EP1149988A2 - Method and apparatus for two-step cam profile switching - Google Patents
Method and apparatus for two-step cam profile switching Download PDFInfo
- Publication number
- EP1149988A2 EP1149988A2 EP01201493A EP01201493A EP1149988A2 EP 1149988 A2 EP1149988 A2 EP 1149988A2 EP 01201493 A EP01201493 A EP 01201493A EP 01201493 A EP01201493 A EP 01201493A EP 1149988 A2 EP1149988 A2 EP 1149988A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- lift
- side member
- cam lobe
- bearing
- 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.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
- F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/185—Overhead end-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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
-
- 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
- F01L2001/186—Split rocking arms, e.g. rocker arms having two articulated parts and means for varying the relative position of these parts or for selectively connecting the parts to move in unison
-
- 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
Definitions
- the present invention relates generally to a method and apparatus for cam profile mode switching. More particularly, the apparatus of the present invention relates to a two-step roller finger follower for cam profile mode switching.
- Vehicle manufacturers have different goals for various vehicle platforms or models.
- the primary goal for one particular model may be to provide relatively high fuel economy, and for another model the goal may be to provide relatively high engine power output.
- the goal of providing relatively high fuel economy can be accomplished through the use of a cam having a relatively low lift and short duration lift profile, whereas high engine power is provided by the use of a cam having a higher lift and longer duration profile.
- the goals of high fuel economy and high power often involve conflicting design choices, and an acceptable tradeoff must be reached between the two competing goals for a particular vehicle model.
- high lift long duration output cams are designed to provide high power output at high engine operating speeds.
- high lift long duration output cams typically result in decreased engine idle quality and reduced low speed torque and drivability due to reduced air mass charged into the cylinder which is associated with the relatively long overlap duration of the opening and closing of the engine valves.
- cams which are designed to increase volumetric efficiency at high engine operating speeds typically reduce volumetric efficiency at lower engine operating speeds.
- a high lift long duration cam improves volumetric efficiency at high engine operating speeds by increasing the flow rate past the valve.
- the longer duration lift provides more time in which to fill the cylinder with air.
- the relatively late closing of the intake valve associated with a long duration cam takes advantage of the inertial effects of the intake charge to further increase high speed volumetric efficiency.
- a low lift short duration cam is best suited for low engine operating speeds due to improved intake charge velocity, which improves volumetric efficiency.
- the increased intake charge velocity also creates a more homogenous mixture that improves combustion by increasing either swirl or tumble.
- the shorter duration cam reduces valve overlap and thereby improves volumetric efficiency at low engine operating speeds.
- the relatively early closing of the intake valves associated with such low lift short duration cams further improves volumetric efficiency at low engine operating speeds.
- the present invention provides a method and apparatus for two-step cam profile mode switching.
- the invention comprises, in one form thereof, a two-step roller finger follower including an elongate body having a first side member and a second side member. A first end and a second end interconnect the first and second side members. The first and second side member define first and second pin orifices, respectively.
- a center roller is disposed between the first and second side members. The center roller defines a shaft orifice therethrough.
- a shaft extends through the shaft orifice.
- a first shaft end is disposed proximate the first side member, and the second shaft end is disposed proximate the second side member.
- the second shaft end defines a shaft bore therein.
- the first shaft end defines a pin chamber therein.
- the shaft bore is substantially concentric with and intersects the pin chamber.
- a locking pin assembly is disposed partially within the shaft bore, the pin chamber and at least one of the pin orifices.
- 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, and is switchable between the first and second positions.
- An advantage of the present invention is that the two-step roller finger follower for cam profile mode switching enables a high lift/long duration and a low lift/short duration activation of an associated valve while occupying substantially the same amount/volume of space as is occupied by a conventional roller finger follower.
- Another advantage of the present invention is that very few component parts are added relative to a conventional roller finger follower.
- a further advantage of the present invention is that the two-step roller finger follower for cam profile mode switching improves engine idle quality and driveability during part-load engine operating conditions by enabling a low lift/short duration activation of an associated valve, and improves volumetric efficiency and power at high engine operating speeds.
- a still further advantage of the present invention is that the two-step roller finger follower for cam profile mode switching employs roller bearings for reduced friction and increased fuel economy for both high-lift and low-lift motion.
- the two-step roller finger follower for cam profile mode switching (two-step RFF) of the present invention is switchable between a first mode and a second mode.
- the two-step RFF transfers rotary motion of at least one outer, such as, for example, a low lift and short duration, cam lobe of a camshaft of an internal combustion engine to pivotal movement of the body of the two-step RFF to thereby actuate an associated valve of the engine in accordance with the lift profile of the at least one outer cam lobe.
- the two-step RFF transfers rotary motion of a center, such as, for example, a high-lift and long duration, cam lobe of the camshaft to pivotal movement of the two-step RFF body to thereby actuate an associated valve in accordance with the lift profile of the center cam lobe.
- a center such as, for example, a high-lift and long duration
- two-step RFF 10 is installed in internal combustion engine 12, and engages camshaft 32 of engine 12.
- One end of two-step RFF 10 engages valve 14 of engine 12, the other end engages a stem 16 of lash adjuster 18.
- two-step RFF 10 includes body 20, locking pin assembly 22, lost motion springs 24a and 24b, central roller 26, bearings 28a, 28b, and hollow shaft 30 (Fig. 3).
- Body 20 includes first end 34, second end 36, elongate first side member 38, and elongate second side member 40.
- First end 34 includes valve stem pallet 42, which receives valve 14 of engine 12.
- Second end 36 defines a hemispherical lash adjuster socket 44 (see Fig. 1), which receives lash adjuster stem 16 of engine 12.
- Each of first side member 38 and second side member 40 extend between and interconnect first end 34 and second end 36.
- Each of first side member 38 and second side member 40 include a respective bearing boss 46a, 46b (Fig. 3) which support a corresponding one of bearings 28a, 28b.
- Body 20 is constructed of, for example, steel, carbon steel, or alloy steel.
- first side member 38 and second side member 40 define a respective pin orifice 50, 52 therethrough.
- pin orifices 50, 52 is concentric with center axis A.
- First side member 38 and second side member 40 each include an inside surface 38a, 40a, respectively.
- Roller aperture 54 is defined between inside surfaces 38a, 40a, and intermediate first end 34 and second end 36.
- Inside surface 38a defines slot 56, which is disposed adjacent roller aperture 54.
- Inside surface 40a defines slot 58, which is disposed adjacent roller aperture 54 and is transversely opposite slot 56.
- Each of slots 56, 58 extend from a respective top surface (not referenced) a to a corresponding bottom surface (not referenced) of first and second side members 38, 40.
- first side member 38 includes bearing boss 46a. Boss 46a surrounds pin orifice 50.
- Retaining clip 64 defines retaining clip orifice 64a, and is secured, such as, for example, by rolling, to boss 46a such that retaining clip orifice 64a is substantially concentric with pin orifice 50.
- second side member 40 includes bearing boss 46b which surrounds pin orifice 52.
- Retaining clip 66 defines retaining clip orifice 66a, and is secured, such as, for example, by rolling, to boss 46b such that retaining clip orifice 66a is substantially concentric with pin orifice 52.
- Locking pin assembly 22 as best shown in Figs. 3 and 4, includes locking pin 74, button 76, and pin spring 78.
- Locking pin 74 includes stem portion 74a and head 74b.
- Locking pin 74 is slidably disposed at least partially within shaft 30, as will be described more particularly hereinafter.
- Button 76 is a substantially cylindrical member having shoulder 76a.
- Button 76 is slidably disposed at least partially within pin orifice 50 in first side member 38 and is selectively received within shaft 30.
- Pin spring 78 is disposed within shaft 30 in association with locking pin 74, and biases locking pin assembly 22 into the first, such as, for example, low-lift, mode.
- Each of locking pin 74 and button 76 are constructed of, for example, steel, carbon steel, or alloy steel.
- Pin spring 78 is constructed of, for example, music or piano wire, and configured as, for example, a coil spring. As will be more particularly described hereinafter, locking pin assembly 22 is operable to switch two-step RFF 10 between the first mode and the second mode.
