JP3966149B2 - Continuously variable valve operating device for internal combustion engine - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a continuously variable valve operating apparatus for an internal combustion engine in which a valve lift amount of a reciprocating valve can be continuously changed using movement of a swing fulcrum of a swing lever.
[0002]
[Prior art]
A gasoline engine (internal combustion engine) is equipped with a continuously variable valve system, and the work of the throttle bubble (adjustment of the intake air amount) is replaced by a reciprocating valve on the intake side, that is, an intake valve, and the pump that the throttle bubble brings It is attempted to reduce the loss.
[0003]
Conventionally, a structure using a swing lever having a swing fulcrum at the upper end portion and a contact surface contacting the intake valve at the lower end portion has been proposed for this continuously variable valve apparatus.
[0004]
For this purpose, a control shaft formed of an eccentric body that can move eccentrically is arranged on one side of the upper part with a rocking lever in between, and a drive cam is arranged in the middle part opposite to the control shaft with the rocking lever in between. Using the eccentric displacement of the control shaft, the swing fulcrum of the swing lever can be moved between the control shaft and the drive cam, and it is necessary to open the valve from the input part formed in the middle part of the swing lever by the drive cam A variable valve mechanism that inputs an appropriate driving force is employed. That is, when the swing fulcrum of the swing lever is swung by the eccentric displacement of the control shaft, the region of the contact surface where the swing lever is tilted and is in contact with the intake valve moves. On the contact surface of the swing lever, a base circle section and a lift section that determines the valve lift amount of the intake valve are formed in series along the control shaft and the drive cam. The valve lift amount of the intake valve is continuously varied by moving the area between the base circle section and the lift section that are in contact with each other. Using the continuously variable valve lift amount, the work of adjusting the intake air amount performed by the throttle valve is substituted (see, for example, Patent Document 1).
[0005]
[Patent Document 1]
JP-A-7-63023 (FIGS. 6 to 8)
[0006]
[Problems to be solved by the invention]
However, even when the eccentric cam is fixed at a certain position, the swing fulcrum moves during the movement of the swing lever. Therefore, it is necessary to maintain the valve closed state by the movement of the swing lever and the roller contact surface shape.
[0007]
For this reason, each component has a difficulty in requiring high machining accuracy.
[0008]
Therefore, the swing fulcrum of the swing lever is held by the lever member so as to swing freely between the control shaft and the cam shaft, and a spring force is applied to the swing lever so that the swing lever It is conceivable to press against the camshaft.
[0009]
In this case, since many parts are laid out in the upper part of the cylinder head, a spring member for applying a spring force is arranged at a point avoiding these parts. During the swinging of the moving lever, there is a possibility that the pressing load may come off in some situations. For this reason, it is difficult to ensure the intended valve lift.
[0010]
SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a continuously variable valve operating apparatus for an internal combustion engine that can stably and accurately control the valve lift amount.
[0011]
[Means for Solving the Problems]
The invention according to claim 1 in order to achieve the above object, the side of the swing lever, one end is connected freely rotating the rocking fulcrum of the swing lever and the other end reciprocally A holding mechanism that pivotally supports the cylinder head at a position that defines the state when the valve is closed, and that pivotally supports the swing fulcrum of the swing lever around the position that defines the state when the valve is closed. the lever is provided, between the swing lever and the retaining lever, and supporting one end portion of the wire forming the winding portions to the rocking lever, to support the other end to the holding lever, swinging around the shaft portion A configuration in which a biasing force in the expanding direction is applied to the lever and the holding lever and a coiled spring member that changes the biasing force according to the variable valve lift amount is employed.
[0012]
With this configuration, during the swing of the swing lever, the swing support point of the swing lever is always fixed on the locus of a circular arc centered on the position that defines the closed state by the holding lever. For this reason, regardless of the magnitude of the valve lift amount, the swing lever is always adjusted for swing displacement based on the valve closing time. In addition, during this swing, the swing lever and the holding lever are given a spring force (biasing force) that is always generated according to the relative angle between the two from the coiled spring member provided around the connecting portion. Therefore, in any situation, the upper end portion of the swing lever is kept in contact with the eccentric body, and the input portion in the middle portion of the swing lever is kept in contact with the drive cam. That is, a normal valve lift control operation is guaranteed.
[0013]
Therefore, the variation in the opening / closing timing of the reciprocating valve is eliminated, and the valve lift amount can be controlled stably and accurately. Moreover, since the coil spring member is assembled to the connecting portion that connects the swing lever and the holding lever, it is not necessary to be restricted by the components laid out above the cylinder head.
