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 swing cam provided with a cam surface having a base circular portion and a lift portion and configured to reciprocate, and a valve operating mechanism for an internal combustion engine provided with the swing cam. It is.
• a rotating cam is provided on a camshaft that is driven to rotate by a crankshaft, and the swinging cam is swung by the rotating cam and moved back and forth.
• a part of the rocker arm is in contact with the cam surface of the swing cam.
• the rocker arm is swung by the cam surface of the swing cam, and the intake or exhaust port is pushed by the rocker arm to open and close the intake or exhaust port.
• Patent Document 1 Japanese Patent Application Laid-Open No. 07-060323.
• the cam surface of the swing cam has a base circle portion, a lift portion, and a ramp portion connecting them, and a large force acts on this cam surface. Therefore, it is necessary to secure the strength by forming the cam surface to a predetermined width. This increases the weight of the tip of the rocking cam, increasing the inertial force of the rocking cam that reciprocates, and it is necessary to ensure the strength of other parts related to this rocking cam. However, there is a problem that the weight is increased, the apparatus is enlarged, and the wear of the contact portion of the swing cam is increased.
• the present invention has been made to solve the conventional problems as described above, and is a rocking cam that is reduced in size and weight, and reduces wear of a contact portion of the rocking cam. It is another object of the present invention to provide a valve mechanism for an internal combustion engine.
• the invention according to claim 1 is a swing cam provided with a cam surface having a base circle portion and a lift portion, and provided to reciprocate, the base circle portion.
• the width of the contact surface is a swing cam formed narrower than the width of the contact surface of the lift portion.
• the invention according to claim 2 is a force shaft that is rotationally driven by a crankshaft of an internal combustion engine, a rotating cam provided on the camshaft, and a swing shaft provided in parallel with the camshaft. And an oscillating cam supported by the oscillating shaft and oscillated by the rotating cam, and the lift amount of the intake valve or exhaust valve of the internal combustion engine is variable.
• the swing cam includes a cam surface having a base circle portion and a lift portion, and is provided so as to reciprocate. A width of a contact surface of the base circle portion is set to be a contact surface of the lift portion.
• the valve operating mechanism of the internal combustion engine is formed narrower than this width.
• the invention described in claim 3 is configured such that the swing cam contacts the rotating cam and a driving force from the rotating cam is applied to the swing cam.
• the rotating cam abutting portion for transmission is provided movably, and a guide portion for guiding the rotating cam abutting portion in a predetermined direction is provided on the swing cam, and a driving force from the rotating cam is applied to the rotating cam abutting portion.
• the rocking cam is rocked by being input to the guide portion via a portion, and by moving the rotating cam contact portion along the guide portion,
• An abutting portion variable mechanism that varies a relative distance from the central axis of the swing shaft is provided, and a valve mechanism for an internal combustion engine that can vary the lift amount of each valve by varying the relative distance. It is characterized by that.
• the contact surface of the base circle portion Since the width is made narrower than the width of the contact surface of the lift portion, the weight of the swing cam can be reduced, so that the inertia force during swing can be reduced. The weight of the product can be reduced.
• the intake valve or exhaust valve of the internal combustion engine is By providing an oscillating cam in which the width of the contact surface of the base circular portion is narrower than the width of the contact surface of the lift portion, the variable valve mechanism is provided in the valve mechanism of the internal combustion engine that can vary the amount of rotation. You can get the above effect.
• FIG. 1 is a longitudinal sectional view of a main part in a state in which an intake valve is closed, showing a variable valve mechanism of an internal combustion engine when a maximum lift amount is required according to Embodiment 1 of the present invention.
• FIG. 2 is a longitudinal sectional view of a main part of the internal combustion engine when the maximum lift amount according to the first embodiment is required, with the intake valve opened.
• FIG. 3 is a vertical cross-sectional view of a main part in a state where an intake valve is closed, showing a variable valve mechanism for an internal combustion engine when a minimum lift amount is required according to the first embodiment.
• FIG. 4 is a longitudinal sectional view of the main part of the internal combustion engine when the minimum lift amount is required according to the first embodiment, with the intake valve opened.
• FIG. 5 shows a swing cam according to the first embodiment, where (a) is a front view and (b) is a bottom view.
• Fig. 6 is a longitudinal sectional view of a main part in a state where an intake valve is closed, showing a variable valve mechanism for an internal combustion engine when a maximum lift amount is required according to Embodiment 2 of the present invention.
