WO2011064852A1 - 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
- WO2011064852A1 WO2011064852A1 PCT/JP2009/069876 JP2009069876W WO2011064852A1 WO 2011064852 A1 WO2011064852 A1 WO 2011064852A1 JP 2009069876 W JP2009069876 W JP 2009069876W WO 2011064852 A1 WO2011064852 A1 WO 2011064852A1
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- WIPO (PCT)
- Prior art keywords
- protrusion
- guide rail
- camshaft
- pin
- projection
- 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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0005—Deactivating 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
- F01L1/12—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
- F01L1/26—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
- F01L1/20—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
- 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
- F01L2250/00—Camshaft drives characterised by their transmission means
- F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
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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
- F01L2250/00—Camshaft drives characterised by their transmission means
- F01L2250/04—Camshaft drives characterised by their transmission means the camshaft being driven by belts
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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
- 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 is displaced in the axial direction by engaging the drive pin with the guide groove.
- the valve drive cam of each cylinder is switched, so that the lift amount of the valve can be changed.
- variable valve operating apparatus that changes the valve opening characteristics, if the contact area between the spiral wall and the projection is small, the surface pressure (contact load / contact area) generated between the two increases. As a result, there is a concern that the wear of the spiral wall portion or the protrusion portion is increased.
- An object of the present invention is to provide a variable valve operating apparatus for an internal combustion engine that can secure a contact area between the two and reduce the surface pressure generated between the two in an excellent manner.
- a first invention is a variable valve operating apparatus for an internal combustion engine, A variable mechanism that is disposed between the cam and the valve and changes a valve opening characteristic of the valve; A switching mechanism for switching the operating state of the variable mechanism, The switching mechanism is A guide rail provided on the outer peripheral surface of the camshaft provided with the cam and provided with a spiral wall; A protrusion that is detachably disposed on the helical wall; An actuator capable of projecting the protrusion toward the guide rail so that the protrusion engages with the helical wall, A mechanism for switching an operating state of the variable mechanism in accordance with a relative displacement between the protrusion and the spiral wall that occurs when the protrusion and the spiral wall are engaged; In a state where the projection is projected toward the guide rail by the actuator, the projection with respect to the spiral wall portion so that the center axis of the projection and the center axis of the camshaft intersect perpendicularly. The arrangement is determined.
- the second invention is the first invention, wherein The protrusion is formed so that the width of the tip portion is smaller than the width of the root portion when viewed from the axial direction of the camshaft, and the width is not larger than that of the root portion in the intermediate portion. It is characterized by.
- the third invention is the second invention, wherein The protrusion is formed so as to be narrowed down toward the axis of the camshaft when viewed from the axial direction of the camshaft in a state of being protruded toward the guide rail by the actuator.
- 4th invention is set in 3rd invention,
- the protrusion is formed in a taper shape that narrows toward the distal end side when viewed from the axial direction of the camshaft.
- the fifth invention is the fourth invention, wherein A guide surface for guiding the tip portion of the projection portion inserted into the spiral wall portion is formed on at least one of the tip portion of the projection portion and the upper portion of the spiral wall portion. It is characterized by being.
- the sixth invention is the fifth invention, wherein
- the guide surface includes a central axis of the protrusion and a center of the camshaft in a state where the tip portion of the protrusion and the upper portion of the spiral wall portion are protruded toward the guide rail by the actuator.
- the surface is inclined to the lower side of the spiral wall portion.
- the protrusion with respect to the spiral wall portion in the state where the protrusion is projected toward the guide rail by the actuator, the protrusion with respect to the spiral wall portion so that the center axis of the protrusion and the center axis of the camshaft intersect perpendicularly.
- the arrangement of has been determined. Accordingly, the arrangement of the protrusions with respect to the spiral wall portion can be determined so as not to be affected by the inclination of the spiral wall portion. For this reason, according to this invention, it becomes possible to ensure the contact area of a helical wall part and a projection part, and to reduce the surface pressure produced between both favorably.
- the contact range between the spiral wall portion and the protrusion is increased from the bottom to the top of the spiral wall portion. It is possible to ensure a wide line shape between. For this reason, it becomes possible to reduce effectively the surface pressure which arises between a helical wall part and a projection part.
- the fifth invention it is possible to guarantee the insertion reliability of the protrusion to the guide rail.
- the guide surface is a surface inclined to the lower side of the spiral wall portion, when the projection portion and the spiral wall portion are in contact with each other under a situation in which the projection portion is not projected by the actuator, the projection surface It can prevent that a part and a helical wall part will be in an engagement state.
- FIG. 1 is a diagram schematically showing an overall configuration of a 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 valve
- Embodiment 2 of this invention It is a figure showing the contact state of the projection part and load receiving surface in Embodiment 2 of this invention. It is a figure for demonstrating the general setting of the clearance of a guide rail and a projection part when a projection part protrudes to the guide rail. It is a figure for demonstrating the change of the contact load according to the clearance gap between the projection part in the linear section of a guide rail, and the wall part by the side of a load receiving surface. It is a figure for demonstrating the guidance method of the projection part using a spring board. It is a figure for demonstrating the guidance method of the projection part using a permanent magnet. It is a figure for demonstrating the guidance method of the projection part using an electromagnet.
- FIG. 1 is a diagram schematically showing an overall configuration of a variable valve apparatus 10 for an internal combustion engine 1 according to Embodiment 1 of the present invention.
- the internal combustion engine 1 has four cylinders (# 1 to # 4) and is an in-line four-cylinder engine in which an explosion stroke is performed in the order of # 1 ⁇ # 3 ⁇ # 4 ⁇ # 2. To do.
- each cylinder of the internal combustion engine 1 is provided with two intake valves and two exhaust valves.
- the configuration shown in FIG. 1 functions as a mechanism for driving two intake valves or two exhaust valves disposed in each cylinder.
- the variable valve operating apparatus 10 of the present 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).
- variable mechanism 20 is interposed between the cams 14 and 16 and the valve 18 of each cylinder. 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).
- variable valve operating apparatus 10 includes 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 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 outer diameter of the second roller 40 is the same as the outer diameter of the first roller 36.
- the rocker shaft 30 is supported by a cam carrier (or a cylinder head or the like) that is a stationary member of the internal combustion engine 1 via a lash adjuster 42.
- the second rocker arm 34 is biased toward the sub cam 16 by receiving a pushing force from the lash adjuster 42.
- the secondary cam is a lift cam having a nose portion unlike the zero lift cam of the present embodiment
- the second rocker arm 34 is driven by the valve spring 22 when the secondary cam lifts the valve 18. Will be pressed against.
- 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 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.
- 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.