- Lost motion springs 24a and 24b are coiled around opposite ends of shaft 30. More particularly, lost motion spring 24a is coiled around the end of shaft 30 proximate second side member 38 and lost motion spring 24b is coiled around the other end of shaft 30 proximate first side member 40. Each of lost motion springs 24a and 24b extend radially from shaft 30 to abuttingly engage each of first end 34 and second end 36 of body 12. Each of lost motion springs 24a and 24b apply a spring force or load upon hollow shaft 30 to thereby bias hollow shaft 30 in the direction of the top surfaces (not referenced) of body 12, i.e., in a direction toward cam shaft 32 (Fig. 1). Lost motion springs 24a and 24b are configured as, for example, torsion springs, and are constructed of, for example, chrome silicon.
- Central roller 26 is a substantially cylindrical hollow member which includes outside surface 26a and central bore or orifice 26b.
- Elongate hollow shaft 30 extends through central orifice 26b, with the ends thereof disposed adjacent a corresponding one of first side member 38 and second side member 40.
- a plurality of needle bearings 80 are disposed intermediate central orifice 26b of roller 26 and hollow shaft 30.
- roller 26 is free to rotate about hollow shaft 30 in an essentially friction free manner.
- Outside surface 26a of roller 26 is configured to engage central, such as, for example, high-lift, cam lobe 32a (Figs. 1 and 5) of camshaft 32.
- Roller 26 is constructed of, for example, steel, carbon steel, or alloy steel.
- Shaft 30 is an elongate substantially cylindrical hollow member extending transversely between first side member 38 and second side member 40.
- Shaft 30 has first end 30a disposed in slot 56 and second end 30b disposed within slot 58.
- Shaft 30 has a predetermined diameter to enable it to freely reciprocate within each of slots 56, 58 in a generally vertical direction while preventing any binding and minimizing movement of shaft 30 toward and away from either of first end 34 and second end 36.
- Shaft 30 defines shaft bore 82 and pin chamber 84.
- Each of shaft bore 82 and pin chamber 84 are substantially concentric relative to central axis A.
- Shaft bore 82 and pin chamber 84 are contiguous with and intersect each other at shoulder 82b.
- Stem portion 74a of locking pin 74 is slidably disposed at least partially within shaft bore 82 and pin chamber 84, and is selectively received within pin orifice 52.
- Pin spring 78 is disposed in abutting engagement with each of head 74b of locking pin 74 and shoulder 82b of shaft bore 82. Pin spring 78 pre-loads or biases locking pin assembly 22 toward an unlocked position to thereby place two-step RFF 10 into a first, or low-lift, mode.
- Button 76 is slidingly disposed at least partially within first pin orifice 50 and is selectively received within pin chamber 84.
- Shaft 28 is constructed of, for example, steel, carbon steel, or alloy steel.
- locking pin assembly 22 is operable to switch two-step RFF 10 between the first mode and the second mode.
- Locking pin assembly 22 is now described in the first, or low-lift, mode as shown in and with reference to Fig. 3.
- first mode locking pin assembly 22 decouples shaft 30 from body 20.
- button 76 is disposed only within pin orifice 50 of first side member 36. A portion of button 76 extends from pin orifice 50 on the side of first side member 38 that is opposite inside surface 38a thereof.
- locking pin 74 is disposed only within shaft bore 82 and pin chamber 84 of shaft 30.
- valve 14 is not actuated in accordance with the lift profile of center cam lobe 32a. Rather, body 20 is pivoted and valve 14 is actuated according to the lift profile of outside cam lobes 32b, 32c, which engage bearings 28a, 28b, respectively.
- locking pin assembly 22 couples shaft 30 to body 20 to thereby transfer rotary motion of center cam lobe 32a (Figs. 1 and 5) to vertical motion of valve 14 (Fig. 1).
- stem portion 74a of locking pin 74 is disposed within each of pin orifice 52 in second side member 40, shaft bore 82 and pin chamber 84, thereby coupling shaft 30 to second side member 40.
- Button 76 in the second mode, is disposed within each of pin chamber 84 and pin orifice 50 of first side member 38. Thus, button 76 couples shaft 30 to first side member 38.
- shaft 30 is coupled to each of first side member 38 and second side member 40, and thus rotary motion of center cam lobe 32a is transferred by roller 26 to shaft 30.
- the coupling of shaft 30 to each of first and second side members 38, 40, respectively, by locking pin assembly 22 transfers the rotary motion of center cam lobe 32a to pivotal movement of body 20 about lash adjuster 18.
- valve 14 is actuated in accordance with the lift profile, such as, for example, a high and long duration lift profile, of center cam lobe 32a.
- camshaft 32 has central axis S and includes center cam lobe 32a.
- Center cam lobe 32a is configured, such as, for example, a high-lift cam lobe.
- Outside cam lobes 32b, 32c Disposed on each side of and adjacent to center cam lobe 32a are outside cam lobes 32b, 32c, which are configured as, for example, low-lift cam lobes relative to center cam lobe 32a.
- Outside cam lobes 32b, 32c and center cam lobe 32a are disposed in a predetermined angular relation relative to each other, and relative to central axis S of camshaft 32.
- Outside cam lobes 32b, 32c have a lift profile which is less in magnitude and duration than the lift profile of center cam lobe 32a.
- two-step RFF 10 is disposed such that outer surface 26a of roller 26 engages center cam lobe 32a, valve stem pallet 42 receives the end of a valve stem (not referenced) of valve 14, and lash adjuster socket 44 engages lash adjuster stem 16.
- locking pin assembly 22 decouples shaft 30 from body 20.
- Bearings 28a, 28b engage outside lobes 32b, 32c of camshaft 32, which pivot body 20 and thereby actuate valve 14 according to the lift profile of outside lobes 32b, 32c.
- Locking pin assembly 22, and thus two-step RFF 10, is selectively placed into and switched between the first and second modes by a control device (not shown), such as, for example, a hydraulic actuating piston (not shown) which is mounted into a bore on the cam bearing tower (not shown) adjacent two-step RFF 10.
- the actuating piston is in axial alignment with button 76 of locking pin assembly 22.
- Pressurized fluid such as, for example, oil, is selectively fed into and removed from the bore of the actuating piston to thereby cause the actuating piston to translate outward or retract inward in a direction toward and away from button 76.
- Locking pin assembly 22, and thus two-step RFF 10, is placed into the second/high-lift mode (Fig. 4), wherein shaft 30 is coupled to body 20, by translating the actuating piston outward and into engagement with button 76.
- the actuating piston overcomes the force of pin spring 78 and slidingly displaces button 76 axially in a direction toward second side member 40.
- the actuating piston displaces at least a portion of button 76 from within pin orifice 50 and into pin chamber 84 of shaft 30.
- the displacement of button 76 into pin chamber 84 results in a corresponding displacement of stem portion 74a of locking pin 74 out of shaft bore 82 and into pin orifice 52 of second side member 40.
- shaft 30 is coupled to each of first side member 38 and second side member 40.
- the actuating piston axially displaces button 76 into pin orifice 50 a predetermined distance in a direction toward second side member 40.
- outside cam lobes 32a, 32b have substantially no operable effect upon the operation of valve 14.
- outside cam lobes 32a, 32b operate to open or lift valve 14 a predetermined small amount and duration.
- the slight activation of valve 14 allows a relatively small amount of air to enter the associated cylinder of engine 12, thereby ensuring a higher intake velocity, a more complete combustion process, and thereby improve driveability under low load conditions and engine idle quality.
- Locking pin assembly 22, and thus two-step RFF 10, is placed into the first/low-lift mode by retracting the actuating piston inward thereby disengaging the actuating piston from contact with button 76.
- pin spring 78 is disposed, or compressed, between shoulder 82b of shaft bore 82 and head 74b of locking pin 74.
- Pin spring 78 exerts an axially directed force against head 74b to thereby pre-load or normally bias locking pin assembly 22 into the first/low-lift mode.
- Pin spring 78 slidingly displaces locking pin 74 axially in the direction of first side member 38 and into abutting engagement with button 76. The displacement of locking pin 74 results in a corresponding displacement of button 76 in the same direction.