[0014]
In addition to the above object, the invention described in claim 2 is provided with holding levers on both sides of the rocking lever so that the bubble lift amount can be controlled with higher accuracy, and the rocking lever is centered on both sides of the rocking lever. As a configuration, a coiled spring member is provided symmetrically to prevent the occurrence of an unbalanced load on the swing lever.
[0015]
According to a third aspect of the present invention, in addition to the above object, one end of the reciprocating valve is swingably supported by a support member so that the swinging fulcrum of the swinging lever can be supported with high accuracy. A rocker arm type having a rocker arm that supports a rotatable roller that comes into contact with the contact surface and a valve body that is opened and closed by swinging the other end of the rocker arm is used. one end to the swing fulcrum pivoted rotatably connected to the swing lever, the other turned in the holding portion formed in the cylinder head roller axis position of the rocker arm end when closed freely supporting lever A member was used.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described based on the first embodiment shown in FIG. 1 and FIG.
[0017]
In FIG. 1, reference numeral 1 denotes a plane of a cylinder head of an internal combustion engine, for example, a multi-cylinder reciprocating gasoline engine. The cylinder head 1 is provided with a combustion chamber (not shown) for each cylinder along the longitudinal direction. An intake port and an exhaust port (both not shown) are provided for each combustion chamber. In the upper part of the cylinder head 1, a valve operating system is provided for each intake port and each exhaust port. Among these valve systems, a continuously variable valve apparatus 2 that substitutes the work of the throttle valve is assembled in the valve system on the intake side.
[0018]
2 shows the configuration of the continuously variable valve gear 2 taken along the line AA in FIG. 1, FIG. 3 shows a cross-sectional view taken along the line BB in FIG. 1, and FIG. FIG. 6 shows an exploded view of the continuously variable valve operating device 2.
[0019]
The continuously variable valve operating apparatus 2 will be described. Reference numeral 4 in FIGS. 2 and 6 denotes a pair of intake valves (only one set is shown: corresponding to a reciprocating valve) assembled to the cylinder head 1 for each cylinder. A rocker arm type valve structure using a rocker arm 5 is used for the intake valve 4 constituting the valve train.
[0020]
Specifically, the rocker arm 5 is formed of a substantially plate-like member extending in a direction perpendicular to the direction in which the cylinders are arranged, for example. The end of the rocker arm 5 disposed on the center side of the combustion chamber swings to a support member, for example, a rocker shaft 6 disposed along the direction in which the cylinders are arranged as shown in FIGS. It is supported freely. The end of the rocker arm 5 on the combustion chamber end side is in contact with the end of a shaft portion 7a extending from a pair of umbrella-shaped valve bodies 7 that are reciprocally attached to the intake port. The valve body 7 is urged in a closing direction, here upward, by a valve spring (not shown) so as to always return to the closed state. A rocker arm roller 8 (corresponding to a roller) is rotatably mounted in the middle of the middle part of the rocker arm 5 in parallel with the rocking shaft of the rocker arm 5. Thereby, when the rocker arm roller 8 is pressed from the upper side, the rocker arm 5 is oscillated and displaced, and the valve body 7 is opened. That is, the intake valve 4 has a structure that opens and closes the intake port when the rocker arm 5 swings and the valve body 7 reciprocates.
[0021]
Reference numeral 10 denotes a variable valve mechanism that constitutes the continuously variable valve apparatus 2. As shown in FIGS. 1 to 4 and 6, the variable valve mechanism 10 is assembled immediately above the intake valve 4 for each cylinder. These variable valve mechanisms 10 all have the same structure. The structure of one of them will be described. Reference numeral 11 denotes a pair of wall-like holders (corresponding to holding parts) which are located on both sides of the rocker arm 5 and are erected on the upper part of the cylinder head 1, and 12 is a rocker arm, for example. The control shaft 13 disposed above the rocking fulcrum 5 and disposed along the cylinder row direction, for example, 13 is disposed substantially above the rocking end of the rocker arm 5 and disposed along the cylinder row direction. It is a camshaft. The camshaft 13 is aligned with the control shaft 12. These shafts 12 and 13 pass through the respective holders 11 arranged for each cylinder so as to be freely rotatable. That is, the shafts 12 and 13 are rotatably supported by the holders 11. The end of the rocker shaft 6 is also supported through the holder 11. Among these, the control shaft 12 is connected to a control drive source, for example, a control motor 14. Thus, the control shaft 12 is rotated by a desired amount of displacement by the operation of the control motor 14 (both clockwise and counterclockwise). The camshaft 13 is connected to a crankshaft (not shown) assembled to a cylinder block (parts to be combined with the cylinder head 1) via a timing gear, a timing chain, and a crank gear (not shown). is there. Thereby, the camshaft 13 is driven to rotate (clockwise) by the crank output.
