EP1783332A1 - Oszillierender nocken und dynamischer ventilmechanismus für verbrennungsmotor - Google Patents

Oszillierender nocken und dynamischer ventilmechanismus für verbrennungsmotor Download PDF

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Publication number
EP1783332A1
EP1783332A1 EP04772154A EP04772154A EP1783332A1 EP 1783332 A1 EP1783332 A1 EP 1783332A1 EP 04772154 A EP04772154 A EP 04772154A EP 04772154 A EP04772154 A EP 04772154A EP 1783332 A1 EP1783332 A1 EP 1783332A1
Authority
EP
European Patent Office
Prior art keywords
cam
rocking
roller
shaft
internal combustion
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
Application number
EP04772154A
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English (en)
French (fr)
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EP1783332B1 (de
EP1783332A4 (de
Inventor
Koichi Hatamura
Hideo Fujita
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.)
Yamaha Motor Co Ltd
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Yamaha Motor Co Ltd
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
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Publication of EP1783332A1 publication Critical patent/EP1783332A1/de
Publication of EP1783332A4 publication Critical patent/EP1783332A4/de
Application granted granted Critical
Publication of EP1783332B1 publication Critical patent/EP1783332B1/de
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/08—Shape of cams
    • 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
    • F01L1/14—Tappets; Push rods
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • 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
    • F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0068—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/08—Valves guides; Sealing of valve stem, e.g. sealing by lubricant

