WO2016052729A1 - エンジンの動弁装置およびロッカーアームの製造方法 - Google Patents
エンジンの動弁装置およびロッカーアームの製造方法 Download PDFInfo
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- WO2016052729A1 WO2016052729A1 PCT/JP2015/078052 JP2015078052W WO2016052729A1 WO 2016052729 A1 WO2016052729 A1 WO 2016052729A1 JP 2015078052 W JP2015078052 W JP 2015078052W WO 2016052729 A1 WO2016052729 A1 WO 2016052729A1
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- Prior art keywords
- rocker arm
- rocker
- arm
- shaft
- pin
- Prior art date
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
-
- 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
- F01L1/146—Push-rods
-
- 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
-
- 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
- F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
- F01L2001/0537—Double overhead camshafts [DOHC]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- 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
- F01L2001/186—Split rocking arms, e.g. rocker arms having two articulated parts and means for varying the relative position of these parts or for selectively connecting the parts to move in unison
-
- 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
- F01L2303/00—Manufacturing of components used in valve arrangements
-
- 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
- F01L2303/00—Manufacturing of components used in valve arrangements
- F01L2303/01—Tools for producing, mounting or adjusting, e.g. some part of the distribution
-
- 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 an engine valve gear capable of switching between a form in which two types of rocker arms are connected to each other and a form in which the connection is released, and a method for manufacturing the rocker arm.
- Patent Document 1 As a conventional valve operating device for this type of engine, for example, there is one described in Patent Document 1.
- the valve gear disclosed in Patent Document 1 converts the rotation of a camshaft into a reciprocating motion by a rocker arm and drives two intake valves or exhaust valves.
- the camshaft has a high-speed cam and two low-speed cams located on both sides of the high-speed cam.
- the high speed cam is formed in a shape in which the valve lift amount is relatively larger than that of the low speed cam.
- the rocker arm is composed of two main arms provided for each intake valve or each exhaust valve, and a sub arm positioned between these main arms.
- the main arm has a slipper with which the low-speed cam of the camshaft contacts, and is supported on the rocker shaft so as to be swingable.
- the main arm is biased toward the low speed cam by a valve spring of an intake valve or an exhaust valve.
- the sub-arm has a slipper with which the camshaft for high speed cam comes into contact, and is swingably supported by the rocker shaft.
- the sub arm is biased toward the high speed cam by a dedicated return spring.
- the main arm and the sub arm are connected and integrated with each other by a hydraulic switching mechanism, or are disconnected and disconnected.
- the switching mechanism includes a switching pin movably provided in the pin hole of the sub arm, a plunger movably provided in the plunger holes of the two main arms, and a hydraulic circuit for supplying hydraulic pressure to these plungers. Etc.
- the switching pin and the two plungers are configured to be located on the same axis when the intake valve or the exhaust valve is closed.
- the main arm and sub arm are integrated when one plunger pushes the switching pin and the other plunger.
- one plunger is fitted in the pin hole of the sub arm and is positioned across the one main arm and the sub arm.
- the switching pin is fitted over the plunger hole of the other main arm so as to straddle between the sub arm and the other main arm.
- the switching pin is pushed back by the other plunger so that one plunger is located only in the main arm and the switching pin is located only in the sub arm. In this way, the sub arm and the main arm are separated and disconnected, so that the sub arm pushed by the high speed cam swings independently, and the main arm pushed by the low speed cam becomes the intake valve or the exhaust valve. Drive.
- the present invention has been made in order to solve such problems, and an engine valve operating device in which a switching pin easily moves when switching between a mode in which two types of rocker arms are connected and a mode in which they are separated, and It aims at providing the manufacturing method of the rocker arm used for a valve operating apparatus.
- a valve operating apparatus for an engine includes a camshaft having a cam for driving an intake valve or an exhaust valve, a rocker shaft parallel to the camshaft, and the rocker shaft.
- a first rocker arm that is swingably supported and is swung by being pushed by the cam, and a return direction that is opposite to a direction in which the first rocker arm is swung by being pushed by the cam.
- a second rocker provided with a spring member for urging the first rocker arm, and a valve pressing part for pressing the intake valve or the exhaust valve, which is swingably supported by the rocker shaft.
- An arm and an axis of the rocker shaft at positions equidistant from the rocker shaft in the first rocker arm and the second rocker arm, respectively.
- a pin hole formed in a row a switching pin provided in the pin hole so as to be movable in the axial direction of the rocker shaft, and moving the switching pin in the axial direction so that the switching pin is the first pin.
- a switching mechanism that switches between a connected state straddling the rocker arm and the second rocker arm and a non-connected state in which the switching pin does not straddle both the rocker arms, and the second rocker
- the arm includes a stopper with which the first rocker arm that swings in the return direction contacts in the disconnected state and the intake valve or the exhaust valve is closed. All the pin holes are positioned on the same axis when abutting against the stopper.
- the method for manufacturing a rocker arm according to the present invention is used in the valve operating apparatus for an engine according to the present invention, wherein the cam follower in contact with the cam in the first rocker arm is a rotating body, and the rotating body is the first rotating body.
- a method of manufacturing a rocker arm which is rotatably supported by a support shaft fitted in a shaft hole of a rocker arm, and has a hollow portion serving as the pin hole of the first rocker arm on the support shaft,
- a cylindrical jig having an outer diameter that fits into the shaft hole of the first rocker arm and an inner diameter that matches the pin hole of the second rocker arm fits into the shaft hole instead of the support shaft.
- the first rocker arm is biased in the direction of approaching the cam by the spring member.
- the first rocker arm swings by the spring force of the spring member and comes into contact with the stopper of the second rocker arm. At this time, all the switching pins are positioned on the same axis.
- a valve operating apparatus for an engine in which a switching pin moves easily and reliably when switching between a form in which the first rocker arm and the second rocker arm are connected and a form in which the first rocker arm is separated. be able to.
- the hole formed in the first rocker arm is a shaft hole larger than the pin hole
- the hole formed in the second rocker arm is a pin hole.
- the first rocker arm and the second rocker arm are formed so that these holes are located on the same axis in the assembled state.
- the assembled state here is a state in which the first rocker arm and the second rocker arm are supported by the rocker shaft and the first rocker arm is in contact with the stopper. Therefore, the above-mentioned switching can be performed more easily and reliably by assembling the valve operating apparatus using the rocker arm formed by this rocker arm manufacturing method.
- FIG. 1 is a side view of a valve gear according to the present invention.
- FIG. 1 illustrates a cylinder head and a rocker housing partly broken.
- FIG. 2 is a plan view of the cylinder head.
- FIG. 2 is drawn with the intake camshaft and exhaust camshaft removed.
- FIG. 3 is a side view for explaining a non-connected state (cylinder deactivation state).
- FIG. 4 is a plan view of the valve gear.
- FIG. 5 is a plan view of a single rocker housing. 6 is a cross-sectional view taken along line VI-VI in FIG. 7 is a cross-sectional view taken along line VII-VII in FIG.
- FIG. 8 is a cross-sectional view of the rocker arm.
- FIG. 9 is an exploded perspective view of the first rocker arm.
- FIG. 10 is a side view for explaining the connected state when the intake valve or the exhaust valve is closed.
- 11 is a cross-sectional view taken along line XI-XI of the second rocker arm and the first switching pin in FIG.
- FIG. 12 is a cross-sectional view for explaining the first step of the rocker arm manufacturing method.
- FIG. 13 is a cross-sectional view for explaining the second step and the third step of the method for manufacturing the rocker arm.
- FIG. 14 is a cross-sectional view for explaining a fourth step of the method for manufacturing the rocker arm.
- FIG. 15 is a plan view of a first rocker arm and a second rocker arm according to the second embodiment.
- FIG. 16 is a side view showing a main part of the valve gear according to the second embodiment.
- the valve gear 1 is mounted on a DOHC type four-cylinder engine 2 mounted on a vehicle (not shown).
- the valve gear 1 includes a switching mechanism 3 (see FIG. 2) in order to switch a plurality of operation modes to be described later. Although the details will be described later, the switching mechanism 3 switches between a mode in which the cylinder is operated normally and a mode in which the cylinder is deactivated.
- the switching mechanism 3 shown in FIG. 2 is provided on the intake valve side (right side in FIG. 2) and exhaust valve side (left side in FIG. 2) of all cylinders.
