WO2011125194A1 - Actionneur de soupape pour moteur à combustion interne - Google Patents

Actionneur de soupape pour moteur à combustion interne Download PDF

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Publication number
WO2011125194A1
WO2011125194A1 PCT/JP2010/056332 JP2010056332W WO2011125194A1 WO 2011125194 A1 WO2011125194 A1 WO 2011125194A1 JP 2010056332 W JP2010056332 W JP 2010056332W WO 2011125194 A1 WO2011125194 A1 WO 2011125194A1
Authority
WO
WIPO (PCT)
Prior art keywords
rocker arm
internal combustion
combustion engine
valve
cam
Prior art date
Application number
PCT/JP2010/056332
Other languages
English (en)
Japanese (ja)
Inventor
明彦 川田
昭夫 木戸岡
Original Assignee
トヨタ自動車株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by トヨタ自動車株式会社 filed Critical トヨタ自動車株式会社
Priority to PCT/JP2010/056332 priority Critical patent/WO2011125194A1/fr
Priority to JP2012509239A priority patent/JP5299564B2/ja
Priority to CN2010800660020A priority patent/CN102892979A/zh
Priority to EP10849438.6A priority patent/EP2557280A4/fr
Priority to US13/636,554 priority patent/US20130042830A1/en
Publication of WO2011125194A1 publication Critical patent/WO2011125194A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/185—Overhead end-pivot rocking arms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—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
    • 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
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F01L2001/467—Lost motion springs
    • 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
    • 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 valve operating apparatus for an internal combustion engine.
  • Patent Document 1 discloses a valve operating apparatus for an internal combustion engine.
  • This conventional valve gear includes a lost motion mechanism that biases the rocker arm in one direction.
  • a cylinder head on which the valve operating device is mounted includes a boss formed by casting around a spark plug insertion cylinder (ignition plug tube).
  • the lost motion mechanism is supported by the boss portion.
  • the boss part (support part) for supporting the urging means such as the lost motion mechanism is formed on the upper surface of the cylinder head by casting as in the conventional technique described above, the molten metal once lowered is again directed upward. There is a need to guide. For this reason, when the fluidity of the molten metal is taken into consideration, the shape of the boss portion is poor in manufacturability and has a lot of meat. As a result, the mass of the internal combustion engine increased, which was a factor that deteriorated the fuel efficiency of the vehicle.
  • An object of the present invention is to provide a valve operating device for an internal combustion engine that can realize easy manufacture and suppression of mass increase of the internal combustion engine.
  • 1st invention is a valve operating apparatus of an internal combustion engine, A transmission member that is interposed between the cam and the valve and transmits the acting force of the cam to the valve; Biasing means for biasing the transmission member in one direction; A holding member for holding the biasing means; With The biasing means is attached to the spark plug tube via the holding member.
  • the second invention is the first invention, wherein
  • the transmission member includes a first rocker arm that swings in synchronization with rotation of the cam,
  • the biasing means is a means for biasing the first rocker arm toward the cam.
  • the third invention is the second invention, wherein The holding member is attached to the spark plug tube in a manner rotatable in the circumferential direction of the spark plug tube,
  • the valve operating apparatus for the internal combustion engine includes: An engagement groove formed in one of the urging means and the first rocker arm at a contact portion between the urging means and the first rocker arm; In the contact portion, a protrusion formed on the other of the biasing means and the first rocker arm, and engaging with the engagement groove; Is further provided.
  • 4th invention is 2nd or 3rd invention
  • the transmission member further includes a second rocker arm capable of pushing the valve
  • the valve operating apparatus of the internal combustion engine further includes a switching mechanism capable of switching between a connected state in which the first rocker arm and the second rocker arm are connected and a non-connected state in which the connection is released.
  • the urging means is a lost motion mechanism that urges the first rocker arm so that the first rocker arm is in contact with the cam.
  • the fifth invention is the first or second invention, wherein
  • the biasing means is a lash adjuster that has a function of expanding and contracting so as to make the tappet clearance zero, and is arranged so as to support a fulcrum of the transmission member.
  • the holding member includes a holding portion that covers the body portion of the urging means from the outside, and an attachment portion that is attached to the spark plug tube.
