WO2003098013A1 - Dispositif d'entrainement de soupape de moteur - Google Patents
Dispositif d'entrainement de soupape de moteur Download PDFInfo
- Publication number
- WO2003098013A1 WO2003098013A1 PCT/JP2003/006236 JP0306236W WO03098013A1 WO 2003098013 A1 WO2003098013 A1 WO 2003098013A1 JP 0306236 W JP0306236 W JP 0306236W WO 03098013 A1 WO03098013 A1 WO 03098013A1
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- WO
- WIPO (PCT)
- Prior art keywords
- valve
- rocker
- rocking
- shaft
- swing
- 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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
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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
- F01L1/14—Tappets; Push rods
- F01L1/143—Tappets; Push rods for use with overhead camshafts
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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
- 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
- F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
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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
- F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
- F01L13/0026—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio by means of an eccentric
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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
- F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
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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
- F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
- F01L2013/0068—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type
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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
Definitions
- the present invention relates to a valve operating device for an engine capable of continuously controlling a valve opening period and a lift amount.
- Engine valve gears that enable continuous control of the valve opening period and lift amount have been put to practical use.
- this type of valve train there is a conventional one disclosed in, for example, Japanese Patent Publication No. 59-500002.
- a swinging member which is swingably driven by the camshaft is provided, and a swinging cam surface of the swinging member and a rocker arm.
- An intermediate rocker is interposed between the valve and the position of the intermediate opening roller to change the valve opening period and the lift amount continuously.
- the present invention has been made in view of the above-described conventional circumstances, and has as its object to provide an engine valve train that can continuously change the valve opening period and the lift amount with a simple structure. I have. Disclosure of the invention
- the invention according to claim 1 is characterized in that the swiveling arm, which is swingably supported by the swiveling shaft, is swung.
- a valve that opens and closes a valve opening of the combustion chamber by opening and closing the valve; and a oscillating member that is oscillated and that is oscillated by driving means.
- An intermediate mouth picker member disposed between the formed swing cam surface and the mouth pushing surface formed on the rocker arm and transmitting the operation of the swing cam surface to the rocking force pushing surface;
- An intermediate rocker moving mechanism for moving a contact point between the rocking cam surface and the rocker pressing surface of the intermediate opening member by rotating the shaft. The feature is that the amount can be adjusted continuously.
- the invention according to claim 2 is the device according to claim 1, wherein the intermediate rocker member is provided with an intermediate rocker roller via an intermediate rocker pin at an end of an intermediate arm portion, and the intermediate locker roller is formed by the swing cam surface.
- the intermediate rocker pin When the intermediate rocker pin is pressed, the intermediate rocker pin directly or through the intermediate arm portion presses the mouth-cutter pressing surface, and the intermediate rocking force moving mechanism is eccentrically eccentric from the rocking shaft in the middle of the rocker shaft.
- a pin is formed, and the base end of the intermediate arm is swingably connected to the eccentric pin.
- the driving means is a cam shaft disposed on a side opposite to a rocking force axis of the mouth arm with the swing member interposed therebetween.
- a base circle portion that does not change the valve lift amount even when the swing angle of the moving member changes and a lift portion that increases the valve lift amount as the swing angle increases are continuously formed.
- the opening portion and the maximum valve lift of the valve become smaller as the intermediate rocker roller and the intermediate rocker pin are moved toward the mouth locker shaft. It is characterized in that the valve open period and the maximum valve lift increase with the movement to the force axis side.
- the driving means is a cam shaft disposed on the same side of the rocking member as the rocker shaft of the rocker arm, and the rocking force surface is A base circle portion that does not change the valve lift amount even when the swing angle of the swing member changes and a lift portion that increases the valve lift amount as the swing angle increases are continuously formed.
- the lift section is arranged so as to be located on the side of the above-mentioned force axis, and the more the intermediate rocker roller and the intermediate rocker pin are moved to the side opposite to the rocker axis, the smaller the valve open period and the maximum valve lift amount become. It is characterized in that the opening period of the valve and the maximum valve lift increase with the movement toward the force axis.