- a cylindrical second switching pin 54R is slidably inserted into 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 relationship between the lock pin 70 and the solenoid 68 is simplified.
- 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). I have. As shown in FIG.
- 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 cam carrier so as to be movable back and forth 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 peripheral surface of the camshaft 12. Further, a columnar protrusion 58 c is provided at the tip of the arm portion 58 b so as to protrude toward the 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 circumferential surface of the cylindrical portion 62.
- the guide rail 64 is formed as a spiral groove.
- the switching mechanism 24 includes an actuator 66 for inserting the protrusion 58 c into the guide rail 64. More specifically, the actuator 66 includes a solenoid 68 that is duty-controlled based on a command from the ECU 26, and a lock pin 70 that contacts the drive shaft 68 a of the solenoid 68.
- the lock pin 70 is formed in a cylindrical shape.
- a spring 72 that generates a biasing force against the thrust of the solenoid 68 is hooked on the lock pin 70, and the other end of the spring 72 is attached to a support member 74 fixed to a cam carrier that is a stationary member. It is hung.
- the thrust of the solenoid 68 can overcome the urging force of the spring 72, so that the lock pin 70 can be advanced.
- the lock pin 70 and the drive shaft 68a are quickly retracted to a predetermined position by the urging force of the spring 72. Further, the movement of the lock pin 70 in the radial direction is restricted by the support member 74.
- the solenoid 68 is a position where the lock pin 70 can press the pressing surface 58d (the surface opposite to the surface on which the protrusion 58c is provided) 58d toward the guide rail 64 at the tip of the arm portion 58b of the slide pin 58.
- the frame is fixed to a stationary member such as a cam carrier.
- the pressing surface 58d is provided in a shape and a position such that the projection 58c can be pressed toward the guide rail 64 by the lock pin 70.
- 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 columnar portion 62 and the stopper 76 on the camshaft 12 side.
- the lock pin 70 driven by the solenoid 68 is 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 urging force of the switch pins 48, 54L, 54R.
- 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 such that the state in which the slide pin 58 is in contact with the lock pin 70 is maintained while the slide pin 58 is displaced from the displacement end Pmax1 to Pmax2.
- the notch 58e is engaged with the lock pin 70 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, the lock pin 70 is formed to be engaged.
- the notch 58e is provided with a guide surface 58f that guides the slide pin 58 away from the cylindrical portion 62 as the lock pin 70 enters the notch 58e.
- FIG. 7 is a diagram illustrating a control state when the valve is operating (during a normal lift operation).
- the drive of the solenoid 68 is turned off, so that the slide pin 58 is free of the urging force of the return spring 56 while being away from the camshaft 12. Therefore, 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.
- the valve stop operation of the present embodiment is an operation of displacing the switching pins 48, 54L, 54R in the retreating direction by the slide pin 58 using the rotational force of the camshaft 12, so that these switching pins 48, 54L, It needs to be performed when the axis of 54R is located in the same straight line, that is, when the first rocker arm 32 is not swinging.
- the guide rail 64 is set so that a section (slide section) in which the slide pin 58 is displaced 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 solenoid 68 is driven in order from the cylinder in which the base circle section first arrives, thereby, as shown in FIG. 58c is inserted into the guide rail 64, and the valve stop operation of each cylinder starts in order. Specifically, the protrusion 58c inserted into the guide rail 64 is guided by the guide rail 64, so that the rotational end of the camshaft 12 is utilized as shown in FIG. The slide operation of the slide pin 58 starts toward the Pmax2 side.
- the slide pin 58 is displaced at the displacement end Pmax2 in a state where the projection 58c abuts against the side wall surface (load receiving surface 64d) of the guide rail 64 and the urging force of the return spring 56 is received. Move towards.
- FIG. 9 is a diagram illustrating a control state when the slide operation is completed.
- 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 lock pin 70.
- 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 predetermined valve return operation such as a return request from a fuel cut is detected by the ECU 26.
- such valve return operation is earlier by a predetermined time required for the operation of the solenoid 68 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).
- a predetermined timing 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 turning off the energization of the solenoid 68 is started.
- the energization of the solenoid 68 is turned off, the engagement between the notch 58e of the slide pin 58 and the lock pin 70 is released.
- the slide pin is turned on using the energization ON / OFF of the solenoid 68, the rotational force of the camshaft 12, and the biasing force of the return spring 56.
- the operating state of the valve 18 can be switched between the valve operating state and the valve stopping state.
- FIG. 11 is a development view of the guide rail 64.
- the slide pin 58 receives the urging force of the return spring 56 via the switching pin 48 and the like. For this reason, when the slide pin 58 is guided by the guide rail 64 and moves from the displacement end Pmax1 to the displacement end Pmax2, the protrusion 58c of the slide pin 58 has one of the guide rails 64 as shown in FIG. In the state of being pressed against the side wall surface 64d, the guide rail 64 moves while resisting the urging force of the return spring 56.
- the side wall surface 64d is particularly referred to as a “load receiving surface 64d”.
- the load generated between the load receiving surface 64d and the projection 58c is expressed as “contact load”. ".
- the “surface pressure” generated between the load receiving surface 64d and the protrusion 58c is a value obtained by dividing the contact load by the contact area between the two.
- FIG. 12 is a diagram showing a configuration referred to for comparison with the configuration of the first embodiment of the present invention. More specifically, the figure shown in the lower part of FIG. 12A is a view of the slide pin and the guide rail viewed from the axial direction of the camshaft, and is shown in the upper part of FIG. The figure is a view of the slide pin and the guide rail as seen from the central axis direction of the protrusion of the slide pin.
- FIG. 12B is a cross-sectional view taken along line AA in FIG.
- the arrangement of the slide pins with respect to the guide rail is determined in a state where the center axis of the protrusion of the slide pin is separated from the center axis of the camshaft.
- FIG. 12B it can be seen that when such an arrangement method is used, the load receiving surface and the protrusion are in contact only at the upper portion of the load receiving surface of the guide rail. In such a contact mode, the contact area between the load receiving surface and the projection is reduced (point contact). For this reason, the surface pressure (contact load / contact area) produced between both becomes large.
- FIG. 13 is a diagram for explaining a method of arranging the slide pins 58 with respect to the guide rails 64 used in the first embodiment of the present invention.
- FIG. 13A in the present embodiment, in a state where the protrusion 58c of the slide pin 58 is protruded from the guide rail 64 by the actuator 66, the center axis of the protrusion 58c and the center axis ( The arrangement of the projections 58c with respect to the guide rail 64 is determined so that the spiral wall (the center axis of the load receiving surface 64d) intersects perpendicularly. According to such an arrangement method, as compared with the arrangement method shown in FIG.
