transverse to the body of the RFF.
  • torsion spring 138 is a double bodied torsion spring.
  • RFF 110 can be alternately configured

Landscapes

  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

La présente invention a trait à un poussoir de commande à galet (10) comportant un corps de forme allongée (20) ayant un premier organe latéral (36), un deuxième organe latéral (38), un support (26) associé au corps, un galet disposé entre les premier et deuxième organes latéraux du support. Le galet y définit un orifice d'arbre avec un arbre creux de forme allongée (54) se prolongeant à travers l'orifice d'arbre. Un ensemble de goupille de verrouillage (22) est disposé au moins en partie au sein de l'arbre creux. L'ensemble de goupille de verrouillage est commutable entre des première et deuxième positions pour le couplage ou découplage de l'arbre par rapport au corps.
EP02742117A 2002-06-17 2002-06-17 Poussoir de commande a galet de desactivation et a deux etages comprenant un support et un ressort a perte de mouvement Withdrawn EP1561013A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2002/019037 WO2004027224A1 (fr) 2000-01-14 2002-06-17 Poussoir de commande a galet de desactivation et a deux etages comprenant un support et un ressort a perte de mouvement

Publications (1)

Publication Number Publication Date
EP1561013A1 true EP1561013A1 (fr) 2005-08-10

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP02742117A Withdrawn EP1561013A1 (fr) 2002-06-17 2002-06-17 Poussoir de commande a galet de desactivation et a deux etages comprenant un support et un ressort a perte de mouvement

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Country Link
EP (1) EP1561013A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013156610A1 (fr) * 2012-04-19 2013-10-24 Eaton Srl Culbuteur

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004027224A1 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013156610A1 (fr) * 2012-04-19 2013-10-24 Eaton Srl Culbuteur
US9470116B2 (en) 2012-04-19 2016-10-18 Eaton Srl Rocker arm
US10196943B2 (en) 2012-04-19 2019-02-05 Eaton Intelligent Power Limited Valve train assembly

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