- Button 76 is thus displaced until shoulder 76a of button 76 contacts retaining clip 64.
- the engagement of shoulder 76a by retaining clip 64 limits the axial displacement of button 76 by pin spring 78, and thereby establishes the first/low-lift mode positions of locking pin 74 and button 76 relative to body 20.
- the interface of locking pin 74 and button 76 is disposed within slot 56 of first side member 38. This axial position permits locking pin 74 to move relative to or slide over button 76 within slot 56 in a direction toward and away from camshaft 32.
- the end of locking pin 74 proximate second side member 40 is disposed within slot 58 of second side member 40. This axial position permits locking pin 74 to move or slide within slot 58 in a direction toward and away from camshaft 32.
- shaft 30 is likewise enabled to move or slide within each of slots 56, 58 in a direction toward and away from camshaft 32.
- lost motion springs 24a and 24b absorb the motion of shaft 30 as roller 26 engages and follows the lift profile of center cam lobe 32a, and ensure that roller 26 remains in contact therewith. Slots 56, 58 retain and guide the movement of shaft 30 as center cam lobe 32a rotates and displaces shaft 30.
- lost motion springs 24a and 24b are coiled around respective ends of shaft 30 proximate to second side member 40 and first side member 38, respectively. Lost motion springs 24a and 24b apply a spring force or load upon shaft 30 to thereby bias shaft 30 in the direction of camshaft 32. As center cam lobe 32a is rotated onto the nose thereof, a downward force is exerted upon shaft 30.
- lost motion springs 24a and 24b upon shaft 28 is overcome by the force exerted by center cam lobe 32a through roller 26 upon shaft 30, thereby resulting in shaft 30 being slidingly displaced downward within slots 56, 58 in a direction away from camshaft 32.
- the downward motion of shaft 30 is absorbed by lost motion springs 24a and 24b.
- center cam lobe 32a is rotated onto the base circle thereof, the load exerted upon shaft 30 by lost motion springs 24a and 24b maintains roller 26 in contact with center cam lobe 32a.
- lost motion springs 24a, 24b bias shaft 30 upward within slots 56, 58 in the direction of camshaft 32 and into a position which enables the return of locking pin assembly 22 into the decoupled or low-lift first mode position.
- pin orifices 50 and 52 registration of pin orifices 50 and 52 relative to shaft bore 82 and pin chamber 84 is conjunctively accomplished by roller 26, bearings 28a, 28b, center cam lobe 32a, outer cam lobes 32b, 32c, and lost motion springs 24a, 24b.
- center cam lobe 32a When center cam lobe 32a is at its base circle or lowest lift profile position, lost motion springs 24a and 24b bias shaft 30 toward camshaft 32, and maintain outer surface 26a of roller 26 engaged with center cam lobe 32a.
- roller 26 and shaft 30 is located by the base circle of center cam lobe 32a, while the position of body 20 is located by the base circle of outer cam lobes 32b and 32c engaging bearings 28b, 28a, respectively, such that shaft bore 82 and pin chamber 84 are axially aligned with pin orifices 50, 52.
- the axial alignment of shaft bore 82 and pin chamber 84 with pin orifices 50, 52 brings stem portion 74a of locking pin 74 into axial alignment with pin orifice 52 and head 74b into axial alignment with pin orifice 50 having button 76 disposed therein.
- Pin spring 78 then displaces locking pin 74 in a direction toward first side member 38.
- Pin spring 78 continues to displace locking pin 74 in a direction toward first side member 38 such that head 74b of locking pin 74 engages and displaces button 76.
- button 76 is displaced from disposition within pin chamber 84. The displacement of locking pin 74 and button 76 continues until shoulder 76a of locking pin 76 engages retaining clip 64.
- two-step RFF 10 in conjunction with outside lobes 32b, 32c of camshaft 32 operate to activate valve 14 in accordance with the lift profile of outside lobes 32b, 32c.
- valve 14 is opened or lifted a predetermined and relatively slight amount for a relatively slight duration relative to the amount and duration of lift imparted to valve 14 with two-step RFF 10 in the second/high-lift mode.
- two step RFF 10 in conjunction with center cam lobe 32a of camshaft 32 operate to activate valve 14 in accordance with the lift profile of center cam lobe 32a.
- center cam lobe 32a With, for example, a relatively high and long duration lift profile, valve 15 is opened or lifted a predetermined and relatively large amount for a relatively long duration relative to the amount and duration of lift imparted to valve 15 with two-step RFF 10 ni the first/low-lift mode.
- the breathing capability and the power capability of the engine under high-engine operating speed are improved.
- valve 14 is actuated at substantially the same time and at a predetermined angular position of camshaft 32, regardless of whether roller finger follower 10 is in the first/low-lift or second/high-lift mode.
- outer or low-lift cam lobes 32b, 32c can be shifted or offset relative to central axis S and relative to center or high-lift cam lobe 32a. Offsetting the angular position of low-lift cam lobes 32b, 32c relative to central axis S and relative to high-lift cam lobe 32a changes the angular position of camshaft 32 at which valve 14 is opened with two-step RFF 10 in the second/high-lift mode relative to the angular position of camshaft 32 at which valve 14 is opened with roller finger follower 10 in the first/low-lift mode.
- the angular position of outer or low-lift cam lobes 32b, 32c relative to central axis S can be offset, such as, for example, by positive (i.e., in the same direction as the rotation of camshaft 32) fifteen degrees relative to the angular position of center or high-lift cam lobe 32a to thereby phase the opening or actuation of valve 14.
- positive i.e., in the same direction as the rotation of camshaft 32
- the peak of outer or low-lift cam lobes 32b, 32c rotationally precede the peak of center or high-lift cam lobe 32a by fifteen degrees.
- valve 14 can be changed and/or adjusted by selecting the predetermined angular relationship of outer/low-lift cam lobes 32b, 32c relative to center or high-lift cam lobe 32a to thereby change opening and closing timing of valve 14, as well as valve overlap, when two-step RFF 10 is in the first/low-lift mode.
- This control over valve lift, valve lift timing, valve opening duration and valve overlap can be used to optimize high speed power while maintaining low speed torque, driveability, and engine idle quality.
- the first/low-lift mode is the default position and the default operating mode of locking pin assembly 22 and two-step RFF 10, respectively.
- two-step RFF 10 can be alternately configured, such as, for example, to have the second or high-lift mode as the default operating position/mode.
- bearings 28a, 28b are secured to body 20 of two-step RFF 10 to engage outside cam lobes 32b, 32c in a relatively frictionless manner.
- two-step RFF 10 can be alternately configured, such as, for example, with slider pads disposed on or integral with the body thereof, to engage outside cam lobes 32b, 32c.
- retaining clips 64 and 66 are secured, such as, for example, by rolling, to a respective boss 46a, 46b.
- two-step RFF 10 may be alternately configured, such as, for example, as having a retaining clip formed integrally with the boss or body, or attached by alternate means, such as, for example, staking or welding.
- each of slots 56 and 58 extend from the bottom surface (not referenced) of first and second side member 38, 40, respectively, to a top surface (not referenced) thereof.
- the slots may be alternately configured, such as, for example, extending only partially toward one or both of the the top and bottom surfaces of the roller finger follower body.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
- The present invention relates generally to a method and apparatus for cam profile mode switching. More particularly, the apparatus of the present invention relates to a two-step roller finger follower for cam profile mode switching.
- Vehicle manufacturers have different goals for various vehicle platforms or models. The primary goal for one particular model may be to provide relatively high fuel economy, and for another model the goal may be to provide relatively high engine power output. The goal of providing relatively high fuel economy can be accomplished through the use of a cam having a relatively low lift and short duration lift profile, whereas high engine power is provided by the use of a cam having a higher lift and longer duration profile. Thus, the goals of high fuel economy and high power often involve conflicting design choices, and an acceptable tradeoff must be reached between the two competing goals for a particular vehicle model.