- the side surface of the protrusion 58c and the load receiving surface 64d face each other in parallel as shown in FIG. 13B.
- the contact area between the load receiving surface 64d and the protrusion 58c increases (becomes linear contact), and the surface pressure generated between the two can be satisfactorily reduced.
- the reason why the contact area between the load receiving surface 64d and the protrusion 58c can be increased by the arrangement method of the present embodiment will be described in detail with reference to FIGS.
- FIG. 14 is a diagram for explaining that the manner of contact between the protrusion 58c and the load receiving surface 64d changes depending on the change in the location of the slide pin 58 with respect to the guide rail 64.
- FIG. 14A is a view of the slide pin 58 and the guide rail 64 viewed from the axial direction of the camshaft 12, and FIG. 14B is perpendicular to the central axis of the camshaft 12.
- 14C is a view of the slide pin 58 and the guide rail 64 viewed from the direction of a straight line (that is, the central axis of the protrusion 58c in the arrangement method of the present embodiment).
- FIG. 14C is a view in FIG. Each sectional view shown in FIG. Note that the pin position P2 in FIG.
- the pin position P1 is a guide while maintaining the central axis of the protrusion 58c parallel to the pin position P2.
- the protrusion 58c is arranged on the near side in the traveling direction of the protrusion 58c.
- the pin position P3 is a protrusion 58c disposed on the inner side of the guide rail 64 in the traveling direction of the protrusion 58c opposite to the pin position P1 with respect to the pin position P2.
- the contact area between the load receiving surface 64d and the protrusion 58c is increased at the pin position P2 to which the arrangement method of this embodiment is applied. It is related to the change in the inclination of the load receiving surface (side wall surface) 64d of the guide rail 64 having a spiral groove shape due to the change in the location of the slide pin 58 with respect to the guide rail 64. That is, the load receiving surface (side wall surface) 64d of the guide rail 64 is a groove cross section in FIG. 14C when viewed from the direction of a straight line perpendicular to the central axis of the camshaft 12 (groove bottom surface of the guide rail).
- the pin position P2 is a surface perpendicular to the groove bottom surface (parallel to the line of sight).
- the load receiving surface (side wall surface) 64d of the guide rail 64 is inclined with respect to the groove bottom surface.
- FIG. 15 is a view for explaining an operation when the guide rail 64 having a spiral groove shape is formed in the cylindrical portion 62.
- a cutting tool flat end mill
- the cylindrical portion 62 is positioned with respect to the tool so that the central axis of the cylindrical portion 62 intersects perpendicularly. In this state, the tool enters a predetermined groove depth. Then, in order to form a spiral groove shape, in a state where the tool enters the cylindrical portion 62, an operation of rotating the cylindrical portion 62 and moving it in the axial direction is performed.
- a point X1 and a point Y1 in FIG. 15A indicate the respective contact points between the lower end portion and the upper end portion of the side wall surface of the guide rail 64 and the tool at the moment of processing at the position shown in FIG. Yes.
- the diagram on the right side in FIG. 15A is a view looking down on the guide rail 64 from the central axis direction of the tool. When viewed from the direction of this figure, the point X1 and the point Y1 are at the same traveling position. In this figure, the point X1 and the point Y1 are slightly shifted so that they can be discriminated.
- FIG. 15B shows a state in which the cylindrical portion 62 has been rotated by 15 ° and processing has proceeded with respect to FIG. 15A.
- a point X2 and a point Y2 in FIG. 15B are points corresponding to the point X1 and the point Y1 at the moment of machining at the position shown in FIG. 15B.
- the point X1 and the point Y1 are different from each other in the traveling position when viewed from the direction shown on the right side of FIG. Will occur.
- the cylindrical part 62 at the time of processing also moves in the axial direction. For this reason, when viewed from the direction shown in the drawing on the right side of FIG.
- the point X1 on the inner diameter side and the point Y1 on the outer diameter side do not pass through the same position in the traveling direction of the guide rail 64.
- Y1 passes inside the point X1.
- the side wall surface of the guide rail 64 is inclined with respect to the bottom surface of the groove except for a portion where the center axis of the tool and the center axis of the cylindrical portion 62 intersect perpendicularly. The higher the height of the side wall surface of the guide rail 64 (i.e., the deeper the groove of the guide rail 64), the larger the inclination of the side wall surface. The inclination increases.
- the side surface of the protrusion 58c and the load receiving surface 64d are formed on the entire load receiving surface 64d. It comes in contact (becomes line contact). As described above, since the contact area between the load receiving surface 64d and the protrusion 58c is increased, it is possible to satisfactorily reduce the surface pressure generated between the both.
- 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.
- a member having an actuator having a mover functioning as a projection of the present invention and a member integrally including a cylindrical portion fixed with a guide rail and two types of cams is attached to the 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.
- the configuration including the guide rail 64 having a spiral groove shape has been described as an example.
- the guide rail in the present invention is not necessarily formed in a groove shape as long as it has a spiral wall portion that can be engaged with the projection portion in order to change the valve opening characteristic of the valve 18. Also good.
- 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. That is, the variable valve operating apparatus of the present invention is not limited to switching between the valve operating state and the valve stop state, and may be one that switches the lift amount and working angle of the valve in two stages.
- the load receiving surface 64d of the guide rail 64 corresponds to the “spiral wall portion” in the first invention.
- the variable valve operating apparatus of the present embodiment is configured in the same manner as the variable valve operating apparatus 10 of the first embodiment described above, except for the points described below.
- FIG. 16 is a view of the guide rail 64 as seen from the direction of a straight line perpendicular to the central axis of the camshaft 12.
- the inclination of the side wall surface of the guide rail 64 is remarkably expressed from the viewpoint of making the explanation easy to understand.
- FIG. 17 is a view showing a range in which the side surface of the protruding portion of the slide pin can be in line contact with the guide rail 64 having a spiral groove shape.
- the contact between the protrusion and the load receiving surface 64d is not a line contact but a contact in a band-like range having a certain width, but here, from the bottom to the top of the load receiving surface 64d. Because it aims to secure the contact length between the two, it is expressed as line contact.
- the load receiving surface 64d is present due to the inclination of the side wall surface of the guide rail 64. Is perpendicular to the groove bottom surface (that is, the range of the load receiving surface 64d that is parallel to the side surface of the protrusion). Then, the range in which such line contact is possible is a range in which the camshaft 12 (columnar portion 62) spreads out in a fan shape from the center to the outside as shown in FIG.
- the reason why the range of the load receiving surface 64d perpendicular to the groove bottom surface is fan-shaped is that the processing of the guide rail 64 has the center axis of the tool and the center axis of the cylindrical portion 62 as described above. This is because the cylindrical portion 62 is rotated in a state where the cylindrical portion 62 is positioned with respect to the tool so as to intersect perpendicularly.