• Fig. 7 is a longitudinal sectional view of a main part in a state where an intake valve is closed, showing a variable valve mechanism for an internal combustion engine when a minimum lift amount is required according to the second embodiment.
• FIG. 8 shows a swing cam according to the second embodiment, where (a) is a front view and (b) is a bottom view.
• Fig. 9 is a longitudinal sectional view of an essential part showing a variable valve mechanism of an internal combustion engine when a maximum lift amount is required according to Embodiment 3 of the present invention, with an intake valve closed.
• FIG. 10 shows a swing cam according to the third embodiment, where (a) is a front view and (b) is a bottom view.
• FIG. 11 is a view showing the swing cam according to the third embodiment, and is a perspective view of the swing cam as viewed obliquely from below.
• FIG. 12 is a longitudinal sectional view of an essential part showing a variable valve mechanism for an internal combustion engine according to Embodiment 4 of the present invention in a state in which an intake valve is closed.
• FIG. 13 shows a swing cam according to the fourth embodiment, where (a) is a front view and (b) is a bottom view.
• FIG. 14 is a longitudinal sectional view of an essential part showing a variable valve mechanism for an internal combustion engine according to Embodiment 5 of the present invention, in a state where an intake valve is closed.
• FIG. 15 shows a swing cam according to the fifth embodiment, where (a) is a front view and (b) is a bottom view.
• FIG. 1 to FIG. 5 are diagrams according to Embodiment 1 of the present invention.
• Reference numeral 1 in FIG. 1 denotes a variable valve mechanism of an intake valve 11 of a gasoline engine as an internal combustion engine.
• the variable valve mechanism 1 is a crankshaft (not shown) of the internal combustion engine. ),
• the rotating cam 3 provided on the camshaft 2,
• the swinging shaft 4 provided parallel to the camshaft 2, and the swinging shaft 4.
• the rocking cam 5 is rocked by the rotating cam 3 and the rocker arm 6 is rocked in conjunction with the rocking cam 5 to open and close the intake valve 11 of the internal combustion engine.
• the first embodiment shows a mechanism on the intake valve 11 side.
• the description of the mechanism on the exhaust valve side is omitted.
• the camshaft 2 is arranged with its longitudinal direction facing the front and back in Fig. 1 (perpendicular to the paper surface), with the central axis O1 as the center. It is driven to rotate at half the rotational speed of the crankshaft of an internal combustion engine.
• the rotating cam 3 is fixed to the outer peripheral surface of the camshaft 2, and the outer peripheral portion protrudes from the arc-shaped base surface 3a and the base surface 3a in plan view as shown in FIG.
• the nose surface 3b and the force are composed.
• central axis 02 of the oscillating shaft 4 is arranged in parallel to the central axis Ol of the camshaft 2.
• the swing cam 5 is fitted to the outer peripheral surface of the swing shaft 4, and the swing shaft 4 A cam surface 5 a for swinging the rocker arm 6 is formed at the lower end of the swing cam 5.
• the cam surface 5a includes an arc-shaped base circle portion 5c centered on the central axis 02, a lift portion 5d for swinging the rocker arm 6, and the lift It has a lamp portion 5e that connects the portion 5d and the base circle portion 5c.
• the width L1 of the contact surface of the base circle portion 5c is formed to be narrower than the width L2 of the contact surface of the lift portion 5d.
• a guide portion 5b which is a long hole, is formed through the middle portion of the swing cam 5 in the longitudinal direction.
• the guide portion 5b has a central axis O of the swing shaft 4.
• a roller shaft 7 having a central axis 03 parallel to 2 is movably threaded.
• the roller shaft 7 is in contact with the base surface 3a or the nose surface 3b of the rotating cam 3 and interlocks therewith, and serves as a “rotating cam contact portion” that transmits the driving force of the rotating cam 3 force to the swing cam 5.
• Roller 8 is provided.
• the guide portion 5b has a long hole shape and is formed so as to guide the roller shaft 7 along the longitudinal direction for a predetermined distance.
• the guide direction is inclined with respect to the radial direction of the camshaft 2. Is formed.
• the roller 8 is formed in a circular shape, and is disposed on the outer peripheral surface of the roller shaft 7 so that the central axis thereof is the same as the central axis 03 of the roller shaft 7.
• the outer peripheral surface of 8 can roll on the base surface 3a and the nose surface 3b of the rotating cam 3.
• the “rotating cam contact portion” that contacts the rotating cam 3 is formed in a roller shape, it can roll on the surface of the rotating cam 3. The loss of driving force transmitted to the “rotating cam contact portion” can be reduced.