- the invention according to claim 5 is the invention according to claim 3 or 4, wherein the camshaft is located in a space surrounded by straight lines connecting the swing center of the swing member and both ends of the swing cam surface and the swing cam surface. And a swing roller that is pressed by the roller.
- the invention according to claim 6 is the method according to any one of claims 3 to 5, wherein the swing member is rotated in a direction to suppress a weight of the swing member from acting on a valve spring that biases the valve to a closed state. It is characterized by having a balance spring that urges.
- the invention of claim 6 is the crankshaft type according to any one of claims 3 to 5, wherein the camshaft is formed by eccentrically integrating a disk-shaped cam plate with a drive shaft.
- the base end of the control rod is rotatably connected to the plate, and the distal end of the control rod is rotatably connected to the swing member.
- FIG. 1 is a cross-sectional side view of an engine valve gear according to a first embodiment of the present invention.
- FIG. 2 is a cross-sectional side view of the first embodiment.
- FIG. 3 is a front perspective view of the first embodiment.
- FIG. 4 is a front view of the first embodiment.
- FIG. 5 is a cam angle-lift characteristic diagram of the first embodiment.
- FIG. 6 is a sectional side view of the device according to the second embodiment of the present invention.
- FIG. 7 is a sectional side view of the device of the first embodiment.
- FIG. 8 is a sectional side view of the device according to the third embodiment of the present invention.
- FIG. 9 is a cross-sectional side view of the device according to the third embodiment.
- FIG. 10 is a front perspective view of the device according to the fourth embodiment of the present invention.
- FIG. 11 is a front view of the device of the fourth embodiment.
- FIG. 12 is a sectional side view of a device according to a fifth embodiment of the present invention.
- FIGS. 1 to 5 are views for explaining a first embodiment of the present invention.
- FIGS. 1 and 2 show a small opening state and a large opening state on the intake valve side of an engine valve train according to the present embodiment.
- 3 and 4 are front perspective and side views, respectively, and
- FIG. 5 is a cam angle-lift characteristic diagram for explaining the operation.
- reference numeral 1 denotes a valve device for opening and closing a valve opening that opens to the combustion chamber, and has the following structure.
- the left and right intake valve openings 2 b are formed in the combustion recess 2 a formed in the cylinder head 2 so as to form the top wall portion of the combustion chamber of the engine. b is led out to the external connection opening of the engine wall while being joined by the intake port 2c.
- Each of the intake valve openings 2 b is opened and closed by a valve head 3 a of the intake valve 3.
- the intake valve 3 is interposed between a retainer 4 mounted on the upper end of the valve shaft 3b so as to be unable to move in the axial direction and a spring seat 5 mounted on the seat surface of the cylinder head 2. Always biased in the closing direction by the valve spring 6.
- a valve operating device 7 is disposed above the intake valve 3, a valve operating device 7 is disposed.
- the valve operating device 7 swings a swing member 9 by an intake force shaft 8 functioning as swing member driving means.
- the rocker arm 11 is rotated by the rocking member 9 via the intermediate rocker 10, and the rocking arm 11 swings to move the intake valve 3 in the axial direction, thereby opening and closing the intake valve opening 1 b. It is configured to be.
- the intake camshaft 8 is disposed in parallel with a crankshaft (not shown), and is rotatably driven by a cam journal formed on the cylinder head 2 and a force cap mounted on an upper mating surface of the journal. And it is supported immovably in the direction perpendicular to the axis and in the axial direction.
- the intake camshaft 8 has one cam nose 8c common to the left and right intake valves, which includes a base circular portion 8a having a constant outer diameter and a lift sound
- the oscillating member 9 includes a pair of oscillating arms 9 supported by an oscillating shaft 12 arranged in parallel to the intake camshaft 8 and immovable in the direction perpendicular to the axis and in the axial direction. a, 9a, a rocking cam surface 9b formed so as to connect the tip portions (lower ends) of the rocking arm portions 9a, and the middle of the rocking arm portions 9a, 9a.