Definitions

  • the present invention relates to a rocking cam, which includes a cam surface having a base circle portion and a lift portion, and which is disposed so as to make reciprocating motion, and relates to a valve mechanism for an internal combustion engine, which is provided with the rocking cam.
  • this type of valve mechanism for an internal combustion engine has: a camshaft rotated by a crankshaft; a rotating cam provided to the camshaft; a rocking cam rocked by the rotating cam for reciprocating motion; and a rocker arm partly coming into contact with a cam surface of the rocking cam.
  • the rocking cam When the rocking cam is rocked, the cam surface thereof allows the rocker arm to be rocked. This motion by the rocker arm presses an intake or exhaust valve to open/close the valve (See Patent Document 1).
  • Patent Document 1 JP-A-H7-063023
  • the cam surface of the rocking cam has a base circle portion, a lift portion and a ramp portion for connecting therebetween
  • the cam surface requires a certain width to secure strength enough to withstand a large force acting on the cam surface.
  • other parts associated with the rocking cam also need to secure certain strength, causing increases in weight of the parts as well as in size of the entire system. This creates additional problem with an increase in wear and the like on a contact portion of the rocking cam.
  • the present invention has been made in order to solve the above-mentioned problems of the prior art. Accordingly, it is an object of the present invention to provide a rocking cam and a valve mechanism for an internal combustion engine, which can achieve reductions in size and weight as well as in wear and the like on a contact portion of the rocking cam.
  • the invention as described in Claim 1 provides a rocking cam including a cam surface having a base circle portion and a lift portion, and disposed so as to make reciprocating motion, in which a width of a contact surface of the base circle portion is formed smaller than a width of a contact surface of the lift portion.
  • the invention as described in Claim 2 provides a valve mechanism for an internal combustion engine, having: a camshaft rotated by a crankshaft of the internal combustion engine; a rotating cam provided to the camshaft; a rocking shaft provided in parallel to the camshaft; and a rocking cam supported with the rocking shaft and freely rockable by the rotating cam and capable of varying a lift amount of an intake valve or an exhaust valve of the internal combustion engine, in which the rocking cam includes a cam surface having a base circle portion and a lift portion, and is disposed so as to make reciprocating motion, and a width of a contact surface of the base circle portion is formed smaller than a width of a contact surface of the lift portion.
  • the invention as described in Claim 3 provides the valve mechanism for an internal combustion engine according to Claim 2, in which the rocking cam is provided with a movable rotating cam abutment portion that comes into contact with the rotating cam to transmit a drive force from the rotating cam to the rocking cam, and provided with a guide portion for guiding the rotating cam abutment portion in a certain direction; the drive force from the rotating cam is inputted to the guide portion via the rotating cam abutment portion so that the rocking cam is rocked; a variable abutment portion mechanism is provided for making a relative distance between the rotating cam abutment portion and a center axis of the rocking shaft variable by making the rotating cam abutment portion movable along the guide portion; and a lift amount of each valve is made variable by thus making the relative distance variable.
  • the rocking cam includes the cam surface having the base circle portion and the lift portion, and is disposed so as to make reciprocating motion, in which the width of the contact surface of the base circle portion is formed smaller than the width of the contact surface of the lift portion. Therefore, weight of the rocking cam can be reduced. This results in a reduction in inertia force of the rocking cam at the time of rocking movement, as well as in a reduction in weight of parts associated with the rocking cam.
  • the valve mechanism for an internal combustion engine which is capable of changing the lift amount of the intake valve or the exhaust valve of the internal combustion engine, is provided with the rocking cam having the base circle portion and the lift portion, with the width of the contact surface of the base circle portion being formed smaller than the width of the contact surface of the lift portion. This allows this variable valve mechanism to provide the above-mentioned effects.
  • FIGs. 1 through 5 illustrate Embodiment 1 of the present invention.
  • reference numeral 1 denotes a variable valve mechanism for an intake valve 11 of an internal combustion gasoline engine.
  • the variable valve mechanism 1 has a camshaft 2 rotated by a crankshaft (not shown) of the internal combustion engine, a rotating cam 3 provided to the camshaft 2, a rocking shaft 4 provided in parallel to the camshaft 2, a rocking cam 5 supported on the rocking shaft 4 and adapted to rock by the rotating cam 3, and a rocker arm 6 that is rocked in synchronization with the rocking cam 5 to open/close the intake valve 11.
  • variable valve mechanism 1 is the same between the intake valve 11 and exhaust valve of the gasoline engine. Accordingly, Embodiment 1 focuses on the mechanism on the intake valve 11 side, and the description of the mechanism on the exhaust valve side is omitted.
  • the camshaft 2 is arranged with its longitudinal direction extending toward the front and back (i.e. in the direction perpendicular to the plane) of FIG. 1.
  • the camshaft 2 is rotated about a center axis O1 at a half rotational speed of that of the crankshaft of the internal combustion engine.
  • the rotating cam 3 is fixed onto the outer peripheral surface of the camshaft 2 and, as shown in FIG. 1, the outer peripheral portion thereof is configured with a base surface 3a that is arc-shaped in plan view, and a nose surface 3b projecting from the base surface 3a.
  • a center axis O2 of the rocking shaft 4 is arranged in parallel to the center axis O1 of the camshaft 2.
  • the rocking cam 5 is in fitting engagement with the outer peripheral surface of the rocking shaft 4, and is supported so as to be rockable about the center axis O2 of the rocking shaft 4.
  • a cam surface 5a for rocking the rocker arm 6 is formed in the lower end portion of the rocking cam 5.
  • a width L1 of a contact surface of the base circle portion 5c is formed smaller than a width L2 of a contact surface of the lift portion 5d.
  • a guide portion 5b as an elongate through-hole is formed at the longitudinally middle portion of the rocking cam 5.