• the “rotating cam contact portion” is a force that is a roller 8 that can roll on the surface of the rotating cam 3, and is not limited to this, and transmits a driving force from the rotating cam 3 to the swing cam 5. If possible, it may slide on the surface of the rotary cam 3.
• a spring 15 that biases the swing cam 5 toward the rotating cam 3 is fitted to the swing shaft 4.
• the swing cam 5 is biased toward the rotating cam 3 by the biasing force of the spring 15, and the outer peripheral surface of the roller 8 always contacts the base surface 3a or the nose surface 3b of the rotating cam 3. is doing.
• variable valve mechanism 1 is provided with a “contact portion varying mechanism” that varies the relative distance between the roller 8 and the central axis 02 of the swing shaft 4.
• a drive shaft 9 provided in a state of being fixed to the swing shaft 4 and one end portion 10a are connected to the roller shaft 7, and the other end portion 10b is driven. And an arm 10 connected to a shaft 9.
• the drive shaft 9 is provided on the oscillating shaft 4 so that the central axis 04 is parallel to the central axis 02 of the oscillating shaft 4 and is in an eccentric position.
• an actuator (not shown) is connected to one end of the oscillating shaft 4 for rotationally driving the oscillating shaft 4 around a central axis 02 within a predetermined angle range.
• the actuator is connected to control means (not shown) for controlling the angle of the actuator according to the operating state of the internal combustion engine.
• the position of 04 changes.
• This arm 10 can maintain a constant distance between the central axis 03 of the roller shaft 7 and the central axis 04 of the drive shaft 9, and the one end 10a has a through-hole into which the roller shaft 7 is fitted. 10c is formed, and the other end portion 10b is formed with a through portion 10d in which a part into which the drive shaft 9 is inserted is opened.
• the roller shaft 7 is rotatably fitted in the through hole 10c of the one end portion 10a, and the drive shaft 9 is pivotally fitted to the through-hole 10d of the other end portion 10b and is not removed by the pin 16. As installed.
• the drive shaft 9 provided on the swing shaft 4 rotates at a predetermined angle around the central axis 02 of the swing shaft 4. Accordingly, the roller shaft 7 is interlocked via the arm 10.
• the arm 10 can move the roller shaft 7 in the guide portion 5b while keeping the distance between the central axis 03 of the roller shaft 7 and the central axis 04 of the drive shaft 9 constant.
• the relative distance between the central axis ⁇ 2 of the shaft 4 and the roller 8 can be varied.
• the rocker arm 6 swings on the rocker arm shaft 12. It is supported and arranged so as to be movable.
• rocker arm 6 is supported by the rocker arm shaft 12 so as to be swingable.
• the rocker arm 6 is not limited to this, and can be swingably supported by a spherical pivot, a hydraulic lash adjuster, or the like.
• the rocker arm 6 is formed with a valve pressing portion 6a that presses the upper surface of a shim 23 attached to an intake valve 11 (described later) at the tip portion, and at the intermediate portion of the rocker arm 6.
• the roller shaft 13 is rotatably provided.
• the roller shaft 13 is rotatably provided with a roller 14, and the outer peripheral surface of the roller 14 can roll on the cam surface 5 a of the swing cam 5.
• a spring 17 that biases the rocker arm 6 toward the swing cam 5 is fitted to the rocker arm shaft 12. As a result, the rocker arm 6 is biased to the swing cam 5 side by the spring 17, and the outer peripheral surface of the roller 14 is always in contact with the cam surface 5 a of the swing cam 5.
• an intake valve 11 pressed by the valve pressing portion 6a is disposed below the valve pressing portion 6a of the rocker arm 6 so as to be movable up and down.
• the intake valve 11 is provided with a collet 20 and an upper retainer 21 at the upper part, and a valve spring 22 is disposed below the upper retainer 21, and the biasing force of the valve spring 22 is used.
• the intake valve 11 is urged toward the rocker arm 6 side. Further, a shim 23 is attached to the upper end of the intake valve 11.
• the intake valve 11 can be moved up and down by interlocking and swinging the rocker arm 6 by swinging the swing cam 5, so that the central axis 02 of the swing shaft 4 and the roller 8
• the lift amount and the maximum lift timing of the intake valve 11 can be adjusted and varied via the rocker arm 6.
• variable valve mechanism 1 configured as described above.
• variable valve mechanism 1 of the internal combustion engine when the maximum lift amount is required will be described in detail with reference to FIGS.
• FIG. 1 shows an internal combustion engine when the maximum lift amount according to the first embodiment of the present invention is required.