- the operation mode switched by the switching mechanism 3 is an all-cylinder operation mode in which four cylinders are operated normally, and a partial cylinder operation mode in which only an arbitrary cylinder among the four cylinders is operated.
- FIG. 2 is drawn in a state where the switching mechanisms 3 are provided in all the cylinders so that the number of cylinders to be operated can be changed when the partial cylinder operation mode is adopted.
- the one-cylinder operation mode is set.
- the 1 ⁇ 2 reduction cylinder operation mode is set.
- a three-cylinder operation mode is set.
- four cylinders are deactivated, all cylinders are deactivated.
- the 1/2 reduction cylinder operation mode can be realized in the first operation mode and the second operation mode in which the operated cylinders are different.
- the first operation mode is an operation mode in which a cylinder (first cylinder) located at one end in the direction in which the four cylinders are arranged and a fourth cylinder (fourth cylinder) counted from one end are operated.
- the second operation mode is an operation mode in which the second cylinder (second cylinder) and the third cylinder (third cylinder) are operated from one end in the direction in which the four cylinders are arranged.
- the switching mechanism 3 is not illustrated in the case of only switching between the 1 / 2-cylinder operation mode and the all-cylinder operation mode, the switching mechanism 3 is usually provided only in the cylinder that is deactivated.
- the 1/2 reduction cylinder operation mode according to the first operation mode and the 1/2 reduction cylinder operation mode according to the second operation mode are based on predetermined rules. It can be switched alternately. For example, since the first operation mode and the second operation mode are switched at predetermined time intervals so that all the cylinders are operated substantially evenly, the 1/2 reduction cylinder operation mode is adopted. Nevertheless, the engine temperature distribution is even.
- the all cylinder deactivation mode is switched, for example, when the accelerator is off. When the all cylinder deactivation mode is adopted, the pumping loss can be reduced because the intake and exhaust of the combustion chamber are prevented from entering and exiting the cylinder only by repeating adiabatic compression and adiabatic expansion in each cylinder.
- the switching mechanism 3 constitutes a part of the valve gear 1 as shown in FIG.
- the valve gear 1 converts the rotations of the intake camshaft 5 and the exhaust camshaft 6 provided in the cylinder head 4 into reciprocating motions by the rocker arm 7, respectively.
- the exhaust valve 9 is driven.
- the portion for driving the intake valve 8 and the portion for driving the exhaust valve 9 in the valve operating device 1 have the same structure. Therefore, in the following, members having the same configuration on the intake valve 8 side and the exhaust valve 9 side will be described on the exhaust valve 9 side, and the members on the intake valve 8 side will be assigned the same reference numerals. The description is omitted.
- the intake camshaft 5 and the exhaust camshaft 6 are each provided with a camshaft body 11 rotatably supported by the cylinder head 4 and a cam 12 provided on the camshaft body 11.
- the intake camshaft 5 and the exhaust camshaft 6 are collectively referred to simply as a camshaft 14.
- the camshaft body 11 is formed in a rod shape with a circular cross section.
- the cam 12 includes a base circle portion 12a and a nose portion 12b.
- the base circle portion 12a has a shape that becomes a part of a cylinder located on the same axis as the camshaft body 11, and is formed in such a size that the valve lift amount of the intake valve 8 or the exhaust valve 9 becomes zero.
- the nose portion 12b is formed in a shape that protrudes from the base circle portion 12a outward in the radial direction by a predetermined protrusion amount in a cross-sectional mountain shape.
- Two intake valves 8 and two exhaust valves 9 are provided for each cylinder, and are supported by the cylinder head 4 so as to be reciprocally movable.
- the two intake valves 8, 8 are arranged at a predetermined interval in the axial direction of the intake camshaft 5.
- the two exhaust valves 9 and 9 are arranged at a predetermined interval in the axial direction of the exhaust camshaft 6.
- the intake valve 8 includes a valve body 8 a that opens and closes an intake port 15 of the cylinder head 4, and a valve shaft 8 b that extends from the valve body 8 a into the valve operating chamber 16 of the cylinder head 4.
- the exhaust valve 9 includes a valve body 9 a that opens and closes the exhaust port 17 of the cylinder head 4 and a valve shaft 9 b that extends from the valve body 9 a into the valve operating chamber 16 of the cylinder head 4.
- the valve shafts 8 b and 9 b are supported via valve shaft guides 8 c and 9 c that are press-fitted into the valve chamber bottom wall 16 a of the cylinder head 4.
- a valve spring 18 that urges the intake valve 8 and the exhaust valve 9 in a closing direction is provided between the distal ends of the valve shafts 8b and 9b and the bottom surface 16b of the valve chamber bottom wall 16a.
- cap-shaped shims 19 are respectively provided at the distal ends of the valve shafts 8b and 9b.
- the upstream end of the intake port 15 opens to one side of the cylinder head 4.
- the downstream end of the intake port 15 opens to the combustion chamber 20 for each cylinder.
- the upstream end of the exhaust port 17 opens to the combustion chamber 20.
- the downstream end of the exhaust port 17 opens to the other side of the cylinder head 4.
- a cylindrical wall portion 21 for attaching and detaching a spark plug (not shown) from above is provided at a portion corresponding to the central portion of the combustion chamber 20 in the cylinder head 4.
- the valve operating chamber 16 of the cylinder head 4 is formed by being surrounded by the cylinder head 4 and a cylinder head cover 4a (see FIG. 1) attached to the cylinder head 4, and a partition wall 22 (see FIG. 1) located between the cylinders. 2) for each cylinder.
- a cylinder head cover 4a (see FIG. 1) attached to the cylinder head 4, and a partition wall 22 (see FIG. 1) located between the cylinders. 2) for each cylinder.
- an intake side journal portion 23 for supporting the intake camshaft 5 and an exhaust side journal portion 24 for supporting the exhaust camshaft 6 are formed at the upper end of the partition wall 22.
- a cam cap 25 is attached to these journal portions 23 and 24 by a plurality of mounting bolts 26 (see FIG. 2).
- the cam cap 25 rotatably supports the intake camshaft 5 and the exhaust camshaft 6 with the journal portions 23 and 24 interposed therebetween.
- the camshaft support portion 27 including the journal portions 23 and 24 and the cam cap 25 is provided on the partition wall 22 between the cylinders described above and the partition walls 28 and 29 at the front end portion and the rear end portion of the cylinder head 4.
- the front end portion and the rear end portion referred to here are an upper end portion and a lower end portion in FIG. 2, and are one end portion and the other end portion in the axial direction of the crankshaft (not shown) of the engine 2.
- a rocker housing unit 31 for supporting a rocker arm 7 to be described later is provided between the camshaft support portions 27 in the cylinder head 4.
- the rocker housing unit 31 according to this embodiment is provided for each cylinder, and is fixed to a support wall portion 32 (see FIG. 1) integrally formed with the cylinder head 4 across the partition wall 22 by fixing bolts 33. ing.
- the support wall portion 32 extends in the axial direction of the crankshaft so as to intersect the cylinder wall portion 21 for attaching and detaching the spark plug.
- the upper end of the cylindrical wall portion 21 is connected to the support wall portion 32, and a circular opening (not shown) that continues to the inside of the cylindrical wall portion 21 is formed in the support wall portion 32.
- the valve chamber bottom wall 16a, the cylinder wall portion 21, the partition wall 22, and the support wall portion 32 all constitute a part of the cylinder head 4 and are integrally formed when the cylinder head 4 is cast.
- the rocker housing unit 31 includes three functional units as shown in FIGS. 4 and 5. These functional parts are the first rocker shaft support part 34 located at the uppermost position in FIG. 5, the second rocker shaft support part 35 located at the lowest position in FIG. 5, and these first and second rocker shaft support parts 35. This is a connecting portion 36 that connects the rocker shaft support portions 34 and 35 together.
- the first and second rocker shaft support portions 34 and 35 and the connecting portion 36 according to this embodiment are integrally formed by casting.
- the first rocker shaft support portion 34 and the second rocker shaft support portion 35 are formed with two circular holes 38 and 39 into which the rocker shaft 37 (see FIG. 4) is fitted. Of the two circular holes, one of the circular holes 38 and 39 is fitted with a rocker shaft 37 that supports the rocker arm 7 for driving the intake valve. The other circular holes 38 and 39 are fitted with a rocker shaft 37 that supports the rocker arm 7 for driving the exhaust valve.