  • the seventh invention is the sixth invention, wherein
  • the cross-sectional shape of the holding portion is a shape obtained by enlarging the cross-sectional shape of the urging means.
  • an eighth invention is any one of the first to seventh inventions, An end of the urging unit opposite to the end contacting the transmission member is received by a base member to which the spark plug tube is fixed.
  • the support portion of the biasing means it is not necessary to form the support portion of the biasing means on the upper surface of the base member such as a cylinder head on which the valve operating device is mounted.
  • the boss portion (supporting portion) containing the waste meat becomes unnecessary, it is possible to facilitate the manufacture of the supporting portion and reduce the mass of the internal combustion engine. For this reason, the deterioration of the fuel consumption performance of the vehicle due to the increase in mass can be prevented.
  • the transmission member including the first rocker arm that swings in synchronization with the cam, and the biasing means for biasing the first rocker arm toward the cam
  • the valve operating apparatus configured as a lost motion mechanism in which the urging means urges the first rocker arm toward the cam, the manufacturing of the support portion of the lost motion mechanism is facilitated and the internal combustion engine Can be reduced.
  • the manufacture of the support portion of the lash adjuster is facilitated and the mass of the internal combustion engine is reduced. be able to.
  • the sixth aspect of the invention in the configuration including the holding member including the holding portion and the mounting portion, it is possible to facilitate the manufacture of the supporting portion of the urging means and reduce the mass of the internal combustion engine.
  • the weight of the holding member can be reduced.
  • the holding member is responsible for only the guide function for guiding the urging means, and the urging force of the urging means is handled by the base member.
  • the holding member since the force acting on the holding member can be reduced, the weight of the holding member can be reduced.
  • FIG. 1 It is a perspective view which shows the structure of the variable valve apparatus of Embodiment 1 of this invention. It is a fragmentary sectional view which shows the structure of the variable valve apparatus shown in FIG. It is a perspective view for demonstrating the characteristic support structure of the lost motion mechanism in Embodiment 1 of this invention. It is a perspective view showing the external shape of the holding member shown in FIG. It is a figure for demonstrating the structure with which a variable valve apparatus is provided in order to position a 1st rocker arm and a lost motion mechanism. It is a figure for demonstrating the effect by the support structure of the lost motion mechanism in Embodiment 1 of this invention.
  • Embodiment 1 FIG. [Basic configuration of valve gear according to Embodiment 1]
  • the valve operating apparatus for an internal combustion engine according to Embodiment 1 of the present invention is configured as a variable valve operating apparatus capable of switching the operating state of a valve between a valve operating state and a valve closing / stopping state.
  • FIG. 1 is a perspective view showing a configuration of a variable valve operating apparatus 10 according to a first embodiment of the present invention.
  • FIG. 2 is a partial cross-sectional view showing the configuration of the variable valve apparatus 10 shown in FIG. More specifically, FIG. 1 shows the configuration of a variable valve operating apparatus 10 for a cylinder having an internal combustion engine. 2A is a plane including the axis line of the rocker shaft 22 and the axis lines of the switching pins 36, 38, and 44, and a part of the variable valve operating apparatus 10 (the rocker arms 18 and 20 and the rocker shaft 22). It is the fragmentary sectional view expressed by cut.
  • each cylinder of the internal combustion engine is provided with two intake valves and two exhaust valves.
  • the configuration shown in FIGS. 1 and 2 functions as a device that drives 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 one sub cam 16 per cylinder.
  • the main cam 14 includes an arc-shaped base circle portion 14a coaxial with the camshaft 12, and a nose portion 14b formed so as to bulge a part of the base circle outward in the radial direction.
  • the subcam 16 is comprised as a cam (zero lift cam) which has only a base circle part.
  • Each cylinder of the internal combustion engine is provided with a first rocker arm 18 and a second rocker arm 20 adjacent to each other.
  • the rocker arms 18 and 20 of each cylinder are supported by a single rocker shaft 22 so as to be rotatable (oscillated).
  • the rocker arms 18 and 20 are interposed between the cams 14 and 16 and the valve 26 as transmission members that transmit the acting force of the main cam 14 to the valve 26.