- Generally, high lift long duration output cams are designed to provide high power output at high engine operating speeds. However, such high lift long duration output cams typically result in decreased engine idle quality and reduced low speed torque and drivability due to reduced air mass charged into the cylinder which is associated with the relatively long overlap duration of the opening and closing of the engine valves. In effect, cams which are designed to increase volumetric efficiency at high engine operating speeds typically reduce volumetric efficiency at lower engine operating speeds. A high lift long duration cam improves volumetric efficiency at high engine operating speeds by increasing the flow rate past the valve. Additionally, the longer duration lift provides more time in which to fill the cylinder with air. Further, the relatively late closing of the intake valve associated with a long duration cam takes advantage of the inertial effects of the intake charge to further increase high speed volumetric efficiency.
- Conversely, a low lift short duration cam is best suited for low engine operating speeds due to improved intake charge velocity, which improves volumetric efficiency. The increased intake charge velocity also creates a more homogenous mixture that improves combustion by increasing either swirl or tumble. Additionally, the shorter duration cam reduces valve overlap and thereby improves volumetric efficiency at low engine operating speeds. Further, the relatively early closing of the intake valves associated with such low lift short duration cams further improves volumetric efficiency at low engine operating speeds.
- Therefore, what is needed in the art is an apparatus and method that enables selectively activating an engine valve according to, and selectively switching between, a high lift long duration cam and a low lift short duration cam.
- Furthermore, what is needed in the art is an apparatus and method that provides a predetermined degree of valve activation for part-load engine operating conditions, and a maximum degree of valve activation for full-load engine operating conditions.
- Moreover, what is needed in the art is an apparatus that enables switching between a high lift long duration cam and a low lift short duration cam, and which uses relatively few component parts and occupies approximately the substantially same space as a conventional roller finger follower.
- The present invention provides a method and apparatus for two-step cam profile mode switching.
- The invention comprises, in one form thereof, a two-step roller finger follower including an elongate body having a first side member and a second side member. A first end and a second end interconnect the first and second side members. The first and second side member define first and second pin orifices, respectively. A center roller is disposed between the first and second side members. The center roller defines a shaft orifice therethrough. A shaft extends through the shaft orifice. A first shaft end is disposed proximate the first side member, and the second shaft end is disposed proximate the second side member. The second shaft end defines a shaft bore therein. The first shaft end defines a pin chamber therein. The shaft bore is substantially concentric with and intersects the pin chamber. A locking pin assembly is disposed partially within the shaft bore, the pin chamber and at least one of the pin orifices. 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, and is switchable between the first and second positions.
- An advantage of the present invention is that the two-step roller finger follower for cam profile mode switching enables a high lift/long duration and a low lift/short duration activation of an associated valve while occupying substantially the same amount/volume of space as is occupied by a conventional roller finger follower.
- Another advantage of the present invention is that very few component parts are added relative to a conventional roller finger follower.
- A further advantage of the present invention is that the two-step roller finger follower for cam profile mode switching improves engine idle quality and driveability during part-load engine operating conditions by enabling a low lift/short duration activation of an associated valve, and improves volumetric efficiency and power at high engine operating speeds.
- A still further advantage of the present invention is that the two-step roller finger follower for cam profile mode switching employs roller bearings for reduced friction and increased fuel economy for both high-lift and low-lift motion.
- The above-mentioned and other features and advantages of this invention, and the manner of attaining them, will become apparent and be better understood by reference to the following description of one embodiment of the invention in conjunction with the accompanying drawings, wherein:
- FIG. 1 is a perspective view of one embodiment of a two-step roller finger follower for cam profile mode switching of the present invention, as installed in an internal combustion engine;
- FIG. 2 is a perspective view of the two-step roller finger follower for cam profile mode switching of Fig. 1;
- FIG. 3 is a partially fragmentary cross-sectional view of the two-step roller finger follower for cam profile mode switching of Fig. 1 with the locking pin assembly in the default, decoupled, or first mode position;
- FIG. 4 is a partially fragmentary cross-sectional view of the two-step roller finger follower for cam profile mode switching of Fig. 1 with the locking pin assembly in the coupled or second mode position; and
- FIG. 5 is a perspective, fragmentary view of one embodiment of the camshaft of Fig. 1.
-
- Corresponding reference characters indicate corresponding parts throughout the several views. The exemplification set out herein illustrates one preferred embodiment of the invention, in one form, and such exemplification is not to be construed as limiting the scope of the invention in any manner.
- Generally, and as will be described more particularly hereinafter, the two-step roller finger follower for cam profile mode switching (two-step RFF) of the present invention is switchable between a first mode and a second mode. In the first mode, the two-step RFF transfers rotary motion of at least one outer, such as, for example, a low lift and short duration, cam lobe of a camshaft of an internal combustion engine to pivotal movement of the body of the two-step RFF to thereby actuate an associated valve of the engine in accordance with the lift profile of the at least one outer cam lobe. In the second mode, the two-step RFF transfers rotary motion of a center, such as, for example, a high-lift and long duration, cam lobe of the camshaft to pivotal movement of the two-step RFF body to thereby actuate an associated valve in accordance with the lift profile of the center cam lobe.
- Referring now to the drawings and particularly to Figs. 1-3, there is shown one embodiment of a two-
step RFF 10 of the present invention. Two-step RFF 10 is installed ininternal combustion engine 12, and engages camshaft 32 ofengine 12. One end of two-step RFF 10 engagesvalve 14 ofengine 12, the other end engages astem 16 oflash adjuster 18. Referring now specifically to Figs. 2 and 3, two-step RFF 10 includesbody 20,locking pin assembly 22, lostmotion springs 24a and 24b,central roller 26,bearings 28a, 28b, and hollow shaft 30 (Fig. 3). -
Body 20 includesfirst end 34,second end 36, elongatefirst side member 38, and elongatesecond side member 40.First end 34 includesvalve stem pallet 42, which receivesvalve 14 ofengine 12.Second end 36 defines a hemispherical lash adjuster socket 44 (see Fig. 1), which receiveslash adjuster stem 16 ofengine 12. Each offirst side member 38 andsecond side member 40 extend between and interconnectfirst end 34 andsecond end 36. Each offirst side member 38 andsecond side member 40 include arespective bearing boss 46a, 46b (Fig. 3) which support a corresponding one ofbearings 28a, 28b.Body 20 is constructed of, for example, steel, carbon steel, or alloy steel. - As best shown in Fig. 3, each of
first side member 38 andsecond side member 40 define arespective pin orifice pin orifices First side member 38 andsecond side member 40 each include aninside surface Roller aperture 54 is defined betweeninside surfaces first end 34 andsecond end 36. Insidesurface 38a definesslot 56, which is disposedadjacent roller aperture 54. Insidesurface 40a definesslot 58, which is disposedadjacent roller aperture 54 and is transverselyopposite slot 56. Each ofslots second side members - As stated above,
first side member 38 includesbearing boss 46a.Boss 46a surroundspin orifice 50. Retainingclip 64 defines retainingclip orifice 64a, and is secured, such as, for example, by rolling, toboss 46a such that retainingclip orifice 64a is substantially concentric withpin orifice 50. Similarly,second side member 40 includes bearing boss 46b which surroundspin orifice 52. Retainingclip 66 defines retaining clip orifice 66a, and is secured, such as, for example, by rolling, to boss 46b such that retaining clip orifice 66a is substantially concentric withpin orifice 52. - Locking
