WO2010137159A1 - 内燃機関の可変動弁装置 - Google Patents
内燃機関の可変動弁装置 Download PDFInfo
- Publication number
- WO2010137159A1 WO2010137159A1 PCT/JP2009/059835 JP2009059835W WO2010137159A1 WO 2010137159 A1 WO2010137159 A1 WO 2010137159A1 JP 2009059835 W JP2009059835 W JP 2009059835W WO 2010137159 A1 WO2010137159 A1 WO 2010137159A1
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- WO
- WIPO (PCT)
- Prior art keywords
- actuator
- combustion engine
- internal combustion
- camshaft
- variable valve
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
- F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/185—Overhead end-pivot rocking arms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
- F01L2001/0537—Double overhead camshafts [DOHC]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
- F01L2013/0052—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams provided on an axially slidable sleeve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- 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
- F01L2810/00—Arrangements solving specific problems in relation with valve gears
- F01L2810/02—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/03—Auxiliary actuators
- F01L2820/031—Electromagnets
Definitions
- This invention relates to a variable valve operating apparatus for an internal combustion engine.
- Patent Document 1 a cam carrier provided with two types of cams is provided for each cylinder, and the cam carrier is moved in the axial direction with respect to a cam main shaft that is rotationally driven.
- a valve mechanism for an internal combustion engine that switches a drive cam is disclosed. More specifically, in this conventional valve operating mechanism, guide grooves formed in a spiral shape are provided at both ends of the outer peripheral surface of each cam carrier.
- an electric actuator that drives a drive pin inserted into and removed from the guide groove is provided for each guide groove.
- the cam carrier can be moved in the axial direction by inserting the drive pin into the guide groove, whereby the valve drive cam of each cylinder is switched and the valve is switched.
- the lift amount can be changed.
- the electric actuator is arranged outside the cylinder head.
- an actuator for switching the valve opening characteristic is provided outside the internal combustion engine as in the technique described in Patent Document 1 described above. If it is provided, it becomes difficult to efficiently cool the actuator. On the other hand, it is desirable that the location of the actuator is set so that a large stress does not act on the actuator when the actuator protrudes toward the guide rail.
- the present invention has been made in order to solve the above-described problems, and provides a variable valve operating apparatus for an internal combustion engine capable of satisfactorily improving an actuator arrangement environment from the viewpoint of improving cooling performance and reducing stress.
- the purpose is to do.
- the internal combustion engine is capable of changing the valve opening characteristics of the first valve and the second valve in accordance with the relative displacement between the projection and the cylindrical portion that occurs when the projection and the guide rail are engaged.
- a variable valve device At least a part of the actuator is attached to the first camshaft when viewed from the axial direction of the first and second camshafts in a state in which the protrusion is not projected toward the guide rail.
- the larger one of the circular diameter of the cylindrical portion and the base circular diameter of the first cam, the circular diameter of the cylindrical portion attached to the second camshaft, and the base circular diameter of the second cam It is characterized by being arranged so as to be within an oval region that is virtually obtained by connecting one of the larger circles.
- the second invention is the first invention, wherein
- the variable valve operating device is: It is disposed between at least one of the first cam and the first valve and between the second cam and the second valve, and at least one of the first valve and the second valve is opened.
- a variable mechanism that changes the valve characteristics;
- a displacement member that switches the operating state of the variable mechanism by moving within a predetermined reciprocating range;
- the protrusion is fixed to the displacement member.
- the third invention is the first or second invention, wherein The protrusion is disposed so as to be within the oval region when viewed from the axial direction of the first and second camshafts in a state where the protrusion is not protruded toward the guide rail. It is characterized by.
- the actuator includes a first mover disposed at a position capable of protruding toward the cylindrical portion attached to the first camshaft in the oval region, and the oval region in the oval region. And a second mover disposed at a position capable of protruding toward the cylindrical portion attached to the second camshaft.
- the fifth invention is the fourth invention, wherein The first movable element and the second movable element are arranged so as to be opposed to each other and at positions where they can project toward the corresponding cylindrical portions.
- the sixth invention is the fourth or fifth invention, wherein
- the actuator is an electromagnetic solenoid actuator, and includes a single electromagnetic coil that drives the first mover and the second mover.
- the seventh invention is the third invention, wherein
- the actuator includes a first mover disposed at a position capable of protruding toward the cylindrical portion attached to the first camshaft in the oval region, and the oval region in the oval region.
- a second mover disposed at a position capable of protruding toward the cylindrical portion attached to the second camshaft,
- the protrusions are between the guide rail attached to the first camshaft and the first mover, and between the guide rail attached to the second camshaft and the second mover. It is characterized by interposing in each.
- the eighth invention is the seventh invention, wherein
- the actuator is an electromagnetic solenoid actuator, and includes a single electromagnetic coil that drives the first mover and the second mover.
- a camshaft support member having a lower bearing portion for supporting the first and second camshafts from the cylinder head side of the internal combustion engine;
- the actuator is attached to the lower bearing portion.
- the tenth invention is the ninth invention, wherein The cylindrical portion is disposed close to the lower bearing portion, The actuator is attached to the lower bearing portion so as to be along at least one of an upper bearing portion that supports the first and second camshafts from the side opposite to the lower bearing portion and the lower bearing portion. It is characterized by.
- An eleventh aspect of the invention is any one of the first to third aspects of the invention, A camshaft support member having a lower bearing portion for supporting the first and second camshafts from the cylinder head side of the internal combustion engine; A head cover that covers the camshaft support member from the opposite side of the cylinder head; and The actuator is arranged on the head cover side with respect to the lower bearing portion.
- the twelfth invention is the eleventh invention, in which An oil injection member that is installed inside the head cover and injects oil into the head cover; The actuator is arranged in an oil injection direction by the oil injection member.
- the thirteenth invention is the eleventh or twelfth invention, A fresh air passage that is installed inside the head cover and circulates fresh air inside the head cover for the treatment of blow-by gas;
- the actuator is arranged in the vicinity of the opening of the fresh air passage inside the head cover.
- the actuator arranged to face the cylindrical portion is arranged so as to be accommodated in the oval region located between the first and second camshafts.
- the actuator can be arranged sufficiently close to the guide rail.
- the actuator in the variable valve operating apparatus for an internal combustion engine having the configuration in which the protrusion is fixed to the displacement member that switches the operating state of the variable mechanism, the actuator can be improved in terms of improving the cooling performance and reducing the stress.
- the arrangement environment can be improved satisfactorily.
- the protrusion is disposed so as to be within the elliptical region in a state where the protrusion does not protrude toward the guide rail.
- the fourth invention when the first and second movers of the actuator are disposed in the oval region, when these movers project the protrusions toward the guide rail, The distance from the movable element to the contact portion of the protrusion with the guide rail can be effectively shortened. As a result, it is possible to satisfactorily reduce the stress acting on the actuator by shortening the distance.
- the first movable element and the second movable element are arranged so as to face each other, the first movable element and the second movable element are driven at the same time. In this case, the driving reaction forces of the two are canceled out. Thereby, the vibration which arises in an actuator at the time of a drive can be suppressed effectively.
- both the first and second movers can be driven simultaneously by instructing a predetermined exciting current to a single electromagnetic coil. Therefore, the number of actuators can be reduced and the size can be reduced.
- the distance from the mover to the contact portion of the protrusion with the guide rail is effectively shortened. be able to.
- the stress acting on the actuator can be more effectively reduced by sufficiently shortening the distance.
- both the first and second movers can be driven simultaneously by instructing a predetermined exciting current to a single electromagnetic coil. Therefore, the number of actuators can be reduced and the size can be reduced.
- the actuator can be reduced in cost and space without the need for providing a new fixing place. Can be mounted inside.
- positioning between the guide rails provided on the first and second camshafts and the actuator can be facilitated.
- the actuator can be efficiently cooled easily by the oil or fresh air supplied to the inside of the head cover (fresh air introduced for blow-by gas processing).
- the oil injected from the oil injection member hits the actuator, so that the actuator can be efficiently cooled.
- the fresh air supplied from the fresh air passage directly hits the actuator, whereby the actuator can be efficiently cooled.
- FIG. 1 is a diagram schematically showing an overall configuration of an intake variable valve operating apparatus for an internal combustion engine according to a first embodiment of the present invention. It is the figure which looked down at the variable mechanism shown in FIG. 1 from the base end part side of the intake valve. It is the figure which looked at the 1st rocker arm from the axial direction (direction of the arrow A in FIG. 2) of a rocker shaft. It is the figure which looked at the 2nd rocker arm from the axial direction (direction of arrow A) of a rocker shaft similarly to FIG. It is a figure for demonstrating the detailed structure of the switching mechanism shown in FIG. It is the figure which looked at the switching mechanism from the axial direction (direction of arrow B in FIG. 5) of the camshaft.
- FIG. 1 It is a figure which shows the control state at the time of valve operating state (at the time of normal lift operation
- FIG. 1 is a diagram schematically showing an overall configuration of an intake variable valve operating apparatus 10 for an internal combustion engine 1 according to Embodiment 1 of the present invention.
- the internal combustion engine 1 is an in-line four-cylinder engine having four cylinders (# 1 to # 4).