  • a cam roller 28 is rotatably attached to the first rocker arm 18 at a position where it can contact the main cam 14.
  • the first rocker arm 18 is urged by a lost motion mechanism 60 described later so that the cam roller 28 is always in contact with the main cam 14.
  • the configuration relating to the lost motion mechanism 60 is a characteristic part of the present embodiment, and will be described in detail later with reference to FIGS.
  • the first rocker arm 18 configured as described above swings about the rocker shaft 22 as a fulcrum by the cooperation of the acting force of the main cam 14 and the urging force of the lost motion mechanism 60.
  • the second rocker arm 20 for driving the two valves 26 is integrally configured so as to surround the first rocker arm 18 from both sides. Further, the second rocker arm 20 is provided with a pad 20a at a position where it can come into contact with the sub cam 16 in the base circle section of the main cam 14. The valve 26 is urged in the valve closing direction by a valve spring 30.
  • the variable valve operating apparatus 10 includes a connected state in which the first rocker arm 18 and the second rocker arm 20 are connected (see FIG. 2A) and a disconnected state in which the connection is released (see FIG. 2B). And a switching mechanism 32 for switching between.
  • the variable valve operating apparatus 10 is provided with such a switching mechanism 32 so that the acting force of the main cam 14 is transmitted to the second rocker arm 20 via the first rocker arm 18 (the above-described coupled state); By switching the state in which the acting force is not transmitted to the second rocker arm 20 (the above-mentioned unconnected state), the valve opening characteristic of the valve 26 can be switched between the valve operating state and the valve closing stop state. ing.
  • a first pin hole 34 a concentric with the cam roller 28 is formed in the bush 34 that functions as a support shaft of the cam roller 28, and the first rocker arm 20 has a first pin hole 34 a.
  • Two second pin holes 20bL and 20bR are formed at positions corresponding to the pin holes 34a.
  • a columnar first switching pin 36 is movably inserted into the first pin hole 34a.
  • a cylindrical second switching pin 38 that is in contact with the first switching pin 36 is movably inserted into one (left side in FIG. 1) of the second pin hole 20bL. In the second pin hole 20bL in which the second switching pin 38 is inserted, the end on the opposite side to the first rocker arm 18 is closed by the cap 40.
  • a return spring 42 that urges the second switching pin 38 toward the first rocker arm 18 is disposed inside the second pin hole 20bL. Further, a cylindrical third switching pin 44 that is in contact with the first switching pin 36 is movably inserted into the second pin hole 20bR on the other side (the right side in FIG. 1).
  • the switching mechanism 32 has a pin driving mechanism for driving the switching pin 36 and the like while resisting the urging force of the return spring 42. More specifically, a link arm 46 having an arm portion 46 a that comes into contact with the third switching pin 44 is disposed on the side of the second rocker arm 20. The link arm 46 is rotatably supported by the rocker shaft 22. Moreover, as shown in FIG. 2, the rocker shaft 22 is formed in a hollow shape. A link shaft 50 is inserted into the rocker shaft 22. The link shaft 50 is a shaft provided to displace the link arm 46 and a link arm (not shown) arranged in another cylinder (not shown) in conjunction with the axial direction of the rocker shaft 22. It is.
  • a protrusion 46 b is provided at the tip of the arm portion 46 a of the link arm 46 at a position where it can protrude toward the peripheral surface of the camshaft 12.
  • the camshaft 12 is provided with a guide rail 54 formed as a spiral groove extending in the circumferential direction at a portion facing the protrusion 46b.
  • the switching mechanism 32 includes an electromagnetic solenoid 56 as an actuator that generates a driving force for engaging (inserting) the protrusion 46 b with the guide rail 54.
  • the electromagnetic solenoid 56 is duty-controlled based on a command from an ECU (Electronic Control Unit) 58 for controlling the operating state of the internal combustion engine.
  • ECU Electronic Control Unit
  • variable valve apparatus 10 of the present embodiment is such that the projection 46b of the link arm 46 is separated from the guide rail 54 in a state where the energization to the electromagnetic solenoid 56 is OFF.