• FIG. 2 is a longitudinal sectional view of a main part of the Seki variable valve mechanism 1 in a state in which the intake valve 11 is closed.
• FIG. 2 is a diagram of the internal combustion engine when the maximum lift amount according to the first embodiment is required.
• FIG. 2 is a longitudinal sectional view of a main part of the variable valve mechanism 1 in a state where an intake valve is opened.
• the roller shaft 7 is moved to the end of the guide portion 5b on the rotating cam 3 side, and the relative distance between the central shaft O2 of the swing shaft 4 and the roller 8 is changed. . That is, the swing shaft 4 is rotated by a predetermined angle by the actuator, and the drive shaft 9 is moved in the circumferential direction of the swing shaft 4. As a result, the roller shaft 7 is interlocked via the arm 10 and moved to the end of the guide portion 5b on the rotating cam 3 side, and the relative distance between the central axis 02 of the swing shaft 4 and the roller 8 changes. .
• the roller 14 is positioned at a position corresponding to the base circle portion 5c of the cam surface 5a of the swing cam 5, and in the closed state, the roller 14 and the base circle portion 5c Since a large contact force does not act between them, even if the width L1 of the base circle 5c is narrow, sufficient durability S can be ensured.
• the rocker arm 6 that is largely swung to the intake valve 11 side presses the upper surface of the shim 23 with a valve pressing portion 6a formed at the front end thereof, thereby greatly lowering the intake valve 11.
• the center shaft 02 of the swing shaft 4 Since the intake valve 11 can be pushed down greatly by greatly changing the relative distance from the roller 14 to the roller 14 that contacts the cam surface 5a of the swing cam 5, the intake valve 11 can be opened with the maximum lift amount. can do.
• variable valve mechanism 1 of the internal combustion engine when the minimum lift amount is required will be described in detail with reference to FIGS.
• FIG. 3 is a longitudinal sectional view of a main part in a state where the intake valve is closed, showing the variable valve mechanism of the internal combustion engine when the minimum lift amount according to the first embodiment of the present invention is required.
• FIG. 4 is a longitudinal sectional view of a main part of the internal combustion engine when the minimum lift amount is required according to the first embodiment in a state where the intake valve is opened.
• the roller shaft 7 is held from the end portion on the rotating cam 3 side as shown in FIG. 1 to the end portion on the swing shaft 4 side of the guide portion 5b. Move and change the relative distance between the central axis ⁇ 2 of the rocking shaft 4 and the roller 8.
• the swing shaft 4 is rotated within a predetermined angle range by the actuator, and the drive shaft 9 is moved in the circumferential direction of the swing shaft 4.
• the roller shaft 7 is interlocked via the arm 10 and moved from the state where the roller shaft 7 is held at the end portion of the rotating cam 3 to the end portion of the guide shaft 5b on the swing shaft 4 side.
• the relative distance between the central axis O 2 of the oscillating shaft 4 and the roller 8 is shortened.
• the swing cam 5 is rotated from the position shown in FIG. 1 to the position shown in FIG. 3 by the urging force of the spring 15.
• the rocker arm 6 swinging slightly toward the intake valve 11 side presses the upper surface of the shim 23 with a valve pressing portion 6a formed at the tip thereof to push down the intake valve 11 slightly.
• the center shaft of the swing shaft 4 is changed. Since the intake valve 11 can be pushed down by changing the relative distance from 02 to the roller 14 in contact with the cam surface 5a of the swing cam 5 to a small extent, in Embodiment 1, the minimum lift amount is used.
• the intake valve 11 can be opened.
• the base circular portion 5c is a force in which the width L1 is narrowly formed. Since a large load does not act on this portion, the strength can be secured. Since a large force acts on the lift portion 5d, the width L2 is widened to ensure strength.
• the swing cam 5 can reduce the weight of the swing cam 5 by reducing the width L1 of the base circular portion 5c. It is possible to reduce the weight of parts related to the swing cam 5 (spring 15 etc.) and to reduce the size of the device. It is possible to reduce the wear of the contact portion of the cam surface 5a.
• the base circular portion 5c is formed at a position separated from the central axis 02, it can contribute to a reduction in inertial force.
• variable valve mechanism 1 of the internal combustion engine configured as described above, the swing cam 5 contacts the rotary cam 3, and the driving force from the rotary cam is applied to the swing cam 5.
• Roller 8 is provided as a rotating cam contact part that transmits to the roller, and by making this roller 8 movable, the contact part variable mechanism that varies the relative distance between the roller 8 and the central axis 02 of the swing shaft 4 By changing the relative distance, the lift amount of each valve can be made variable, so that the structure can be simplified and the construction can be made inexpensively.