- the protrusion when viewed from the axial direction of the camshaft 12 is used. It can be said that it is effective to form so as to fall within the fan-shaped range.
- FIG. 18 is a diagram for explaining the shape of the protrusion 80c of the slide pin 80 in the second embodiment of the present invention. Also in the present embodiment, in the state in which the projection 80c is projected toward the guide rail 64 by the actuator 66, the center axis of the camshaft 12 and the center axis of the projection 80c intersect perpendicularly with respect to the guide rail 64. The arrangement of the protrusions 80c is determined.
- the camshaft 12 is seen from the axial direction of the camshaft 12 in a state in which the protrusions 80 c are projected toward the guide rail 64 by the actuator 66.
- Projection 80c is formed so as to be narrowed toward the axial center. More specifically, the protrusion 80 c is formed so as to have a tapered shape with the tip end side becoming thinner as viewed from the axial direction of the camshaft 12. Thereby, when it sees from the axial direction of the cam shaft 12, it can form so that the projection part 80c may be settled in the said fan-shaped range.
- FIG. 19 is a diagram illustrating a contact state between the protrusion 80c and the load receiving surface 64d according to the second embodiment of the present invention.
- the protrusion 80c is formed so as to have a tapered shape with the tip end side becoming thinner as viewed from the axial direction of the camshaft 12.
- the protrusion of the present invention is formed so as to be narrowed down toward the axis of the camshaft when viewed from the axial direction of the camshaft in a state of being projected toward the guide rail by the actuator.
- the protrusion may have a shape that is narrowed down by a curve instead of a straight line when viewed from the axial direction of the camshaft, or is narrowed down in a stepwise manner toward the tip side.
- the protrusion may be a shape. Furthermore, when the idea of the shape of the protrusion in the present invention is broadly understood, the protrusion has a width at the tip portion that is smaller than the width of the root portion when viewed from the axial direction of the camshaft, and the root at the intermediate portion. What is necessary is just to be formed so that a width
- FIG. 20 is a diagram for explaining a general setting of the clearance between the guide rail 64 and the protrusion 58 c when the protrusion 58 c protrudes from the guide rail 64.
- the axial position of the camshaft 12 of the protrusion 58c relative to the guide rail 64 is the center of the protrusion 58c as shown in FIG.
- the guide rail 64 is set so as to coincide with the center of the groove width (that is, the left and right clearances are equal).
- the probability that the projection 58c and the side wall surface of the guide rail 64 interfere with each other in the straight section can be minimized. If the protrusion 58c is too close to the load receiving surface 64d side of the guide rail 64 in the straight section, the protrusion 58c and the groove upper surface of the guide rail 64 interfere with each other, and the protrusion 58c enters the guide rail 64. May not enter. On the other hand, if the protrusion 58c is too close to the facing surface 64e side of the guide rail 64, the protrusion 58c does not enter the guide rail 64 in the straight section, and the protrusion 58c protrudes in the subsequent inclined section (slide section). The portion 58 c can enter the guide rail 64. Therefore, in the prior art, there is a tendency that the protrusion is assembled close to the opposing surface side of the guide rail so that the engagement failure between the protrusion and the guide rail does not occur.
- FIG. 21 is a diagram for explaining a change in contact load according to the clearance between the protrusion 58c and the wall portion on the load receiving surface 64d side in the straight section of the guide rail 64.
- FIG. 21A shows an example in which the clearance between the protrusion 58c and the wall portion on the load receiving surface 64d side is small
- FIG. 21B shows the protrusion 58c on the load receiving surface 64d side. The example with a large clearance with a wall part is shown.
- the collision point between the protrusion 58c and the load receiving surface 64d is a position close to the straight section of the guide rail 64. Since such a position is a position where the wall portion of the guide rail 64 starts to slightly tilt with respect to the straight section, the angle at which the projection 58c and the load receiving surface 64d come into contact with each other becomes small. For this reason, the reaction force received by the protrusion 58c from the load receiving surface 64d is reduced, and the contact load generated between the two is reduced.
- FIG. 21B when the clearance is large, the collision point between the projection 58c and the load receiving surface 64d is far from the straight section of the guide rail 64 with respect to FIG.
- FIG. 22 is a view for explaining a method of guiding the protrusion 58 c using the spring plate 82.
- the configuration shown in FIG. 22 includes a spring plate 82 at a portion on the facing surface 64 e side in the straight section of the guide rail 64. According to such a configuration, the protrusion 58c can be guided to the load receiving surface 64d side by utilizing the repulsive force of the spring. Thereby, the clearance can be reduced, and the contact load generated between the protrusion 58c and the load receiving surface 64d can be reliably reduced.
- FIG. 23 is a view for explaining a method of guiding the protrusion 58 c using the permanent magnet 84.
- the configuration shown in FIG. 23 includes a permanent magnet 84 at a portion on the load receiving surface 64 d side in the straight section of the guide rail 64. According to such a configuration, the protrusion 58c can be guided to the load receiving surface 64d side using the magnetic force generated by the permanent magnet 84.
- FIG. 24 is a diagram for explaining a method for guiding the protrusion 58 c using the electromagnet 86.
- the configuration shown in FIG. 24 includes an electromagnet 86 at a portion on the load receiving surface 64 d side in the straight section of the guide rail 64. According to such a configuration, the electromagnet 86 is energized in synchronism with the operation of projecting the protrusion 58 c toward the guide rail 64 by the actuator 66, thereby loading the protrusion 58 c using the magnetic force generated by the electromagnet 86. It can be guided to the receiving surface 64d side.
- FIG. 25 is a view for explaining a method for guiding the protrusion 58 c using the oil injection nozzle 88.
- the configuration shown in FIG. 25 is provided with an oil injection nozzle 88 for injecting engine oil at a portion on the facing surface 64e side in the straight section of the guide rail 64.
- an oil passage is formed so that engine oil that lubricates each part of the internal combustion engine is also supplied to the oil injection nozzle 88, thereby discharging oil injected from the oil injection nozzle 88.
- the protrusion 58c can be guided to the load receiving surface 64d side by using force.
- Embodiment 3 a third embodiment of the present invention will be described with reference to FIGS.
- the variable valve operating apparatus of the present embodiment is obtained by further adding the configuration described below to the variable valve operating apparatus 10 having the configuration shown in FIGS. .