- the first rocker shaft support portion 34 has a base portion 34a attached to the support wall portion 32 and a convex portion 34b protruding upward from the base portion 34a. Two circular holes 38 into which one end of the rocker shaft 37 is fitted are formed in the convex portion 34b.
- the two circular holes 38 of the first rocker shaft support portion 34 are non-through holes.
- One end of the rocker shaft 37 is fitted in the circular hole 38.
- a first oil passage 40 is connected to the circular hole 38.
- the first oil passage 40 is formed in the circular hole 38 to guide oil from the oil supply portion 41 (see FIG. 6) of the cylinder head 4.
- the oil supply part 41 is configured using the support wall part 32.
- the second rocker shaft support portion 35 has a base portion 35a attached to the support wall portion 32 and a convex portion 35b protruding upward from the base portion 35a.
- Two circular holes 39 into which the other end of the rocker shaft 37 is fitted are formed in the convex portion 35b.
- the circular hole 39 is a through hole.
- the rocker shaft 37 is engaged with a stopper pin 42 press-fitted into the convex portion 35b from above, and is prevented from coming off and rotating.
- An oil hole 43 including a non-through hole that opens at one end of the rocker shaft 37 (one end supported by the first rocker shaft support portion 34) is formed in the axial center portion of the rocker shaft 37.
- communication holes 44 that communicate the inside and outside of the rocker shaft 37 are formed at three locations in the middle of the rocker shaft 37.
- the oil sent from the oil supply unit 41 to the circular hole 38 through the first oil passage 40 is supplied from the communication hole 44 to the outside of the rocker shaft through the oil hole 43 in the rocker shaft 37.
- the first oil passage 40 can be provided in the second rocker shaft support portion 35.
- the circular hole 38 of the first rocker shaft support portion 34 is a through hole
- the circular hole 39 of the second rocker shaft support portion 35 is a non-through hole.
- the rocker shaft 37 is attached to the rocker housing unit 31 so that the opening end of the oil hole 43 is located in the second rocker shaft support portion 35.
- the base portion 35a of the second rocker shaft support portion 35 is formed in a shape projecting on both sides from the convex portion 35b.
- Cylinder holes 45 are formed in both end portions of the base portion 35a. These cylinder holes 45 are non-through holes extending in parallel with the axis of the camshaft 14 and open toward one side where the first rocker shaft support portion 34 is located.
- hydraulic pistons 46 constituting a part of the switching mechanism 3 described above are movably fitted.
- the hydraulic piston 46 corresponds to a “pressor” in the sixth aspect of the invention.
- a second oil passage 47 is connected to the cylinder hole 45.
- the second oil passage 47 includes an intake valve side cylinder hole 45 located on one end side of the base portion 35 a and an exhaust valve side cylinder hole 45 located on the other end side in the hydraulic pressure supply portion 48 of the cylinder head 4.
- the hydraulic pressure supply part 48 is configured using the support wall part 32.
- the hydraulic piston 46 has a pressing plate 46 a that protrudes from the cylinder hole 45.
- the pressing plate 46a is formed larger than the cylinder hole 45 in a direction perpendicular to the axis of the camshaft.
- the connecting portion 36 of the rocker housing unit 31 is formed in a plate shape extending in the axial direction of the camshaft 14.
- a circular hole 36a is formed through the connecting portion 36 so as to be concentrically connected to the circular opening (not shown) of the support wall portion 32 described above.
- the rocker arm 7 is formed of a plurality of members as shown in FIGS.
- the plurality of members include a first rocker arm 52, a second rocker arm 54, first to third switching pins 55 to 57, and the like.
- the first rocker arm 52 has a roller 51 that contacts the cam 12.
- a valve pressing portion 53 for pressing the intake valve 8 or the exhaust valve 9 is provided at the swinging end portion of the second rocker arm 54.
- the first to third switching pins 55 to 57 are for selectively connecting the first rocker arm 52 and the second rocker arm 54.
- the first rocker arm 52 includes a first arm piece 52a and a second arm piece 52b that are swingably supported by the rocker shaft 37, and these first and second arms.
- the two connecting pieces 52c and 52d that connect the pieces 52a and 52b are formed in a U-shape when viewed from the front.
- the rocker shaft 37 is slidably fitted in a through hole 58 formed in the first arm piece 52a and the second arm piece 52b.
- FIG. 9 One end of the first arm piece 52a and the second arm piece 52b that are supported by the rocker shaft 37 and directed to the camshaft 14 when viewed from the axial direction of the rocker shaft 37 are shown in FIG. As shown in FIG. 9, a protrusion 59 is provided.
- a roller 51 is inserted between the first arm piece 52a and the second arm piece 52b.
- the roller 51 constitutes a cam follower composed of a rotating body that contacts the cam 12.
- the roller 51 is rotatably supported by a support shaft 62 fitted in the shaft hole 61 of the first arm piece 52a and the second arm piece 52b via a needle bearing (not shown).
- the axis of the support shaft 62 is parallel to the axis of the rocker shaft 37.
- a part of the outer peripheral surface of the roller 51 faces the rocker shaft 37 as shown in FIG.
- a central communication hole 44 among the three communication holes 44 described above is provided in a portion of the rocker shaft 37 facing the roller 51.
- a first pin hole 63 made of a through hole is formed in the shaft center portion of the support shaft 62.
- a first switching pin 55 is fitted in the first pin hole 63 so as to be movable in the axial direction of the rocker shaft 37.
- the first switching pin 55 is formed in a cylindrical shape. Further, the first switching pin 55 is formed longer than the width of the first rocker arm 52 (the length of the first rocker arm 52 in the axial direction of the rocker shaft 37) by a predetermined length.
- a convex portion 64 protruding from the first rocker arm 52 in the first switching pin 55 is accommodated in a concave portion 65 of the second rocker arm 54 described later.
- a return spring member 66 is provided between the connecting piece 52 d of the first rocker arm 52 and the cylinder head 4.
- the spring member 66 has a first rocker arm in a direction in which the roller 51 is pressed against the cam 12, in other words, in a return direction that is opposite to the direction in which the first rocker arm 52 is pushed by the cam 12 and swings. 52 is energized. Therefore, the first rocker arm 52 swings against the spring force of the spring member 66 when pressed by the cam 12.
- the second rocker arm 54 includes a first arm half 71 and a second arm half 72 that are swingably supported by the rocker shaft 37, and these arm halfs. It has the 1st connection part 73 and the 2nd connection part 74 which connect the parts 71 and 72.
- the first and second arm halves 71 and 72 and the first and second connecting portions 73 and 74 according to this embodiment are integrally formed by integral molding.
- the rocker shaft 37 is slidably fitted in a through hole 75 formed in the first arm half 71 and the second arm half 72.
- a second pin hole 81 formed of a non-through hole is formed in an intermediate portion of the first arm half 71.
- the second switching hole 56 is accommodated in the second pin hole 81.
- a vent hole 81a that communicates the inside and outside of the second pin hole 81 is formed.
- a third pin hole 82 formed of a through hole is formed in an intermediate portion of the second arm half portion 72.
- the third pin hole 82 accommodates a part of the first switching pin 55 and the third switching pin 56.
- a circlip 83 is provided at one end of the third pin hole 82 (the end located on the side opposite to the first arm half 71). The circlip 83 corresponds to the “retaining member” according to the invention described in claim 6.
- the first arm half portion 71 and the second arm half portion 72 are disposed at positions sandwiching the first rocker arm 52 from both sides in the axial direction while being supported by the rocker shaft 37 in a swingable manner. .
- a projection 76 is provided in the intermediate portion of the second arm half 72 and directed to the camshaft 14.
- a disk portion 77 is provided at a portion of the camshaft 14 facing the protrusion 76 as shown by a two-dot chain line in FIG.
- the disc portion 77 is formed in a disc shape having the same diameter as the base disc portion 12 a of the cam 12, and is provided at a position adjacent to the cam 12. As shown in FIG.
- a gap d ⁇ b> 1 is formed between the disk portion 77 and the protrusion 76 when the valve pressing portion 53 of the second rocker arm 54 is in contact with the shim 19.
- the protrusion 76 hits the disk portion 77 when the second rocker arm 54 jumps and swings toward the camshaft 14 due to vibration or the like, and restricts further swinging of the second rocker arm 54.
- the protrusion 76 has a slight gap d ⁇ b> 2 from the disk portion 77 of the cam shaft 14 in a state where the roller 51 of the first rocker arm 52 is in contact with the base circle portion 12 a of the cam 12. Are close to each other.