  • the link arm 46 is configured to be positioned at the displacement end Pmax1 under the urging force of the return spring 42.
  • the first rocker arm 18 and the second rocker arm 20 are connected via the switching pins 36 and 38.
  • a valve operating state in which the acting force of the main cam 14 is transmitted from the first rocker arm 18 to the both valves 26 via the second rocker arm 20 is achieved.
  • the link arm 46 pushed by the drive shaft 56a rotates when the electromagnetic solenoid 56 is energized.
  • the protrusion 46b is engaged with the guide rail 54, and as a result, the link arm 46 is configured to be displaced toward the displacement end Pmax2.
  • the protrusion 46 b is separated from the camshaft 12, and the link arm 46 and the drive shaft 56 a of the electromagnetic solenoid are connected.
  • the link arm 46 is configured to be held in a state where the urging force of the return spring 42 is received by engagement. In the state shown in FIG.
  • the operation state of the valve 26 is controlled by using the switching pin 36 and the like by switching ON / OFF of the energization to the electromagnetic solenoid 56. It is possible to switch between an operating state and a closed valve stop state.
  • the configuration of the pin drive mechanism is not limited to the above configuration, and for example, the switching pin 36 or the like may be driven using an electric motor or hydraulic pressure.
  • FIG. 3 is a perspective view for explaining a characteristic support structure of the lost motion mechanism 60 according to the first embodiment of the present invention. More specifically, FIG. 3 is a partial cross-sectional view showing the components mounted on the cylinder head 62 at the center position of the lost motion mechanism 60.
  • an ignition plug tube 66 for guiding the attachment / detachment of the ignition plug 64 is press-fitted into the central portion of the cylinder head 62 that functions as a base member on which the variable valve apparatus 10 is mounted.
  • An attachment portion 68 a of a holding member 68 that holds the lost motion mechanism 60 is attached to the spark plug tube 66.
  • FIG. 4 is a perspective view showing the outer shape of the holding member 68 shown in FIG.
  • the holding member 68 includes, in addition to the mounting portion 68a, a holding portion 68b that holds the lost motion mechanism 60, and a connecting portion 68c that connects the mounting portion 68a and the holding portion 68b. I have. That is, the lost motion mechanism 60 of this embodiment is attached to the spark plug tube 66 via the holding member 68.
  • the spark plug tube 66 is formed in a cylindrical shape, and the attachment portion 68a fitted into the spark plug tube 66 is also formed in a cylindrical shape with both ends open. Further, the attachment portion 68 a is supported by the spark plug tube 66 in such a manner that the holding member 68 is rotatable in the circumferential direction of the spark plug tube 66.
  • the lost motion mechanism 60 includes a lost motion spring 70 and a lifter 72 interposed between the lost motion spring 70 and the first rocker arm 18.
  • the holding portion 68b of the holding member 68 has a cylindrical shape with both ends open.
  • the lost motion spring 70 and the lifter 72 are accommodated in the holding portion 68b.
  • the lifter 72 is formed in a cylindrical shape having one end opened and the other end closed.
  • the lost motion spring 70 is housed inside the lifter 72. More specifically, one end of the lost motion spring 70 is in contact with the top 72 a of the closed lifter 72, and the other end is in contact with the cylinder head 62. That is, the lost motion spring 70 is configured to urge the first rocker arm 18 toward the main cam 14 via the top portion 72 a of the lifter 72 while using the cylinder head 62 as a seating surface for receiving the spring load. ing.
  • the holding portion 68b is formed so as to cover the side surface of the lifter 72, which is the body portion of the lost motion mechanism 60, and the side surface of the lost motion spring 70 from the outside.
  • the cross-sectional shape (annular circle) of the holding portion 68b cut in the direction perpendicular to the axis of the lost motion mechanism 60 is an enlarged shape of the cross-sectional shape (circular shape) of the lifter 72.
  • FIG. 5 is a diagram for explaining a configuration provided in the variable valve gear 10 for positioning the first rocker arm 18 and the lost motion mechanism 60. More specifically, FIG. 5 (A) is a view of the first rocker arm 18 from the direction of the portion where the lost motion mechanism 60 contacts, and FIG. 5 (B) shows the lifter 72 from the top 72a side. FIG. 5 (A) is a view of the first rocker arm 18 from the direction of the portion where the lost motion mechanism 60 contacts, and FIG. 5 (B) shows the lifter 72 from the top 72a side.