  • a roller 8 is provided to the roller shaft 7 as a "rotating cam abutting portion” that contacts and operates in synchronization with a base surface 3a or a nose surface 3b of the rotating cam 3, for transmitting the drive force from the rotating cam 3 to the rocking cam 5.
  • the guide portion 5b is formed in the shape of an elongate hole so as to guide the roller shaft 7 along its longitudinal direction over a predetermined distance, and the guiding direction at this time is inclined with respect to the radial direction of the camshaft 2.
  • the roller 8 is formed in a circular shape, and is arranged on the outer peripheral surface of the roller shaft 7 so that the center axis of the roller 8 becomes the same as the center axis O3 of the roller shaft 7.
  • the outer peripheral surface of the roller 8 is capable of rolling on the base surface 3a and nose surface 3b of the rocking cam 3.
  • the rotating cam abutment portion which abuts the rotating cam 3 is formed in the shape of a roller to rotate on the rotating cam 3 face. This reduces loss of the drive force transmitted from the rotating cam 3 to "the rotating cam abutment portion.”
  • the rotating cam abutment portion is the roller 8 which rotates on the rotating cam 3 face, but is not limited to this.
  • the rotating cam abutment portion may be the one which slides on the rotating cam 3 face, as long as the drive force from the rotating cam 3 is transmitted to the rocking cam 5.
  • a spring 15 for urging the rocking cam 5 toward the rotating cam 3 side is in fitting engagement with the rocking shaft 4.
  • the rocking cam 5 is urged toward the rotating cam 3 side by the urging force of the spring 15, so that the outer peripheral surface of the roller 8 is in constant contact with the base surface 3a or nose surface 3b of the rotating cam 3.
  • variable valve mechanism 1 is provided with "a variable abutment portion mechanism" for making the relative distance between the roller 8 and the center axis O2 of the rocking shaft 4 variable.
  • variable abutment portion mechanism has a drive shaft 9 fixedly provided onto the rocking shaft 4, and an arm 10 whose one end portion 10a is connected to the roller shaft 7 and whose other end portion 10b is connected to the drive shaft 9.
  • the drive shaft 9 is provided to the rocking shaft 4 in such a manner that a center axis O4 thereof is located in parallel and eccentrically to the center axis O2 of the rocking shaft 4.
  • an actuator (not shown) for rotating the rocking shaft 4 within a predetermined angle range about the center axis O2 is connected to one end portion of the rocking shaft 4.
  • control means (not shown) for controlling the angle of the actuator according to the operational state of the internal combustion engine.
  • the drive shaft 9 turns by a predetermined angle about the center axis O2 of the rocking shaft 4, whereby the position of the center axis O4 changes relative to the center axis O2 of the rocking shaft 4.
  • the arm 10 is capable of keeping the distance between the center axis O3 of the roller shaft 7 and the center axis O4 of the drive shaft 9 constant.
  • a through-hole 10c, with which the roller shaft 7 is fitted, is formed at the one end portion 10a of the arm 10, and an insertion portion 10d, into which the drive shaft 9 is inserted and which is partially open, is formed at the other end portion 10b thereof.
  • the roller shaft 7 is rotatably fitted with the through-hole 10c at the one end portion 10a
  • the drive shaft 9 is rotatably fitted with the insertion portion 10d at the other end portion 10b and mounted in place with a pin 16 so as to prevent dislodging thereof.
  • the drive shaft 9 provided to the rocking shaft 4 is turned by a predetermined angle about the center axis O2 of the rocking shaft 4, and the roller shaft 7 is operated in synchronization with this turning movement through the arm 10.
  • the roller shaft 7 can be thus moved within the guide portion 5b while keeping the distance between the center axis O3 of the roller shaft 7 and the center axis O4 of the drive shaft 9 constant with the arm 10, whereby the relative distance between the center axis O2 of the rocking shaft 4 and the roller 8 can be made variable.
  • rocker arm 6 is rockably supported with the rocker arm shaft 12, the configuration is not limited to this.
  • the rocker arm 6 may be rockably supported with a spherical pivot, hydraulic lash adjuster, or the like.
  • valve pressing portion 6a is formed at the distal end portion of the rocker arm 6 for pressing on the upper surface of a shim 23 fitted on an intake valve 11 which will be described later.
  • a roller 14 is rotatably provided to the roller shaft 13, and the outer peripheral surface of the roller 14 is capable of rolling on the cam surface 5a of the rocking cam 5.
  • a spring 17 for urging the rocker arm 6 toward the rocking cam 5 side is in fitting engagement with the rocker arm shaft 12.
  • the rocker arm 6 is urged toward the rocking cam 5 side by means of the spring 17, so that the outer peripheral surface of the roller 14 is in constant contact with the cam surface 5a of the rocking cam 5.
  • the intake valve 11 pressed by the valve pressing portion 6a is arranged below the valve pressing portion 6a of the rocker arm 6 so as to be vertically movable.
  • the intake valve 11 has a collet 20 and an upper retainer 21 that are provided in its upper portion.
  • a valve spring 22 is arranged below the upper retainer 21.
  • the intake valve 11 is urged toward the rocker arm 6 side by the urging force of the valve spring 22. Further, the shim 23 is fitted on the upper end portion of the intake valve 11.
  • the intake valve 11 can be vertically moved by rocking the rocker arm 6 in synchronization with the rocking motion of the rocking cam 5.
  • the relative distance between the center axis O2 of the rocking cam 4 and the roller 8 variable to adjust the rocking start position of the rocking cam 5 the lift amount and the maximum lift timing of the intake valve 11 can be adjusted and made variable through the rocker arm 6.
  • variable valve mechanism 1 Operation of the variable valve mechanism 1 constructed as above will next be described.
  • variable valve mechanism 1 for an internal combustion engine when the maximum lift amount is required, with reference to FIGs. 1 and 2.
  • FIG. 1 is a longitudinal sectional view of the main portion of variable valve mechanism 1 of the internal combustion engine according to Embodiment 1 of the present invention when the maximum lift amount is required, illustrating the state in which the intake valve 11 is closed.
  • FIG. 2 is a longitudinal sectional view of the main portion of the variable valve mechanism 1 of the internal combustion engine according to Embodiment 2 of the present invention when the maximum lift amount is required, illustrating the state in which the intake valve is open.