- a roller shaft 9c disposed in parallel with the swing shaft 12 and passing through the left and right swing arms 9a, 9a; and a swing roller rotatably supported by the roller shaft 9c. 9d.
- the oscillating roller 9d is always in rolling contact with the cam nozzle 8c.
- the rocking shaft 12 penetrates through the base (upper end) of the rocking arm 9a in a rockable manner.
- a pair of left and right balance springs 13 made of a coil spring are mounted on the swing shaft 12.
- One end 13a of this balance spring 13 is engaged with the edge of the swing arm 9a on the side opposite to the cam shaft between the swing shaft 12 and the roller shaft 9c, and the other end 13b is a cylinder. Locked to head 2.
- the balance spring 13 urges the swing member 9 so that the swing roller 9 d comes into contact with the cam nose 8 c of the intake camshaft 8, whereby the weight of the swing member 9 is applied to the valve spring 6. Avoid working.
- the oscillating cam surface 9b has a substantially plate shape in which a base circular portion 9e and a lift portion 9f are formed in a curved shape forming a continuous surface.
- the rocking member 9 has a base circular part 9 e with a rocker
- the lift portion 9f is disposed closer to the shaft 14 side so as to be positioned closer to the shaft 14 opposite to the opener shaft.
- the base circle portion 9 e is formed in an arc shape having a radius R1 with the center of the swing shaft 12 as the swing center a, so that the base circle portion 9 e presses the swing roller 9 d. During this period, even if the swing angle of the swing member 9 increases, the intake valve 3 is in the fully closed position and is not lifted.
- the lift portion 9f moves the intake valve 3 as the portion near the top of the lift portion 8b of the intake camshaft 8 presses the swing roller 9d, that is, as the swing angle of the swing member 9 increases.
- the lift section 9f includes a ramp section having a constant speed, an acceleration section in which the speed changes, and a lift section having a substantially constant speed.
- the rocker arm 11 is formed by integrally forming left and right arm portions 1 Id to extend forward (toward the intake valve) from a cylindrical base portion 1 lc, and the base portion 11 c is connected to the intake cam shaft 8. It is swingably supported by an opener shaft 14 arranged in parallel and on the cylinder axis side.
- a valve pressing surface 11a is formed at the lower end of the tip of each of the arms 11d so as to press a shim 3c mounted on the upper end of the valve shaft 3b of the intake valve 3.
- the upper edge of each arm section 1 1d has a rocker pin for the intermediate rocker 10
- 1b is formed so as to form an arc having a radius R2 centered on the swing center a of the swing member 9 when viewed in the camshaft direction when the valve is fully closed.
- the opening shaft 14 is configured so that its rotation angle position can be freely controlled by a drive mechanism (not shown).
- An eccentric pin portion 14a is formed in the middle of the mouth shaft 14 so as to have a smaller diameter than the other portions and to be eccentric radially outward from the shaft center b of the mouth shaft 14.
- the intermediate arm of the intermediate rocker 10 is attached to this eccentric pin 14a.
- a locking recess 10c formed at the base end of 10b is rotatably locked.
- the tip ends of a pair of left and right intermediate arms 10 b are connected and fixed to each other with a rocker pin 10 a extending in the direction of the cam shaft.
- Roller 10d is rotatably supported.
- the ends of the intermediate arms 1 Ob may be connected to each other by engaging the rocker pins 10a.
- the mouth roller 10 d is in rolling contact with the lower surface of the swing cam surface 9 b of the swing member 9, and the rocker pin 10 a is in sliding contact with the upper surface of the rocker pressing surface 1 lb of the rocker arm 11. ing.
- the rocker lever ratio is Lv / Lc, and the greater the lever ratio, the greater the cam nose height.
- the valve lift increases.