- Each cylinder of the internal combustion engine 1 is provided with two intake valves 18 and two exhaust valves (not shown).
- the intake variable valve operating apparatus 10 for driving the intake valve 18 will be described as an example, and the exhaust variable valve operating apparatus 70 (see FIG. 11) is basically the intake variable valve operating apparatus. Since the configuration is the same as that of FIG. 10, detailed description thereof is omitted here.
- the intake variable valve operating apparatus 10 of this embodiment includes a camshaft 12.
- the camshaft 12 is connected to a crankshaft (not shown) by a timing chain or a timing belt, and is configured to rotate at a half speed of the crankshaft.
- the camshaft 12 is formed with one main cam 14 and two sub cams 16 per cylinder.
- the main cam 14 is disposed between the two sub cams 16.
- the main cam 14 has an arcuate base circle portion 14a (see FIG. 3) coaxial with the camshaft 12, and a nose portion 14b (see FIG. 3) formed so as to bulge a part of the base circle radially outward. 3).
- the sub cam 16 is comprised as a cam (zero lift cam) which has only a base circle part (refer FIG. 4).
- a variable mechanism 20 is interposed between the cams 14 and 16 of each cylinder and an intake valve (hereinafter sometimes simply referred to as “valve”) 18. That is, the acting force of the cams 14 and 16 is transmitted to the two valves 18 via the variable mechanism 20.
- the valve 18 is opened and closed using the acting force of the cams 14 and 16 and the urging force of the valve spring 22.
- the variable mechanism 20 is a mechanism that changes the valve opening characteristic of the valve 18 by switching between a state in which the acting force of the main cam 14 is transmitted to the valve 18 and a state in which the acting force of the sub cam 16 is transmitted to the valve 18. .
- the state where the acting force of the sub cam 16 is transmitted to the valve 18 means a state where the valve 18 does not open and close (valve stop state).
- the intake variable valve operating apparatus 10 of the present embodiment is provided with a switching mechanism 24 for driving each variable mechanism 20 and switching the operation state of the valve 18 for each cylinder.
- the switching mechanism 24 is driven according to a drive signal from an ECU (Electronic Control Unit) 26.
- the ECU 26 is an electronic control unit for controlling the operating state of the internal combustion engine 1 and controls the switching mechanism 24 based on an output signal from the crank position sensor 28 or the like.
- the crank position sensor 28 is a sensor that detects the rotational speed of the output shaft (crankshaft) of the internal combustion engine 1.
- FIG. 2 is a view of the variable mechanism 20 shown in FIG. 1 as viewed from the base end side of the intake valve 18.
- the variable mechanism 20 includes a rocker shaft 30 disposed in parallel with the camshaft 12.
- a first rocker arm 32 and a pair of second rocker arms 34 ⁇ / b> R and 34 ⁇ / b> L are rotatably attached to the rocker shaft 30.
- the first rocker arm 32 is disposed between the two second rocker arms 34R and 34L.
- the left and right second rocker arms 34R and 34L may be simply referred to as the second rocker arm 34.
- FIG. 3 is a view of the first rocker arm 32 as viewed from the axial direction of the rocker shaft 30 (the direction of arrow A in FIG. 2).
- FIG. 4 shows the second rocker arm 34 as in FIG. It is the figure seen from 30 axial directions (direction of arrow A).
- a first roller 36 is rotatably attached to the end of the first rocker arm 32 on the opposite side of the rocker shaft 30 at a position where it can contact the main cam 14.
- the first rocker arm 32 is urged by a coil spring 38 attached to the rocker shaft 30 so that the first roller 36 is always in contact with the main cam 14.
- the first rocker arm 32 configured as described above swings about the rocker shaft 30 as a fulcrum by the cooperation of the acting force of the main cam 14 and the biasing force of the coil spring 38.
- the base end portion of the valve 18 (specifically, the base end portion of the valve stem) is in contact with the end portion of the second rocker arm 34 opposite to the rocker shaft 30.
- a second roller 40 is rotatably attached to the central portion of the second rocker arm 34.
- the rocker shaft 30 is supported by the cylinder head 74 (see FIG. 11) via the lash adjuster 42. For this reason, the second rocker arm 34 is biased toward the sub cam 16 by receiving a pushing force from the lash adjuster 42.
- the position of the second roller 40 relative to the first roller 36 is such that the first roller 36 contacts the base circle portion 14a of the main cam 14 (see FIG. 3) and the second roller 40 is the base of the sub cam 16.
- the axis of the second roller 40 and the axis of the first roller 36 are determined so as to be on the same straight line L as shown in FIG. ing.
- the switching mechanism 24 is a mechanism for switching connection / disconnection between the first rocker arm 32 and the second rocker arm 34, and thereby, the operating force of the main cam 14 is transmitted to the second rocker arm 34. Then, the operation state of the valve 18 can be switched between the valve operation state and the valve stop state by switching the state where the acting force is not transmitted to the second rocker arm 34.
- FIG. 5 is a diagram for explaining a detailed configuration of the switching mechanism 24 shown in FIG.
- the variable mechanism 20 is represented using a cross section cut at the axial center position of the rollers 36 and 40.
- the mounting position of the camshaft 12 relative to the mounting position of the variable mechanism 20 is shown in a state different from the actual mounting position except for the axial position of the camshaft 12.
- a first pin hole 46 is formed in the first support shaft 44 of the first roller so as to penetrate in the axial direction.
- One rocker arm 32 is open on both side surfaces.
- a cylindrical first switching pin 48 is slidably inserted into the first pin hole 46.
- the outer diameter of the first switching pin 48 is substantially equal to the inner diameter of the first pin hole 46, and the axial length of the first switching pin 48 is substantially equal to the length of the first pin hole 46.
- the end opposite to the first rocker arm 32 is closed inside the second support shaft 50L of the second roller 40 on the second rocker arm 34L side, and the end on the first rocker arm 32 side is closed.
- a second pin hole 52L is formed.
- a second pin hole 52R is formed in the second support shaft 50R of the second roller 40 on the second rocker arm 34R side so as to penetrate in the axial direction, and both ends of the second pin hole 52R. Is open on both side surfaces of the second rocker arm 34R.
- the inner diameters of the second pin holes 52R and 52L are equal to the inner diameter of the first pin hole 46.
- a cylindrical second switching pin 54L is slidably inserted into the second pin hole 52L.
- a return spring 56 that urges the second switching pin 54L toward the first rocker arm 32 (hereinafter referred to as “the advancement direction of the switching pin”) is disposed inside the second pin hole 52L. Yes.
- the outer diameter of the second switching pin 54L is substantially equal to the inner diameter of the second pin hole 52L.
- the length in the axial direction of the second switching pin 54L is shorter than the second pin hole 52L, and the second switching pin 54L is pushed into the second pin hole 52L and the second switching pin 54L is pushed in the second switching hole 54L.
- the tip of the pin 54L is adjusted so as to slightly protrude from the side surface of the second rocker arm 34L. Further, it is assumed that the return spring 56 is configured to constantly bias the second switching pin 54L toward the first rocker arm 32 in the mounted state.
- a cylindrical second switching pin 54R is slidably inserted into the second pin hole 52R.
- the outer diameter of the second switching pin 54R is substantially equal to the inner diameter of the second pin hole 52R, and the axial length of the second switching pin 54R is substantially equal to the length of the second pin hole 52R.
- the relative positions of the three pin holes 46, 52L, and 52R described above are such that the first roller 36 is in contact with the base circle portion 14a of the main cam 14 (see FIG. 3) and the second roller 40 is in contact with the sub cam 16. It is determined so that the axial centers of the three pin holes 46, 52L, and 52R are located on the same straight line when contacting the base circle (see FIG. 4).
- FIG. 6 is a view of the switching mechanism 24 as seen from the axial direction of the camshaft 12 (the direction of arrow B in FIG. 5).
- the switching mechanism 24 uses the rotational power of the cams 14 and 16 to displace a slide pin 58 for displacing the switching pins 48, 54L and 54R toward the second rocker arm 34L (in the retracting direction of the switching pin).
- the slide pin 58 includes a cylindrical portion 58 a having an end surface that comes into contact with the end surface of the second switching pin 54 ⁇ / b> R.
- the cylindrical portion 58a is supported by a support member 60 fixed to the cylinder head 74 (see FIG. 11) so as to be movable forward and backward in the axial direction and rotatable in the circumferential direction.
- a rod-like arm portion 58b is provided at the end portion of the cylindrical portion 58a opposite to the second switching pin 54R so as to protrude outward in the radial direction of the cylindrical portion 58a. That is, the arm portion 58b is configured to be rotatable about the axis of the cylindrical portion 58a. As shown in FIG. 6, the distal end portion of the arm portion 58 b is configured to extend to a position facing the outer peripheral surface of the camshaft 12. Further, a protrusion 58c is provided at the tip of the arm 58b so as to protrude toward the outer peripheral surface of the camshaft 12.
- a cylindrical portion 62 having an outer diameter larger than that of the camshaft 12 is formed on the outer peripheral surface of the camshaft 12 facing the protruding portion 58c.
- a spiral guide rail 64 extending in the circumferential direction is formed on the outer peripheral surface of the cylindrical portion 62.