  • the roller shaft 7 is moved to the rotating cam 3-side end portion of the guide portion 5b, thereby changing the relative distance between the center axis O2 of the rocking shaft 4 and the roller 8. That is, the rocking shaft 4 is turned by a predetermined angle by the actuator, causing the drive shaft 9 to move in the circumferential direction of the rocking shaft 4.
  • the roller shaft 7 is operated in synchronization with this movement via the arm 10 so as to be moved to the rotating cam 3-side end portion of the guide portion 5b, whereby the relative distance between the center axis O2 of the rocking shaft 4 and the roller 8 changes.
  • the roller 14 is located at the position corresponding to the base circle portion 5c of the cam surface 5a of the rocking cam 5. Since no large abutment force acts between the roller 14 and the base circle portion 5c in the valve closure state, a sufficient durability can be secured even through the width L1 of the base circle portion 5c is small.
  • the valve pressing portion 6a formed at the distal end portion of the rocker arm 6 that has thus undergone large rocking movement to the intake valve 11 side presses on the upper surface of the shim 23 to push down the intake valve 11 by a large distance.
  • the roller shaft 7 to the end portion of the guide portion 5b in the rotating cam 3 side to make the relative distance between the center axis O2 of the rocking shaft 4 and the roller 8 variable, the relative distance between the center axis O2 of the rocking shaft 4 and the roller 14 in contact with the cam surface 5a of the rocking cam 5 can be largely changed, whereby the intake valve 11 can be pushed down by a large distance to bring the intake valve 11 into an open state at the maximum lift amount.
  • the width L2 of the lift portion 5d is made large because a large reaction force acts on the cam surface 5a of the rocking cam 5, thereby making it possible to secure strength.
  • the rocking shaft 4 is turned within a predetermined angle range by the actuator, causing the drive shaft 9 to move in the circumferential direction of the rocking shaft 4.
  • the roller shaft 7 is operated in synchronization with this movement via the arm 10 so that the roller shaft 7 is moved to the rocking shaft 4-side end portion of the guide portion 5b from the state where it is retained at the rotating cam 3-side end portion, whereby the relative distance between the center axis O2 of the rocking shaft 4 and the roller 8 decreases.
  • the rocking cam 5 turns from the position as shown in FIG. 1 to the position as shown in FIG. 3 due to the urging force of the spring 15.
  • the roller shaft 7 to the rocking shaft 4-side end portion of the guide portion 5b to make the relative distance between the center axis O2 of the rocking shaft 4 and the roller 8 variable the relative distance between the center axis O2 of the rocking shaft 4 and the roller 14 in contact with the cam surface 5a of the rocking cam 5 can be subjected to a small change to push down the intake valve 11 by a small distance, whereby, in Embodiment 1, the intake valve 11 can be brought into an open state at the minimum lift amount.
  • the width L1 of the base circle portion 5c is small, since no large load acts on this portion, a requisite strength can be secured for the base circle portion 5c. Because a large load acts on the lift portion 5d, the width L2 thereof is made larger to secure a requisite strength.
  • Weight of the rocking cam 5 can be reduced because of the small width L1 of the base circle portion 5c. This results in a reduction in inertia force of the rocking cam 5 at the time of rocking movement, as well as in a reduction in weight of parts associated with the rocking cam 5 (e.g. spring 15). This allows the whole system to be smaller while reducing wear on a contact portion of the cam surface 5a.
  • the base circle portion 5c is formed in a position apart from the center axis O2, and therefore can more contribute to the reduced inertia force.
  • the rocking cam 5 is provided with the roller 8 or the rotating cam abutment portion that comes into contact with the rotating cam 3 to transmit the drive force from the rotating cam to the rocking cam 5.
  • the valve mechanism 1 is provided with the variable abutment portion mechanism for making the relative distance between the roller 8 and the center axis O2 of the rocking shaft 4 variable by making the roller 8 movable; the lift amount or the like of each valve is made variable by thus making the relative distance variable, whereby the structure can be simplified to achieve low-cost construction.
  • the load from the rotating cam 3 is input to the roller 8, and the load is directly transmitted from the roller 8 to the guide portion 5a of the rocking cam 5. Then, the load is transmitted from the rocking cam 5 to the intake valve 11 via the rocker arm 6. Thus, no large load acts on the arm 10 that supports the roller 8, and since the arm 10 serves the sole function of moving the roller 8 along the guide portion 5a, not so large strength is required for the arm 10.
  • FIGs. 6 through 8 illustrate Embodiment 2 of the present invention.
  • FIG. 6 is a longitudinal sectional view of the main portion of the variable valve mechanism for the internal combustion engine when the maximum lift amount is required, illustrating the state in which the intake valve is closed.
  • FIG. 7 is a longitudinal sectional view of the main portion of the variable valve mechanism for the internal combustion engine when the minimum lift amount is required, illustrating the state in which the intake valve is closed.
  • the rocker arm 6 which opens and closes an intake valve 11 as in Embodiment 1 is not provided, but a rocking cam 5 directly moves the intake valve 11 upward and downward to open and close the intake valve 11.
  • the rocking cam 5 is formed in the shape of a comma-shaped bead.
  • the rocking cam 5 is fitted on the peripheral surface of a rocking shaft 4 and supported so as to be rockable about the center axis O2 of the rocking shaft 4.
  • the rocking cam 5 includes a cam surface 5a having a base circle portion 5c, a lift portion 5d and a ramp portion 5e.
  • a width L1 of a contact surface of the base circle portion 5c is formed smaller than a width L2 of a contact surface of the lift portion 5d.
  • the bottom end of the rocking cam 5 is formed with a cam surface 5a.
  • the cam surface 5a is curved toward the intake valve 11 to form a projection, and depresses a lifter 26 of the intake valve 11 to vertically move the intake valve 11.
  • the upper portion of the cam surface 5a is formed with a guide portion 5b, along which a roller shaft 7 having a roller 8 slides.