- FIG. 26 is a diagram for describing the shapes of the guide surfaces 90f and 92f provided on the protrusion 90c of the slide pin 90 and the groove upper portion of the guide rail 92 according to the third embodiment of the present invention. More specifically, FIG. 26 shows the center of the protrusion 90 c in a state where the protrusion 90 c of the slide pin 90 protrudes from the guide rail 92 by the actuator 66 between the tip of the protrusion 90 c and the groove upper portion of the guide rail 92. It is the figure seen from the normal line direction of the virtual plane containing the intersection line of an axis line and the center axis line of the camshaft.
- guide surfaces 90f and 92f for guiding the tip of the projection 90c inserted into the guide rail 92 are formed at the tip of the projection 90c and the groove upper portion of the guide rail 92, respectively. ing. More specifically, the guide surfaces 90f and 92f are formed by a load receiving surface (spiral) when the tip of the projection 90c and the groove upper portion of the guide rail 92 (the load receiving surface 92d thereof) are viewed from the normal direction. Shaped wall portion) 92d is formed as a surface inclined downward.
- FIG. 26A shows a state in which the protrusion 90 c and the guide rail 92 are in contact with each other when the protrusion 90 c is inserted into the guide rail 92. Such a contact state is caused by the axial displacement of the camshaft 12 between the protrusion 90c and the guide rail 92.
- the guide surfaces 90f and 92f are provided, as shown in FIG. 26 (A), even if the positional deviation occurs, the guide surfaces 90f and 92f project. The leading end of the portion 90 c is guided so as to fit into the guide rail 92. As a result, the positional deviation is corrected. For this reason, it is possible to ensure the insertion reliability of the protrusion 90c into the guide rail 92 while reducing the clearance between the protrusion 90c and the guide rail 92.
- FIG. 27 is a diagram for explaining the effect obtained by providing the guide surfaces 90f and 92f on the protrusion 90c and the guide rail 92.
- the guide surfaces 90f and 92f are provided, the protrusion 90c can be inserted (engaged) into the guide rail 92 without the clearance. Therefore, the arrangement of the protrusion 90c with respect to the guide rail 92 may be determined so that the protrusion 90c is inserted into the guide rail 92 while being always guided by the guide surfaces 90f and 92f without providing the clearance. .
- FIG. 27 is a diagram for explaining the effect obtained by providing the guide surfaces 90f and 92f on the protrusion 90c and the guide rail 92.
- the protrusion 90c contacts the side wall surface (load receiving surface 92d) of the guide rail 92 in the straight section.
- the acceleration ( ⁇ impact load) at the time of contact can be reduced as compared with the case where the projection 90c collides with the load receiving surface 92d of the guide rail 92 in the inclined section.
- a buffer portion (a part with a gentle inclination) provided to reduce the acceleration when the protrusion 90c contacts the load receiving surface 92d. ) Can be shortened.
- the length of the inclined section is constant and the stroke amount of the projection 90c guided by the guide rail 92 is constant, the inclination of the entire inclined section is moderated by shortening the buffer section. The acceleration ( ⁇ impact load) acting on the protrusion 90c when passing through the inclined section can be reduced.
- FIG. 28 is a diagram for explaining the centripetal force generated in the slide pin when the protrusion and the side wall surface of the guide rail come into contact with each other. Note that the description related to FIG. 28 is for a configuration that does not include the guide surfaces 90f and 92f of the present embodiment.
- a frictional force acts between the side wall surface rotating around the camshaft axis and the protrusion.
- a force (centripetal force) for pulling the protrusion to the center of the camshaft acts on the slide pin provided with the protrusion.
- the projection may be held in a state of being engaged with the guide rail even though it is not pushed by the actuator. Then, in a situation where a valve stop request is not issued, when the protrusion comes into contact with the side wall surface of the guide rail due to vibration generated by the internal combustion engine 1, the protrusion and guide rail are May engage and the slide pin may be displaced in the axial direction until the valve is stopped.
- FIG. 29 is a diagram illustrating the force acting on the guide surface 90f of the protrusion 90c when the guide surface 90f of the protrusion 90c comes into contact with the guide surface 92f of the guide rail 92.
- the guide surface 90f of the projection 90c exerts a vertical drag from the guide surface 92f. Will receive.
- the guide surface 90f of the projection 90c is biased to release the slide pin 90 (projection 90c) from the guide rail 92 (hereinafter referred to as “pin release biasing force”). Will act).
- the guide surface 90f of the protrusion 90c is brought into contact with the guide surface 90f even when the protrusion 90c comes into contact with the guide rail 92 due to vibration or the like generated by the internal combustion engine 1.
- the insertion of the projection 90c into the guide rail 92 can be restricted by the pin release biasing force that acts. Thereby, it is possible to prevent an unintended valve stop state from occurring due to the action of the centripetal force during the operation of the internal combustion engine 1.
- the guide surfaces 90f and 92f are provided on both the tip end portion of the projection 90c of the slide pin 90 and the groove upper portion of the guide rail 92.
- the present invention is not limited to such a configuration, and the guide surface as described above is provided only on one of the tip of the protrusion and the upper part of the spiral wall of the guide rail. It may be provided.
- the guide surfaces 90f and 92f are guided to reduce the contact load (impact load) by reducing the clearance between the protrusion 90c and the side wall surface of the guide rail 92.
- the arrangement of the protrusion 90c with respect to the guide rail 92 is determined so that the protrusion 90c is inserted into the guide rail 92.
- a configuration as shown in FIG. 30 below may be adopted.
- FIG. 30 is a diagram for explaining another configuration capable of reducing the contact load generated between the protrusion 90c of the slide pin 90 and the load receiving surface 94d of the guide rail 94.
- the straight section in the guide rail 94 shown in FIG. 30 is configured such that the groove width gradually decreases from the insertion position (pin insertion position) of the protrusion 90c toward the inclined section. According to such a configuration, at the pin insertion location, the clearance can be sufficiently secured, and the insertion reliability of the projection 90c into the guide rail 94 can be ensured.
- the protrusion 90c and the load receiving surface 94d can be brought into contact with each other in a straight section where the acceleration when the protrusion 90c contacts the load receiving surface 94d is small. .
- the said contact load can be reduced.
- the pin release urging force is obtained using the guide surfaces 90f and 92f.
- the configuration for obtaining such a pin release urging force is not limited to the above, and for example, the configuration shown in FIGS. 31 to 33 below may be used.
- FIG. 31 is a diagram for explaining a method for applying a pin release biasing force using the torsion coil spring 96.
- the configuration shown in FIG. 31 includes a torsion coil spring 96 wound around the rotation shaft of the slide pin 90.
- One end of the torsion coil spring 96 is hooked on a retaining portion 90g of the slide pin 90, and the other end is hooked on a support portion 98 provided in a stationary member of the internal combustion engine 1 such as a cam carrier.
- the pin discharge biasing force can be obtained using the repulsive force of the torsion coil spring 96.