- the guide rail 64 is formed as a spiral groove.
- the switching mechanism 24 includes an electromagnetic solenoid actuator 66 for engaging (inserting) the protrusion 58 c with the guide rail 64.
- the detailed configuration of the actuator 66 will be described later with reference to FIGS.
- the actuator 66 has a place where the movable element 66a can press the pressing surface 58d (the surface opposite to the surface on which the protruding portion 58c is provided) 58d of the arm portion 58b of the slide pin 58 toward the guide rail 64. Is arranged. In other words, the pressing surface 58d is provided in a shape and a position where the protrusion 58c can be pressed toward the guide rail 64 by the movable element 66a.
- the arm portion 58b of the slide pin 58 is set to be rotatable around the axis of the columnar portion 58a within a range constrained by the cylindrical portion 62 and the stopper 68 on the camshaft 12 side.
- the mover 66a driven by the actuator 66 has the pressing surface 58d of the arm portion 58b.
- the positional relationship of each component is set so that it can be surely contacted.
- the direction of the spiral in the guide rail 64 of the camshaft 12 is such that when the camshaft 12 rotates in the predetermined rotational direction shown in FIG.
- the switching pins 48, 54L, 54R are set so as to be displaced in a direction approaching the rocker arms 32, 34 against the biasing force.
- the second switching pin 54L is inserted into both the second pin hole 52L and the first pin hole 46, and the first switching pin 48 is in the first pin hole 46.
- the position of the slide pin 58 when inserted into both the second pin hole 52R and the second pin hole 52R is referred to as “displacement end Pmax1”.
- the slide pin 58 is positioned at the displacement end Pmax1, the first rocker arm 32 and the second rocker arms 34R and 34L are all connected.
- the position of the base end 64a of the guide rail 64 in the axial direction of the camshaft 12 is set to coincide with the position of the protrusion 58c when the slide pin 58 is positioned at the displacement end Pmax1.
- the position of the terminal end 64b of the guide rail 64 in the axial direction of the camshaft 12 is set to coincide with the position of the protrusion 58c when the slide pin 58 is positioned at the displacement end Pmax2. That is, in the present embodiment, the slide pin 58 is configured to be displaceable between the displacement ends Pmax1 and Pmax2 within the range in which the protrusion 58c is guided by the guide rail 64.
- the guide rail 64 includes a guide rail 64 as a predetermined section on the terminal end 64 b side after the slide pin 58 reaches the displacement end Pmax ⁇ b> 2 as the camshaft 12 rotates. Is provided with a shallow bottom portion 64c that gradually becomes shallower. In addition, the depth of parts other than the shallow bottom part 64c in the guide rail 64 is constant.
- the arm portion 58b of the present embodiment is provided with a notch portion 58e formed in a concave shape by notching a part of the pressing surface 58d.
- the pressing surface 58d is provided so that the state in contact with the movable element 66a is maintained while the slide pin 58 is displaced from the displacement end Pmax1 to Pmax2.
- the notch 58e is engaged with the movable element 66a when the projection 58c is taken out to the surface of the cylindrical portion 62 by the action of the shallow bottom portion 64c in a state where the slide pin 58 is located at the displacement end Pmax2. It is provided in the part which can be combined.
- the notch 58e can restrict the rotation of the arm 58b in the direction in which the protrusion 58c is inserted into the guide rail 64, and can restrict the slide pin 58 from moving in the advance direction of the switching pin. In this manner, it is formed so as to be engaged with the mover 66a. More specifically, the notch portion 58e is provided with a guide surface 58f that guides the slide pin 58 away from the cylindrical portion 62 as the movable element 66a enters the notch portion 58e.
- FIG. 7 is a diagram illustrating a control state when the valve is operating (during a normal lift operation).
- the drive of the actuator (solenoid) 66 is turned OFF, so that the slide pin 58 is separated from the camshaft 12 and the return spring 56 Under the urging force, it is located at the displacement end Pmax1.
- the first rocker arm 32 and the two second rocker arms 34 are connected via switching pins 48 and 54L.
- the acting force of the main cam 14 is transmitted from the first rocker arm 32 to both valves 18 via the left and right second rocker arms 34R and 34L. Therefore, the normal lift operation of the valve 18 is performed according to the profile of the main cam 14.
- FIG. 8 is a diagram illustrating a control state at the start of the valve stop operation.
- the valve stop operation is performed, for example, when a request for executing a predetermined valve stop operation such as a fuel cut request of the internal combustion engine 1 is detected by the ECU 26.
- a valve stop operation is an operation of displacing the switching pins 48, 54L, 54R in the retracting direction by the slide pin 58 using the rotational force of the camshaft 12, and therefore, the switching pins 48, 54L, 54R. Need to be performed when the shaft centers of the first rocker arm 32 are positioned on the same straight line, that is, when the first rocker arm 32 is not swinging.
- the guide rail 64 is set so that the displacement section of the slide pin 58 in the withdrawal direction of the switching pin is within the base circle section. For this reason, when the ECU 26 detects a request to execute a predetermined valve stop operation, the actuator 66 is driven in order from the cylinder in which the base circle section first arrives. 58c is inserted into the guide rail 64, and the valve stop operation of each cylinder starts in order. Then, the protrusion 58c inserted into the guide rail 64 is guided by the guide rail 64, and thus, using the rotational force of the camshaft 12, as shown in FIG. 8 (A), toward the displacement end Pmax2 side. The slide operation of the slide pin 58 is started.
- FIG. 9 is a diagram illustrating a control state when the slide operation is completed.
- the slide pin 58 moves toward the displacement end Pmax2 in a state where the urging force of the return spring 56 is received by the protrusion 58c coming into contact with the side surface of the guide rail 64.
- FIG. 9A shows the timing when the slide pin 58 reaches the displacement end Pmax2 and the slide operation at the time of the valve stop request is completed, that is, the first switching pin 48 and the second switching pin 54L are respectively in the first pin hole 46.
- the timing when the connection between the first rocker arm 32 and the second rocker arms 34R and 34L is released by being within the second pin hole 52L is shown.
- FIG. 9B the position of the protrusion 58c in the guide rail 64 has not yet reached the shallow bottom 64c.
- FIG. 10 is a diagram illustrating a control state during a holding operation in which the slide pin 58 is held by the mover 66a.
- valve return operation for returning from the valve stop state to the valve operation state is performed, for example, when a request for executing a predetermined valve return operation such as a return request from a fuel cut is detected by the ECU 26.
- a valve return operation is earlier by a predetermined time required for the operation of the actuator 66 than the start timing of the ECU 26 at a predetermined timing (the base circle section where the switching pin 48 and the like can move).
- the timing is started by turning off the power to the actuator 66 at the timing.
- the energization of the actuator 66 is turned off, the engagement between the notch 58e of the slide pin 58 and the mover 66a is released.
- the force to hold the first switching pin 48 and the second switching pin 54L against the urging force of the return spring 56 disappears in the first pin hole 46 and the second pin hole 52L, respectively.
- the slide pin 58 can be moved in the advance direction of the switching pin.
- the first rocker arm 32 and the two second rocker arms 34 can be quickly switched from the unconnected state to the connected state and the valve stop operation can be started during one base circle section.
- the slide pin 58 can be returned to the original position (Pmax1). Thereby, the operation state of the valve 18 can be quickly returned to the valve operation state.
- the return spring is obtained by engaging the mover 66a with the notch 58e after the slide pin 58 reaches the displacement end Pmax2 where the slide operation of the slide pin 58 is completed.
- the function of holding the slide pin 58 so as not to be displaced from the displacement end Pmax2 toward the displacement end Pmax1 by the urging force 56 is movable from the side surface of the guide rail 64 that engages with the protrusion 58c. It can be transferred to the child 66a.
- the protrusion 58c is set to be separated from the camshaft 12 as described above.
- the holding of the slide pin 58 is changed to the movable element 66a that is stationary in the axial direction, so that friction and wear caused by sliding with the rotating camshaft 12 are generated. It can be avoided. More specifically, the elimination of the friction can improve the fuel efficiency of the internal combustion engine 1 and the wear of the slide pin 58 is eliminated, so that the control position of the switching pin 48 and the like is stabilized, so that the valve 18 It is possible to ensure good switchability of the operation state.
- the mover 66a of the actuator 66 provided for performing the insertion of the projection 58c, the switching pin 48, and the like are moved.
- the holding function is realized with the notch 58e provided on the slide pin 58 provided. For this reason, it is possible to obtain the intake variable valve operating apparatus 10 that can satisfactorily switch the operation state of the valve 18 using a simplified configuration without increasing the number of parts.
- FIG. 11 is a perspective view for explaining the arrangement of the electromagnetic solenoid actuator 66 shown in FIG. More specifically, in FIG. 11, the intake variable valve operating apparatus 10 is located on the left side, and the exhaust variable valve operating apparatus 70 is located on the right side. Further, the cut surface in FIG. 11 is that of the cylinder head 74 and its mounting member cut at the center of the # 4 cylinder. In FIG.
- FIG. 12 is a cross-sectional view of the electromagnetic solenoid actuator 66 viewed from the axial direction of the camshafts 12 and 72. More specifically, FIG. 12 is a view of a cross section in which the mounting member of the cylinder head 74 is cut at the center of the actuator 66 as viewed from the # 4 cylinder side.