  • the rocking shaft 4 is provided with a spring (not shown) for urging the rocking cam 5 toward the rotating cam 3.
  • the rocking cam 5 is thereby urged toward the rotating cam 3 by the urging force of the spring, so that the peripheral surface of the roller shaft 7 is normally in contact with the guide portion 5b, and the peripheral surface of the roller 8 is normally in contact with a base surface 3a or a nose surface 3b of the rotating cam 3.
  • the drive shaft 9 provided to the rocking shaft 4 is turned by a predetermined angle about the center axis O2 of the rocking shaft 4, and the roller shaft 7 is operated in synchronization with this turning movement through the arm 10.
  • the roller shaft 7 can be thus moved within the guide portion 5b while keeping the distance between the center axis O3 of the roller shaft 7 and the center axis O4 of the drive shaft 9 constant with the arm 10, whereby the relative distance between the center axis O2 of the rocking shaft 4 and the roller 8 can be made variable. Therefore, the lift amount and the maximum lift timing of the intake valve 11 can be adjusted and made variable.
  • the width L1 of the base circle portion 5c is small, as in the Embodiment described above, since no large load acts on this portion, a requisite strength can be secured for the base circle portion 5c. Because a large load acts on the lift portion 5d, the width L2 thereof is made larger to secure a requisite strength.
  • Weight of the rocking cam 5 can be reduced because of the small width L1 of the base circle portion 5c. This results in a reduction in inertia force of the rocking cam 5 at the time of rocking movement, as well as in a reduction in weight of parts associated with the rocking cam 5 (e.g. spring 15). This allows the whole system to be smaller while reducing wear on a contact portion of the cam surface 5a.
  • Embodiment 2 is of the same construction and operation as Embodiment 1 of the present invention, so repetitive description will not be repeated.
  • FIGs. 9 through 11 are longitudinal sectional views of the main portion of valve mechanism for an internal combustion engine according to Embodiment 3 of the present invention, illustrating a state in which the intake valve is closed.
  • a rocker arm 6 has a roller 14 that comes into contact with a cam surface 5a of a rocking cam 5, a roller arm 6c for supporting the roller 14, which is operated in synchronization with the rocking motion of the rocking cam 5, and a rocker arm main body 6d that rocks in synchronization with the roller arm 6c to vertically move an intake valve 11.
  • a leaf spring 28 is used to urge the roller arm 6c to the rocking cam 5 side to bring the roller 14 and the cam surface 5a of the rocking cam 5 into contact with each other.
  • the cam surface 5a has a base circle portion 5c, a lift portion 5d, and a ramp portion 5e, and a width L1 of the base circle portion 5c is formed smaller than a width L2 of the lift portion 5d.
  • roller arm 6c is freely movable to a predetermined position. By changing the contact position between the roller 14 provided to the roller arm 6c and the cam surface 5a of the rocking cam 5, the life amount of each valve or the like can be adjusted.
  • an eccentric shaft 29 is fixedly provided to the rocker arm shaft 12 in such a manner that a center axis O7 thereof is located in parallel and eccentrically to the center axis O5 of the rocker arm shaft 12.
  • the roller arm 6c of the rocker arm 6 is rotatably locked onto the eccentric shaft 29 by means of the leaf spring 28.
  • the roller arm 6c has an engaging portion 6e formed at its one end.
  • the engaging portion 6e engages with the outer peripheral surface of the eccentric shaft 29, and is so shaped as to be capable of sliding on the outer peripheral surface of the eccentric shaft 29.
  • a fitting engagement portion 6f Formed at a position adjacent to the engaging portion 6e is a fitting engagement portion 6f with which the leaf spring 28 for integrally locking the roller arm 6c and the eccentric shaft 29 in place is brought into fitting engagement so as to prevent dislodging thereof.
  • a through-hole 6g with which the roller shaft 13 supporting the roller 14 that slides on the cam surface 5a of the rocking cam 5 is brought into fitting engagement, is formed at the other end of the roller arm 6c.
  • a pressing portion 6h for pressing the rocker arm main body 6d to the intake valve 11 side when the roller arm 6c rocks to the intake valve 11 side in synchronization with the rocking motion of the rocking cam 5.
  • the rocker arm main body 6d of the rocker arm 6 is rockably supported and arranged on the rocker arm shaft 12, and has the valve pressing portion 6a formed at is distal end portion.
  • the valve pressing portion 6a presses on the upper surface of the shim 23 fitted on the intake valve 11. Further, a contact surface 6i with which a distal end portion 28b of the leaf spring 28, which will be described later, comes into contact is formed above the valve pressing portion 6a, and a guide portion 6j pressed on by the pressing portion 6h formed in the rocker arm 6c is formed above the contact surface 6i.
  • the leaf spring 28 is formed into a predetermined configuration by bending a planar spring at several locations. More specifically, the leaf spring 28 is formed in a configuration allowing fitting engagement with the fitting engagement portion 6f of the roller arm 6c and with the eccentric shaft 29, and has formed therein a locking portion 28a for integrally locking the roller arm 6c and the eccentric shaft 29 onto each other. Further, the distal end portion 28b of the leaf spring 28 on the roller arm 6c side extends to the roller 14 side and comes into contact with the contact surface 6i formed in the rocker arm main body 6d.
  • leaf spring 28 is formed in such a configuration as to urge the roller arm 6c and the rocker arm main body 6d so as to spread out from each other when the roller arm 6c and the eccentric shaft 29 are integrally locked onto each other by the locking portion 28a.
  • a predetermined clearance A is provided between a pressing portion 6h of the roller arm 6c and a guide portion 6j of the rocker arm main body 6d.
  • roller arm 6c is integrally locked onto the eccentric shaft 29 by the leaf spring 28 so that the roller arm 6c can slide on the outer peripheral surface of the eccentric shaft 29, when the rocking cam 5 is rocked, the roller arm 6c is caused via the roller 14 and the roller shaft 13 to rock to the intake valve 11 side against the urging force of the leaf spring 28. Further, as the rocker arm 6c is rocked to the intake valve 11 side, the pressing portion 6h of the roller arm 6c presses on the guide portion 6j of the rocker arm main body 6d, causing the rocker arm main body 6d to rock to the intake valve 11 side, thereby making it possible to open and close the intake valve 11.