pin assembly 22, as best shown in Figs. 3 and 4, includes lockingpin 74,button 76, andpin spring 78. Lockingpin 74 includesstem portion 74a and head 74b. Lockingpin 74 is slidably disposed at least partially withinshaft 30, as will be described more particularly hereinafter.Button 76 is a substantially cylindrical member having shoulder 76a.Button 76 is slidably disposed at least partially withinpin orifice 50 infirst side member 38 and is selectively received withinshaft 30.Pin spring 78 is disposed withinshaft 30 in association with lockingpin 74, and biases lockingpin assembly 22 into the first, such as, for example, low-lift, mode. Each of lockingpin 74 andbutton 76 are constructed of, for example, steel, carbon steel, or alloy steel.Pin spring 78 is constructed of, for example, music or piano wire, and configured as, for example, a coil spring. As will be more particularly described hereinafter, lockingpin assembly 22 is operable to switch two-step RFF 10 between the first mode and the second mode. - Lost motion springs 24a and 24b are coiled around opposite ends of
shaft 30. More particularly, lostmotion spring 24a is coiled around the end ofshaft 30 proximatesecond side member 38 and lost motion spring 24b is coiled around the other end ofshaft 30 proximatefirst side member 40. Each of lostmotion springs 24a and 24b extend radially fromshaft 30 to abuttingly engage each offirst end 34 andsecond end 36 ofbody 12. Each of lostmotion springs 24a and 24b apply a spring force or load uponhollow shaft 30 to thereby biashollow shaft 30 in the direction of the top surfaces (not referenced) ofbody 12, i.e., in a direction toward cam shaft 32 (Fig. 1). Lost motion springs 24a and 24b are configured as, for example, torsion springs, and are constructed of, for example, chrome silicon. -
Central roller 26 is a substantially cylindrical hollow member which includes outsidesurface 26a and central bore or orifice 26b. Elongatehollow shaft 30 extends through central orifice 26b, with the ends thereof disposed adjacent a corresponding one offirst side member 38 andsecond side member 40. A plurality of needle bearings 80 are disposed intermediate central orifice 26b ofroller 26 andhollow shaft 30. Thus,roller 26 is free to rotate abouthollow shaft 30 in an essentially friction free manner. Outsidesurface 26a ofroller 26 is configured to engage central, such as, for example, high-lift,cam lobe 32a (Figs. 1 and 5) ofcamshaft 32.Roller 26 is constructed of, for example, steel, carbon steel, or alloy steel. -
Shaft 30 is an elongate substantially cylindrical hollow member extending transversely betweenfirst side member 38 andsecond side member 40.Shaft 30 hasfirst end 30a disposed inslot 56 and second end 30b disposed withinslot 58.Shaft 30 has a predetermined diameter to enable it to freely reciprocate within each ofslots shaft 30 toward and away from either offirst end 34 andsecond end 36.Shaft 30 defines shaft bore 82 andpin chamber 84. Each of shaft bore 82 andpin chamber 84 are substantially concentric relative to central axis A. Shaft bore 82 andpin chamber 84 are contiguous with and intersect each other at shoulder 82b.Stem portion 74a of lockingpin 74 is slidably disposed at least partially within shaft bore 82 andpin chamber 84, and is selectively received withinpin orifice 52.Pin spring 78 is disposed in abutting engagement with each of head 74b of lockingpin 74 and shoulder 82b of shaft bore 82.Pin spring 78 pre-loads or biases lockingpin assembly 22 toward an unlocked position to thereby place two-step RFF 10 into a first, or low-lift, mode.Button 76 is slidingly disposed at least partially withinfirst pin orifice 50 and is selectively received withinpin chamber 84. Shaft 28 is constructed of, for example, steel, carbon steel, or alloy steel. - As described above, locking
pin assembly 22 is operable to switch two-step RFF 10 between the first mode and the second mode. Lockingpin assembly 22 is now described in the first, or low-lift, mode as shown in and with reference to Fig. 3. In the first mode, lockingpin assembly 22 decouplesshaft 30 frombody 20. In this first or decoupled mode,button 76 is disposed only withinpin orifice 50 offirst side member 36. A portion ofbutton 76 extends frompin orifice 50 on the side offirst side member 38 that is opposite insidesurface 38a thereof. Similarly, lockingpin 74 is disposed only within shaft bore 82 andpin chamber 84 ofshaft 30. No portion of lockingpin 74 is disposed withinpin orifice 52 and no portion ofbutton 76 is disposed withinpin chamber 84 when lockingpin assembly 22 is in the first or low-lift mode. Thus,shaft 30 is not coupled to either offirst side member 38 orsecond side member 40 ofbody 20. Therefore, as rotary motion ofcenter cam lobe 32a is transferred byroller 26 to shaft 28, shaft 28 is correspondingly displaced relative tobody 20. More particularly, rotary motion ofcenter cam lobe 32a is transferred viaroller 26 to reciprocation ofshaft 30 within each ofslots camshaft 32. In contrast to the first or high-lift mode, rotary motion ofcenter cam lobe 32a is not transferred by shaft 28 to pivotal movement ofbody 20, and thereforevalve 14 is not actuated in accordance with the lift profile ofcenter cam lobe 32a. Rather,body 20 is pivoted andvalve 14 is actuated according to the lift profile ofoutside cam lobes 32b, 32c, which engagebearings 28a, 28b, respectively. - In the second, or high-lift, mode, as shown in Fig. 4, locking
pin assembly 22couples shaft 30 tobody 20 to thereby transfer rotary motion ofcenter cam lobe 32a (Figs. 1 and 5) to vertical motion of valve 14 (Fig. 1). In this second or coupled mode, stemportion 74a of lockingpin 74 is disposed within each ofpin orifice 52 insecond side member 40, shaft bore 82 andpin chamber 84, thereby couplingshaft 30 tosecond side member 40.Button 76, in the second mode, is disposed within each ofpin chamber 84 andpin orifice 50 offirst side member 38. Thus,button 76couples shaft 30 tofirst side member 38. With lockingpin assembly 22 in the second mode, as described above,shaft 30 is coupled to each offirst side member 38 andsecond side member 40, and thus rotary motion ofcenter cam lobe 32a is transferred byroller 26 toshaft 30. The coupling ofshaft 30 to each of first andsecond side members pin assembly 22 transfers the rotary motion ofcenter cam lobe 32a to pivotal movement ofbody 20 about lashadjuster 18. Thus,valve 14 is actuated in accordance with the lift profile, such as, for example, a high and long duration lift profile, ofcenter cam lobe 32a. - As best shown in Fig. 5,
camshaft 32 has central axis S and includescenter cam lobe 32a.Center cam lobe 32a is configured, such as, for example, a high-lift cam lobe. Disposed on each side of and adjacent to centercam lobe 32a areoutside cam lobes 32b, 32c, which are configured as, for example, low-lift cam lobes relative tocenter cam lobe 32a.Outside cam lobes 32b, 32c andcenter cam lobe 32a are disposed in a predetermined angular relation relative to each other, and relative to central axis S ofcamshaft 32.Outside cam lobes 32b, 32c have a lift profile which is less in magnitude and duration than the lift profile ofcenter cam lobe 32a. - In use, two-
step RFF 10 is disposed such thatouter surface 26a ofroller 26 engagescenter cam lobe 32a, valve stempallet 42 receives the end of a valve stem (not referenced) ofvalve 14, and lashadjuster socket 44 engages lashadjuster stem 16. With two-step RFF 10 in the first, or low lift, mode (Fig. 3), lockingpin assembly 22 decouplesshaft 30 frombody 20.Bearings 28a, 28b engage outsidelobes 32b, 32c ofcamshaft 32, whichpivot body 20 and thereby actuatevalve 14 according to the lift profile ofoutside lobes 32b, 32c. Lockingpin assembly 22, and thus two-step RFF 10, is selectively placed into and switched between the first and second modes by a control device (not shown), such as, for example, a hydraulic actuating piston (not shown) which is mounted into a bore on the cam bearing tower (not shown) adjacent two-step RFF 10. The actuating piston is in axial alignment withbutton 76 of lockingpin assembly 22. Pressurized fluid, such as, for example, oil, is selectively fed into and removed from the bore of the actuating piston to thereby cause the actuating piston to translate outward or retract inward in a direction toward and away frombutton 76. - Locking
pin assembly 22, and thus two-step RFF 10, is placed into the second/high-lift mode (Fig. 4), whereinshaft 30 is coupled tobody 20, by translating the actuating piston outward and into engagement withbutton 76. The actuating piston overcomes the force ofpin spring 78 and slidingly displacesbutton 76 axially in a direction towardsecond side member 40. The actuating piston displaces at least a portion ofbutton 76 from withinpin orifice 50 and intopin chamber 84 ofshaft 30. The displacement ofbutton 76 intopin chamber 84 results in a corresponding displacement ofstem portion 74a of lockingpin 74 out of shaft bore 82 and intopin orifice 52 ofsecond side member 40. Thus,shaft 30 is coupled to each offirst side member 38 andsecond side member 40. The actuating piston axially displacesbutton 76 into pin orifice 50 a predetermined distance in a direction towardsecond side member 40. - With locking
pin assembly 22, and thus two-step RFF 10 in the second/high-lift mode, outsidecam lobes 32a, 32b have substantially no operable effect upon the operation ofvalve 14. However, with locking pin assembly andRFF 10 in the first/low-lift mode (Fig. 3), outsidecam lobes 32a, 32b operate to open or lift valve 14 a predetermined small amount and duration. The slight activation ofvalve 14 allows a relatively small amount of air to enter the associated cylinder ofengine 12, thereby ensuring a higher intake velocity, a more complete combustion process, and thereby improve driveability under low load conditions and engine idle quality. - Locking