• the load from the rotating cam 3 is input to the roller 8, and the load is directly transmitted to the guide portion 5 a of the swing cam 5 from this roller 8 force.
• the load is transmitted to the intake valve 11 via Therefore, the arm 10 supporting the roller 8 does not receive a large load, and the arm 10 simply has a function of moving the roller 8 along the guide portion 5a. It is not necessary to increase the strength of the so much.
• FIGS. 6 to 8 are diagrams according to Embodiment 2 of the present invention, and FIG. 6 shows an intake valve that shows a variable valve mechanism of an internal combustion engine when the maximum lift amount is necessary. It is a principal part longitudinal cross-sectional view of the state which closed the valve.
• FIG. 7 is a longitudinal sectional view of a main part of the variable valve mechanism of the internal combustion engine when the minimum lift amount is required, with the intake valve closed.
• This embodiment 2 is configured such that the intake valve 11 is directly moved up and down by the swing cam 5 without opening and closing the rocker arm 6 that opens and closes the intake valve 11 of the first embodiment. It has been.
• the rocking cam 5 is formed in a curved ball shape and is fitted to the outer peripheral surface of the rocking shaft 4 so as to be centered on the central axis 02 of the rocking shaft 4. Swayable and supported
• the swing cam 5 has a cam surface 5a having a base circle portion 5c, a lift portion 5d, and a ramp portion 5e, and the contact surface of the base circle portion 5c.
• the width L1 of the lift It is formed narrower than the width L2 of the contact surface of the part 5d.
• a cam surface 5a is formed at the lower end portion of the swing cam 5 so as to be convexly curved toward the intake valve 11 and press the lifter 26 of the intake valve 11 to move up and down.
• a guide portion 5b on which the roller shaft 7 provided with the roller 8 is slid is formed on the upper side of the cam surface 5a.
• the roller shaft 7 is connected to one end 10a of an arm 10 connected to the drive shaft 9, and the roller 8 rotatably supported by the roller shaft 7 is brought into contact with the rotating cam 3. ing.
• the swing shaft 4 is provided with a spring (not shown) that biases the swing cam 5 toward the rotary cam 3.
• a spring (not shown) that biases the swing cam 5 toward the rotary cam 3.
• the swing cam 5 is biased toward the rotating cam 3 by the biasing force of the spring, the outer peripheral surface of the roller shaft 7 is always in contact with the guide portion 5b, and the outer peripheral surface of the roller 8 is always at the base of the rotating cam 3. Touching surface 3a or nose surface 3b.
• the state in which the roller shaft 7 is moved to the distal end side of the guide portion 5b and the relative distance between the central axis 02 of the swing shaft 4 and the roller 8 is varied is as follows: Since the intake valve 11 can be largely pushed down by the cam surface 5a of the swing cam 5, the maximum lift amount is achieved in the second embodiment.
• the roller shaft 7 is moved to the swing shaft 4 side of the guide portion 5b, and the relative distance between the central axis 02 of the swing shaft 4 and the roller 8 is varied.
• the intake valve 11 can be pushed down slightly by the cam surface 5a of the swinging force 5, the second embodiment Then, it becomes the minimum lift amount.
• the base circle portion 5c is formed with a narrow width L1, but since a large load does not act on this portion, the strength is increased. It can be secured. Since a large force acts on the lift portion 5d, the width L2 is widened to ensure strength.
• the swing cam 5 can reduce the weight of the swing cam 5 by reducing the width L1 of the base circular portion 5c. It is possible to reduce the weight of parts related to the swing cam 5 (spring 15 etc.), to reduce the size of the device, and to wear the contact portion of the cam surface 5a. Can be reduced.
• FIGS. 9 to 11 are longitudinal cross-sectional views of the main part in a state where the intake valve showing the valve operating mechanism of the internal combustion engine according to the third embodiment is closed.
• roller arm 6 is in contact with the cam surface 5a of the swing cam 5.
• a roller arm 6c that supports the roller 14 and interlocks with the swing of the swing cam 5
• a rocker arm body 6d that swings in conjunction with the roller arm 6c and moves the intake valve 11 up and down.
• roller arm 6c is biased toward the swing cam 5 by the leaf spring 28 so that the roller 14 and the cam surface 5a of the swing cam 5 are brought into contact with each other.
• the cam surface 5a has a base circular portion 5c as in the above-described embodiments.