  • roller arm 6c is urged to the rocking cam 5 side by the leaf spring 28, so the outer peripheral surface of the roller 14 provided to the roller arm 6c is held in constant contact with the cam surface 5a of the rocking cam 5.
  • an actuator for rotating the rocker arm shaft 12 within a predetermined angle range about the center axis O5 is connected to one end portion of the rocker arm shaft 12.
  • control means for controlling the angle of the actuator according to the operational state of the internal combustion engine.
  • the eccentric shaft 29 provided to the rocker arm shaft 12 is turned by a predetermined angle about the center axis O5 of the rocker arm shaft 12. Further, when the eccentric shaft 29 is turned by the predetermined angle, the roller arm 6c operating in synchronization therewith is moved, for example, from the position indicated by the solid line in FIG. 9 to a predetermined position indicated by the chain double-dashed line in FIG. 9. Then, once the roller arm 6c has been moved to the predetermined position, the contact point where the cam surface 5a of the rocking cam 5 and the roller 14 provided to the roller arm 6c come into contact with each other changes. The rocking amount of the rocker arm main body 6d can be thus changed, which makes it possible to adjust the lift amount or the like of the intake valve 11 that is vertically moved by the rocker arm 6.
  • the predetermined clearance (A) provided between the pressing portion 6h and the guide portion 6j allows the intake valve 11 to be reliably opened/closed even when, due to a rise in the temperature of the internal combustion engine, the intake valve 11 undergoes thermal expansion to cause upward jumping of the valve.
  • valve mechanism 1 for an internal combustion engine constructed as described above in which the lift amount or the like of each valve can be adjusted by making the roller arm 6c be movable to the predetermined position and changing the contact position between the roller 14 provided to the roller arm 6c and the cam surface 5a of the rocking cam 5, the roller arm 6c is urged toward the rocking cam 5 side by the leaf spring 28. Accordingly, when the roller arm 6c has been moved to the predetermined position and the contact position between the roller 14 and the cam surface 5a changes, the roller 14 of the rocker arm 6 and the cam surface 5a of the rocking cam 5 constantly come into contact with each other, thereby making it possible to prevent adhesive wear.
  • the width L1 of the base circle portion 5c is small, as in the Embodiments described above, since no large load acts on this portion, a requisite strength can be secured for the base circle portion 5c. Because a large load acts on the lift portion 5d, the width L2 thereof is made larger to secure a requisite strength.
  • Weight of the rocking cam 5 can be reduced because of the small width L1 of the base circle portion 5c. This results in a reduction in inertia force of the rocking cam 5 at the time of rocking movement, as well as in a reduction in weight of parts associated with the rocking cam 5 (e.g. spring 15).
  • the base circle portion 5c is formed in a position apart from the center axis O2, and therefore can more contribute to the reduced inertia force.
  • Embodiment 3 is of the same construction and operation as Embodiment 1 of the present invention, so repetitive description will not be repeated.
  • Embodiment 3 is of the same construction and operation as Embodiment 1 of the present invention, so repetitive description will not be repeated.
  • FIGs. 12 and 13 are longitudinal sectional views of the main portion of a valve mechanism for an internal combustion engine according to Embodiment 4 of the present invention, illustrating a state in which the intake valve is closed.
  • the valve mechanism 1 for an internal combustion engine according to Embodiment 4 is capable of adjusting the lift amount or the like of each valve by making the rocking shaft 4 movable to a predetermined position.
  • a roller 33 is arranged on the outer peripheral surface of the rocking shaft 4.
  • the roller 33 is in contact with a guide portion 19a formed in the cylinder head main body 19 for guiding the rocking shaft 4 to a predetermined position.
  • the rocking shaft 4 is provided to the cylinder head main body 19 such that, when the rocking cam 5 is pressed by a control cam 34 that will be described next, the rocking shaft 4 can move in synchronization with the rocking cam 12 within a range from a position indicated by the solid line in FIG. 12 to that indicated by the chain double-dashed line in FIG. 12.
  • the control cam 34 is fixed onto the outer peripheral surface of a control shaft 35 provided in parallel to the camshaft 2. Further, the outer peripheral portion of the control cam 34 contacts the rocking cam 5 and is formed in a configuration allowing the rocking shaft 4 to be guided to a predetermined position by rotating the control cam 34 in a predetermined angle.
  • the cam surface 5a of the rocking cam 5 has a base circle portion 5c, a lift portion 5d, and a ramp portion 5e, and a width L1 of the base circle portion 5c is formed smaller than a width L2 of the lift portion 5d.
  • an actuator for rotating the control shaft 35 within a predetermined angle range about a center axis O8 of the control shaft 35 is connected to one end portion of the control shaft 35.
  • control means for controlling the angle of the actuator according to the operational state of the internal combustion engine.
  • the rocker arm 6 which makes reciprocating motion while rocking within a predetermined range in synchronization with the rocking cam 5, is of the same construction as that of Embodiment 1. That is, the rocker arm 6 has the valve pressing portion 6a formed therein, is provided with the roller shaft 13 and the roller 14, and is rockably supported on the rocker arm shaft 12.
  • the rocker arm shaft 12 is provided with the torsion spring 17 as a spring member for bringing the roller 14 and the cam surface 5a into constant contact with each other.
  • the control cam 34 is rotated by a predetermined angle about the center axis O8 of the control shaft 35.
  • the roller 33 is caused via the rocking cam 5 to slide on the guide portion 19a of the cylinder head main body 19 so as to be moved, for example, from the position indicated by the solid line in FIG. 12 to a predetermined position indicated by the chain double-dashed line in FIG. 12.
  • the rocking shaft 4 is moved, the position of the cam surface 5a of the rocking cam 5 changes.
  • the rocking amount of the rocker arm 6 can be thus changed, which makes it possible to adjust the lift amount or the like of the intake valve 11 that is vertically moved by the rocker arm 6.