- the components of the variable valve gears 10 and 70 such as the main cam 14 and the sub cam 16 are shown on the intake side so that their belongings can be understood. Symbol “IN”, symbol “EX” indicating the exhaust side, and cylinder number “# ⁇ ” are appropriately added to the end of the reference symbol of each component.
- the actuator 66 is disposed so as to be sandwiched between the intake camshaft 12 and the exhaust camshaft 72 in the internal combustion engine 1 (cylinder head 74). More specifically, the actuator 66 is arranged so that most of the actuator 66 falls within a region surrounded by a one-dot chain line shown in FIG. The region surrounded by the alternate long and short dash line is an oval region virtually obtained by connecting the base circle of the intake-side main cam 14IN and the base circle of the exhaust-side main cam 14EX. In FIG. 11, the actuators 66 other than the # 3 cylinder are not shown, but the actuators 66 of each cylinder are disposed so as to face each cylindrical portion 62 (each guide rail 64).
- the actuator 66 is disposed so as to be within the above-mentioned region when viewed from the axial direction of the camshafts 12 and 72, and in the axial direction of the camshafts 12 and 72, the respective camshafts 12 and 72 are arranged. It is arranged within the range of length.
- the actuator 66 includes an actuator body 66b in which an electromagnetic solenoid is built.
- the actuator body 66b includes two movable elements 66aIN and 66aEX. These movers 66aIN and 66aEX are configured to face each other and protrude toward the guide rails 64IN and 64EX.
- the actuator 66 includes a fixed portion 66c configured integrally with the actuator body 66b.
- the actuator 66 is disposed so that the entire actuator body 66b can be accommodated in the region as shown in FIG.
- the two movable elements 66aIN and 66aEX are directed from the center in the region (that is, the intermediate position between the intake camshaft 12 and the exhaust camshaft 72) to the guide rails 64IN and 64EX located at both ends of the region. It is arranged at a position where it can protrude.
- the protrusions 58cIN and 58cEX are also positions where they can come into contact with the movable elements 66aIN and 66aEX via the slide pins 58IN and 58EX in the above-described region, and are engaged with and disengaged from the guide rails 64IN and 64EX. Arranged at any position. In other words, the protrusions 58cIN and 58cEX are arranged so as to be interposed between the movable elements 66aIN and 66aEX and the guide rails 64IN and 64EX in the region.
- the state shown in FIG. 12 shows a state in which the protrusions 58cIN and 58cEX are separated from the guide rails 64IN and 64EX by inserting the drive shafts 66aIN and 66aEX into the notches 58eIN and 58eEX.
- the protrusions 58cIN and 58cEX are arranged so as to be within the above-described region even when they are separated from the guide rails 64IN and 64EX.
- a cam carrier 76 having a lower bearing portion 76a that supports the intake camshaft 12 and the exhaust camshaft 72 is assembled.
- the lower bearing portion 76a is disposed so as to bridge the intake side and the exhaust side between the cylinders.
- a cam cap 78 that functions as an upper bearing portion that supports the camshafts 12 and 72 from the opposite side of the lower bearing portion 76a is disposed on the lower bearing portion 76a.
- the actuator 66 is attached to the cam carrier 76 using a lower bearing portion 76 a for supporting the camshafts 12 and 72.
- the fixed portion 66 c of the actuator 66 is placed on the cam cap 78 so as to match the fastening portion at the center of the cam cap 78, and then the cam cap 78 is interposed.
- the actuator 66 is fixed to the lower bearing portion 76a of the cam carrier 76 via the cam cap 78 by fastening the fixing portion 66c to the lower bearing portion 76a with the fastening bolt 82.
- the actuator 66 is attached to the lower bearing portion 76a along the cam cap 78 and the lower bearing portion 76a.
- FIG. 13 is a diagram for explaining the details of the positioning method of the actuator 66 by the cam carrier 76.
- a peripheral portion of the actuator 66 in the lower bearing portion 76a of the cam carrier 76 is provided with a recess 76b formed in a shape along the outer shape of the actuator body 66b.
- the actuator 66 is fastened to the lower bearing portion 76 a by the fastening bolt 82 via the cam cap 78 in a state where a part of the actuator body 66 b is fitted in the recess 76 b.
- positioning using the cam carrier 76 is performed.
- the reliable positioning method of the actuator with respect to the cam carrier (and the cam cap) is not limited to the method shown in FIG. 13 and may be as follows, for example. That is, the lower bearing portion of the cam carrier may be provided with a convex portion formed in a shape along the outer shape of the actuator body, and the actuator may be positioned using the convex portion.
- the actuator includes a fixing portion formed in a C-shaped cross section so as to cover the cam carrier and the cam cap from both the upper and lower sides, and then the fixing portion, the cam cap, and the like from one side of the fixing portion.
- the actuator may be fixed to the cam carrier and the cam cap by a through bolt penetrating the cam carrier and a nut engaged with the through bolt on the other side of the fixing portion.
- the actuator 66 (actuator main body 66b) of the present embodiment is disposed within the internal combustion engine 1 (cylinder head 74) within the above-described region represented by the alternate long and short dash line. It is arranged between the exhaust camshaft 72.
- oil is supplied into the cylinder head using an oil shower pipe or the like for lubrication of the valve operating device.
- the actuator 66 can be efficiently cooled by the oil supplied into the cylinder head 74 as compared with the case where the actuator is attached to the outside of the cylinder head.
- overheating of the electromagnetic coil 88 in the actuator 66 can be suppressed, and a decrease in the response of the actuator 66 due to overheating can be prevented well.
- the actuator 66 (actuator body 66b) is disposed so as to be within the above-described region, and the actuator 66 is disposed so as to face the guide rail 64, so that the actuator 66 is sufficiently located with respect to the guide rail 64. Can be placed close to.
- the actuator 66 protrudes the protrusion 58c toward the guide rail 64
- the distance from the movable element 66a of the actuator 66 to the contact portion of the protrusion 58c with the guide rail 64 can be easily shortened.
- the stress acting on the actuator 66 can be favorably reduced by shortening the distance. Further, by shortening the distance, it is possible to ensure good responsiveness when the protrusions 58c are driven by the actuator 66.
- the movers 66aIN and 66aEX of the actuator 66 are located at both ends of the region from the center in the region (that is, an intermediate position between the intake camshaft 12 and the exhaust camshaft 72) so as to face each other. It arrange
- the movable elements 66aIN and 66aEX are arranged so as to oppose each other, when the movable elements 66aIN and 66aEX are driven at the same time, the driving reaction forces of the two are canceled out. Thereby, the vibration which arises in the actuator 66 at the time of a drive can be suppressed effectively. For this reason, it becomes possible to operate the switching mechanism 24 for stopping the valve with high accuracy.
- each protrusion 58c is interposed between each movable element 66a and each guide rail 64 in the region even when the protrusion 58c is separated from each guide rail 64. It is arranged like that. According to such a configuration, when each movable element 66a protrudes the protrusion 58c toward the guide rail 64, the distance from the movable element 66a to the contact portion of the protrusion 58c with the guide rail 64 is effectively increased. It can be shortened. As a result, by sufficiently shortening the distance, it is possible to more effectively reduce the stress acting on the actuator 66, and more sufficiently ensure the responsiveness when the projection 58c is driven by the actuator 66. Is possible.
- the actuator 66 is attached to the cam carrier 76 using the fastening portion of the cam cap 78 in the lower bearing portion 76a. According to such a fixing method of the actuator 66, by using an existing member provided to support the camshafts 12 and 72, the actuator 66 can be reduced in cost and space without the need for providing a new fixing place. Can be mounted inside the internal combustion engine 1.
- the actuator 66 (actuator body 66b) is attached to the lower bearing portion 76a along the cam cap 78 and the lower bearing portion 76a.
- the position of the lower bearing portion 76a is defined between the cam shafts 12 and 72, and the cam cap 78 is positioned with respect to the lower bearing portion 76a. For this reason, by positioning the actuator 66 along the cam cap 78 and the lower bearing portion 76a, the positioning of the actuator 66 with the guide rail 64 provided on the camshafts 12 and 72 can be facilitated.
- FIG. 14 is a cross-sectional view for explaining the internal structure of the actuator main body 66b of the electromagnetic solenoid actuator 66. As shown in FIG.
- the actuator main body 66 b includes a stator 84. Inside the stator 84, an inner fixed iron core 86 made of a magnetic material is disposed. In addition, an electromagnetic coil 88 is provided on the outer periphery of the inner fixed iron core 86 inside the stator 84.
- Both end portions 86a and 86b of the inner fixed iron core 86 are formed in a disc shape.
- the actuator body 66b includes a pair of permanent magnets 90 and 92 so as to face the end portions 86a and 86b.
- One (left side in FIG. 14) of the permanent magnet 90 is fixed to the intake side movable element 66a on the surface opposite to the surface facing the end portion 86a, and the other (right side in FIG. 14).
- 92 is fixed to the exhaust-side movable element 66a on the surface opposite to the surface facing the end portion 86b.
- the permanent magnet 90 is configured such that the surface fixed to the mover 66a is an N pole and the surface facing the end portion 86a is an S pole.