• the lift portion 5d and the ramp portion 5e have a width L1 of the base circle portion 5c narrower than the width L2 of the lift portion 5d.
• roller arm 6c is movable to a predetermined position, and each valve is changed by changing the contact position between the roller 14 provided on the roller arm 6c and the cam surface 5a of the swing cam 5. It is possible to adjust the lift amount.
• the central axis 07 is parallel to the central axis 05 of the rocker arm shaft 12 and is eccentric with respect to the rocker arm shaft 12.
• the eccentric shaft 29 is fixed to the eccentric shaft 29, and the roller arm 6 c of the rocker arm 6 is locked to the eccentric shaft 29 by a leaf spring 28.
• This roller arm 6c is formed with an engaging portion 6e having a shape that engages with the outer peripheral surface of the eccentric shaft 29 at one end and is slidable on the outer peripheral surface of the eccentric shaft 29. At a position adjacent to 6e, there is formed a fitting portion 6f that is fitted so that the leaf spring 28 that integrally locks the roller arm 6c and the eccentric shaft 29 does not come off. Further, at the other end, a through hole 6 g is formed in which a roller shaft 13 on which a roller 14 sliding on the cam surface 5a of the swing cam 5 is supported is fitted, and below the through hole 6g. Is formed with a pressing portion 6h that presses the rocker arm body 6d toward the intake valve 11 when the roller arm 6c is interlocked and swings toward the intake valve 11 as the swing cam 5 swings.
• the rocker arm body 6d of the rocker arm 6 is disposed to be swingably supported by the rocker arm shaft 12, and is a valve that presses the upper surface of the shim 23 that is attached to the intake valve 11 at the tip.
• a pressing portion 6a is formed.
• a contact surface 6i that contacts a tip portion 28b of a leaf spring 28 described later is formed, and on the upper side of the contact surface 6i, a pressure formed on the roller arm 6c is formed.
• a guide portion 6j that is pressed by the portion 6h is formed.
• the leaf spring 28 is formed into a predetermined shape by bending a plate-like spring at a plurality of locations. Specifically, the leaf spring 28 is bent into a shape that fits into the fitting portion 6f of the roller arm 6c and a shape that fits into the eccentric shaft 29, and the roller arm 6c and the eccentric shaft 29 are integrated. A locking portion 28a to be locked is formed. Further, the tip 28b of the plate spring 28 on the roller arm 6c side extends to the roller 14 side and comes into contact with a contact surface 6i formed on the rocker arm body 6d.
• the leaf spring 28 is configured to bias the roller arm 6c and the rocker arm body 6d in a direction to expand when the roller arm 6c and the eccentric shaft 29 are integrally locked by the locking portion 28a. Is formed.
• a predetermined clearance A is provided between the pressing portion 6h of the roller arm 6c and the guide portion 6j of the rocker arm main body 6d.
• the roller arm 6c can be slid so that it can slide on the outer peripheral surface of the eccentric shaft 29. Since the roller arm 6c is integrally locked to the eccentric shaft 29 by the screw 28, when the swing cam 5 is swung, the roller arm 6c is biased by the leaf spring 28 via the roller 14 and the roller shaft 13. against the intake valve 11 side. Further, when the roller arm 6c is swung to the intake valve 11 side, the rocker arm body 6d is swung to the intake valve 11 side by pressing the guide portion 6j of the rocker arm body 6d by the pressing portion 6h of the roller arm 6c. Thus, the intake valve 11 can be opened and closed.
• roller arm 6c is urged toward the swing cam 5 by the leaf spring 28, and the outer peripheral surface of the roller 14 provided on the roller arm 6c is always in contact with the cam surface 5a of the swing cam 5. Yes.
• an actuator (not shown) for rotating the rocker arm shaft 12 in a predetermined angle range around the central axis 05 is connected to one end portion of the rocker arm shaft 12.
• the actuator is connected to control means (not shown) for controlling the angle of the actuator according to the operating state of the internal combustion engine.
• the eccentric shaft 29 provided on the rocker arm shaft 12 rotates at a predetermined angle around the central axis 05 of the rocker arm shaft 12. Is done.
• the roller arm 6c is interlocked. For example, the roller arm 6c moves from the position shown by the solid line in FIG. 9 to the predetermined position shown by the two-dot chain line in FIG. Is done.
• the roller arm 6c is moved to a predetermined position, the contact point between the cam surface 5a of the swing cam 5 and the roller 14 provided on the roller arm 6c changes, so that the rocker arm body 6d is swung. The amount of movement can be changed, and the lift amount of the intake valve 11 moved up and down by the rocker arm 6 can be adjusted.