- This gap d2 is narrower than the gap d1 shown in FIG.
- a valve clearance d ⁇ b> 3 is formed between the valve pressing portion 53 of the second rocker arm 54 and the shim 19.
- first connecting portion 73 The swing end portions of the first arm half portion 71 and the second arm half portion 72 are connected to each other by a first connecting portion 73.
- valve pressing portions 53 that press the shims 19 of the intake valve 8 or the exhaust valve 9 are provided. That is, the second rocker arm 54 simultaneously presses two intake valves 8 or exhaust valves 9 per cylinder.
- the base parts supported by the rocker shaft 37 in the first arm half part 71 and the second arm half part 72 are connected to each other by a second connection part 74.
- the second connecting portion 74 constitutes a “connecting portion” in the third aspect of the invention.
- the second connecting portion 74 is disposed at one end of the first arm half 71 and the second arm half 72 supported by the rocker shaft 37, and is connected to the camshaft. 14 and 14 are connected to each other. Moreover, the 2nd connection part 74 has crossed the 1st rocker arm 52 in planar view, as shown in FIG. For this reason, when the first rocker arm 52 swings toward the cam 12 with respect to the second rocker arm 54, the protrusion 59 of the first rocker arm 52 approaches the second connecting portion 74.
- a stopper 78 (see FIG. 3) that contacts the protrusion 59 of the first rocker arm 52 is provided on the lower surface (the surface opposite to the cam 12) of the second connecting portion 74.
- the protrusion 59 abuts against the stopper 78 when the first rocker arm 52 is swung by the spring force of the spring member 66 while the intake valve 8 or the exhaust valve 9 is closed.
- the protrusion 59 comes into contact with the stopper 78, the first rocker arm 52 and the second rocker arm 54 are integrally biased in the return direction by the spring force of the spring member 66 thereafter.
- the first to third pin holes 63, 81, and 82 are kept aligned on the same axis. Therefore, the first to third switching pins 55 to 57 can be easily and reliably switched to the connected state shown in FIG. In this connected state, the first switching pin 55 moves to a position straddling the first pin hole 63 and the third pin hole 82, and the second switching pin 56 is moved to the first pin hole 63. And the second pin hole 81.
- the stopper 78 is positioned in the concave space S below the cam 12 at the stopper contact position of the first rocker arm 52 where the protrusion 59 of the first rocker arm 52 contacts the stopper 78. is doing.
- the concave space S refers to a space surrounded by the cam 12 of the camshaft 14, the roller 51 of the first rocker arm 52, and the rocker shaft 37 when viewed from the axial direction of the rocker shaft 37.
- the state in which the protrusion 59 of the first rocker arm 52 contacts the stopper 78 is simply referred to as a “stopper contact state”.
- a concave portion 65 for accommodating the convex portion 64 of the first switching pin 55 is formed on the inner side surface of the first arm half portion 71 facing the first rocker arm 52, as shown in FIG. Yes.
- the second pin hole 81 opens into the recess 65.
- a concave portion 65 is formed on the inner surface of the second arm half portion 72 that faces the first rocker arm 52, although not shown, like the first arm half portion 71.
- the third pin hole 82 opens into the recess 65.
- the recess 65 of the first arm half 71 and the recess 65 of the second arm half 72 are formed in the same shape at the same position when viewed from the axial direction of the rocker shaft 37.
- the non-restricting portion 65a is configured so that the first rocker arm 52 swings with respect to the second rocker arm 54 and the maximum swing without restricting the passage of the convex portion 64 in a state where a predetermined condition is satisfied. It is formed in a shape that allows rocking between positions.
- the state in which the predetermined condition is satisfied is a state in which the first rocker arm 52 is supported by the rocker shaft 37 and is capable of swinging with respect to the second rocker arm 54 (a non-connection described later) State).
- the swing start position is a position of the first rocker arm 52 when the roller 51 is in contact with the base circle portion 12a of the cam 12.
- the maximum swinging position is the position of the first rocker arm 52 when the portion of the nose portion 12b where the protrusion amount is largest is in contact with the roller 51.
- the restricting portion 65b restricts the passage of the convex portion 64 so that the first rocker arm 52 exceeds the maximum swing position with respect to the second rocker arm 54. Regulate swinging. That is, the restricting portion 65b is formed in a shape that intersects the movement locus of the convex portion 64 when the first rocker arm 52 swings beyond the maximum swing position, as indicated by a two-dot chain line in FIG. Has been.
- the restricting portion 65b is formed in the opening 84 located on one end side of the recess 65 having a groove shape.
- the opening 84 opens toward the lower side of the second rocker arm 54 (in the direction opposite to the camshaft 14).
- the restricting portion 65 b is formed so that the opening width of the opening 84 is larger than the outer diameter of the convex portion 64.
- the convex portion 64 can enter and exit the concave portion 65 through the opening 84 in a state where the first rocker arm 52 is not supported by the rocker shaft 37. That is, the restricting portion 65 b is formed in a shape that allows the convex portion 64 to pass in a state where the first rocker arm 52 is not supported by the rocker shaft 37.
- the second pin hole 81 and the third pin hole 82 of the second rocker arm 54 cross the first arm half 71 and the second arm half 72 so as to cross the rocker shaft. 37 extends parallel to the axis.
- the distance between the center line of the second pin hole 81 and the third pin hole 82 and the axis of the rocker shaft 37 is the distance between the center line of the first pin hole 63 of the first rocker arm 52 and the rocker shaft 37. It is consistent with the distance between the axis.
- the first to third pin holes 63, 81, 82 are formed at positions equidistant from the rocker shaft 37 in the first rocker arm 52 and the second rocker arm 54.
- the first pin hole 63, the second pin hole 81, and the third pin hole 82 have a swing angle of the first rocker arm 52 and a swing angle of the second rocker arm 54 in advance. It is positioned on the same axis in a state where a predetermined angle is obtained.
- the predetermined angle is an angle when the intake valve 8 or the exhaust valve 9 is closed (when the valve lift amount becomes 0), and is an angle when the above-described stopper is in contact.
- the hole diameters of the second pin hole 81 and the third pin hole 82 coincide with the hole diameter of the first pin hole 63.
- a second switching pin 56 is movably fitted in the second pin hole 81, and the second switching pin 56 faces the first rocker arm 52.
- An urging spring member 85 is provided.
- the second switching pin 56 is formed in a bottomed cylindrical shape, and is inserted into the second pin hole 81 in a state where the bottom portion faces the first switching pin 55.
- the length of the second switching pin 56 is a length that can be accommodated in the second pin hole 81 as shown by a two-dot chain line in FIG.
- the spring member 85 is provided between the inner bottom portion of the second switching pin 56 and the bottom portion of the second pin hole 81.
- the second switching pin 56 is pushed by the spring force of the spring member 85, and the first switching pin 55 is in a stopper contact state where the first to third pin holes 63, 81, 82 are located on the same axis. Is pressed against one end. In this stopper contact state, the first switching pin 55 is pushed to the other end side by the second switching pin 56.
- the third switching pin 57 is movably fitted in the third pin hole 82.
- the third switching pin 57 and the first switching pin 55 and the second switching pin 56 described above constitute a “switching pin” in the present invention.
- the third switching pin 57 has a large-diameter portion 57 a that faces the first switching pin 55, and a small-diameter portion 57 b that protrudes from the large-diameter portion 57 a toward the outside of the second rocker arm 54. Yes.
- a stepped portion 86 is formed at the boundary portion between the large diameter portion 57a and the small diameter portion 57b.
- the outer diameter of the small diameter portion 57 b is smaller than the inner diameter of the circlip 83 provided in the third pin hole 82.
- the front end surface of the small diameter portion 57b faces the pressing plate 46a of the hydraulic piston 46 described above.
- the length of the third switching pin 57 in the axial direction is slightly shorter than the length of the third pin hole 82 as shown by a two-dot chain line in FIG. For this reason, even if the hydraulic piston 46 moves forward until it hits the second arm half 72, the entire third switching pin 57 is accommodated in the second arm half 72, and the first switching pin 55 Both ends protrude from the first rocker arm 52 substantially evenly.
- the first to third switching pins 55 to 57 are pushed toward the hydraulic piston 46 by the spring force of the spring member 85 when the stopper piston is in contact and the hydraulic piston 46 is inactive. 8 is moved to a connecting position indicated by a solid line.