pin assembly 22, and thus two-step RFF 10, is placed into the first/low-lift mode by retracting the actuating piston inward thereby disengaging the actuating piston from contact withbutton 76. As stated above,pin spring 78 is disposed, or compressed, between shoulder 82b of shaft bore 82 and head 74b of lockingpin 74.Pin spring 78 exerts an axially directed force against head 74b to thereby pre-load or normally bias lockingpin assembly 22 into the first/low-lift mode.Pin spring 78 slidingly displaces lockingpin 74 axially in the direction offirst side member 38 and into abutting engagement withbutton 76. The displacement of lockingpin 74 results in a corresponding displacement ofbutton 76 in the same direction.Button 76 is thus displaced until shoulder 76a ofbutton 76contacts retaining clip 64. The engagement of shoulder 76a by retainingclip 64 limits the axial displacement ofbutton 76 bypin spring 78, and thereby establishes the first/low-lift mode positions of lockingpin 74 andbutton 76 relative tobody 20. - In the first/low-lift mode, the interface of locking
pin 74 andbutton 76 is disposed withinslot 56 offirst side member 38. This axial positionpermits locking pin 74 to move relative to or slide overbutton 76 withinslot 56 in a direction toward and away fromcamshaft 32. Similarly, in the first/low-lift mode, the end of lockingpin 74 proximatesecond side member 40 is disposed withinslot 58 ofsecond side member 40. This axial positionpermits locking pin 74 to move or slide withinslot 58 in a direction toward and away fromcamshaft 32. Thus,shaft 30 is likewise enabled to move or slide within each ofslots camshaft 32. - In the first/low-lift mode, lost
motion springs 24a and 24b absorb the motion ofshaft 30 asroller 26 engages and follows the lift profile ofcenter cam lobe 32a, and ensure thatroller 26 remains in contact therewith.Slots shaft 30 ascenter cam lobe 32a rotates and displacesshaft 30. As stated above, lostmotion springs 24a and 24b are coiled around respective ends ofshaft 30 proximate tosecond side member 40 andfirst side member 38, respectively. Lost motion springs 24a and 24b apply a spring force or load uponshaft 30 to thereby biasshaft 30 in the direction ofcamshaft 32. Ascenter cam lobe 32a is rotated onto the nose thereof, a downward force is exerted uponshaft 30. The force of lostmotion springs 24a and 24b upon shaft 28 is overcome by the force exerted bycenter cam lobe 32a throughroller 26 uponshaft 30, thereby resulting inshaft 30 being slidingly displaced downward withinslots camshaft 32. The downward motion ofshaft 30 is absorbed by lostmotion springs 24a and 24b. Ascenter cam lobe 32a is rotated onto the base circle thereof, the load exerted uponshaft 30 by lostmotion springs 24a and 24b maintainsroller 26 in contact withcenter cam lobe 32a. Ascenter cam lobe 32a returns to its zero lift profile, lostmotion springs 24a, 24b biasshaft 30 upward withinslots camshaft 32 and into a position which enables the return of lockingpin assembly 22 into the decoupled or low-lift first mode position. - It should be particularly noted that registration of
pin orifices pin chamber 84 is conjunctively accomplished byroller 26,bearings 28a, 28b,center cam lobe 32a,outer cam lobes 32b, 32c, and lostmotion springs 24a, 24b. Whencenter cam lobe 32a is at its base circle or lowest lift profile position, lostmotion springs 24a and 24b biasshaft 30 towardcamshaft 32, and maintainouter surface 26a ofroller 26 engaged withcenter cam lobe 32a. The position ofroller 26 andshaft 30 is located by the base circle ofcenter cam lobe 32a, while the position ofbody 20 is located by the base circle ofouter cam lobes 32b and32c engaging bearings 28b, 28a, respectively, such that shaft bore 82 andpin chamber 84 are axially aligned withpin orifices pin chamber 84 withpin orifices stem portion 74a of lockingpin 74 into axial alignment withpin orifice 52 and head 74b into axial alignment withpin orifice 50 havingbutton 76 disposed therein.Pin spring 78 then displaces lockingpin 74 in a direction towardfirst side member 38.Pin spring 78 continues to displace lockingpin 74 in a direction towardfirst side member 38 such that head 74b of lockingpin 74 engages and displacesbutton 76. Thus,button 76 is displaced from disposition withinpin chamber 84. The displacement of lockingpin 74 andbutton 76 continues until shoulder 76a of lockingpin 76 engages retainingclip 64. - In the first/low-lift mode, two-
step RFF 10 in conjunction withoutside lobes 32b, 32c ofcamshaft 32 operate to activatevalve 14 in accordance with the lift profile ofoutside lobes 32b, 32c. By configuringoutside lobes 32b, 32c with, for example, a low and short duration lift profile,valve 14 is opened or lifted a predetermined and relatively slight amount for a relatively slight duration relative to the amount and duration of lift imparted tovalve 14 with two-step RFF 10 in the second/high-lift mode. Thus, the quality of engine idle and low-speed/load driveability are improved by two-step RFF 10 operating in the first/low-lift mode, and by using two-step RFF 10 in conjunction with a camshaft which incorporates outside or low-lift cam lobes that provide a low and short duration lift profile by whichvalve 14 is actuated. - In the second/high-lift mode, two
step RFF 10 in conjunction withcenter cam lobe 32a ofcamshaft 32 operate to activatevalve 14 in accordance with the lift profile ofcenter cam lobe 32a. By configuringcenter cam lobe 32a with, for example, a relatively high and long duration lift profile, valve 15 is opened or lifted a predetermined and relatively large amount for a relatively long duration relative to the amount and duration of lift imparted to valve 15 with two-step RFF 10 ni the first/low-lift mode. Thus, the breathing capability and the power capability of the engine under high-engine operating speed are improved. - The predetermined angular relationship of outer or low-
lift cam lobes 32b, 32c and central or high-lift cam lobe 32a relative to each other and relative to central axis S ofcamshaft 32 is fixed such that, for example, the maximum lift or peak of each cam lobe are at a predetermined angular position relative to central axis S. Thus,valve 14 is actuated at substantially the same time and at a predetermined angular position ofcamshaft 32, regardless of whetherroller finger follower 10 is in the first/low-lift or second/high-lift mode. It is to be understood, however, that the angular position of one or both of outer or low-lift cam lobes 32b, 32c can be shifted or offset relative to central axis S and relative to center or high-lift cam lobe 32a. Offsetting the angular position of low-lift cam lobes 32b, 32c relative to central axis S and relative to high-lift cam lobe 32a changes the angular position ofcamshaft 32 at whichvalve 14 is opened with two-step RFF 10 in the second/high-lift mode relative to the angular position ofcamshaft 32 at whichvalve 14 is opened withroller finger follower 10 in the first/low-lift mode. - More particularly, the angular position of outer or low-
lift cam lobes 32b, 32c relative to central axis S can be offset, such as, for example, by positive (i.e., in the same direction as the rotation of camshaft 32) fifteen degrees relative to the angular position of center or high-lift cam lobe 32a to thereby phase the opening or actuation ofvalve 14. Withcam lobes lift cam lobes 32b, 32c rotationally precede the peak of center or high-lift cam lobe 32a by fifteen degrees. With two-step RFF 10 in the first/low-lift mode, outer or low-lift cam lobes 32b, 32c engagebearings 28a, 28b, respectively, to thereby slightlyopen valve 14. Thus, the opening ofvalve 14 with two-step RFF 10 in the first/low-lift mode is changed or phased from the opening ofvalve 14 with two-step RFF 10 in the second/high-lift mode due to the advanced angular position of outer or low-lift cam lobes 32b, 32c relative to center or high-lift cam lobe 32a. Therefore, the opening or actuation ofvalve 14 can be changed and/or adjusted by selecting the predetermined angular relationship of outer/low-lift cam lobes 32b, 32c relative to center or high-lift cam lobe 32a to thereby change opening and closing timing ofvalve 14, as well as valve overlap, when two-step RFF 10 is in the first/low-lift mode. This control over valve lift, valve lift timing, valve opening duration and valve overlap can be used to optimize high speed power while maintaining low speed torque, driveability, and engine idle quality. - In the embodiment shown, the first/low-lift mode is the default position and the default operating mode of locking
pin assembly 22 and two-step RFF 10, respectively. However, it is to be understood that two-step RFF 10 can be alternately configured, such as, for example, to have the second or high-lift mode as the default operating position/mode. - In the embodiment shown,
bearings 28a, 28b are secured tobody 20 of two-step RFF 10 to engage outsidecam lobes 32b, 32c in a relatively frictionless manner. However, it is to be understood that two-step RFF 10 can be alternately configured, such as, for example, with slider pads disposed on or integral with the body thereof, to engage outsidecam lobes 32b, 32c. - In the embodiment shown, retaining
clips respective boss 46a, 46b. However, it is to be understood that two-step RFF 10 may be alternately configured, such as, for example, as having a retaining clip formed integrally with the boss or body, or attached by alternate means, such as, for example, staking or welding. - In the embodiment shown, each of
slots second side member - While this invention has been described as having a preferred design, the present invention can be further modified within the spirit and scope of this disclosure. This application is therefore intended to cover any variations, uses, or adaptations of the present invention using the general principles disclosed herein. Further, this application is intended to cover such departures from the present disclosure as come within the known or customary practice in the art to which this invention pertains and which fall within the limits of the appended claims.