- the position of the intermediate rocker roller 10d and the intermediate rocker pin 10a of the intermediate rocker 10 is changed to the above-mentioned swing cam surface 9b by the drive mechanism by changing the rotation angle position of the mouth lock shaft 14 by the drive mechanism. It moves along a 1 lb surface, which continuously changes the valve opening angle and lift.
- the drive mechanism controls the rotation angle position of the opener shaft 14 such that, for example, the opening degree and the lift amount of the valve increase as the opening degree increases according to the opening degree of the accelerator pedal.
- the eccentric pin portion 14a of the opening shaft 14 has the oscillating cam surface 9b.
- the contact c between the rocker roller 10d and the rocking cam surface 9b is located farthest from the lift portion 9f. Further, since the contact point c is closest to the swing center b of the mouthpiece 11 and the Lc is the smallest, the mouth lever ratio (Lv / Lc) becomes maximum. Therefore, the lift curve is the curve in Fig. 5.
- the mouth shaft 14 rotates so that the eccentric pin 14 a comes closest to the swing cam surface 9 b side.
- the contact point c 'of the intermediate rocker roller 10d with the swing cam surface 9b of the intermediate rocker roller 10d is located closest to the lift section 9f, more specifically, the lift section 9f and the base circle section 9e. It is located near the boundary with.
- the rocker lever ratio (Lv / Lc) is minimized because the contact point c 'is separated from the rocking center b of the rocker arm 11 and the above Lc is maximized. Therefore, the lift curve becomes curve C3 in FIG. Then, as the state shifts from the small opening state to the large opening state, the lift force continuously changes from the curve C1 to the curve C3 in FIG.
- the curves C 1 ′ to C 3 ′ in FIG. 5 show the lift curves of the comparative example when the rock lever ratio is constant. That is, this comparative example device was set so as to have the same characteristics as the lift curve in the large opening state of the present invention, and the change in the lift amount when shifting to the small opening state side from here was compared. It is. As is clear from the figure, in the case of the comparative example device in which the rocker lever ratio is constant, the comparison is made with the same opening compared to the present embodiment in which the mouth opening lever ratio is set larger in the small opening state side. The amount of lift in the case is large.
- the outer part of the valve opening period represents a ramp section having a lift height corresponding to the valve clearance.
- the valve clearance in the cold state is such that the valve clearance is low. Because of this, it does not open, and in the hot operating state, it opens slightly from near the end of the ramp section due to thermal expansion of the bulb shaft.
- the swing member 9 swings with the rotation of the cam shaft 8, and the swing cam surface 9b of the swing member 9 swings the intermediate rocker roller 10d with the swing of the swing member 9.
- the intermediate rocker member 10 is rocked by being pressed, the intermediate rocker pin 10a of the intermediate rocker member 10 drives the rocker arm 11 to rock, and the rocking arm 11 opens the intake valve 3. Drive closed.
- the phase of the valve lift curve does not change at all between the large opening and the small opening, so that the versatility is high. That is, for example, a common mechanism and common components can be used for the left and right banks of the V-type engine.
- the structure Since the rotation of the opening shaft 14 is used to move the intermediate rocker member 10, the structure is very simple, and as a result, the valve opening period and the maximum lift amount can be controlled. Accuracy can be increased.
- the valve can be continuously moved along the pressing surface 11b, and the valve opening period and the lift amount can be continuously changed by a very simple structure.
- the opener shaft 14 which is the rocking center of the rocker arm 11 and the eccentric pin portion 14a which is the rocking center of the intermediate rocker member 10 are located close to each other, the opening and closing of the valve The amount of slip between the intermediate rocker pin 10a of the intermediate rocker member 10 and the rocker pressing surface 11b of the rocker arm 11 can be significantly reduced.
- the cam when viewed in the cam axis direction, the cam is located in a space surrounded by each straight line connecting the swing center a of the swing member 9 and both ends of the swing cam surface 9 and the swing cam surface 9 b. Since the oscillating roller 9 d pressed by the shaft is provided, the bending moment generated in the supporting portion of the oscillating roller 9 d by the rotational force of the camshaft 8 is transmitted to the oscillating port, for example, as in the prior art described above. —The size of the swinging member can be reduced as compared with the case where the roller is supported on the tip of a separate arm, and as a result the rigidity of the swinging member can be increased.