- the permanent magnet 92 is configured such that the surface facing the end portion 86b is the S pole and the surface fixed to the mover 66a is the S pole.
- the actuator body 66 b includes an outer fixed iron core 94 having a surface facing the N-pole side surface of the permanent magnet 90 on the outer side of the permanent magnet 90, and the permanent magnet 92 on the outer side of the permanent magnet 92.
- An outer fixed iron core 96 having a surface facing the surface on the S pole side of the magnet 92 is provided.
- the attractive force generated between the outer fixed iron cores 94 and 96 and the permanent magnets 90 and 92 is set to be larger than the attractive force generated between the inner fixed iron core 86 and the permanent magnets 90 and 92 when energized. Has been.
- FIG. 15 is a view for explaining the operation of the actuator 66 shown in FIG. As described above, the actuator 66 drives the left and right movers 66aIN and 66aEX to which the permanent magnets 90 and 92 are respectively fixed by the single electromagnetic coil 88 arranged at the center.
- FIG. 15A is a diagram when the exciting current is supplied to the electromagnetic coil 88 so that the left end 86a of the inner fixed iron core 86 becomes the S pole and the right end 86b becomes the N pole. .
- a repulsive force is generated between the magnetic pole formed on the inner fixed iron core 86 and the magnetic poles of the left and right permanent magnets 90 and 92, respectively.
- the exciting current in the direction shown in FIG. 15A is supplied to the permanent magnets 90 and 92 that are attracted to the inner fixed iron core 86, the left and right movable elements 66aIN and 66aEX are moved to the outer sides. It comes to stick out.
- FIG. 15B shows an excitation current in a direction opposite to that shown in FIG. 15A so that the left end 86a of the inner fixed core 86 becomes the N pole and the right end 86b becomes the S pole.
- FIG. 6 is a diagram when the electromagnetic coil 88 is supplied.
- an attractive force is generated between the magnetic poles formed on the inner fixed iron core 86 and the magnetic poles of the left and right permanent magnets 90 and 92, respectively. Therefore, when the exciting current in the direction shown in FIG. 15B is supplied to the permanent magnets 90 and 92 that are attracted to the outer fixed iron cores 94 and 96, the left and right movable elements 66aIN and 66aEX are moved. Each will come back inside.
- the ECU 26 commands the single electromagnetic coil 88 with a predetermined excitation current, thereby simultaneously driving both the intake side and exhaust side movable elements 66aIN and 66aEX. can do. Therefore, the number of actuators 66 can be reduced and the size can be reduced, the cost of hardware can be reduced by reducing the number of actuators 66 and the size can be reduced, and the cost of the control system of the actuator 66 can be reduced (reduction of control ports). Etc.). Furthermore, according to the actuator that can be operated simultaneously in two directions, such as the actuator 66, it is possible to cancel the driving reaction forces of the two movers. Thereby, the vibration which arises in an actuator at the time of a drive can be suppressed effectively.
- the actuator 66 in a state where the permanent magnets 90, 92 are protruded to a position where they contact the outer fixed iron cores 94, 96 (valve stop state), the outer fixed iron cores 94, 96 and the permanent magnets 90, 92 are.
- the position of the mover 66a is held by the suction force generated between the movable member 66a and the movable member 66a.
- the mover is caused by the attractive force generated between the inner fixed iron core 86 and the permanent magnets 90 and 92.
- the position 66a is maintained.
- Embodiment 1 With respect to the cylindrical part 62 to which the axial position of the camshafts 12 and 72 is restrained when the protrusion 58c protruded by the actuator 66 and the guide rail 64 are engaged.
- a configuration in which the valve opening characteristic of the valve 18 changes from the valve operating state to the valve stop state as the slide pin 58 to which the protrusion 58c is fixed is relatively displaced is described as an example.
- the variable valve apparatus that is the subject of the present invention is not limited to such a configuration, and may be a variable valve apparatus having the following configuration, for example.
- an actuator having a mover functioning as a protrusion of the present invention is provided, and a member including a cylindrical portion to which a guide rail is fixed and two types of cams are attached to a camshaft so as to be movable in the axial direction.
- the member including the cylindrical portion and the two types of cams is displaced relative to the actuator (protrusion) in which the axial position of the camshaft is constrained. Accordingly, the valve opening characteristics of the valve are changed.
- variable valve operating device for both the intake valve and the exhaust valve
- variable valve operating device according to the present invention includes the intake valve and the exhaust valve. It may be provided for at least one of them.
- the intake valves provided with the two movers 66aIN and 66aEX and the single electromagnetic coil 88 and driven by the two actuators 66 and 72 by the single actuator 66, respectively. 18 and the valve opening characteristics of the exhaust valve are changed.
- the actuator in the present invention is not limited to such a configuration, and may be two actuators separately provided for each of the first and second camshafts. Further, even when the actuators are separately provided for the respective camshafts as described above, by arranging the two movable elements so as to face each other as in the first embodiment described above, In the case where the mover is driven at the same time, the driving reaction forces of the two are canceled out. Thereby, also in this case, vibration generated in the actuator during driving can be effectively suppressed.
- the description has been given by taking as an example a configuration that is a large part of the actuator 66 and the entirety of the actuator body 66b is within the above-described region shown in FIG.
- the actuator according to the present invention only needs to be at least a part of which is arranged in the region.
- first camshaft and the second camshaft in the present invention are not limited to such a configuration.
- the first camshaft drives one intake valve and one exhaust valve in the same cylinder.
- the second camshaft may drive the other intake valve and the other exhaust valve in the same cylinder.
- the base circle diameter of the main cams 14IN and 14EX is larger than the circular diameter of the cylindrical portions 62IN and 62EX.
- the placement location of the actuator 66 is specified in association with an oval region virtually obtained by connecting the base circle of the cam 14EX.
- the oval region used for specifying the location of the actuator in the present invention is not limited to that defined in this way. That is, in the present invention, when the configuration has a configuration in which the circular diameter of the cylindrical portion is larger than the base circular diameter of the cam, the region is defined using the circular portion of the cylindrical portion.
- the sub cam 16 is configured as a zero lift cam
- the sub cam in the present invention is not limited to the zero lift cam. That is, the cam may be provided with a nose portion that allows a lift smaller than that of the main cam 14 to be obtained.
- the intake valve 18 is the “first valve” in the first invention
- the main cam 14IN is the “first cam” in the first invention
- the intake camshaft 12 is the first cam.
- the “first camshaft” in the first aspect of the invention is an exhaust valve (not shown) provided in the exhaust variable valve operating apparatus 70 in the “second valve” of the first aspect of the invention
- the main cam 14EX is the first camshaft.
- the exhaust camshaft 72 corresponds to the “second camshaft” in the first invention, corresponding to the “second cam” in the invention.
- the range defined by the displacement end Pmax1 and the displacement end Pmax2 is the “reciprocating range” in the second invention
- the slide pin 58 is the “displacement member” in the second invention.
- the mover 66aIN and the mover 66aEX correspond to the “first mover” and the “second mover” in the fifth or seventh invention.
- the cam carrier 76 corresponds to the “camshaft support member” in the ninth aspect of the invention.
- the cam cap 78 corresponds to the “upper bearing portion” according to the tenth aspect of the present invention.
- Embodiment 2 of the present invention will be described with reference to FIG.
- the configuration of the variable valve devices 100 and 120 of the present embodiment is the same as that of the variable valve devices 10 and 70 of the first embodiment described above, except that the configuration related to the electromagnetic solenoid actuator 102 is different. To do.
- FIG. 16 is a diagram for explaining a specific configuration of the electromagnetic solenoid actuator 102 according to the second embodiment of the present invention.
- the same components as those shown in FIG. 12 are denoted by the same reference numerals, and the description thereof is omitted or simplified.
- the exhaust variable valve operating apparatus 120 is basically configured in the same manner as the intake variable valve operating apparatus 100, and therefore detailed description thereof is omitted here.
- the 16 includes an arm portion 104b formed in an L shape, and includes a slide pin 104 configured to be movable and rotatable in the axial direction about the axis of the columnar portion 104a.
- the electromagnetic solenoid actuator 102 is configured such that the protrusion 104c fixed to the slide pin 104 can be engaged with the guide rail 64 by applying a thrust of the movable element 102a to the slide pin 104. Yes.
- a part of the actuator 102 is disposed so as to be within the region shown in FIG. 16 set in the same manner as the region shown in FIG.
- the actuator 102 is fixed to the cam cap 106 with a fastening bolt 108 via the fixing portion 102c.
- the actuator 102 is disposed on the head cover 110 side with respect to the lower bearing portion 76a, and more specifically, the end portion (lower end) of the actuator body 102b is disposed lower than the upper surface of the cam cap 106.
- the mounting position of the actuator 102 can be kept low. Thereby, interference with other component parts arranged on the head cover 110 can be easily avoided. Further, it is possible to easily avoid a reduction in the volume of the PCV (positive crankcase ventilation) chamber 112 provided for separating the blowby gas and oil existing in the head cover 110.
- PCV positive crankcase ventilation
- a baffle plate 114 is provided on the back surface of the head cover 110.
- the actuator 102 is disposed in a space below the baffle plate 114 as a result of the mounting position being kept low by the above-described fixing method.