  • valve mechanism 1 which makes the lift amount or the like of each valve variable by moving the rocking shaft 4 to a predetermined position
  • the rocker arm 6 is urged to the rocking cam 5 side by the torsion spring 17, so even when the rocking shaft 4 has been moved to the predetermined position, and the position of the cam surface 5a of the rocking cam 5 changes, the roller 14 of the rocker arm 6 and the cam surface 5a of the rocking cam 5 constantly come into contact with each other. Adhesive wear can be thus prevented.
  • the width L1 of the base circle portion 5c is small, as in the Embodiments described above, since no large load acts on this portion, a requisite strength can be secured for the base circle portion 5c. Because a large load acts on the lift portion 5d, the width L2 thereof is made larger to secure a requisite strength.
  • Weight of the rocking cam 5 can be reduced because of the small width L1 of the base circle portion 5c. This results in a reduction in inertia force of the rocking cam 5 at the time of rocking movement, as well as in a reduction in weight of parts associated with the rocking cam 5 (e.g. spring 15).
  • the base circle portion 5c formed in a position apart from the center axis O2, can more contribute to the reduced inertia force.
  • Embodiment 4 is of the same construction and operation as Embodiment 1 of the present invention, so repetitive description will not be repeated.
  • FIGs. 14 and 15 are longitudinal sectional views of the main portion of a valve mechanism for an internal combustion engine according to Embodiment 5 of the present invention, illustrating a state in which the intake valve is closed.
  • Embodiment 5 provides the valve mechanism 1 for an internal combustion engine in which the rotating cam 3 has a tapered configuration, and the contact position between the outer peripheral portion of the rotating cam 3 and the rocking cam 5 is changed by moving the rotating cam 3 in the direction of the center axis O1 of the camshaft 2, thereby making it possible to adjust the lift amount or the like of each valve.
  • the rotating cam 3 is fixed onto the outer peripheral surface of the camshaft 2.
  • the outer peripheral portion of the rotating cam 3 is constructed with the base surface 3a that is arc-shaped in plan view, and the nose surface 3b projecting from the base surface 3a.
  • the base surface 3a and the nose surface 3b are formed in the tapered configuration in the direction of the center axis O1 (in the direction perpendicular to the sheet plane) of FIG. 14.
  • an actuator for moving the camshaft 2 within a predetermined range in the direction of the center axis O1 is connected to one end portion of the camshaft 2.
  • control means for controlling the angle of the actuator according to the operational state of the internal combustion engine.
  • the outer peripheral surface of the roller 8 provided to the rocking cam 5 rocked by the rotating cam 3 is capable of sliding on the base surface 3a and base surface 3b of the rotating cam 3 formed in the tapered configuration.
  • the cam surface 5a of the rocking cam 5 has a base circle portion 5c, a lift portion 5d, and a ramp portion 5e, and a width L1 of the base circle portion 5c is formed smaller than a width L2 of the lift portion 5d.
  • the rocker arm 6 which makes reciprocating motion while rocking within a predetermined range in synchronization with the rocking cam 5, is of the same construction as that of Embodiment 4. That is, the rocker arm 6 has the valve pressing portion 6a formed therein, is provided with the roller shaft 13 and the roller 14, and is rockably supported on the rocker arm shaft 12.
  • the rocker arm shaft 12 is provided with the torsion spring 17 for bringing the roller 14 and the cam surface 5a into constant contact with each other.
  • the rotating cam 3 moves within a predetermine range in the direction of the center axis O1 of the camshaft 2. Since the rotating cam 3 is formed in the tapered configuration, when the rotating cam 3 is moved with the predetermined range, the rocking cam 5 is caused via the roller shaft 7 and the roller 8 to move, for example, from the position indicated by the solid line in FIG. 14 to a predetermined position indicated by the double-dashed chain line in FIG. 14. Then, when the rocking cam 5 has been moved to the predetermined position, the position of the cam surface 5a of the rocking cam 5 changes. Therefore, the rocking amount of the rocker arm 6 can be changed, which makes it possible to adjust the lift amount or the like of the intake valve 11 that is vertically moved by the rocker arm 6.
  • valve mechanism 1 constructed as described above, in which the rotating cam 3 is tapered, and the lift amount or the like of each valve variable is made variable by moving the rotating cam 3 in the direction of the center axis O1 of the camshaft 2 and changing the contact position between the outer peripheral portion of the rotating cam 3 and the rocking cam 5, the rocker arm 6 is urged to the rocking cam 5 side by the torsion spring 17, so even when the rocking shaft 4 has been moved to the predetermined position, and the position of the cam surface 5a of the rocking cam 5 changes, the roller 14 of the rocker arm 6 and the cam surface 5a of the rocking cam 5 constantly come into contact with each other. Adhesive wear can be thus prevented.
  • the width L1 of the base circle portion 5c is small, as in the Embodiments described above, since no large load acts on this portion, a requisite strength can be secured for the base circle portion 5c. Because a large load acts on the lift portion 5d, the width L2 thereof is made larger to secure a requisite strength.
  • Weight of the rocking cam 5 can be reduced because of the small width L1 of the base circle portion 5c. This results in a reduction in inertia force of the rocking cam 5 at the time of rocking movement, as well as in a reduction in weight of parts associated with the rocking cam 5 (e.g. spring 15).
  • the base circle portion 5c is formed in a position apart from the center axis O2, and therefore can more contribute to the reduced inertia force.
  • Embodiment 5 is of the same construction and operation as Embodiment 1 of the present invention, so repetitive description will not be repeated.
  • the present invention is applied to the variable valve mechanism 1 provided with the rocking cam 5, the present invention is not limited to this construction.
  • the present invention may also be applied to any valve mechanism incapable of changing the lift amount or the like.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP04772154A 2004-08-25 2004-08-25 Oszillierender nocken und dynamischer ventilmechanismus für verbrennungsmotor Expired - Lifetime EP1783332B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2004/012193 WO2006021997A1 (ja) 2004-08-25 2004-08-25 揺動カム及び内燃機関の動弁機構