• the roller arm 6c configured as described above can be freely moved to a predetermined position, and the position of contact between the roller 14 provided on the roller arm 6c and the cam surface 5a of the swing cam 5 can be changed.
• the valve mechanism 1 of the internal combustion engine that can adjust the lift amount of the Since the roller 6c is biased to the swing cam 5 side by the leaf spring 28, the rocker arm 6c is moved to a predetermined position, and the rocker arm 6c is moved even if the contact position between the roller 14 and the cam surface 5a changes. Since the 6 roller 14 and the cam surface 5a of the swing cam 5 are always in contact, it is possible to prevent adhesive wear.
• the base circle portion 5c is formed with a narrow width L1, but a large load does not act on this portion. Strength can be secured. Since a large force acts on the lift portion 5d, the width L2 is widened to ensure strength.
• the swing cam 5 can reduce the weight of the swing cam 5 by reducing the width L1 of the base circular portion 5c, so that the inertia force during swing is reduced. Therefore, it is possible to reduce the weight of the parts (spring 15 and the like) related to the swing cam 5.
• the base circle portion 5c is formed at a position separated from the central axis 02, it can contribute to a reduction in inertial force.
• FIGS. 12 and 13 are longitudinal cross-sectional views of the main part in a state in which the intake valve showing the valve mechanism of the internal combustion engine according to the fourth embodiment is closed.
• the fourth embodiment is a valve mechanism 1 for an internal combustion engine that can adjust the lift amount and the like of each valve by making the swing shaft 4 freely movable to a predetermined position.
• a roller 33 is disposed on the outer peripheral surface of the swing shaft 4, and the roller 33 is formed on the cylinder head body 19. Is in contact with a guide portion 19a that guides to a predetermined position.
• the swing shaft 4 can move in the range shown by the solid line in FIG. 12 to the two-dot chain line in FIG. As shown in FIG.
• This control cam 34 is provided in parallel to the camshaft 2. It is fixed to the outer periphery of the shaft 35. The outer peripheral portion of the control cam 34 is in contact with the swing cam 5 and is formed in a shape that can guide the swing shaft 4 to a predetermined position by rotationally driving the control cam 34 at a predetermined angle.
• the cam surface 5a of the swing cam 5 is formed with a base circle portion 5c, a lift portion 5d, and a ramp portion 5e.
• the width L1 of the base circle portion 5c is as follows.
• the lift portion 5d is narrower than the width L2.
• control shaft 35 is connected to an actuator (not shown) that drives the control shaft 35 to rotate within a predetermined angular range around the central axis 08 of the control shaft 35.
• actuator not shown
• Control means for controlling the angle of the actuator according to the operating state of the internal combustion engine is connected to the actuator.
• the rocker arm 6 that reciprocates by swinging within a predetermined range in conjunction with the swing cam 5 has the same configuration as that of the first embodiment, and has a valve pressing portion 6a and a roller shaft. 13 and a roller 14 are provided, and are supported by a rocker arm shaft 12 so as to be swingable.
• the rocker arm shaft 12 is provided with a torsion spring 17 as a spring member that always contacts the roller 14 and the cam surface 5a.
• control cam 34 when the control shaft 35 is rotated by a predetermined angle by the actuator, the control cam 34 is rotated by a predetermined angle around the central axis 08 of the control shaft 35.
• the roller 33 slides on the guide portion 19a of the cylinder head body 19 through the swing cam 5 by the control cam 34, for example, at the position indicated by the solid line in FIG. From FIG. 12, the oscillating shaft 4 is moved to a predetermined position as shown by a two-dot chain line in FIG.
• the base circle portion 5c is formed with a narrow width L1, but a large load does not act on this portion. Strength can be secured. Since a large force acts on the lift portion 5d, the width L2 is widened to ensure strength.
• the swing cam 5 can reduce the weight of the swing cam 5 by reducing the width L1 of the base circular portion 5c. Therefore, it is possible to reduce the weight of the parts (spring 15 and the like) related to the swing cam 5.
• the base circle portion 5c is formed at a position separated from the central axis 02, it can contribute to a reduction in inertial force.
• FIG. 14 and FIG. 15 are main part longitudinal sectional views showing a state in which the intake valve showing the valve mechanism of the internal combustion engine according to the fifth embodiment is closed.