- the baffle plate 114 is provided with an oil shower pipe 116 including an injection hole 116a for injecting oil toward each roller member (for example, the first roller 36 and the like) included in the intake variable valve operating apparatus 100.
- the oil shower pipe 116 is also provided with an injection hole 116b for injecting oil toward each actuator body 102b.
- the actuator 102 is arranged in the oil injection direction by the injection hole 116 b of the oil shower pipe 116.
- the baffle plate 114 is provided with a fresh air passage 118 for circulating fresh air inside the head cover 110 for the treatment of blow-by gas.
- the fresh air passage 118 is formed with an opening 118a for applying fresh air toward each actuator body 102b.
- the actuator 102 is disposed in the vicinity of the opening 118 a of the fresh air passage 118 inside the head cover 110.
- the oil injected from the oil shower pipe 116 hits the actuator body 102b, so that the actuator body 102b incorporating the electromagnetic coil can be efficiently cooled. Furthermore, the fresh air supplied from the fresh air passage 118 directly hits the actuator main body 102b, whereby the actuator main body 102b can be efficiently cooled. Thereby, the temperature of the actuator 102 can be stabilized, and the robustness of the response of the actuator 102 can be improved.
- the cam carrier 76 corresponds to the “camshaft support member” in the eleventh aspect of the invention.
- the oil shower pipe 116 corresponds to the “oil injection member” in the twelfth aspect of the invention.
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Abstract
Description
尚、出願人は、本発明に関連するものとして、上記の文献を含めて、以下に記載する文献を認識している。
前記第1バルブと同一気筒内に配置される第2バルブを駆動するための第2カムが固定もしくは軸方向の移動自在に取り付けられた第2カムシャフトと、
前記第1および第2カムシャフトに、それぞれ固定もしくは軸方向の移動自在に取り付けられた円筒部の外周面に設けられたガイドレールと、
前記ガイドレールに係脱自在に配置された突起部と、
前記円筒部と対向して配置され、前記突起部を前記ガイドレールに向けて突き出し可能なアクチュエータと、を備え、
前記突起部と前記ガイドレールとの係合時に生ずる前記突起部と前記円筒部との相対的な変位に伴って、前記第1バルブおよび前記第2バルブの開弁特性が変化する内燃機関の可変動弁装置であって、
前記アクチュエータの少なくとも一部が、前記突起部が前記ガイドレールに向けて突き出されていない状態において、前記第1および第2カムシャフトの軸方向から見て、前記第1カムシャフトに取り付けられた前記円筒部の円径および前記第1カムのベース円径のうちの何れか大きい方の円と、前記第2カムシャフトに取り付けられた前記円筒部の円径および前記第2カムのベース円径のうちの何れか大きい方の円とを繋げて仮想的に得られる長円状の領域内に収まるように配置されていることを特徴とする。
前記可変動弁装置は、
前記第1カムと前記第1バルブとの間、および、前記第2カムと前記第2バルブとの間の少なくとも一方に配置され、前記第1バルブおよび前記第2バルブのうちの少なくとも一方の開弁特性を変更する可変機構と、
所定の往復範囲内で移動することにより前記可変機構の動作状態を切り換える変位部材と、を更に備え、
前記突起部は、前記変位部材に固定されていることを特徴とする。
前記突起部は、当該突起部が前記ガイドレールに向けて突き出されていない状態において、前記第1および第2カムシャフトの軸方向から見て、前記長円状の領域内に収まるように配置されていることを特徴とする。
前記アクチュエータは、前記長円状の領域内において前記第1カムシャフトに取り付けられた前記円筒部に向けて突き出し可能な位置に配置された第1可動子と、前記長円状の領域内において前記第2カムシャフトに取り付けられた前記円筒部に向けて突き出し可能な位置に配置された第2可動子と、を含むことを特徴とする。
前記第1可動子と前記第2可動子とは、互いに対向するようにして、それぞれに対応する前記円筒部に向けて突き出し可能な位置に配置されていることを特徴とする。
前記アクチュエータは、電磁ソレノイド式のアクチュエータであって、前記第1可動子および前記第2可動子を駆動する単一の電磁コイルを含むことを特徴とする。
前記アクチュエータは、前記長円状の領域内において前記第1カムシャフトに取り付けられた前記円筒部に向けて突き出し可能な位置に配置された第1可動子と、前記長円状の領域内において前記第2カムシャフトに取り付けられた前記円筒部に向けて突き出し可能な位置に配置された第2可動子と、を含み、
前記突起部は、前記第1カムシャフトに取り付けられた前記ガイドレールと前記第1可動子との間、および、前記第2カムシャフトに取り付けられた前記ガイドレールと前記第2可動子との間にそれぞれ介在していることを特徴とする。
前記アクチュエータは、電磁ソレノイド式のアクチュエータであって、前記第1可動子および前記第2可動子を駆動する単一の電磁コイルを含むことを特徴とする。
前記第1および第2カムシャフトを内燃機関のシリンダヘッド側から支持するロア軸受部を有するカムシャフト支持部材を更に備え、
前記アクチュエータは、前記ロア軸受部に取り付けられていることを特徴とする。
前記円筒部は、前記ロア軸受部に近接して配置されており、
前記アクチュエータは、前記第1および第2カムシャフトを前記ロア軸受部と反対側から支持するアッパー軸受部、および前記ロア軸受部のうちの少なくとも一方に沿うようにして、前記ロア軸受部に取り付けられていることを特徴とする。
前記第1および第2カムシャフトを内燃機関のシリンダヘッド側から支持するロア軸受部を有するカムシャフト支持部材と、
前記カムシャフト支持部材をシリンダヘッドの反対側から覆うヘッドカバーと、を更に備え、
前記アクチュエータは、前記ロア軸受部に対して前記ヘッドカバー側に配置されていることを特徴とする。
前記ヘッドカバーの内部に設置され、当該ヘッドカバーの内部にオイルを噴射するオイル噴射部材を更に備え、
前記アクチュエータは、前記オイル噴射部材によるオイルの噴射方向に配置されていることを特徴とする。
前記ヘッドカバーの内部に設置され、ブローバイガスの処理のために当該ヘッドカバーの内部に新気を流通させる新気通路を更に備え、
前記アクチュエータは、前記ヘッドカバーの内部における前記新気通路の開口部の近傍に配置されていることを特徴とする。
10、100 吸気可変動弁装置
12 吸気カムシャフト
14 主カム
14a ベース円部
14b ノーズ部
16 副カム
18 吸気バルブ
20 可変機構
24 切換機構
26 ECU(Electronic Control Unit)
32 第1ロッカーアーム
34L、34R 第2ロッカーアーム
46 第1ピン孔
48 第1切換ピン
52L、52R 第2ピン孔
54L、54R 第2切換ピン
56 リターンスプリング
58、104 スライドピン
58a 円柱部
58b、104b アーム部
58c、104c 突起部
58d 押圧面
58e 切欠部
58f 案内面
60 支持部材
62 円筒部
64 ガイドレール
64a 基端
64b 終端
64c 浅底部
66、102 電磁ソレノイド式アクチュエータ
66a、102a 可動子
66b、102b アクチュエータ本体
66c、102c 固定部
70、120 排気可変動弁装置
72 排気カムシャフト
74 シリンダヘッド
76 カムキャリア
76a ロア軸受部
76b カムキャリアの凹部
78、106 カムキャップ
84 ステータ
86 内側固定鉄心
86a、86b 内側固定鉄心の端部
88 電磁コイル
90、92 永久磁石
94、96 外側固定鉄心
110 ヘッドカバー
112 PCV室
114 バッフルプレート
116 オイルシャワーパイプ
116a、116b 噴射孔
118 新気通路
118a 開口部
Pmax1、Pmax2 変位端
先ず、図1乃至図14を参照して、本発明の実施の形態1について説明する。
[可変動弁装置の基本構成]
図1は、本発明の実施の形態1の内燃機関1の吸気可変動弁装置10の全体構成を概略的に示す図である。
ここでは、内燃機関1は、4つの気筒(#1~#4)を有する直列4気筒型エンジンであるものとする。また、内燃機関1の個々の気筒には、2つの吸気バルブ18と2つの排気バルブ(図示省略)とが備わっているものとする。尚、ここでは、吸気バルブ18を駆動するための吸気可変動弁装置10を例にとって説明を行うものとし、排気可変動弁装置70(図11参照)については、基本的に吸気可変動弁装置10と同様に構成されているため、ここではその詳細な説明を省略する。