Claims (20)
- A two-step roller finger follower (10) for use with an internal combustion engine (12), said two-step roller finger follower comprising:an elongate body (20) having a first side member (38) and a second side member (40), a first end (34) and a second end (36) interconnecting and spacing apart said first and second side member, said first and second side member defining a first and second pin orifice (50), (52), respectively;a center roller (26) disposed between said first and second side member intermediate said first end and said second end of said body, said center roller defining a shaft orifice (26b) therethrough;an elongate shaft (30) extending through said shaft orifice, said shaft having a first shaft end (30a) and a second shaft end (30b), said first shaft end being disposed proximate said first side member, said second shaft end being disposed proximate said second side member, said second shaft end defining a shaft bore (82) therein, said first shaft end defining a pin chamber (84) therein, said shaft bore being substantially concentric with and intersecting said pin chamber; anda locking pin assembly (22) disposed partially within each of said shaft bore, said pin chamber and at least one of said pin orifices, said locking pin assembly having a first position wherein said shaft is decoupled from said body and a second position wherein said shaft is coupled to said body, said locking pin assembly being switchable between said first position and said second position.
- The two-step roller finger follower (10) of claim 1, further comprising:a first bearing (28a) rotatably secured to said body; anda second bearing (28b) rotatably secured to said body.
- The two-step roller finger follower (10) of claim 2, wherein each of said first bearing and said second bearing are configured for engaging a respective outside cam lobe (32b), (32c) carried by a camshaft (32) of the internal combustion engine.
- The two-step roller finger follower (10) of claim 2, wherein said first bearing (28a) and said second bearing (28b) are rotatably affixed to a respective one of said first side member (38) and said second side member (40).
- The two-step roller finger follower (10) of claim 2, further comprising a first bearing boss (46a) disposed on said first side member, a second bearing boss (46b) disposed on said second side member, said first bearing being rotatably disposed upon said first bearing boss, said second bearing being rotatably disposed upon said second bearing boss.
- The two-step roller finger follower (10) of claim 5, further comprising a first retaining clip (64) secured to said first bearing boss and being configured to retain said first bearing in disposition upon said first bearing boss, a second retaining clip (66) secured to said second bearing boss and being configured to retain said second bearing in disposition upon said second bearing boss.
- An internal combustion engine (12), comprising:a camshaft (32); anda two-step roller finger follower (10), said two-step roller finger follower including:an elongate body (20) having a first side member (38) and a second side member (40), a first end (34) and a second end (36) interconnecting and spacing apart said first and second side member, said first and second side member defining a first and second pin orifice (50), (52), respectively;a center roller (26) disposed between said first and second side member intermediate said first end and said second end of said body, said roller defining a shaft orifice (26b) therethrough;an elongate shaft (30) extending through said shaft orifice, said shaft having a first shaft end (30a) and a second shaft end (30b), said first shaft end being disposed proximate said first side member, said second shaft end being disposed proximate said second side member, said second shaft end defining a shaft bore (82) therein, said first shaft end defining a pin chamber (84) therein, said shaft bore being substantially concentric with and intersecting said pin chamber; anda locking pin assembly (22) disposed partially within each of said shaft bore, said pin chamber and at least one of said pin orifices, said locking pin assembly having a first position wherein said shaft is decoupled from said body and a second position wherein said shaft is coupled to said body, said locking pin assembly being switchable between said first position and said second position.
- The internal combustion engine (12) of claim 7, further comprising:a center cam lobe (32a) and at least one outside cam lobe (32b), (32c) carried by said camshaft, said center cam lobe engaging said center roller (26); andat least one bearing (28a), (28b) rotatably secured to said body, each of said at least one outside cam lobe engaging a respective one of said at least one bearing.
- The internal combustion engine (12) of claim 8, wherein said center cam lobe comprises a high-lift cam lobe (32a), said at least one outside cam lobe comprises two low-lift cam lobes (32b), (32c) disposed on respective sides of and adjacent to said high-lift cam lobe, said at least one bearing comprises a first bearing (28a) and a second bearing (28b), each of said first and said second bearings engaging a respective one of said two low-lift cam lobes.
- The internal combustion engine (12) of claim 9, wherein said low-lift cam lobe has at least one of a lower magnitude of lift and a shorter duration lift relative to said high-lift cam lobe.
- The internal combustion engine (12) of claim 8, wherein each of said at least one bearing is rotatably affixed to a respective one of said first side member and said second side member.
- The internal combustion engine (12) of claim 11, wherein said first side member and said second side member include a respective bearing boss (46a), (46b), each of said at least one bearing being disposed on a corresponding bearing boss.
- The internal combustion engine (12) of claim 8, wherein said center cam lobe and said at least one outside cam lobe are disposed in a predetermined angular position relative to a central axis S of said camshaft.
- The internal combustion engine (12) of claim 8, wherein said center cam lobe is disposed in a first angular position relative to a central axis of said camshaft, each of said at least one outside cam lobe being disposed in a second angular position relative to said central axis of said camshaft, said first angular position being different from said second angular position.
- A method of switching cam profiles of at least one of an intake and exhaust valve (14) of an internal combustion engine, said method comprising the steps of:rotating a camshaft (32) having a high-lift cam lobe 32a and at least one associated low-lift cam lobe (32b), (32c);normally activating the valve with at least one low-lift cam lobe of the camshaft while absorbing the motion of the high-lift cam lobe; andselectively activating the valve with the high-lift cam lobe.
- The method of claim (15), wherein the high-lift cam lobe (32a) has a first amount of lift, said low-lift cam lobe (32b), (32c) has a second amount of lift, said first amount of lift being greater than said second amount of lift.
- The method of claim 15, wherein the high-lift cam lobe has a first duration of lift, said low-lift cam lobe has a second duration of lift, said first duration of lift being greater than said second duration of lift.
- The method of claim 15, wherein said normally activating step comprises the at least one low-lift cam lobe (32b), (32c) engaging a corresponding at least one bearing (28a), (28b), said at least one bearing being rotatably secured to the body (20) of a roller finger follower (10) associated with the valve.
- The method of claim (15), wherein said normally activating step comprises absorbing with a lost motion spring (24a), (24b) the displacement of a center roller (26) of a roller finger follower (10) associated with the valve, the center roller engaging and being displaced by the high-lift cam lobe (32a).