- FIG. 32 is a diagram for explaining a method for applying a pin release urging force using the compression coil spring 100.
- the configuration shown in FIG. 32 includes a compression coil spring 100 having one end hooked to the slide pin 90 and the other end hooked to a support portion (not shown). According to such a configuration, the pin discharge biasing force can be obtained using the repulsive force of the compression coil spring 100.
- FIG. 33 is a diagram for explaining a method for applying a pin release urging force using the permanent magnet 102.
- the configuration shown in FIG. 33 includes an arm portion 90h extending on the opposite side to the arm portion 90b with respect to the rotation axis of the slide pin 90, and a permanent magnet 102 at a position close to the arm portion 90h.
- the pin release biasing force can be obtained using the attractive force of the permanent magnet 102.
- a tensile force of a pulling spring (not shown) may be used.
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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。
カムとバルブとの間に配置され、当該バルブの開弁特性を変更する可変機構と、
前記可変機構の動作状態を切り換える切換機構と、を備え、
前記切換機構は、
前記カムが備えられたカムシャフトの外周面に備えられ、螺旋状の壁部が設けられたガイドレールと、
前記螺旋状の壁部に係脱自在に配置された突起部と、
前記突起部が前記螺旋状の壁部と係合するように前記ガイドレールに向けて前記突起部を突き出し可能なアクチュエータと、を含み、
前記突起部と前記螺旋状の壁部との係合時に生ずる前記突起部と前記螺旋状の壁部との相対的な変位に伴って、前記可変機構の動作状態を切り換える機構であって、
前記アクチュエータによって前記突起部が前記ガイドレールに向けて突き出された状態において、前記突起部の中心軸線と前記カムシャフトの中心軸線とが垂直に交わるように、前記螺旋状の壁部に対する前記突起部の配置が決定されていることを特徴とする。
前記突起部は、前記カムシャフトの軸方向から見て、付け根部分の幅よりも先端部分の幅が小さくなり、かつ、中間部分において前記付け根部分よりも幅が大きくならないように形成されていることを特徴とする。
前記突起部は、前記アクチュエータによって前記ガイドレールに向けて突き出された状態において、前記カムシャフトの軸方向から見て、当該カムシャフトの軸心に向けて絞り込まれるように形成されていることを特徴とする。
前記突起部は、前記カムシャフトの軸方向から見て、先端側に細くなるテーパ状に形成されていることを特徴とする。
前記突起部の先端部分および前記螺旋状の壁部の上部のうちの少なくとも一方に、前記螺旋状の壁部に対して挿入される前記突起部の前記先端部分を案内するガイド面が形成されていることを特徴とする。
前記ガイド面は、前記突起部の前記先端部分および前記螺旋状の壁部の前記上部を、前記アクチュエータによって前記ガイドレールに向けて突き出された状態における前記突起部の中心軸線と前記カムシャフトの中心軸線との交線を含む仮想平面の法線方向から見て、前記螺旋状の壁部の下方側に傾斜する面であることを特徴とする。
10 可変動弁装置
12 カムシャフト
14 主カム
16 副カム
18 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
48 第1切換ピン
54L、54R 第2切換ピン
56 リターンスプリング
58、80、90 スライドピン
58c、80c、90c 突起部
62 円柱部
64、92、94 ガイドレール
64a 基端
64b 終端
64c 浅底部
64d、92d、94d 荷重受け面(側壁面)
64e 対向面(側壁面)
66 アクチュエータ
68 ソレノイド
70 ロックピン
82 バネ板
84、102 永久磁石
86 電磁石
88 オイル噴射ノズル
90f 突起部側のガイド面
92f ガイドレール側のガイド面
96 ねじりコイルばね
100 圧縮コイルばね
Pmax1、Pmax2 変位端
先ず、図1乃至図15を参照して、本発明の実施の形態1について説明する。
[可変動弁装置の全体構成]
図1は、本発明の実施の形態1の内燃機関1の可変動弁装置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)を有し、#1→#3→#4→#2の順で爆発行程が行われる直列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つの吸気バルブと2つの排気バルブとが備わっているものとする。そして、図1に示す構成は、各気筒に配設された2つの吸気バルブ、或いは2つの排気バルブを駆動する機構として機能するものとする。
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、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。尚、図6以降の図においては、ロックピン70とソレノイド68との関係を簡略化して図示している。
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、カムキャリア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、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、ソレノイド68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。本実施形態の弁停止動作は、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。
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をロックピン70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、ロックピン70がその退出方向に少し変位する。その後、ソレノイド68によって駆動され続けているロックピン70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、ロックピン70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ソレノイド68の動作に要する所定時間分だけ早いタイミング)でソレノイド68への通電をOFFとすることが開始される。ソレノイド68への通電がOFFとされると、スライドピン58の切欠部58eとロックピン70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可変動弁装置10によれば、ソレノイド68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。
図11は、ガイドレール64の展開図である。