次に、図2乃至図4を参照して、可変機構20の詳細な構成を説明する。
図2は、図1に示す可変機構20を、吸気バルブ18の基端部側から見下ろした図である。
可変機構20は、カムシャフト12と平行に配置されたロッカーシャフト30を備えている。図2に示すように、ロッカーシャフト30には、1つの第1ロッカーアーム32と、一対の第2ロッカーアーム34R、34Lとが回転自在に取り付けられている。第1ロッカーアーム32は、2つの第2ロッカーアーム34R、34Lの間に配置されている。尚、本明細書では、左右の第2ロッカーアーム34R、34Lを特に区別しないときには、単に第2ロッカーアーム34と表記する場合がある。
図3に示すように、第1ロッカーアーム32におけるロッカーシャフト30の反対側の端部には、主カム14と接することができる位置に、第1ローラ36が回転可能に取り付けられている。第1ロッカーアーム32は、ロッカーシャフト30に取り付けられたコイルスプリング38によって、第1ローラ36が主カム14と常に当接するように付勢されている。上記のように構成された第1ロッカーアーム32は、主カム14の作用力とコイルスプリング38の付勢力との協働により、ロッカーシャフト30を支点として揺動するようになる。
次に、図5および図6を参照して、切換機構24の詳細な構成を説明する。
切換機構24は、第1ロッカーアーム32と第2ロッカーアーム34との連結/非連結を切り換えるための機構であり、これにより、主カム14の作用力が第2ロッカーアーム34に伝達される状態と、当該作用力が第2ロッカーアーム34に伝達されない状態とを切り換えて、バルブ18の動作状態を弁稼動状態と弁停止状態との間で切り換えることができるようになっている。
図6は、切換機構24をカムシャフト12の軸方向(図5中の矢視Bの方向)から見た図である。
切換機構24は、カム14、16の回転動力を利用して、切換ピン48、54L、54Rを第2ロッカーアーム34L側に向けて(切換ピンの退出方向に)変位させるためのスライドピン58を備えている。スライドピン58は、図5に示すように、第2切換ピン54Rの端面と当接する端面を有する円柱部58aを備えている。円柱部58aは、シリンダヘッド74(図11参照)に固定された支持部材60によって、軸方向に進退自在であって、周方向に回転自在に支持されている。
次に、図7乃至図10を参照して、吸気可変動弁装置10の動作について説明する。
(弁稼動状態時)
図7は、弁稼動状態時(通常のリフト動作時)の制御状態を示す図である。
この場合には、図7(B)に示すように、アクチュエータ(ソレノイド)66の駆動がOFFとされており、これにより、スライドピン58は、カムシャフト12から離れた状態で、リターンスプリング56の付勢力を受けて、変位端Pmax1に位置している。この状態では、図7(A)に示すように、第1ロッカーアーム32と2つの第2ロッカーアーム34とが切換ピン48、54Lを介して連結されている。その結果、主カム14の作用力が第1ロッカーアーム32から左右の第2ロッカーアーム34R、34Lを介して双方のバルブ18に伝達されるようになる。このため、主カム14のプロフィールに従って、通常のバルブ18のリフト動作が行われるようになる。
図8は、弁停止動作の開始時の制御状態を示す図である。
弁停止動作は、例えば、内燃機関1のフューエルカット要求等の所定の弁停止動作の実行要求がECU26によって検知された際に行われる。このような弁停止動作は、カムシャフト12の回転力を利用してスライドピン58によって切換ピン48、54L、54Rをその退出方向に変位させる動作であるため、これらの切換ピン48、54L、54Rの軸心が同一直線状に位置する時、すなわち、第1ロッカーアーム32が揺動していない時に行われる必要がある。
図9は、スライド動作の完了時の制御状態を示す図である。
スライド動作の実行中には、ガイドレール64の側面に突起部58cが当接することによって、リターンスプリング56の付勢力が受け止められた状態で、スライドピン58が変位端Pmax2に向けて移動していく。図9(A)は、スライドピン58が変位端Pmax2に到達して弁停止要求時のスライド動作が完了したタイミング、すなわち、第1切換ピン48および第2切換ピン54Lがそれぞれ第1ピン孔46および第2ピン孔52L内に収まるようになったことで、第1ロッカーアーム32と第2ロッカーアーム34R、34Lとの連結が解除されたタイミングを示している。また、このタイミングでは、図9(B)に示すように、ガイドレール64内における突起部58cの位置は、未だ浅底部64cに達していない。
図10は、スライドピン58を可動子66aによって保持する保持動作時の制御状態を示す図である。
上記図9に示すスライド動作完了時から更にカムシャフト12が回転すると、突起部58cは、溝が徐々に浅くなる浅底部64cに差し掛かる。その結果、浅底部64cの作用によって、スライドピン58がカムシャフト12から離れる方向に回転させられるようになる。そして、浅底部64cによって溝が浅くなるにつれ、可動子66aがその退出方向に少し変位する。その後、アクチュエータ66によって駆動され続けている可動子66aが切欠部58eに一致するようになるまでスライドピン58が更に回転すると、可動子66aと当接するスライドピン58側の部位が押圧面58dから切欠部58eへと切り替わる。
弁停止状態から弁稼動状態に戻すための弁復帰動作は、例えば、フューエルカットからの復帰要求等の所定の弁復帰動作の実行要求がECU26によって検知された際に行われる。このような弁復帰動作は、図10に示す制御状態において、ECU26が所定のタイミング(切換ピン48等が移動可能となるベース円区間の開始タイミングよりもアクチュエータ66の動作に要する所定時間分だけ早いタイミング)でアクチュエータ66への通電をOFFとすることで開始される。アクチュエータ66への通電がOFFとされると、スライドピン58の切欠部58eと可動子66aとの係合が解かれることになる。その結果、リターンスプリング56の付勢力に抗して第1切換ピン48および第2切換ピン54Lをそれぞれ第1ピン孔46および第2ピン孔52Lに留めておく力が消滅することになる。
以上のように構成された本実施形態の吸気可変動弁装置10によれば、アクチュエータ66への通電のON、OFFとカムシャフト12の回転力とリターンスプリング56の付勢力とを利用して、スライドピン58の軸方向位置を変位端Pmax1からPmax2の間で移動させることで、弁稼動状態と弁停止状態との間でバルブ18の動作状態を切り換えることが可能となる。
(電磁ソレノイド式アクチュエータの配置場所および固定手法)
先ず、図11および図12を参照して、電磁ソレノイド式アクチュエータ66の配置場所および固定手法について説明する。
図11は、図5に示す電磁ソレノイド式アクチュエータ66の配置を説明するための斜視図である。より具体的には、図11において左側に位置するのが吸気可変動弁装置10であり、右側に位置するのが排気可変動弁装置70である。また、図11における切断面は、#4気筒の中心で切断されたシリンダヘッド74およびその搭載部材のものである。また、図11においては、#3気筒に対してのみ電磁ソレノイド式アクチュエータ66を代表して図示しており、他の気筒についてはアクチュエータ66の図示を省略している。
図12は、電磁ソレノイド式アクチュエータ66を、カムシャフト12、72の軸方向から見た断面図である。より具体的には、図12は、アクチュエータ66の中心においてシリンダヘッド74の搭載部材が切断された断面を、#4気筒側から見た図である。
尚、図11、12においては、主カム14、副カム16等の可変動弁装置10、70の各構成要素については、それらの所属が分かるようにするために、吸気側であることを示す符号「IN」、排気側であることを示す符号「EX」、および気筒番号「#○」を、それぞれ各構成要素の参照符号の末尾に適宜付すようにしている。
カムキャリア76のロア軸受部76aにおけるアクチュエータ66の周辺部位は、アクチュエータ本体66bの外形に沿う形状で形成された凹部76bが設けられている。そして、図13に示すように、アクチュエータ66は、アクチュエータ本体66bの一部が凹部76bに嵌め込まれた状態で、固定部66cがカムキャップ78を介してロア軸受部76aに締結ボルト82によって締結されることで、カムキャリア76を用いた位置決めがなされている。このような手法によれば、アクチュエータ66の駆動時に当該アクチュエータ66に作用する反力によって、カムキャリア76(およびカムキャップ78)に対するアクチュエータ66の固定位置がずれてしまうのを確実に抑制することができる。これにより、弁停止を行うための切換機構24の精度の良い作動を確保することができる。尚、カムキャリア(およびカムキャップ)に対するアクチュエータの確実な位置決め手法は、図13に示す手法に限らず、例えば、次のようなものであってもよい。すなわち、カムキャリアのロア軸受部に、アクチュエータ本体の外形に沿う形状で形成された凸部を設けるようにし、当該凸部を利用して、アクチュエータの位置決めを行うようにしてもよい。或いは、アクチュエータが、カムキャリアおよびカムキャップを上下両側から覆うように断面C字状に形成された固定部を備えるようにしたうえで、当該固定部の一方側から当該固定部、カムキャップ、およびカムキャリアを貫通する通しボルトと、当該固定部の他方側で当該通しボルトに噛み合わされるナットとによって、アクチュエータをカムキャリアおよびカムキャップに固定するものであってもよい。
次に、図14および図15を参照して、電磁ソレノイド式アクチュエータ66の内部構造について説明する。
図14は、電磁ソレノイド式アクチュエータ66のアクチュエータ本体66bの内部構造を説明するための断面図である。
以上説明したように、アクチュエータ66は、中央に配置された単一の電磁コイル88によって、永久磁石90、92がそれぞれ固定された左右の可動子66aIN、66aEXを駆動するものである。
また、上述した実施の形態1においては、変位端Pmax1と変位端Pmax2とで規定される範囲が前記第2の発明における「往復範囲」に、スライドピン58が前記第2の発明における「変位部材」に、それぞれ相当している。
また、上述した実施の形態1においては、可動子66aINおよび可動子66aEXが前記第5または第7の発明における「第1可動子」および「第2可動子」に相当している。
また、上述した実施の形態1においては、カムキャリア76が前記第9の発明における「カムシャフト支持部材」に相当している。