- the non-operating state of the hydraulic piston 46 is a state in which no hydraulic pressure is applied to the hydraulic piston 46.
- the connection position is a position where the movement of the third switching pin 57 is restricted when the stepped portion 86 contacts the circlip 83.
- the first switching pin 55 is located across the first rocker arm 52 and the second arm half 72 of the second rocker arm 54.
- the second switching pin 56 is located across the first rocker arm 52 and the first arm half portion 71 of the second rocker arm 54.
- the first to third switching pins 55 to 57 are positioned at the coupling positions, whereby the first rocker arm 52 and the second rocker arm 54 are coupled to each other, and the rocker shaft 37 is the center. Can be swung.
- the rotation of the cam 12 is converted into a reciprocating motion by the first rocker arm 52 and the second rocker arm 54, and the intake valve 8 or the exhaust valve 9 is driven.
- the third switching pin 57 is pressed against the circlip 83 and held at the coupling position.
- the third switching pin 57 moves as the second rocker arm 54 swings in a state in which a clearance is formed between the hydraulic piston 46 and the pressing plate 46a. Even if the first and second rocker arms 52 and 54 swing as described above, a part of the pressing plate 46a is formed so as to be opposed to the third switching pin 57.
- the hydraulic piston 46 retreats to a position that does not prevent the first to third switching pins 55 to 57 from moving to the coupling position when in the non-operating state.
- the first to third switching pins 55 to 57 are pushed by the hydraulic piston 46, and the unconnected position indicated by a two-dot chain line in FIG. Move to.
- the pressing plate 46 a of the hydraulic piston 46 contacts the second arm half 72.
- the third switching pin 57 is accommodated in the third pin hole 82. Both ends of the first switching pin 55 slightly protrude from the first rocker arm 52 and enter into the recesses 65 of the first and second arm halves 71 and 72.
- the second switching pin 56 is accommodated in the second pin hole 81.
- the first to third switching pins 55 to 57 are located at the non-connection position, the connection state between the first rocker arm 52 and the second rocker arm 54 is released.
- the first rocker arm 52 and the second rocker arm 54 can swing individually, the first rocker arm 52 is pushed by the cam 12 and swings as shown in FIG. Only the second rocker arm 54 does not swing.
- the intake valve 8 or the exhaust valve 9 is kept closed, the cylinder is deactivated.
- the outer diameters of the first to third switching pins 55 to 57 according to this embodiment are such that even if the first rocker arm 52 swings with respect to the second rocker arm 54 as shown in FIG. When viewed from the axial direction, the portions are always set so as to face each other.
- the switching mechanism 3 provided in the valve gear 1 moves the first to third switching pins 55 to 57 in the axial direction to move the first and second rocker arms 52. , 54 are switched between a connected state and the rocker arms 7 are separated from each other.
- the switching mechanism 3 includes a first pressing portion 91 and a second pressing portion 92.
- the first pressing portion 91 pushes one end in the axial direction (second switching pin 56) of the first to third switching pins 55 to 57 toward the other end side in the axial direction.
- the second pressing portion 92 pushes the other end in the axial direction (third switching pin 57) of the first to third switching pins 55 to 57 toward one end side in the axial direction.
- the first pressing portion 91 according to this embodiment is constituted by a spring member 85 provided on the second rocker arm 54.
- the second pressing portion 92 includes a rocker housing unit 31 fixed to the cylinder head 4 and a hydraulic piston 46 that is movably provided on the rocker housing unit 31 and presses the tip of the third switching pin 57. ing.
- the rocker housing unit 31 corresponds to the “support member” in the invention described in claim 6.
- first rocker arm 52 and the second rocker arm 54 will be described with reference to FIGS. This manufacturing method is performed by first to fourth steps described later.
- first step as shown in FIG. 12, a cylindrical jig 93 is fitted into the shaft hole 61 of the first rocker arm 52 instead of the support shaft 62.
- the outer diameter of the cylindrical jig 93 is an outer diameter that fits into the shaft hole 61 of the first rocker arm 52.
- the inner diameter of the cylindrical jig 93 coincides with the inner diameters of the second pin hole 81 and the third pin hole 82 of the second rocker arm 54.
- the first to second pin holes 81 and 82 of the second rocker arm 54 and the hollow portion 93a of the cylindrical jig 93 are connected to the first to second pins.
- one rod-shaped jig 94 is fitted.
- the rod-shaped jig 94 is formed in a cylindrical shape having an outer diameter that fits into the hollow portion 93 a (first pin hole 63) and the second and third pin holes 81 and 82.
- the first rocker arm 52 is held in contact with the stopper 78 of the second rocker arm 54.
- the through holes 58 and 75 for allowing the rocker shaft 37 to pass through the first rocker arm 52 and the second rocker arm 54 are co-machined with a drill 95.
- the drill 95 is passed through the held first rocker arm 52 and the second rocker arm 54, and holes (through holes 58 and 75) for passing the rocker shaft 37 are processed.
- the assembling work of the rocker arm 7 is performed.
- This assembling operation is performed by a temporary assembly step of temporarily combining the first rocker arm 52 and the second rocker arm 54 and a connecting step of passing the rocker shaft 37 through both the rocker arms 52 and 54.
- the first rocker arm 52 to which the roller 51 and the first switching pin 55 are assembled, the second rocker to which the second and third switching pins 56 and 57 and the spring member 85 are assembled.
- the arm 54 is combined to form one assembly.
- the convex portion 64 of the first switching pin 55 is inserted into the concave portion 65 of the second rocker arm 54 from the opening portion 84.
- both the rocker arms 7 are placed between the first rocker shaft support portion 34 and the second rocker shaft support portion 35 of the rocker housing unit 31 with the convex portion 64 positioned in the concave portion 65. Insert the rocker shaft 37 through these members.
- the first and second rocker arms 52 and 54 are supported by the rocker shaft 37 in this way, the first switching pin 55 cannot come out of the recessed portion 65, so that the first rocker arm 52 and the first rocker arm 52
- the two rocker arms 54 are kept in a combined state. For this reason, the rocker arm 7 can be handled while being attached to the rocker housing unit 31.
- the rocker arm 7 is assembled to the cylinder head 4 by attaching the rocker housing unit 31 to the support wall portion 32 of the cylinder head 4 with a fixing bolt 33.
- the first rocker arm 52 is urged in the direction of approaching the cam 12 by the spring member 66.
- the first rocker arm 52 swings by the spring force of the spring member 66 and comes into contact with the stopper 78 of the second rocker arm 54.
- the first to third pin holes 63, 81, and 82 are positioned on the same axis, and all the switching pins 55 to 57 are positioned on the same axis. If the first to third switching pins 55 to 57 are held on the same axis, they can easily move between the connected position and the non-connected position.
- the first to third switching is performed when switching between the connected state in which the first rocker arm 52 and the second rocker arm 54 are integrated and the disconnected state in which they are separated. It is possible to provide a valve operating apparatus for an engine in which the pins 55 to 57 move easily and reliably.
- valve gear 1 when the first rocker arm 52 abuts against the stopper 78, the spring force of the spring member 66 is transmitted to the second rocker arm 54 via the stopper 78.
- the second rocker arm 54 is biased in the return direction by the spring force of the spring member 66. For this reason, according to this embodiment, it is possible to prevent the first rocker arm 52 from excessively swinging in the return direction from the second rocker arm 54.
- the stopper 78 according to this embodiment is provided by using the second connecting portion 74 located at the base portion of the second rocker arm 54. For this reason, space can be saved as compared with the case where a member functioning exclusively as the stopper 78 is attached to the second rocker arm 54, and the stopper 78 can be easily obtained. Therefore, according to this embodiment, the stopper 78 can be provided while achieving weight reduction and cost reduction. Moreover, since the second connecting portion 74 that also serves as the stopper 78 is provided at the base portion, the moment of inertia around the rocker shaft can be reduced. For this reason, the second rocker arm 54 can swing at a high speed despite having the stopper 78.
- the position where the stopper 78 is provided is not limited to the second connecting portion 74. That is, the stopper 78 can be provided on the first and second arm halves 71 and 72 and the first connecting portion 73 of the second rocker arm 54.
- the first rocker arm 52 has a cam follower (roller 51) with which the cam 12 comes into contact.