  • FIG. 5 is a diagram for explaining a configuration provided in the variable valve gear 10 for positioning the first rocker arm 18 and the lost motion mechanism 60. More specifically, FIG. 5 (A) is a view of the first rocker arm 18 from the direction of the portion where the lost motion mechanism 60 contacts, and FIG. 5 (B) shows the lifter 72 from the top 72a side. FIG.
  • an engagement groove 72b is formed in the top portion 72a (the outer surface) of the lifter 72 that comes into contact with the first rocker arm 18. More specifically, the engagement groove 72 b is formed so that the center in the width direction of the groove crosses the outer surface of the top portion 72 a while passing through the axis of the lifter 72.
  • a protruding pad 18a that engages with the engaging groove 72b is formed in a portion of the first rocker arm 18 that faces the top portion 72a. More specifically, the pad 18 a is formed so as to extend along the moving direction of the first rocker arm 18 when the first rocker arm 18 is viewed from the lifter 72.
  • FIG. 6 is a diagram for explaining the effect of the support structure of the lost motion mechanism 60 in the first embodiment of the present invention.
  • the lost motion mechanism 60 of this embodiment is attached to the spark plug tube 66 via the holding member 68.
  • the boss portion including the waste is not necessary, so that the support portion can be easily manufactured and the mass of the internal combustion engine can be reduced. For this reason, the deterioration of the fuel consumption performance of the vehicle due to the increase in mass can be prevented.
  • processing costs can be reduced.
  • the first rocker arm 18 is disposed between the second rocker arms 20 that push the two valves 26.
  • the first rocker arm 18 is disposed so as to be sandwiched between the two valves 26 in each cylinder.
  • the spark plug tube 66 is installed at the center of each cylinder.
  • the two valves 26 are generally equidistant from the center of each cylinder in which the spark plug tube 66 is installed, and the cylinder head is based on the center of each cylinder. 62 is arranged at a symmetrical position in the longitudinal direction. Therefore, as a result, the first rocker arm 18 and the spark plug tube 66 are arranged close to each other as shown in FIG.
  • the lost motion mechanism 60 is attached to such a spark plug tube 66 via a holding member 68.
  • the connection part 68c of the holding member 68 can be shortened.
  • the rigidity of the holding member 68 can be secured satisfactorily, and the weight of the holding member 68 can be reduced.
  • one end of the lost motion spring 70 is in contact with the top 72 a of the closed lifter 72, and the other end is in contact with the cylinder head 62.
  • the holding portion 68b of the holding member 68 is responsible for only the guide function for guiding the expansion and contraction of the lost motion mechanism 60, and the spring load of the lost motion spring 70 is the cylinder head 62 that is the base member. Will be in charge. As a result, since the force acting on the holding member 68 can be reduced, the weight of the holding member 68 can be reduced.
  • the cross-sectional shape of the holding portion 68b cut in the direction perpendicular to the axis of the lost motion mechanism 60 is an enlarged shape of the cross-sectional shape of the lifter 72.
  • FIG. 7 is a cross-sectional view of the lost motion mechanism 60 and the first rocker arm 18 taken along the axial position of the lost motion mechanism 60 as viewed from the advancing direction of the engagement groove 72b.
  • the attachment portion 68 a of the holding member 68 is supported by the spark plug tube 66 in such a manner that the holding member 68 is rotatable in the circumferential direction of the spark plug tube 66.
  • the engagement groove 72 b formed on the lifter 72 and the pad 18 a formed on the first rocker arm 18 engage with each other, thereby positioning the lifter 72 with respect to the first rocker arm 18. Done.
  • the lost motion mechanism 60 is held by a separate holding member 68 from the cylinder head 62, unlike the above-described configuration, when the configuration for fixing the rotation position of the mounting portion with respect to the spark plug tube is employed, Such a problem arises. That is, when the contact point between the first rocker arm and the lost motion mechanism deviates from the center of the lost motion mechanism, a force that pushes the lost motion spring in the radial direction acts on the holding member. Therefore, it is important to accurately position the lost motion mechanism with respect to the first rocker arm.