- a balance spring 13 which urges the oscillating member 9 to rotate in a direction to suppress the weight of the oscillating member 9 from acting on the valve spring 6 which urges the valve to the closed state. Therefore, the provision of the swing member 9 does not increase the load on the valve spring 6. Therefore, it is not necessary to set a large spring load of the valve spring 6, and the followability of the valve during high-speed rotation can be secured.
- FIG. 6 and 7 are views for explaining the second embodiment according to the fourth aspect of the present invention.
- the same reference numerals as those in FIG. 2 denote the same or corresponding parts.
- the drum shaft 8 and the oscillating member 9 are arranged symmetrically with respect to the first embodiment with the straight line A interposed therebetween.
- the cam shaft 8 is disposed on the same side of the rocker member 9 as the mouth shaft 14 of the rocker arm 11.
- the swinging member 9 is arranged so that the lift portion 9f is located on the side of the mouth shaft 14 and has an intermediate opening roller 10 and an intermediate opening pin 10.
- the intermediate rocker roller 10 Od and the intermediate rocking pin 10 a of the intermediate rocker member 10 are not connected.
- FIG. 8 and 9 are views for explaining the third embodiment of the present invention, in which the same reference numerals as those shown in FIG. 2 denote the same or corresponding parts.
- the third embodiment is an example in which the camshaft is a crankshaft. That is, the crankshaft (camshaft) 18 is formed by integrating a disc-shaped cam plate 19b eccentrically with respect to the drive shaft 19a in the middle of the drive shaft 19a. A base end portion 20a of a plate-shaped connecting rod 20 is rotatably mounted on the cam plate 19b, and a distal end portion 20b of the connecting rod 10 is provided on the rocking member 9. It is rotatably connected to the roller shaft 9c.
- the cam plate 19b is eccentrically rotated about the axis d of the drive shaft 19a, whereby the connecting rod 20 is rotated.
- the rocker arm 1 is moved through the intermediate rocker member 10 by the rocking motion. 1 drives the intake valve 3 to open and close.
- the camshaft is constituted by the crank system
- the swing member 9 can be easily and reliably swung with good followability, and the valve opening period and the lift amount can be controlled with high accuracy. Further, the need for a balance spring is eliminated.
- FIGS. 10 and 11 are diagrams for explaining the fourth embodiment of the present invention.
- the same reference numerals as those in FIG. 2 denote the same or corresponding parts.
- the fourth embodiment is an example in which the left and right intake valves 3, 3 'are provided with independent valve operating devices 7, 7, respectively. Specifically, the left and right swing members 9 and 9 ′ are swung by the left and right cam nose 8 c and 8 c ′ of the intake camshaft 8, and the left and right swing members 9 and 9 ′ are moved by the swing members 9 and 9 ′.
- the left and right rocker arms 1 and 1 ⁇ are oscillated via the left and right intermediate mouth lockers 10 and 10 ', and the intake valves 3, 3 ′ Is moved back and forth in the axial direction, thereby opening and closing the intake valve openings 2 b and 2 b ′.
- the left and right valve trains 7 and 7 ' are provided independently, the left and right cam nose 8c and 8c' and the left and right swing cam surfaces 9b are provided. , 9b ', and the left and right intake valves 3, 3' can be operated with different timings and valve lifts by appropriately setting the shape and dimensions of the left and right intermediate rockers 10, 10 '. It is possible.
- FIG. 12 is for explaining the fifth embodiment of the present invention, and the same reference numerals as those in FIGS. 9 and 10 indicate the same or corresponding parts.
- the intermediate rocker roller 10 d is pressed by the rocking cam surface 9 b of the rocking member 9, and the pressing portion 1 Oe is pressed on the side of the tip of the intermediate arm portion 1 Ob with the rocker arm 11 in the vertical direction.