また、カムキャップ78が前記第10の発明における「アッパー軸受部」に相当している。
次に、図16を参照して、本発明の実施の形態2について説明する。
本実施形態の可変動弁装置100、120の構成は、電磁ソレノイド式アクチュエータ102に関連する構成が異なる点を除き、上述した実施の形態1の可変動弁装置10、70と同様であるものとする。
また、上述した実施の形態2においては、オイルシャワーパイプ116が前記第12の発明における「オイル噴射部材」に相当している。
Claims (13)
- 内燃機関の気筒内の第1バルブを駆動するための第1カムが固定もしくは軸方向の移動自在に取り付けられた第1カムシャフトと、
前記第1バルブと同一気筒内に配置される第2バルブを駆動するための第2カムが固定もしくは軸方向の移動自在に取り付けられた第2カムシャフトと、
前記第1および第2カムシャフトに、それぞれ固定もしくは軸方向の移動自在に取り付けられた円筒部の外周面に設けられたガイドレールと、
前記ガイドレールに係脱自在に配置された突起部と、
前記円筒部と対向して配置され、前記突起部を前記ガイドレールに向けて突き出し可能なアクチュエータと、を備え、
前記突起部と前記ガイドレールとの係合時に生ずる前記突起部と前記円筒部との相対的な変位に伴って、前記第1バルブおよび前記第2バルブの開弁特性が変化する内燃機関の可変動弁装置であって、
前記アクチュエータの少なくとも一部が、前記突起部が前記ガイドレールに向けて突き出されていない状態において、前記第1および第2カムシャフトの軸方向から見て、前記第1カムシャフトに取り付けられた前記円筒部の円径および前記第1カムのベース円径のうちの何れか大きい方の円と、前記第2カムシャフトに取り付けられた前記円筒部の円径および前記第2カムのベース円径のうちの何れか大きい方の円とを繋げて仮想的に得られる長円状の領域内に収まるように配置されていることを特徴とする内燃機関の可変動弁装置。 - 前記可変動弁装置は、
前記第1カムと前記第1バルブとの間、および、前記第2カムと前記第2バルブとの間の少なくとも一方に配置され、前記第1バルブおよび前記第2バルブのうちの少なくとも一方の開弁特性を変更する可変機構と、
所定の往復範囲内で移動することにより前記可変機構の動作状態を切り換える変位部材と、を更に備え、
前記突起部は、前記変位部材に固定されていることを特徴とする請求項1記載の内燃機関の可変動弁装置。 - 前記突起部は、当該突起部が前記ガイドレールに向けて突き出されていない状態において、前記第1および第2カムシャフトの軸方向から見て、前記長円状の領域内に収まるように配置されていることを特徴とする請求項1または2記載の内燃機関の可変動弁装置。
- 前記アクチュエータは、前記長円状の領域内において前記第1カムシャフトに取り付けられた前記円筒部に向けて突き出し可能な位置に配置された第1可動子と、前記長円状の領域内において前記第2カムシャフトに取り付けられた前記円筒部に向けて突き出し可能な位置に配置された第2可動子と、を含むことを特徴とする請求項1乃至3の何れか1項記載の内燃機関の可変動弁装置。
- 前記第1可動子と前記第2可動子とは、互いに対向するようにして、それぞれに対応する前記円筒部に向けて突き出し可能な位置に配置されていることを特徴とする請求項4記載の内燃機関の可変動弁装置。
- 前記アクチュエータは、電磁ソレノイド式のアクチュエータであって、前記第1可動子および前記第2可動子を駆動する単一の電磁コイルを含むことを特徴とする請求項4または5記載の内燃機関の可変動弁装置。
- 前記アクチュエータは、前記長円状の領域内において前記第1カムシャフトに取り付けられた前記円筒部に向けて突き出し可能な位置に配置された第1可動子と、前記長円状の領域内において前記第2カムシャフトに取り付けられた前記円筒部に向けて突き出し可能な位置に配置された第2可動子と、を含み、
前記突起部は、前記第1カムシャフトに取り付けられた前記ガイドレールと前記第1可動子との間、および、前記第2カムシャフトに取り付けられた前記ガイドレールと前記第2可動子との間にそれぞれ介在していることを特徴とする請求項3記載の内燃機関の可変動弁装置。 - 前記アクチュエータは、電磁ソレノイド式のアクチュエータであって、前記第1可動子および前記第2可動子を駆動する単一の電磁コイルを含むことを特徴とする請求項7記載の内燃機関の可変動弁装置。
- 前記第1および第2カムシャフトを内燃機関のシリンダヘッド側から支持するロア軸受部を有するカムシャフト支持部材を更に備え、
前記アクチュエータは、前記ロア軸受部に取り付けられていることを特徴とする請求項1乃至8の何れか1項記載の内燃機関の可変動弁装置。 - 前記円筒部は、前記ロア軸受部に近接して配置されており、
前記アクチュエータは、前記第1および第2カムシャフトを前記ロア軸受部と反対側から支持するアッパー軸受部、および前記ロア軸受部のうちの少なくとも一方に沿うようにして、前記ロア軸受部に取り付けられていることを特徴とする請求項9記載の内燃機関の可変動弁装置。 - 前記第1および第2カムシャフトを内燃機関のシリンダヘッド側から支持するロア軸受部を有するカムシャフト支持部材と、
前記カムシャフト支持部材をシリンダヘッドの反対側から覆うヘッドカバーと、を更に備え、
前記アクチュエータは、前記ロア軸受部に対して前記ヘッドカバー側に配置されていることを特徴とする請求項1乃至3の何れか1項記載の内燃機関の可変動弁装置。 - 前記ヘッドカバーの内部に設置され、当該ヘッドカバーの内部にオイルを噴射するオイル噴射部材を更に備え、
前記アクチュエータは、前記オイル噴射部材によるオイルの噴射方向に配置されていることを特徴とする請求項11記載の内燃機関の可変動弁装置。 - 前記ヘッドカバーの内部に設置され、ブローバイガスの処理のために当該ヘッドカバーの内部に新気を流通させる新気通路を更に備え、
前記アクチュエータは、前記ヘッドカバーの内部における前記新気通路の開口部の近傍に配置されていることを特徴とする請求項11または12記載の内燃機関の可変動弁装置。
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US12/676,830 US8191520B2 (en) | 2009-05-29 | 2009-05-29 | Variable valve operating apparatus for internal combustion engine |
PCT/JP2009/059835 WO2010137159A1 (ja) | 2009-05-29 | 2009-05-29 | 内燃機関の可変動弁装置 |
JP2010502591A JP5158190B2 (ja) | 2009-05-29 | 2009-05-29 | 内燃機関の可変動弁装置 |
CN2009801003644A CN101978141B (zh) | 2009-05-29 | 2009-05-29 | 内燃机的可变气门装置 |
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JP4752949B2 (ja) * | 2009-05-28 | 2011-08-17 | トヨタ自動車株式会社 | 内燃機関の可変動弁装置 |
JP5273257B2 (ja) | 2009-11-25 | 2013-08-28 | トヨタ自動車株式会社 | 内燃機関の可変動弁装置 |
WO2011064845A1 (ja) | 2009-11-25 | 2011-06-03 | トヨタ自動車株式会社 | 内燃機関の可変動弁装置 |
DE102011104382A1 (de) * | 2011-06-16 | 2012-12-20 | Daimler Ag | Brennkraftmaschinenventiltriebvorrichtung für ein Kraftfahrzeug |
JP2014047623A (ja) * | 2012-08-29 | 2014-03-17 | Honda Motor Co Ltd | 可変動弁装置 |
US9399964B2 (en) | 2014-11-10 | 2016-07-26 | Tula Technology, Inc. | Multi-level skip fire |
US11236689B2 (en) | 2014-03-13 | 2022-02-01 | Tula Technology, Inc. | Skip fire valve control |
CN109026407B (zh) * | 2014-11-10 | 2020-08-07 | 图拉技术公司 | 运行内燃发动机的方法和发动机控制器 |
SE539832C2 (en) * | 2016-04-28 | 2017-12-12 | Scania Cv Ab | A valve drive for an internal combustion engine with variable control of valves |
DE102017205538A1 (de) * | 2017-03-31 | 2018-10-04 | Mahle International Gmbh | Ventiltrieb für eine Brennkraftmaschine |
JP6922715B2 (ja) * | 2017-12-15 | 2021-08-18 | トヨタ自動車株式会社 | 内燃機関の潤滑油供給装置 |
DE102018117234A1 (de) * | 2018-07-17 | 2020-01-23 | Schaeffler Technologies AG & Co. KG | Modul für einen hubvariablen Ventiltrieb einer Brennkraftmaschine |
CN109268173B (zh) * | 2018-11-14 | 2023-12-19 | 南京工程学院 | 一种无级可变的内燃机进气系统 |
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US20110126786A1 (en) | 2011-06-02 |
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JP5158190B2 (ja) | 2013-03-06 |
US8191520B2 (en) | 2012-06-05 |
CN101978141B (zh) | 2012-09-05 |
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