  • the engaging portion 72a of the holding member 68 is configured to be rotatable with respect to the spark plug tube 66, and the engaging groove 72b formed in the lifter 72 and the first rocker arm are configured.
  • the lost motion mechanism 60 can be accurately positioned with respect to the first rocker arm 18 without increasing the number of parts.
  • the main cam 14 is the “cam” in the first invention
  • the first rocker arm 18 is the “transmission member” in the first invention
  • the lost motion mechanism 60 is the It corresponds to the “biasing means” in the first invention.
  • the pad 18a formed on the first rocker arm 18 corresponds to the “projection” in the third aspect of the invention.
  • the cylinder head 62 corresponds to the “base member” in the eighth invention.
  • FIG. 8 is a diagram schematically showing the configuration of the valve gear 80 according to Embodiment 2 of the present invention.
  • the same components as those shown in FIG. 1 are denoted by the same reference numerals, and the description thereof is omitted or simplified.
  • the rocker arm 84 as a transmission member interposed between the cam 82 and the valve 26.
  • the lash adjuster 88 has a function of expanding and contracting so that the tappet clearance is zero.
  • the spark plug tube 66 is press-fitted into the cylinder head 62 also in this embodiment.
  • the lash adjuster 88 is attached to the spark plug tube 66 via a holding member 90.
  • the holding member 90 includes an attachment portion 90a attached to the spark plug tube 66, a holding portion 90b that holds the lash adjuster 88, and a connecting portion 90c that connects the attachment portion 90a and the holding portion 90b.
  • One end of the lash adjuster 88 is in contact with the other end of the rocker arm 84 as described above.
  • the other end of the lash adjuster 88 is in contact with the cylinder head 62. That is, the lash adjuster 88 is configured to be able to urge the rocker arm 84 toward the cam 82 while using the cylinder head 62 as a seating surface that receives a load acting on the lash adjuster 88 via the rocker arm 84. Yes.
  • the holding portion 90b is formed so as to cover the side surface of the lash adjuster 88, which is the body portion of the lash adjuster 88, from the outside.
  • the cross-sectional shape (annular circle) of the holding portion 90b cut in the direction perpendicular to the axis of the lash adjuster 88 is an enlarged shape of the cross-sectional shape (circular shape) of the lash adjuster 88.
  • the protrusion 88 a of the lash adjuster 88 that functions as a fulcrum of the rocker arm 84 is configured to engage with an engagement groove 84 a provided at the other end of the rocker arm 84.
  • the lash adjuster 88 that is used as a biasing unit that biases the rocker arm 84 that is a transmission member is attached to the spark plug tube 66 via the holding member 90. .
  • the need for the boss portion including the sacrificial meat is eliminated, so that the support portion can be easily manufactured and the mass of the internal combustion engine can be reduced. For this reason, the deterioration of the fuel consumption performance of the vehicle due to the increase in mass can be prevented.
  • the same effects as those of the first embodiment described above can be obtained.
  • the rocker arm 84 corresponds to the “transmission member” in the first invention
  • the lash adjuster 88 corresponds to the “biasing means” in the first invention.
  • Embodiment 1 it demonstrated taking the case of the structure in which the lost motion mechanism 60 which urges
  • the configuration of the valve operating apparatus for the internal combustion engine to which the present invention is applicable is not limited to the above, and may be, for example, a configuration as shown in FIG.
  • FIG. 9 is a diagram schematically showing the configuration of another valve gear applicable to the present invention.
  • the variable valve operating apparatus 100 shown in FIG. 9 includes a first rocker arm 102 similar to the first rocker arm 18 as a transmission member interposed between the main cam 14 and the valve 26 (not shown in FIG. 9). I have. More specifically, one end of the first rocker arm 102 is rotatably supported by the rocker shaft 22, and a cam roller 104 is installed at the center of the first rocker arm 102. Further, a lost motion arm 106 formed in an L shape is fixed to the other end of the first rocker arm 102.