- the mouthpiece pressing surface 11b of the mouthpiece 11 is pressed by a pressing surface 10f formed on the lower surface of the tip of the pressing portion 10e.
- the intermediate rocker 10 is formed such that the base end of the intermediate arm 1Ob is bifurcated and mounted on the eccentric pin 14a. Pinch As described above, the locking pin 10g is penetrated and attached to the forked portion so as to be rotatably connected to the mouth opening shaft 14.
- the rocker arm 11 is pressed by the pressing surface 1 Off having a large radius of curvature formed on the intermediate rocker 10.
- the contact stress on the mouth pressing surface can be reduced, and the number of parts can be reduced.
- the swing member 9 is supported by the swing shaft 12 .
- the swing member 9 may be supported by a spherical pivot.
- the drive means for swinging the swing member 9 is the camshaft 8 or 18.
- the drive means is not limited to the camshaft 8, but may be a solenoid type cylinder type. In other words, any type can be adopted as long as it can swing drive the swinging member 9 at a speed corresponding to the engine rotation speed.
- the rocking cam surface of the rocking member rocks the rocker arm via the intermediate rocker member, and the rocking arm is Open and close the valve.
- the intermediate force moving mechanism rotates the rocking force shaft, the contact point between the rocking force surface and the force pressing surface of the intermediate mouth catcher member moves continuously, thereby opening the valve.
- the period and the maximum lift can be continuously adjusted.
- the rotation operation of the rocking force shaft is used to move the intermediate rocking force member, so the structure is very simple, and as a result, the valve The control accuracy of the open period and the maximum lift can be improved.
- the intermediate rocker roller and the intermediate rocker pin are arranged at the distal end of the intermediate rocker member, and the base end of the intermediate rocker member can swing on the eccentric pin formed in the middle of the rocker shaft.
- the intermediate opener roller and intermediate opener pin can be moved continuously along the swing cam surface and the opener pressing surface, and the valve opening period and lift amount can be continuously reduced by a very simple structure. Can be changed to
- the intermediate rocking member accompanying opening and closing of the valve is provided.
- the amount of slip between the intermediate pin or the intermediate arm and the mouth pressing surface of the mouth arm can be greatly reduced.
- the swing member swings the rocker arm via the intermediate opening member by the rotation of the force shaft, and the valve is driven to open and close.
- the opening period and the maximum valve lift amount of the valve become smaller as the intermediate rocker member is moved toward the rocking force shaft side, and the valve opening period and the maximum valve lift amount become larger as the intermediate rocker member is moved toward the non-opener shaft side.
- rocker lever ratio Lv / Lc is large, and it is easy to secure the maximum valve lift in spite of the short valve opening period. Therefore, it is possible to reduce the bombing loss and improve the combustion, prevent the ramp speed from decreasing, and improve the controllability of the valve opening / closing timing.
- the swing member swings the rocker arm via the intermediate rocker member by the rotation of the cam shaft, and the valve is driven to open and close.
- the middle rocker The opening period and the maximum valve lift amount of the valve become smaller as the member is moved toward the non-mouth shaft side, and the valve opening period and the maximum valve lift amount become larger as the member is moved toward the locking force shaft side.
- the cam shaft is pressed into a space surrounded by each straight line connecting the swing center of the swing member and both ends of the swing cam surface and the swing cam surface. Since the swinging roller is provided, the bending moment acting on the supporting portion of the swinging roller due to the rotational force of the camshaft can be reduced, and as a result, the rigidity of the swinging member can be increased.
- a structure in which the swing roller is supported at the tip of the arm is employed, so that a large bending moment acts on the base of the arm, which is disadvantageous in securing rigidity.
- the balance spring for rotatingly biasing the swinging member in a direction for suppressing the weight of the swinging member from acting on the valve spring for biasing the valve to the closed state. Since the swing member is provided, the load on the valve spring does not increase. Therefore, it is not necessary to set a large spring load of the valve spring, and it is possible to secure the followability of the valve during high-speed rotation while avoiding an increase in the loss horsepower due to the valve spring.