• the rotating cam 3 is tapered, and the rotating cam 3 is moved in the direction of the central axis O1 of the camshaft 2, so that the outer peripheral portion of the rotating cam 3 and the swing cam 5 are
• This is a valve operating mechanism 1 for an internal combustion engine that can adjust the lift amount and the like of each valve by changing the contact position.
• the rotating cam 3 is fixed to the outer peripheral surface of the camshaft 2, and the outer peripheral portion of the rotating cam 3 is connected to the arc-shaped base surface 3a in plan view.
• Base surface 3a force It consists of protruding nose surface 3b.
• the base surface 3a and the nose surface 3b are formed in a taper shape in the central axis Ol direction (direction perpendicular to the paper surface) in FIG.
• An actuator (not shown) is connected to one end of the camshaft 2 to move the camshaft 2 within a predetermined range in the direction of the central axis 01, and this actuator is connected to the internal combustion engine.
• Control means (not shown) for controlling the movement of the actuator according to the operating state is connected.
• the outer peripheral surface of the roller 8 provided on the rocking cam 5 rocked by the rotating cam 3 is slidable on the base surface 3a and the base surface 3b of the rotating cam 3 formed in a tapered shape. It is an outer peripheral surface.
• a base circle portion 5c, a lift portion 5d, and a ramp portion 5e are formed on the cam surface 5a of the swing cam 5, and the width L1 of the base circle portion 5c is formed. However, it is formed narrower than the width L2 of the lift part 5d.
• the rocker arm 6 that reciprocates by swinging within a predetermined range in conjunction with the swing cam 5 has the same configuration as that of the fourth embodiment, includes a valve pressing portion 6a, and a roller shaft. 13 and a roller 14 are provided, and are supported by a rocker arm shaft 12 so as to be swingable.
• the rocker arm shaft 12 is provided with a torsion spring 17 that always contacts the roller 14 and the cam surface 5a.
• the rotating cam 3 is moved in the predetermined direction in the direction of the central axis Ol of the camshaft 2.
• the rotating cam 3 is formed in a taper shape, so that the rotating cam 3 passes, for example, the roller shaft 7 and the roller 8 and is, for example, a solid line in FIG.
• the swing cam 5 is moved from the position shown in FIG. 14 to a predetermined position shown by a two-dot chain line in FIG.
• the swing cam 5 When the swing cam 5 is moved to a predetermined position, the position of the cam surface 5a of the swing cam 5 changes, so that the swing amount of the rocker arm 6 can be changed. It is possible to adjust the lift amount of the intake valve 11 that is moved up and down.
• the rotary cam 3 configured as described above is tapered, and the rotary cam 3 is moved in the direction of the central axis O1 of the camshaft 2 so that the outer peripheral portion of the rotary cam 3 and the swing cam 5 are
• the rocker arm 6 is biased to the swing cam 5 side by the torsion spring 17, so that the swing shaft Even if 4 is moved to the specified position and the position of the cam surface 5a of the swing cam 5 changes, the roller 14 of the rocker arm 6 and the cam surface 5a of the swing cam 5 are always in contact with each other. It can be prevented.
• the base circular portion 5c has a width similar to that of each of the above embodiments. Although LI is narrowly formed, a large load does not act on this part, so strength can be secured. Since a large force acts on the lift portion 5d, the width L2 is widened to ensure strength.
• the swing cam 5 can reduce the weight of the swing cam 5 by reducing the width L1 of the base circular portion 5c. Therefore, it is possible to reduce the weight of the parts (spring 15 and the like) related to the swing cam 5.
• the base circle portion 5c is formed at a position separated from the central axis 02, and therefore can contribute to a reduction in inertial force.
• the present invention is applied to the swing cam 5 used in the variable valve mechanism 1.
• the present invention is not limited to this. It is possible to apply this invention.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Valve Device For Special Equipments (AREA)
• Valve-Gear Or Valve Arrangements (AREA)

Priority Applications (6)

Applications Claiming Priority (1)

Related Child Applications (1)

Publications (1)

Family

ID=35967220

Family Applications (1)

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Families Citing this family (2)

Citations (2)

• 2004
  • 2004-08-25 WO PCT/JP2004/012193 patent/WO2006021997A1/ja active Application Filing
  • 2004-08-25 AT AT04772154T patent/ATE507371T1/de not_active IP Right Cessation
  • 2004-08-25 DE DE602004032479T patent/DE602004032479D1/de active Active
  • 2004-08-25 EP EP04772154A patent/EP1783332B1/de not_active Not-in-force
  • 2004-08-25 CA CA002541726A patent/CA2541726A1/en not_active Abandoned

Patent Citations (2)

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