- the second connecting portion 74 is connected to the cam 12 of the camshaft 14 when viewed from the axial direction of the rocker shaft 37 at the stopper contact position of the first rocker arm 52 where the first rocker arm 52 contacts the stopper 78.
- the cam follower (roller 51) and the rocker shaft 37 are located in the concave space S (see FIG. 10). For this reason, according to this embodiment, since the stopper 78 is provided in the dead space, the valve operating device 1 can be equipped with the stopper 78 without increasing its size.
- a concave portion 65 through which the convex portion 64 of the first switching pin 55 passes is formed on the side wall of the second rocker arm 54 facing the first rocker arm 52.
- the recess 65 has a non-regulating part 65a and a restricting part 65b.
- the first rocker arm 52 can be reduced in weight, thickness, and structure, so that the manufacturing cost can be kept low. Further, when the first rocker arm 52 is reduced in weight, the spring force of the spring member 66 that biases the first rocker arm 52 can be set small, so that the friction loss can be reduced. .
- the support shaft 62 that rotatably supports the roller 51 is not detached, a member for preventing the support shaft 62 from coming off is press-fitted into the first rocker arm 52. Or the work of fixing to the first rocker arm 52 by caulking becomes unnecessary. That is, the supporting shaft 62 can be prevented from coming off without performing processing that deforms the first rocker arm 52, so that the first rocker arm 52 can be formed with high accuracy.
- the manufacturing error of the first switching pin 55 is not affected. This is because an error can be allowed by the depth of the recess 65. Since the manufacturing error is much smaller than the depth of the recess 65, the influence of the error is eliminated.
- the second rocker arm 54 includes a circlip 83 that contacts the stepped portion 86 of the third switching pin 57. Therefore, the circlip 83 can prevent the third switching pin 57 from coming off, so that the operation of assembling the third switching pin 57 to the second rocker arm 54 can be easily performed. Further, when the hydraulic piston 46 is in an inoperative state and the first to third switching pins 55 to 57 are in the coupling position, the third switching pin 57 swings up and down together with the second rocker arm 54. However, at that time, the third switching pin 57 is not unnecessarily pressed against the hydraulic piston 46. For this reason, the contact portion between the third switching pin 57 and the hydraulic piston 46 is not easily worn.
- the shaft hole 61 formed in the first rocker arm 52 is assembled even though the hole diameter is larger than the second and third pin holes 81 and 82.
- the first rocker arm 52 and the second rocker arm 54 are formed so that these holes are positioned exactly on the same axis.
- the assembled state here is a state in which the first rocker arm 52 and the second rocker arm 54 are supported by the rocker shaft 37 and the first rocker arm 52 is in contact with the stopper 78. Therefore, by assembling the valve operating apparatus 1 using the rocker arm 7 formed by this rocker arm manufacturing method, the first rocker arm 52 and the second rocker arm 54 are separated from the integrated form. Switching to the form can be performed more easily and reliably.
- the engine valve operating apparatus can be configured as shown in FIGS. 15 and 16.
- 15 and 16 the same or equivalent members as those described with reference to FIGS. 1 to 14 are denoted by the same reference numerals, and detailed description thereof is omitted.
- the second rocker arm 54 according to this embodiment includes a first cam follower 101 and a second cam follower 102. These cam followers 101 and 102 are each constituted by a roller having the same diameter as the roller 51 of the first rocker arm 52.
- the first cam follower 101 is inserted into a hole 103 formed in the first arm half 71 and is rotatably supported by a first cylindrical shaft 104 via a bearing (not shown).
- the first cylindrical shaft 104 is formed in a bottomed cylindrical shape, and is fixed to the first arm half 71 by a positioning pin 105 press-fitted into the first arm half 71.
- a second switching pin 56 is movably fitted in the hollow portion of the first cylindrical shaft 104, and a spring member 85 that biases the second switching pin 56 is accommodated. .
- the second cam follower 102 is inserted into a hole 106 formed in the second arm half 72 and is rotatably supported by a second cylindrical shaft 107 via a bearing (not shown).
- the second cylindrical shaft 107 is formed in a cylindrical shape that penetrates the second arm half 72.
- the second cylindrical shaft 107 is fixed to the second arm half 72 by a positioning pin 108 press-fitted into the second arm half 72.
- a third switching pin 57 is movably fitted to the inner peripheral portion of the second cylindrical shaft 107, and a circlip 83 that restricts the movement of the third switching pin 57 is provided. Yes.
- the first cylindrical shaft 104 and the second cylindrical shaft 107 are located on the same axis as the support shaft 62 of the first rocker arm 52 in a predetermined state.
- the predetermined state here is a state in which the first rocker arm 52 and the second rocker arm 54 are both supported by the rocker shaft 37 and the first rocker arm 52 is in contact with the stopper 78.
- the camshaft 14 includes a first cam 111 that contacts the roller 51 of the first rocker arm 52 and the first and second of the second rocker arm 54. And two second cams 112 that come into contact with the cam followers 101 and 102.
- the first cam 111 has a nose portion 111a and a base circle portion 111b.
- the second cam 112 has a nose portion 112a and a base circle portion 112b.
- the protruding amount of the nose portion 112 a of the second cam 112 is smaller than the protruding amount of the nose portion 111 a of the first cam 111.
- the first rocker arm 52 and the second rocker arm 54 are connected and integrated, whereby the intake valve 8 or the exhaust valve 9 is driven by the first cam 111. Further, when the first rocker arm 52 and the second rocker arm 54 are separated, the intake valve 8 or the exhaust valve 9 is driven by the second cam 112. Therefore, according to this embodiment, the first drive mode in which the valve lift amount of the intake valve 8 or the exhaust valve 9 is increased, and the second drive mode in which the valve lift amount of the intake valve 8 or the exhaust valve 9 is decreased. It is possible to provide an engine valve gear that can be switched between forms.
- the rocker housing unit 31 used when adopting the first and second embodiments described above is one in which the first and second rocker shaft support portions 34 and 35 and the connecting portion 36 are integrally formed. .
- these three functional parts of the rocker housing unit 31 can be formed individually.
- a member that becomes the first rocker shaft support portion 34 and a member that becomes the second rocker shaft support portion 35 are coupled to the member that becomes the connecting portion 36 with a bolt (not shown), thereby providing a rocker housing.
- a single body 31 can be formed.
- the pressing element of the switching mechanism 3 is configured by the hydraulic piston 46
- the pressing element can be constituted by a swinging lever.
- the lever is swingably supported by the rocker housing unit 31 in a state where one swinging end portion is in contact with the third switching pin 57 and the other end portion is in contact with the hydraulic piston 46.
- SYMBOLS 1 Valve operating apparatus, 2 ... Engine, 3 ... Switching mechanism, 4 ... Cylinder head, 5 ... Intake camshaft, 6 ... Exhaust camshaft, 8 ... Intake valve, 9 ... Exhaust valve, 12 ... Cam, 14 ... Camshaft 31 ... Rocker housing unit, 37 ... Rocker shaft, 46 ... Hydraulic piston, 52 ... First rocker arm, 54 ... Second rocker arm, 55 ... First switching pin, 56 ... Second switching pin, 57 ... third switching pin, 57a ... large diameter part, 57b ... small diameter part, 60 ... roller, 61 ... shaft hole, 63 ... first pin hole, 64 ...