- the force shaft is of a crankshaft type having a cam plate, and the cam plate and the swinging member are connected by a connector, so that the swinging member can follow the swinging member easily and reliably. The swing drive can be performed with good efficiency, and the control accuracy of the valve opening angle and lift can be improved.
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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AU2003244097A AU2003244097A1 (en) | 2002-05-17 | 2003-05-19 | Engine valve driver |
JP2004505512A JP4276621B2 (ja) | 2002-05-17 | 2003-05-19 | エンジンの動弁装置 |
EP03752676.1A EP1515009B1 (en) | 2002-05-17 | 2003-05-19 | Engine valve driver |
CA002486440A CA2486440A1 (en) | 2002-05-17 | 2003-05-19 | Valve train device for engine |
US10/990,619 US7069890B2 (en) | 2002-05-17 | 2004-11-17 | Valve train device for an engine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002143036 | 2002-05-17 | ||
JP2002/143036 | 2002-05-17 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/990,619 Continuation US7069890B2 (en) | 2002-05-17 | 2004-11-17 | Valve train device for an engine |
Publications (1)
Publication Number | Publication Date |
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WO2003098013A1 true WO2003098013A1 (fr) | 2003-11-27 |
Family
ID=29545008
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/006236 WO2003098013A1 (fr) | 2002-05-17 | 2003-05-19 | Dispositif d'entrainement de soupape de moteur |
Country Status (6)
Country | Link |
---|---|
US (1) | US7069890B2 (ja) |
EP (1) | EP1515009B1 (ja) |
JP (1) | JP4276621B2 (ja) |
AU (1) | AU2003244097A1 (ja) |
CA (1) | CA2486440A1 (ja) |
WO (1) | WO2003098013A1 (ja) |
Cited By (3)
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JP2008157034A (ja) * | 2006-12-20 | 2008-07-10 | Yamaha Motor Co Ltd | エンジンの連続可変式動弁装置 |
CN100406691C (zh) * | 2004-02-17 | 2008-07-30 | 本田技研工业株式会社 | 用于内燃机的气门机构 |
JP2009133289A (ja) * | 2007-12-03 | 2009-06-18 | Ogino Kogyo Kk | エンジンの動弁装置 |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
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CA2518949A1 (en) | 2003-03-11 | 2004-09-23 | Yamaha Hatsudoki Kabushiki Kaisha | Variable valve mechanism for internal combustion engine |
JP4248344B2 (ja) | 2003-05-01 | 2009-04-02 | ヤマハ発動機株式会社 | エンジンの動弁装置 |
JP4248343B2 (ja) * | 2003-05-01 | 2009-04-02 | ヤマハ発動機株式会社 | エンジンの動弁装置 |
JP2005069014A (ja) * | 2003-08-25 | 2005-03-17 | Yamaha Motor Co Ltd | 内燃機関の動弁機構 |
ITTO20050326A1 (it) * | 2005-05-12 | 2006-11-13 | Luigi Conti | Motore a combustione interna con valvole ad alzata variabile |
JP2006329084A (ja) | 2005-05-26 | 2006-12-07 | Yamaha Motor Co Ltd | エンジンの動弁装置 |
JP2006329164A (ja) * | 2005-05-30 | 2006-12-07 | Yamaha Motor Co Ltd | 複数気筒エンジン |
EP1923546B1 (en) * | 2005-09-08 | 2012-06-06 | Honda Motor Co., Ltd. | Valve drive device for engine |
JP5174547B2 (ja) * | 2007-07-10 | 2013-04-03 | ヤマハ発動機株式会社 | 吸気システムおよびそれを備えた自動二輪車 |
KR100986355B1 (ko) * | 2008-07-23 | 2010-10-08 | 현대자동차주식회사 | 슬라이드형 연속 가변 밸브 리프트 장치 |