Publications (3)

Publication Number Publication Date
EP1783332A1 true EP1783332A1 (de) 2007-05-09
EP1783332A4 EP1783332A4 (de) 2010-06-02
EP1783332B1 EP1783332B1 (de) 2011-04-27

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Application Number Title Priority Date Filing Date
EP04772154A Expired - Lifetime EP1783332B1 (de) 2004-08-25 2004-08-25 Oszillierender nocken und dynamischer ventilmechanismus für verbrennungsmotor

Country Status (5)

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EP (1) EP1783332B1 (de)
AT (1) ATE507371T1 (de)
CA (1) CA2541726A1 (de)
DE (1) DE602004032479D1 (de)
WO (1) WO2006021997A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007033821A1 (de) * 2007-07-18 2009-01-22 Hydraulik-Ring Gmbh Arbeitskurve eines variablen Ventiltriebs
CN103089365A (zh) * 2013-02-28 2013-05-08 长城汽车股份有限公司 用于发动机的可变气门升程驱动装置的致动机构

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006018510A1 (de) * 2006-04-21 2007-10-25 Schaeffler Kg Schwinghebel für einen hubvariablen Ventiltrieb

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3380582B2 (ja) * 1993-03-23 2003-02-24 マツダ株式会社 エンジンのバルブタイミング制御装置
JPH07133709A (ja) * 1993-09-17 1995-05-23 Mazda Motor Corp エンジンのバルブタイミング可変装置

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO2006021997A1 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007033821A1 (de) * 2007-07-18 2009-01-22 Hydraulik-Ring Gmbh Arbeitskurve eines variablen Ventiltriebs
DE102007033821B4 (de) * 2007-07-18 2013-10-31 Hydraulik-Ring Gmbh Arbeitskurve eines variablen Ventiltriebs
CN103089365A (zh) * 2013-02-28 2013-05-08 长城汽车股份有限公司 用于发动机的可变气门升程驱动装置的致动机构
CN103089365B (zh) * 2013-02-28 2015-05-06 长城汽车股份有限公司 用于发动机的可变气门升程驱动装置的致动机构

Also Published As

Publication number Publication date
DE602004032479D1 (de) 2011-06-09
EP1783332B1 (de) 2011-04-27
WO2006021997A1 (ja) 2006-03-02
CA2541726A1 (en) 2006-03-02
EP1783332A4 (de) 2010-06-02
ATE507371T1 (de) 2011-05-15

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