  • variable valve operating apparatus 100 includes a lost motion mechanism 108 that urges the first rocker arm 102 toward the main cam 14 via the lost motion arm 106.
  • the lost motion mechanism 108 includes a lost motion spring 110 and a lifter 112 interposed between the lost motion spring 110 and the lost motion arm 106.
  • the spark plug tube 66 is press-fitted into the cylinder head 62.
  • the lost motion mechanism 108 is attached to the spark plug tube 66 via a holding member 114.
  • the holding member 114 includes an attachment portion 114 a attached to the spark plug tube 66 and a holding portion 114 b that holds the lost motion mechanism 108.
  • the connection part is not provided, but the holding part 114b is attached to the attachment part 114a in the perpendicular direction.
  • an engagement groove 112 b that engages with a pad 106 a provided on the lost motion arm 106 is formed on the top 112 a of the lifter 112.
  • 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, for example, in the case of the configuration of the variable valve apparatus 10 described above, a secondary cam provided with a nose portion that allows a lift smaller than that of the main cam 14 may be used. According to the configuration including such a secondary cam, the lift amount (and / or operating angle) of the valve can be switched in two stages by the main cam and the secondary cam.
  • variable valve apparatus 10 has been described as an example.
  • valve gear that is the subject of the present invention is not limited to that configured as a variable valve gear as described above in the second embodiment. That is, it may be provided with a holding member that holds a biasing means that biases the transmission member interposed between the cam and the valve.
  • the first rocker arm 18 and the like have been described as examples of biasing targets by the lost motion mechanism 60 and the lash adjuster 88 that function as biasing means.
  • the transmission member in the present invention is not limited to the rocker arm. In other words, it may be anything that is interposed between the cam and the valve and transmits the acting force of the cam to the valve.
  • the engagement groove 72b is formed in the top portion 72a of the lifter 72 of the lost motion mechanism 60, and the engagement groove 72b is formed at a portion facing the lifter 72 in the first rocker arm 18.
  • An example in which the engaging pad (projection) 18a is formed has been described.
  • the present invention is not limited to this.
  • a protrusion such as a pad is formed on the top portion 72a side of the lifter 72 that is a biasing means, and the first rocker arm 18 side that is a transmission member is formed.
  • An engagement groove may be formed.
  • the lost motion mechanism 60 that urges the first rocker arm 18 toward the main cam 14 in the pushing direction has been described as an example.
  • the configuration of the urging means in the present invention is not limited to this, and for example, an urging force may be generated in a direction in which the transmission member such as the first rocker arm 18 is drawn.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Ignition Installations For Internal Combustion Engines (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

La présente invention se rapporte à un actionneur de soupape pour moteur à combustion interne. L'actionneur de soupape comprend un moyen de sollicitation destiné à solliciter un organe de transmission qui transmet la force d'actionnement d'une came à une soupape. Une pièce de support du moyen de sollicitation peut être fabriquée plus facilement, et les augmentations de la masse du moteur à combustion interne peuvent être limitées grâce à l'utilisation de l'actionneur de soupape. L'actionneur de soupape comprend un premier culbuteur (18), qui est disposé entre une came principale (14) et une soupape (26), pour transmettre la force d'actionnement de la came principale (14) à la soupape (26). L'actionneur de soupape comprend un mécanisme à mouvement perdu (60) destiné à solliciter le premier culbuteur (18) dans une direction. L'actionneur de soupape comprend un organe de maintien (68) destiné à maintenir le mécanisme à mouvement perdu (60). Le mécanisme à mouvement perdu (60) est ajusté sur un tube de bougie d'allumage (66), l'organe de maintien (68) étant intercalé entre eux.