RU2476691C2 (ru) * | 2009-03-26 | 2013-02-27 | Федеральное государственное унитарное предприятие "Центральный ордена Трудового Красного Знамени научно-исследовательский автомобильный и автомоторный институт "НАМИ" | Регулируемый привод клапана впуска рабочей среды в цилиндр двигателя |
CN103147818B (zh) * | 2013-02-28 | 2015-05-06 | 长城汽车股份有限公司 | 可变气门升程驱动装置、发动机和车辆 |
CN103161538B (zh) * | 2013-02-28 | 2015-04-22 | 长城汽车股份有限公司 | 用于发动机的可变气门升程驱动装置的摇臂机构 |
DE102016114664A1 (de) * | 2015-10-08 | 2017-04-13 | Toyota Jidosha Kabushiki Kaisha | Ventilbetätigungsvorrichtung für eine Brennkraftmaschine |
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US5189998A (en) * | 1991-07-23 | 1993-03-02 | Atsugi Unisia Corporation | Valve mechanism of internal combustion engine |
JPH1136833A (ja) * | 1997-07-22 | 1999-02-09 | Otix:Kk | 可変動弁機構 |
US20010052329A1 (en) * | 2000-02-11 | 2001-12-20 | Frank Himsel | Variable valve drive for load control of a positive ignition internal combustion engine |
JP2003106123A (ja) * | 2001-09-28 | 2003-04-09 | Otics Corp | 可変動弁機構 |
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DE3519319A1 (de) * | 1985-05-30 | 1986-12-04 | Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart | Variable ventilsteuerung fuer eine hubkolben-brennkraftmaschine |
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2003
- 2003-05-19 EP EP03752676.1A patent/EP1515009B1/en not_active Expired - Lifetime
- 2003-05-19 JP JP2004505512A patent/JP4276621B2/ja not_active Expired - Fee Related
- 2003-05-19 CA CA002486440A patent/CA2486440A1/en not_active Abandoned
- 2003-05-19 AU AU2003244097A patent/AU2003244097A1/en not_active Abandoned
- 2003-05-19 WO PCT/JP2003/006236 patent/WO2003098013A1/ja active Application Filing
-
2004
- 2004-11-17 US US10/990,619 patent/US7069890B2/en not_active Expired - Lifetime
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US4572118A (en) * | 1981-12-31 | 1986-02-25 | Michel Baguena | Variable valve timing for four-stroke engines |
US5189998A (en) * | 1991-07-23 | 1993-03-02 | Atsugi Unisia Corporation | Valve mechanism of internal combustion engine |
JPH1136833A (ja) * | 1997-07-22 | 1999-02-09 | Otix:Kk | 可変動弁機構 |
US20010052329A1 (en) * | 2000-02-11 | 2001-12-20 | Frank Himsel | Variable valve drive for load control of a positive ignition internal combustion engine |
JP2003106123A (ja) * | 2001-09-28 | 2003-04-09 | Otics Corp | 可変動弁機構 |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN100406691C (zh) * | 2004-02-17 | 2008-07-30 | 本田技研工业株式会社 | 用于内燃机的气门机构 |
JP2008157034A (ja) * | 2006-12-20 | 2008-07-10 | Yamaha Motor Co Ltd | エンジンの連続可変式動弁装置 |
JP4726775B2 (ja) * | 2006-12-20 | 2011-07-20 | ヤマハ発動機株式会社 | エンジンの連続可変式動弁装置 |
JP2009133289A (ja) * | 2007-12-03 | 2009-06-18 | Ogino Kogyo Kk | エンジンの動弁装置 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2003098013A1 (ja) | 2005-09-15 |
JP4276621B2 (ja) | 2009-06-10 |
EP1515009A4 (en) | 2011-06-29 |
US20050229882A1 (en) | 2005-10-20 |
EP1515009B1 (en) | 2013-04-17 |
US7069890B2 (en) | 2006-07-04 |
CA2486440A1 (en) | 2003-11-27 |
EP1515009A1 (en) | 2005-03-16 |
AU2003244097A1 (en) | 2003-12-02 |
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