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- Engineering & Computer Science (AREA)
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- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
カムシャフトは、高速用カムと、この高速用カムの両側に位置する二つの低速用カムとを有している。高速用カムは、低速用カムよりバルブリフト量が相対的に多くなる形状に形成されている。
メインアームは、カムシャフトの低速用カムが接触するスリッパを有しており、ロッカーシャフトに揺動自在に支持されている。このメインアームは、吸気弁または排気弁のバルブスプリングによって低速用カムに向けて付勢されている。
以下、本発明に係るエンジンの動弁装置およびロッカーアームの製造方法の一実施の形態を図1~図14によって詳細に説明する。
1/2減筒運転形態は、運転される気筒が異なる第1の運転形態と第2の運転形態とにおいて実現可能である。第1の運転形態は、4つの気筒が並ぶ方向の一端に位置する気筒(第1気筒)と、一端から数えて4番目の気筒(第4気筒)とが運転される運転形態である。第2の運転形態は、4つの気筒が並ぶ方向の一端から数えて2番目の気筒(第2気筒)と、3番目の気筒(第3気筒)とが運転される運転形態である。
全気筒休止形態は、例えばアクセルオフ時に切替えられる。全気筒休止形態が採られると、各気筒において断熱圧縮と断熱膨張とが繰り返されるだけで燃焼室に対する吸気、排気の出入りがなくなるから、ポンピングロスを低減することができる。
隔壁22の上端部には、図1に示すように、吸気カムシャフト5を支持するための吸気側ジャーナル部23と、排気カムシャフト6を支持するための排気側ジャーナル部24とが形成されている。これらのジャーナル部23,24には、カムキャップ25が複数の取付用ボルト26(図2参照)によって取付けられている。
第1のロッカーシャフト支持部34は、図6に示すように、支持壁部32に取付けられる基部34aと、この基部34aから上方に突出した凸部34bとを有している。凸部34bには、ロッカーシャフト37の一端部が嵌合する2つの円形孔38が形成されている。
油圧ピストン46は、図4に示すように、シリンダ孔45から突出する押圧用プレート46aを有している。この押圧用プレート46aは、シリンダ孔45よりカムシャフトの軸線とは直交する方向に大きく形成されている。
ロッカーハウジング単体31の連結部36は、カムシャフト14の軸線方向に延びる板状に形成されている。この連結部36には、上述した支持壁部32の円形開口(不図示)に同心的に連なるよう円形穴36aが貫通形成されている。
第1のアーム片52aと第2のアーム片52bとの間には、ローラ51が挿入されている。このローラ51は、カム12に接触する回転体からなるカムフォロアを構成するものである。
第2のアーム半部72の中間部分には、貫通孔からなる第3のピン孔82が形成されている。第3のピン孔82には、詳細は後述するが、第1の切替ピン55の一部と第3の切替ピン56とが収容される。第3のピン孔82の一端部(第1のアーム半部71とは反対側に位置する端部)には、サークリップ83が設けられている。このサークリップ83は、請求項6記載の発明でいう「抜け止め部材」に相当するものである。
この円盤部77と突起76との間には、図3に示すように、第2のロッカーアーム54の弁押圧部53がシム19に接触している状態において、隙間d1が形成されている。突起76は、第2のロッカーアーム54が振動等によりカムシャフト14に向けて跳ねて揺動したときに円盤部77に当たり、それ以上の第2のロッカーアーム54の揺動を規制する。
第1のアーム半部71と第2のアーム半部72におけるロッカーシャフト37に支持される基部どうしは、第2の連結部74によって互いに連結されている。この実施の形態においては、第2の連結部74によって請求項3記載の発明でいう「連結部」が構成されている。
第2のアーム半部72における第1のロッカーアーム52と対向する内側面には、図示してはいないが、第1のアーム半部71と同様に凹部65が形成されている。第3のピン孔82は、この凹部65内に開口している。第1のアーム半部71の凹部65と、第2のアーム半部72の凹部65とは、ロッカーシャフト37の軸線方向から見て同一位置に、同一形状に形成されている。
揺動開始位置とは、カム12のベース円部12aにローラ51が接触しているときの第1のロッカーアーム52の位置である。最大揺動位置とは、ノーズ部12bの最も突出量が多くなる部位がローラ51と接触しているときの第1のロッカーアーム52の位置である。
第2のロッカーアーム54の第2のピン孔81と第3のピン孔82は、図8に示すように、第1のアーム半部71と第2のアーム半部72を横切るようにロッカーシャフト37の軸線と平行に延びている。
第2のピン孔81には、図8に示すように、第2の切替ピン56が移動自在に嵌合しているとともに、この第2の切替ピン56を第1のロッカーアーム52に向けて付勢するばね部材85が設けられている。第2の切替ピン56は、有底円筒状に形成されており、底部が第1の切替ピン55と対向する状態で第2のピン孔81内に挿入されている。
第3の切替ピン57の軸線方向の長さは、図8中に二点鎖線で示すように、第3のピン孔82の長さより僅かに短い。このため、油圧ピストン46が第2のアーム半部72に当たるまで前進したとしても、第3の切替ピン57の全体が第2のアーム半部72の中に収容され、第1の切替ピン55の両端部が第1のロッカーアーム52から略均等に突出する。
この実施の形態による第1~第3の切替ピン55~57の外径は、図3に示すように、第1のロッカーアーム52が第2のロッカーアーム54に対して揺動したとしても、軸線方向から見て一部が常に互いに対向する大きさに設定されている。
この切替機構3は、図4に示すように、第1の押圧部91と第2の押圧部92とを有している。第1の押圧部91は、第1~第3の切替ピン55~57における軸線方向の一端(第2の切替ピン56)を軸線方向の他端側に向けて押す。第2の押圧部92は、第1~第3の切替ピン55~57における軸線方向の他端(第3の切替ピン57)を軸線方向の一端側に向けて押す。この実施の形態による第1の押圧部91は、第2のロッカーアーム54に設けられたばね部材85によって構成されている。
第4のステップにおいては、図14に示すように、第1のロッカーアーム52と第2のロッカーアーム54とにロッカーシャフト37を通すための貫通孔58,75をドリル95で共加工する。言い換えれば、保持された第1のロッカーアーム52と第2のロッカーアーム54とにドリル95が通され、ロッカーシャフト37を通すための穴(貫通孔58,75)が加工される。
このような製造方法を採用することにより、エンジン組み立て状態において、第1のロッカーアーム52が第2のロッカーアーム54のストッパ78に当接したとき、すなわち吸気弁8または排気弁9が閉じているとき、各ロッカーアーム52,54のピン孔(第1~第3のピン孔63,81,82)が高精度に整列する。
仮組ステップにおいては、ローラ51および第1の切替ピン55が組み付けられた第1のロッカーアーム52と、第2、第3の切替ピン56,57およびばね部材85が組み付けられた第2のロッカーアーム54とを組み合わせて一つの組立体を形成する。この際、第1の切替ピン55の凸部64を第2のロッカーアーム54の凹部65内に開口部84から挿入する。
第1~第3の切替ピン55~57は、同一軸線上に保持されていると、連結位置と非連結位置との間を容易に移動することができる。
したがって、この実施の形態によれば、第1のロッカーアーム52と第2のロッカーアーム54とが一体化される連結状態と、分離する非連結状態とを切替えるときに第1~第3の切替ピン55~57が容易かつ確実に移動するエンジンの動弁装置を提供することができる。
このため、この実施の形態によれば、第1のロッカーアーム52が第2のロッカーアーム54より復帰方向へ過度に揺動することを防ぐことができる。
このため、専らストッパ78として機能する部材を第2のロッカーアーム54に取り付ける場合と較べて省スペース化を図ることができるとともに、ストッパ78を簡易に得ることができる。
したがって、この実施の形態によれば、軽量化と低コスト化とを図りながらストッパ78を備えることができる。しかも、ストッパ78を兼用した第2の連結部74が基部に設けられているから、ロッカーシャフト回りの慣性モーメントを小さくできる。このため、この第2のロッカーアーム54は、ストッパ78を備えているにもかかわらず、高速で揺動することが可能なものとなる。
なお、ストッパ78を設ける位置は、第2の連結部74に限定されることはない。すなわち、ストッパ78は、第2のロッカーアーム54の第1、第2のアーム半部71,72や第1の連結部73に設けることができる。
このため、この実施の形態によれば、ストッパ78がデッドスペース内に設けられるから、動弁装置1が大型化することなくストッパ78を装備することができる。
このため、サークリップ83で第3の切替ピン57の抜け止めを行うことができるから、この第3の切替ピン57を第2のロッカーアーム54に組付ける作業を容易に行うことができる。また、油圧ピストン46が非作動状態で第1~第3の切替ピン55~57が連結位置にあるとき、第3の切替ピン57は第2のロッカーアーム54と共に上下に揺動する。しかし、その際、第3の切替ピン57が不必要に油圧ピストン46に押し付けられることがない。このため、この第3の切替ピン57と油圧ピストン46との接触部が磨耗し難い。
本発明に係るエンジンの動弁装置は、図15および図16に示すように構成することができる。図15および図16において、図1~図14によって説明したものと同一もしくは同等の部材については、同一符号を付し、詳細な説明は省略する。