PCT/JP2010/056332 2010-04-07 2010-04-07 Actionneur de soupape pour moteur à combustion interne WO2011125194A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/JP2010/056332 WO2011125194A1 (fr) 2010-04-07 2010-04-07 Actionneur de soupape pour moteur à combustion interne
JP2012509239A JP5299564B2 (ja) 2010-04-07 2010-04-07 内燃機関の動弁装置
CN2010800660020A CN102892979A (zh) 2010-04-07 2010-04-07 内燃机的气门装置
EP10849438.6A EP2557280A4 (fr) 2010-04-07 2010-04-07 Actionneur de soupape pour moteur à combustion interne
US13/636,554 US20130042830A1 (en) 2010-04-07 2010-04-07 Valve operating apparatus for internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/056332 WO2011125194A1 (fr) 2010-04-07 2010-04-07 Actionneur de soupape pour moteur à combustion interne

Publications (1)

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WO2011125194A1 true WO2011125194A1 (fr) 2011-10-13

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US (1) US20130042830A1 (fr)
EP (1) EP2557280A4 (fr)
JP (1) JP5299564B2 (fr)
CN (1) CN102892979A (fr)
WO (1) WO2011125194A1 (fr)

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Publication number Priority date Publication date Assignee Title
JP6420783B2 (ja) 2016-03-31 2018-11-07 本田技研工業株式会社 可変動弁装置
DE102017114575A1 (de) * 2017-06-29 2019-01-03 Man Truck & Bus Ag Variabler Ventiltrieb
AT521311B1 (de) * 2018-05-22 2020-07-15 Avl List Gmbh Ventiltrieb einer brennkraftmaschine
JP6932179B2 (ja) * 2019-12-27 2021-09-08 ヤマハ発動機株式会社 ロストモーション機構、動弁装置およびエンジン

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0246006U (fr) * 1988-09-24 1990-03-29
JPH06280522A (ja) 1993-03-29 1994-10-04 Mazda Motor Corp エンジンのシリンダヘッド構造
JP2000087719A (ja) * 1998-09-11 2000-03-28 Honda Motor Co Ltd 内燃機関の潤滑構造
JP2000240418A (ja) 1998-12-23 2000-09-05 Honda Motor Co Ltd 内燃機関の動弁装置
JP2002242629A (ja) * 2001-02-20 2002-08-28 Yamaha Motor Co Ltd 内燃エンジンの可変動弁機構
JP2007327378A (ja) 2006-06-07 2007-12-20 Honda Motor Co Ltd 点火プラグチューブの取付構造

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0313582Y2 (fr) * 1985-11-18 1991-03-27
JPS6318109A (ja) * 1986-07-09 1988-01-26 Honda Motor Co Ltd 内燃機関の動弁機構
JP3319794B2 (ja) * 1993-01-18 2002-09-03 本田技研工業株式会社 内燃機関のｓｏｈｃ型動弁装置
DE19806675A1 (de) * 1998-02-18 1999-08-19 Daimler Chrysler Ag Vorrichtung zur variablen Steuerung der Ventile einer Hubkolben-Brennkraftmaschine
DE69926475T2 (de) * 1998-12-22 2006-04-06 Honda Giken Kogyo K.K. Ventilsteuerungseinrichtung für eine Brennkraftmaschine
US7406932B2 (en) * 2005-08-15 2008-08-05 Honda Motor Co., Ltd. Lift-variable valve-operating system for internal combustion engine
JP2008190441A (ja) * 2007-02-06 2008-08-21 Honda Motor Co Ltd 可変動弁機構におけるリフト量調整装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0246006U (fr) * 1988-09-24 1990-03-29
JPH06280522A (ja) 1993-03-29 1994-10-04 Mazda Motor Corp エンジンのシリンダヘッド構造
JP2000087719A (ja) * 1998-09-11 2000-03-28 Honda Motor Co Ltd 内燃機関の潤滑構造
JP2000240418A (ja) 1998-12-23 2000-09-05 Honda Motor Co Ltd 内燃機関の動弁装置
JP2002242629A (ja) * 2001-02-20 2002-08-28 Yamaha Motor Co Ltd 内燃エンジンの可変動弁機構
JP2007327378A (ja) 2006-06-07 2007-12-20 Honda Motor Co Ltd 点火プラグチューブの取付構造

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2557280A4 *

Also Published As

Publication number Publication date
EP2557280A4 (fr) 2013-06-12
US20130042830A1 (en) 2013-02-21
EP2557280A1 (fr) 2013-02-13
CN102892979A (zh) 2013-01-23
JPWO2011125194A1 (ja) 2013-07-08
JP5299564B2 (ja) 2013-09-25

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