スライドピン58は、切換ピン48等を介してリターンスプリング56の付勢力を受ける。このため、スライドピン58がガイドレール64に案内されて変位端Pmax1から変位端Pmax2に移動する際には、図11に示すように、スライドピン58の突起部58cは、ガイドレール64の一方の側壁面64dに押し付けられた状態で、リターンスプリング56の付勢力に抗しつつガイドレール64内を移動するようになる。ここでは、この側壁面64dを、特に「荷重受け面64d」と称する。そして、スライドピン58の突起部58cが荷重受け面64dに押し付けられた状態でガイドレール64内を摺動する際に、荷重受け面64dと突起部58cとの間に生ずる荷重を、「接触荷重」と称する。また、荷重受け面64dと突起部58cとの間に生ずる「面圧」は、上記接触荷重を両者の接触面積で除した値である。
図13は、本発明の実施の形態1において用いられる、ガイドレール64に対するスライドピン58の配置手法を説明するための図である。
図13(A)に示すように、本実施形態では、アクチュエータ66によってスライドピン58の突起部58cがガイドレール64に突き出された状態において、突起部58cの中心軸線とカムシャフト12の中心軸線(螺旋状の壁部(荷重受け面64d)の中心軸線)とが垂直に交わるように、ガイドレール64に対する突起部58cの配置が決定されている。このような配置手法によれば、上記図12に示す配置手法と比べ、図13(B)に示すように、突起部58cの側面と荷重受け面64dとが平行に対向するようになる。これにより、荷重受け面64dと突起部58cとの接触面積が大きくなり(線接触になり)、両者の間に生ずる面圧を良好に低減させることが可能となる。以下、図14乃至図16を参照して、本実施形態の配置手法によって、荷重受け面64dと突起部58cとの接触面積の拡大を図ることができる理由について詳述する。
切削用工具(フラットエンドミル)を用いて円柱部62の外周面に螺旋状のガイドレール64を形成する際には、図15(A)の左側の図が示すように、当該工具の中心軸線と円柱部62の中心軸線とが垂直に交わるように当該工具に対して円柱部62が位置決めされる。そして、この状態で、工具が所定の溝深さまで進入する。そして、螺旋状の溝形状を形成するために、工具が円柱部62に進入した状態で、円柱部62を回転させるとともに軸方向に対して移動させる動作が行われる。
以上説明した理由により、ピン位置P2に対してガイドレール64における突起部58cの進行方向の後方位置となるピン位置P1においてピン位置P2と同一方向からガイドレール64を見た場合には、図14(C)中の溝断面S1が示すように、ガイドレール64の荷重受け面(側壁面)64dは、溝の内側に向けて傾くことになる。このため、この場合には、上記図12で示したケースと同様に、突起部58cと荷重受け面64dとは、荷重受け面64dの上部のみにおいて接触するようになる(点接触となる)。また、ピン位置P2に対してガイドレール64における突起部58cの進行方向の前方位置となるピン位置P3においてピン位置P2と同一方向からガイドレール64を見た場合には、図14(C)中の溝断面S3が示すように、ガイドレール64の荷重受け面(側壁面)64dは、溝の外側に向けて傾くことになる。このため、この場合には、突起部58cと荷重受け面64dとは、荷重受け面64dの下部のみにおいて接触するようになる(点接触となる)。
次に、図16乃至図19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は、以下に説明する点を除き、上述した実施の形態1の可変動弁装置10と同様に構成されているものとする。
突起部58cと荷重受け面64dとの間に生ずる面圧を下げるためには、両者の接触面積を増やすことが望ましい。そのためには、両者の接触部を点接触から線接触のように広げることが望ましい。そして、両者の接触部を広げるためには、荷重受け面64dの底部から上部までの間で突起部58cとの接触が広く確保できるようになっていることが望ましい。
本実施形態においても、アクチュエータ66によって突起部80cがガイドレール64に向けて突き出された状態において、カムシャフト12の中心軸線と突起部80cの中心軸線とが垂直に交わるように、ガイドレール64に対する突起部80cの配置が決定されている。
上記のように形成された突起部80cを備えたことにより、荷重受け面64dとの局所的な接触が回避され、図19に示すように、突起部80cと荷重受け面64dとの接触範囲を、荷重受け面64dの底部から上部までの間でライン状に広く確保することが可能となる。このように、本実施形態の構成によれば、突起部80cと荷重受け面64dとの接触面積の増加によって、両者の間に生ずる面圧を効果的に低減させることができる。
次に、図20乃至図25を参照して、スライドピンの突起部とガイドレールの荷重受け面との間に生ずる接触荷重を低減させるための構成について説明する。尚、このような構成は、上述した実施の形態1、2の構成の何れに対しても付加的に適用可能なものであるが、ここでは、上述した実施の形態1の構成に対して適用された例について説明する。
ガイドレール64の直線区間において突起部58cがガイドレールに突き出された状態において、ガイドレール64に対する突起部58cのカムシャフト12の軸方向位置は、図20に示すように、突起部58cの中心とガイドレール64の溝幅の中心とが一致するように(すなわち、左右のクリアランスが同等となるように)設定されることが一般的である。このような設定によれば、組み付け誤差が発生しても、突起部58cとガイドレール64の側壁面とが直線区間において干渉する確率を最小にすることができる。また、直線区間において突起部58cがガイドレール64の荷重受け面64d側に寄り過ぎていると、突起部58cとガイドレール64の溝上面とが干渉して、突起部58cがガイドレール64内に入らなくなる可能性がある。逆に、突起部58cがガイドレール64の対向面64e側に寄り過ぎていた場合には、直線区間において突起部58cがガイドレール64内に入らなくてもその後の傾斜区間(スライド区間)において突起部58cがガイドレール64内に入ることができる。従って、従来においては、突起部とガイドレールとの係合不良が起きないように、突起部をガイドレールの対向面側に寄せて組み付ける傾向があった。
図22に示す構成は、ガイドレール64の直線区間における対向面64e側の部位に、バネ板82を備えたものである。このような構成によれば、バネの反発力を利用して突起部58cを荷重受け面64d側に誘導することができる。これにより、上記クリアランスを小さくすることができ、突起部58cと荷重受け面64dとの間に生ずる接触荷重を確実に低減させることができる。
図23に示す構成は、ガイドレール64の直線区間における荷重受け面64d側の部位に、永久磁石84を備えたものである。このような構成によれば、永久磁石84が発する磁力を利用して突起部58cを荷重受け面64d側に誘導することができる。
図24に示す構成は、ガイドレール64の直線区間における荷重受け面64d側の部位に、電磁石86を備えたものである。このような構成によれば、アクチュエータ66によって突起部58cをガイドレール64に向けて突き出す動作と同期させて電磁石86に通電を行うことにより、電磁石86が発する磁力を利用して突起部58cを荷重受け面64d側に誘導することができる。
図25に示す構成は、ガイドレール64の直線区間における対向面64e側の部位に、エンジンオイルを噴射するオイル噴射ノズル88を備えたものである。このような構成によれば、内燃機関の各部を潤滑するエンジンオイルがオイル噴射ノズル88にも供給されるように油路を形成しておくことで、オイル噴射ノズル88から噴射されるオイルの吐出力を利用して突起部58cを荷重受け面64d側に誘導することができる。
次に、図26乃至図29を参照して、本発明の実施の形態3について説明する。
本実施形態の可変動弁装置は、上述した実施の形態2における図18、19に示す構成を備える可変動弁装置10に対して、以下に説明する構成が更に加えられたものであるとする。
上記のガイド面90f、92fを備えるようにすれば、上記クリアランスが無くてもガイドレール92への突起部90cの挿入(係合)が可能となる。そこで、上記クリアランスを設けずに、常にガイド面90f、92fにより案内されながらガイドレール92への突起部90cの挿入が行われるように、ガイドレール92に対する突起部90cの配置を決定してもよい。これにより、図27に示すように、ガイドレール92の傾斜区間に突起部90cが到達する前に、直線区間において突起部90cがガイドレール92の側壁面(荷重受け面92d)に接触するように構成することができる。その結果、傾斜区間において突起部90cがガイドレール92の荷重受け面92dに衝突する場合と比べ、接触時の加速度(≒衝撃荷重)を低減することができる。