この実施の形態による第2のロッカーアーム54は、第1のカムフォロア101と第2のカムフォロア102とを備えている。これらのカムフォロア101,102は、それぞれ第1のロッカーアーム52のローラ51と同径のローラによって構成されている。
一方、この実施の形態によるカムシャフト14は、図16に示すように、第1のロッカーアーム52のローラ51に接触する第1のカム111と、第2のロッカーアーム54の第1、第2のカムフォロア101,102に接触する2つの第2のカム112とを備えている。第1のカム111は、ノーズ部111aとベース円部111bとを有している。第2のカム112は、ノーズ部112aとベース円部112bとを有している。
第2のカム112のノーズ部112aの突出量は、第1のカム111のノーズ部111aの突出量より少ない。
このため、この実施の形態によれば、吸気弁8または排気弁9のバルブリフト量が多くなる第1の駆動形態と、吸気弁8または排気弁9のバルブリフト量が少なくなる第2の駆動形態とを切替えることが可能なエンジンの動弁装置を提供することができる。
Claims (7)
- 吸気弁または排気弁を駆動するためのカムを有するカムシャフトと、
前記カムシャフトと平行なロッカーシャフトと、
前記ロッカーシャフトに揺動自在に支持され、前記カムによって押されて揺動する第1のロッカーアームと、
前記第1のロッカーアームが前記カムによって押されて揺動する方向とは逆方向である復帰方向へ前記第1のロッカーアームを付勢するばね部材と、
前記ロッカーシャフトに揺動自在に支持され、前記吸気弁または前記排気弁を押圧する弁押圧部が揺動端部に設けられた第2のロッカーアームと、
前記第1のロッカーアームおよび第2のロッカーアームにおける前記ロッカーシャフトから等距離の位置に、それぞれ前記ロッカーシャフトの軸線と平行に形成されたピン孔と、
前記ピン孔に前記ロッカーシャフトの軸線方向へ移動自在に設けられた切替ピンと、
前記切替ピンを前記軸線方向に移動させることにより、前記切替ピンが前記第1のロッカーアームと前記第2のロッカーアームとに跨がる連結状態と、前記切替ピンが前記両ロッカーアームに跨がることがない非連結状態とを切替える切替機構とを備え、
前記第2のロッカーアームは、前記非連結状態でかつ前記吸気弁または排気弁が閉じている状態において、前記復帰方向へ揺動する前記第1のロッカーアームが当接するストッパを有し、前記第1のロッカーアームが前記ストッパに当接したとき、全ての前記ピン孔が同一軸線上に位置付けられることを特徴とするエンジンの動弁装置。 - 請求項1記載のエンジンの動弁装置において、
前記第1のロッカーアームが前記ストッパに当接することにより前記ばね部材のばね力が前記ストッパを介して前記第2のロッカーアームに伝達され、前記第2のロッカーアームが前記ばね部材のばね力によって前記復帰方向に付勢されることを特徴とするエンジンの動弁装置。 - 請求項1または請求項2記載のエンジンの動弁装置において、
前記第2のロッカーアームは、
前記第1のロッカーアームを前記軸線方向の両側から挟む位置に配設された一対のアーム半部と、
これらのアーム半部に一体形成され、両アーム半部における前記ロッカーシャフトに支持される基部どうしを連結する連結部とを有し、
前記ストッパは、前記連結部に設けられていることを特徴とするエンジンの動弁装置。 - 請求項3記載のエンジンの動弁装置において、
前記第1のロッカーアームは、前記カムが接触するカムフォロアを有し、
前記連結部は、前記第1のロッカーアームが前記ストッパに当接する第1のロッカーアームのストッパ当接位置において、前記ロッカーシャフトの軸方向から見て、前記カムと、前記カムフォロアと、前記ロッカーシャフトとによって囲まれる凹空間に位置していることを特徴とするエンジンの動弁装置。 - 請求項1ないし請求項4のうちいずれか一つに記載のエンジンの動弁装置において、
前記切替ピンは、
前記第1のロッカーアームに設けられた第1の切替ピンを含み、かつ前記連結状態で同一軸線上に並ぶ複数のピンによって構成され、
前記第1の切替ピンの前記軸線方向の長さは、前記第1のロッカーアームの前記軸線方向の幅より長く、
前記第2のロッカーアームにおける前記第1のロッカーアームと対向する側壁には、前記第1の切替ピンにおける第1のロッカーアームより突出した凸部を収容する凹部が形成され、
前記凹部は、
前記第1のロッカーアームが前記ロッカーシャフトに支持されている状態であってかつ前記非連結状態において、前記凸部の通過を規制することなく前記第1のロッカーアームが前記第2のロッカーアームに対して揺動開始位置と最大揺動位置との間で揺動することを許容する非規制部と、
前記第1のロッカーアームが前記ロッカーシャフトに支持されている状態であってかつ前記非連結状態において、前記凸部の通過を規制することにより前記第1のロッカーアームが前記第2のロッカーアームに対して前記最大揺動位置を越えて揺動することを規制する規制部とを有し、
前記規制部は、前記第1のロッカーアームが前記ロッカーシャフトに支持されていない状態においては、前記凸部の通過を許容する形状に形成されていることを特徴とするエンジンの動弁装置。 - 請求項1ないし請求項5のうちいずれか一つに記載のエンジンの動弁装置において、
前記切替機構は、
前記切替ピンにおける軸線方向の一端を前記軸線方向の他端側に向けて押す第1の押圧部と、
前記切替ピンにおける軸線方向の他端を前記軸線方向の一端側に向けて押す第2の押圧部とを有し、
前記第1の押圧部と第2の押圧部のうち、いずれか一方の押圧部は、
前記カムシャフトを有するシリンダヘッドに固定された支持部材と、
前記支持部材に移動自在に設けられて前記切替ピンの先端を押す押圧子とを有し、
この押圧子によって押される前記切替ピンは、
前記ロッカーアームに移動自在に嵌合する大径部と、
この大径部から前記ロッカーアームの外に向けて突出して前記押圧子と対向する小径部とを有し、
この切替ピンを支持するロッカーアームは、前記大径部と小径部との境界部分に形成された段部に接触する抜け止め部材を備えていることを特徴とするエンジンの動弁装置。 - 請求項1ないし請求項6のうちいずれか一つに記載のエンジンの動弁装置に用いられ、前記第1のロッカーアームにおける前記カムが接触するカムフォロアが回転体で、この回転体が前記第1のロッカーアームの軸孔に嵌合される支軸に回転自在に支持され、かつ前記支軸には前記第1のロッカーアームの前記ピン孔となる中空部を有するロッカーアームの製造方法であって、
前記第1のロッカーアームの前記軸孔に嵌合する外径を有するとともに前記第2のロッカーアームのピン孔と内径が一致する円筒状治具が前記支軸の代わりに前記軸孔に嵌合される第1のステップと、
前記第2のロッカーアームの前記ピン孔と前記円筒状治具の中空部とに前記切替ピンの代わりに1本の棒状治具が嵌合される第2のステップと、
前記第1のロッカーアームが前記第2のロッカーアームの前記ストッパに当接した状態で保持される第3のステップと、
保持された前記第1のロッカーアームと第2のロッカーアームとにドリルが通され、前記ロッカーシャフトを通すための穴が加工される第4のステップとを有することを特徴とするロッカーアームの製造方法。
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Patent Citations (6)
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JPS61122308U (ja) * | 1985-01-21 | 1986-08-01 | ||
JPS61250318A (ja) * | 1985-04-26 | 1986-11-07 | Mazda Motor Corp | エンジンの動弁装置 |
JPH086569B2 (ja) * | 1987-07-13 | 1996-01-24 | 本田技研工業株式会社 | 内燃機関の動弁装置 |
JPH01176704U (ja) * | 1988-05-31 | 1989-12-18 | ||
JPH1018826A (ja) * | 1996-06-28 | 1998-01-20 | Otix:Kk | 可変動弁機構 |
JP2014062500A (ja) * | 2012-09-21 | 2014-04-10 | Otics Corp | 内燃機関の可変動弁機構 |
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US11193403B2 (en) * | 2017-06-30 | 2021-12-07 | Yamaha Hatsudoki Kabushiki Kaisha | Valve spring retainer and internal combustion engine |
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Publication number | Publication date |
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JP6244473B2 (ja) | 2017-12-06 |
EP3203044A1 (en) | 2017-08-09 |
JPWO2016052729A1 (ja) | 2017-06-22 |
EP3203044A4 (en) | 2017-08-09 |
EP3203044B1 (en) | 2019-12-04 |
US20170298787A1 (en) | 2017-10-19 |
US10215063B2 (en) | 2019-02-26 |
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