- The method of claim (15), wherein said selectively activating step comprises coupling the center roller (26) of a roller finger follower (10) to the roller finger follower body (20), the center roller engaging the high-lift cam lobe (32a) and transferring the motion of the high-lift cam lobe to the roller finger follower body to thereby activate the valve.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US19971600P | 2000-04-26 | 2000-04-26 | |
US199716P | 2000-04-26 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1149988A2 true EP1149988A2 (en) | 2001-10-31 |
EP1149988A3 EP1149988A3 (en) | 2001-11-14 |
EP1149988B1 EP1149988B1 (en) | 2005-11-02 |
Family
ID=22738725
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01201493A Expired - Lifetime EP1149988B1 (en) | 2000-04-26 | 2001-04-25 | Method and apparatus for two-step cam profile switching |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1149988B1 (en) |
DE (1) | DE60114501T2 (en) |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003042507A1 (en) * | 2001-11-14 | 2003-05-22 | Ina-Schaeffler Kg | Cam follower of a valve gear of an internal combustion engine |
WO2003042510A1 (en) * | 2001-11-14 | 2003-05-22 | Ina-Schaeffler Kg | Drag lever of a valve mechanism in an internal combustion engine |
EP1318278A2 (en) * | 2001-12-04 | 2003-06-11 | Delphi Technologies, Inc. | Roller finger follower |
WO2007035673A2 (en) | 2005-09-16 | 2007-03-29 | Timken Us Corporation | Switching finger follower assembly |
EP2063074A1 (en) * | 2007-11-21 | 2009-05-27 | Delphi Technologies, Inc. | Bearing design for a roller finger follower |
US7546822B2 (en) | 2004-03-03 | 2009-06-16 | Timken Us Corporation | Switching finger follower assembly |
WO2011113702A1 (en) * | 2010-03-18 | 2011-09-22 | Schaeffler Technologies Gmbh & Co. Kg | Switchable lever for a valve drive of an internal combustion engine |
WO2013156610A1 (en) * | 2012-04-19 | 2013-10-24 | Eaton Srl | A rocker arm |
US10400639B2 (en) | 2015-11-20 | 2019-09-03 | Man Truck & Bus Ag | Variable valve train with a rocker arm |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
RO132154A2 (en) | 2016-03-21 | 2017-09-29 | Schaeffler Technologies AG & Co.KG | Change-over arrangement with cams |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04143409A (en) * | 1990-10-03 | 1992-05-18 | Nissan Motor Co Ltd | Variable valve system for internal combustion engine |
JPH0571318A (en) * | 1991-09-11 | 1993-03-23 | Nissan Motor Co Ltd | Rocker arm of internal combustion engine |
JP3319794B2 (en) * | 1993-01-18 | 2002-09-03 | 本田技研工業株式会社 | SOHC type valve train for internal combustion engine |
DE9406190U1 (en) * | 1994-04-14 | 1994-06-09 | INA Wälzlager Schaeffler KG, 91074 Herzogenaurach | Device for the simultaneous actuation of at least two gas exchange valves |
FR2731043B1 (en) * | 1995-02-24 | 1997-04-04 | Renault | VARIABLE DISTRIBUTION DEVICE FOR INTERNAL COMBUSTION ENGINE |
-
2001
- 2001-04-25 DE DE60114501T patent/DE60114501T2/en not_active Expired - Fee Related
- 2001-04-25 EP EP01201493A patent/EP1149988B1/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
None |
Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003042510A1 (en) * | 2001-11-14 | 2003-05-22 | Ina-Schaeffler Kg | Drag lever of a valve mechanism in an internal combustion engine |
WO2003042507A1 (en) * | 2001-11-14 | 2003-05-22 | Ina-Schaeffler Kg | Cam follower of a valve gear of an internal combustion engine |
EP1318278A2 (en) * | 2001-12-04 | 2003-06-11 | Delphi Technologies, Inc. | Roller finger follower |
US7546822B2 (en) | 2004-03-03 | 2009-06-16 | Timken Us Corporation | Switching finger follower assembly |
WO2007035673A2 (en) | 2005-09-16 | 2007-03-29 | Timken Us Corporation | Switching finger follower assembly |
WO2007035673A3 (en) * | 2005-09-16 | 2007-05-24 | Timken Us Corp | Switching finger follower assembly |
EP2305966A1 (en) * | 2005-09-16 | 2011-04-06 | Koyo Bearings USA, LLC | Switching finger follower assembly |
EP2063074A1 (en) * | 2007-11-21 | 2009-05-27 | Delphi Technologies, Inc. | Bearing design for a roller finger follower |
WO2011113702A1 (en) * | 2010-03-18 | 2011-09-22 | Schaeffler Technologies Gmbh & Co. Kg | Switchable lever for a valve drive of an internal combustion engine |
US8794205B2 (en) | 2010-03-18 | 2014-08-05 | Schaeffler Technologies Gmbh & Co. Kg | Switchable lever for a valve drive of an internal combustion engine |
WO2013156610A1 (en) * | 2012-04-19 | 2013-10-24 | Eaton Srl | A rocker arm |
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 |
US10400639B2 (en) | 2015-11-20 | 2019-09-03 | Man Truck & Bus Ag | Variable valve train with a rocker arm |
Also Published As
Publication number | Publication date |
---|---|
DE60114501T2 (en) | 2006-04-27 |
EP1149988A3 (en) | 2001-11-14 |
EP1149988B1 (en) | 2005-11-02 |
DE60114501D1 (en) | 2005-12-08 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6502536B2 (en) | Method and apparatus for two-step cam profile switching | |
EP1172528B1 (en) | Valve drive device of four-stroke cycle engine | |
US7469669B2 (en) | Variable valve train mechanism of internal combustion engine | |
US5592906A (en) | Method and device for variable valve control of an internal combustion engine | |
US8047168B2 (en) | Continuously variable valve lift system for engine | |
US6340010B1 (en) | Valve operating device for internal combustion engine with variable valve timing and valve-lift characteristic mechanism | |
EP1725744A1 (en) | Switching finger follower assembly | |
EP1149988B1 (en) | Method and apparatus for two-step cam profile switching | |
CN108729969B (en) | Variable valve gear | |
JPH06101437A (en) | Valve system of engine | |
EP1515009A1 (en) | Engine valve driver | |
JPH0258445B2 (en) | ||
KR102454349B1 (en) | Switching rocker arm | |
CN209040909U (en) | A kind of valve Biodge device that electromagnetic type can collapse | |
US6932035B1 (en) | Cylinder valve operating system for internal combustion engine | |
US20020152974A1 (en) | Apparatus for adjusting valve lift | |
US20050098135A1 (en) | Engine valve actuator assembly | |
US8490587B2 (en) | Cam drive | |
KR20000071212A (en) | Operating mechanisms for valves | |
JPH0333414A (en) | Valve system of 4 cycle engine | |
JPS606564Y2 (en) | Valve mechanism of internal combustion engine | |
JP2584890Y2 (en) | Valve train for internal combustion engine | |
JPS62267514A (en) | Controlling variable valve-action-mode type tappet for internal combustion engine | |
JPH0543203Y2 (en) | ||
CA1289828C (en) | Valve operating mechanism for internal combustion engine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): DE FR GB Kind code of ref document: A2 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
17P | Request for examination filed |
Effective date: 20020514 |
|
AKX | Designation fees paid |
Free format text: DE FR GB |
|
17Q | First examination report despatched |
Effective date: 20050128 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: SPATH, MARK. J. Inventor name: FOGARTY, RYAN D. Inventor name: HARRIS, WAYNE S. Inventor name: LEE, JONGMIN Inventor name: HENDRIKSMA, NICK J. Inventor name: FERNANDEZ, HERMES A. |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REF | Corresponds to: |
Ref document number: 60114501 Country of ref document: DE Date of ref document: 20051208 Kind code of ref document: P |
|
ET | Fr: translation filed | ||
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20060803 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20070425 Year of fee payment: 7 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20070411 Year of fee payment: 7 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20080502 Year of fee payment: 8 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20080425 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20081231 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080425 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20091103 |