ガイドレールの側壁面とスライドピンの突起部とが接触した場合には、カムシャフトの軸心を中心として回転している上記側壁面と突起部との間に摩擦力が作用する。その結果、突起部が設けられたスライドピンに対して、突起部をカムシャフトの中心に引き込む力(向心力)が作用する。その結果、アクチュエータによって押されていないにも関わらず、突起部がガイドレールと係合した状態に保持されてしまう場合がある。そうすると、弁停止要求が出されていない状況下で、内燃機関1が発する振動等によって突起部がガイドレールの側壁面に接触してしまった場合に、上記向心力の作用によって突起部とガイドレールとが係合し、弁停止状態に至るまでスライドピンが軸方向に変位してしまうことが起こり得る。
本実施形態の構成では、図29に示すように、突起部90cのガイド面90fがガイドレール92のガイド面92fに押し付けられると、突起部90cのガイド面90fは、ガイド面92fから垂直抗力を受けることとなる。そして、このような垂直抗力が働くと、突起部90cのガイド面90fには、ガイドレール92からスライドピン90(突起部90c)を外側に放出させる付勢力(以下、「ピン放出付勢力」と称する)が作用することとなる。
また、上述した実施の形態3においては、突起部90cとガイドレール92の側壁面とのクリアランスの低減による接触荷重(衝撃荷重)の低減を図るために、上記ガイド面90f、92fにより案内されながらガイドレール92への突起部90cの挿入が行われるように、ガイドレール92に対する突起部90cの配置を決定している。しかしながら、上記の構成に代え、以下の図30に示すような構成を採用するようにしてもよい。
図30に示すガイドレール94における直線区間は、突起部90cの挿入箇所(ピン挿入箇所)から傾斜区間に近づくにつれ、溝幅が徐々に狭まるように構成されている。このような構成によれば、ピン挿入箇所においては、上記クリアランスを十分に確保して、ガイドレール94への突起部90cの挿入確実性を保証することができる。また、上記のような構成によれば、突起部90cが荷重受け面94dに接触する際の加速度が小さい区間である直線区間において、突起部90cと荷重受け面94dとが接触させられるようになる。これにより、傾斜区間において突起部90cが荷重受け面94dに衝突する場合と比べ、上記接触荷重を低減することができる。
また、上述した実施の形態3においては、上記ガイド面90f、92fを利用して、上記ピン放出付勢力を得るようにしている。しかしながら、このようなピン放出付勢力を得るための構成は、上記のものに限らず、例えば、以下の図31乃至図33に示すような構成であってもよい。
図31に示す構成は、スライドピン90の回転軸に巻き掛けられたねじりコイルばね96を備えている。ねじりコイルばね96の一端は、スライドピン90の掛留部90gに掛け留められており、その他端は、カムキャリア等の内燃機関1の静止部材が備える支持部98に掛け留められている。このような構成によれば、ねじりコイルばね96の反発力を利用して、上記ピン放出付勢力を得ることができる。
図32に示す構成は、一端がスライドピン90に掛け留められ、他端が図示省略する支持部に掛け留められた圧縮コイルばね100を備えている。このような構成によれば、圧縮コイルばね100の反発力を利用して、上記ピン放出付勢力を得ることができる。
図33に示す構成は、スライドピン90の回転軸に対してアーム部90bと反対側に延びるアーム部90hを備えるとともに、当該アーム部90hに近接する位置に、永久磁石102を備えている。このような構成によれば、永久磁石102の吸引力を利用して、上記ピン放出付勢力を得ることができる。尚、このような永久磁石102の吸引力に代え、引きばね(図示省略)の引張り力を利用するものであってもよい。
Claims (6)
- カムとバルブとの間に配置され、当該バルブの開弁特性を変更する可変機構と、
前記可変機構の動作状態を切り換える切換機構と、を備え、
前記切換機構は、
前記カムが備えられたカムシャフトの外周面に備えられ、螺旋状の壁部が設けられたガイドレールと、
前記螺旋状の壁部に係脱自在に配置された突起部と、
前記突起部が前記螺旋状の壁部と係合するように前記ガイドレールに向けて前記突起部を突き出し可能なアクチュエータと、を含み、
前記突起部と前記螺旋状の壁部との係合時に生ずる前記突起部と前記螺旋状の壁部との相対的な変位に伴って、前記可変機構の動作状態を切り換える機構であって、
前記アクチュエータによって前記突起部が前記ガイドレールに向けて突き出された状態において、前記突起部の中心軸線と前記カムシャフトの中心軸線とが垂直に交わるように、前記螺旋状の壁部に対する前記突起部の配置が決定されていることを特徴とする内燃機関の可変動弁装置。 - 前記突起部は、前記カムシャフトの軸方向から見て、付け根部分の幅よりも先端部分の幅が小さくなり、かつ、中間部分において前記付け根部分よりも幅が大きくならないように形成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、前記アクチュエータによって前記ガイドレールに向けて突き出された状態において、前記カムシャフトの軸方向から見て、当該カムシャフトの軸心に向けて絞り込まれるように形成されていることを特徴とする請求項2記載の内燃機関の可変動弁装置。
- 前記突起部は、前記カムシャフトの軸方向から見て、先端側に細くなるテーパ状に形成され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。
- 前記突起部の先端部分および前記螺旋状の壁部の上部のうちの少なくとも一方に、前記螺旋状の壁部に対して挿入される前記突起部の前記先端部分を案内するガイド面が形成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。
- 前記ガイド面は、前記突起部の前記先端部分および前記螺旋状の壁部の前記上部を、前記アクチュエータによって前記ガイドレールに向けて突き出された状態における前記突起部の中心軸線と前記カムシャフトの中心軸線との交線を含む仮想平面の法線方向から見て、前記螺旋状の壁部の下方側に傾斜する面であることを特徴とする請求項5記載の内燃機関可変動弁装置。
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DE112009005395.5T DE112009005395B4 (de) | 2009-11-25 | 2009-11-25 | Variable Ventilbetätigungsvorrichtung für einen Verbrennungsmotor |
JP2011543033A JP5273257B2 (ja) | 2009-11-25 | 2009-11-25 | 内燃機関の可変動弁装置 |
US13/500,671 US8955476B2 (en) | 2009-11-25 | 2009-11-25 | Variable valve operating apparatus for internal combustion engine |
PCT/JP2009/069876 WO2011064852A1 (ja) | 2009-11-25 | 2009-11-25 | 内燃機関の可変動弁装置 |
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US8955476B2 (en) | 2015-02-17 |
DE112009005395T5 (de) | 2012-09-06 |
US20120222635A1 (en) | 2012-09-06 |
JP5273257B2 (ja) | 2013-08-28 |
DE112009005395T8 (de) | 2012-11-08 |
JPWO2011064852A1 (ja) | 2013-04-11 |
DE112009005395B4 (de) | 2016-11-03 |
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