[0022]
A rocking lever 15 having, for example, a substantially L shape is disposed immediately above the rocker arm roller 8 as shown in FIGS. The rocking lever 15 has a lower portion extending in the lateral direction (rocking fulcrum to rocking end) along the rocker arm roller 8 as a short side, passes between the control shaft 12 and the crankshaft 13 and extends between them. A plate-like component having an upper portion extending upward as a longitudinal side is used. The lower end surface on the short side is brought into contact with the outer peripheral surface of the rocker arm roller 8. The lower end surface on the short side is a contact surface 16 with respect to the rocker arm roller 8.
[0023]
As shown in FIG. 2, the upper end portion of the swing lever 15 is adjacent to the control shaft 12, and the intermediate portion is adjacent to the camshaft 13. Among them, a holding shaft 17 (corresponding to a shaft portion) formed of, for example, a short shaft member is fixed to the upper end portion of the swing lever 15 so as to penetrate in the cylinder row direction. The holding shaft 17 forms a swing fulcrum A at the upper end of the swing lever 15. The swing fulcrum A is a side of the swing lever 15 and a holding lever disposed between the swing lever 15 and the holder 11, for example, a pair of L-shaped holding levers 18. 4 is held between the control shaft 12 and the camshaft 13 so as to be swingable around a position that defines the state when the valve 4 is closed. Specifically, for example, the pair of holding levers 18 has a through hole portion 19 in the upper portion as shown in FIG. 6, and a shaft portion 20 that protrudes laterally parallel to the axis of the through hole portion 19 in the lower portion. An L-shaped lever member having a length from the center of the through-hole portion 19 to the center of the shaft portion 20 as a length dimension from the swing fulcrum A to the center of the rocker arm roller 8 when the valve is closed is used. Yes (FIG. 6 shows only one side). As shown in FIGS. 3 and 4, the through hole 19 of each holding lever 18 is rotatably inserted into each holding shaft end of the swing lever 15 and is connected to the upper end of the swing lever 15. The upper end portions of the holding shaft 17 and the holding lever 18 are connected to the connecting portion J, and the swing lever 15 and the holding lever 18 are rotatably connected. Each shaft portion 20 is rotatably fitted in a support hole 21 formed in the lower portion of each holder 11 in accordance with the center position of the rocker arm roller 8 when the valve is closed. As a result, the swing fulcrum A of the swing lever 15 can be moved around its axis centering on the roller center of the rocker arm roller 8 when the valve is closed.
[0024]
Further, around the end of the holding shaft (one side) into which the holding lever 18 is inserted, a coiled spring member, for example, a short-length coil spring member 24 is assembled as shown in FIG. Specifically, for example, as shown in FIG. 6, the coil spring member 24 includes a winding portion 25 in which the strands are spirally wound and ends of the strands protruding from the respective end portions in the axial direction. It consists of parts having parts 26a and 26b. Of these, the winding portion 25 is fitted around a part of the upper end portion of the holding lever 18, for example, the boss portion 18b protruding forward from the lever main body 18a, as shown in FIG. An end 26a protruding toward the swing lever 15 is inserted into a locking hole 15a formed on the side of the swing lever 15 and locked to the swing lever 15, and is an end protruding toward the holding lever 18 side. The portion 26 b is inserted into a locking hole 18 c formed on the side of the holding lever 18 and locked to the holding lever 18. The coil spring member 24 is assembled in a state in which the winding portion 25 is twisted in the direction of reducing the diameter. The spring force caused by the torsional displacement causes each of the swing lever 15 and the holding lever 18 to be assembled. The biasing force is given in the direction of spreading around the holding shaft 17 (swinging fulcrum A).
[0025]
The cam surface of a plate-shaped eccentric cam 12a (corresponding to an eccentric body) in which a circular contact surface 22 formed on the outer peripheral surface of the upper end portion of the swing lever 15 is eccentrically provided on the control shaft 12 by this urging force. It is made to contact | abut with respect to (outer peripheral surface) from a horizontal direction. In addition, the outer peripheral surface of the roller 23 provided in the intermediate side portion adjacent to the camshaft 13 in the swing lever 14 is the cam surface (outer peripheral surface) of the drive cam 13a provided in the camshaft 13, for example, in a substantially triangular circle shape. It is made to contact | abut from the downward direction (or horizontal direction) with respect to. When the eccentric cam 12a is displaced eccentrically by the structure in which the contact surface 22 is pressed against the eccentric cam 12a, the swing fulcrum A of the swing lever 14 follows the movement of the eccentric cam 12a, and the shaft of the rocker arm roller 8 is moved. I move around my heart. Further, the structure in which the roller 23 is pressed against the drive cam 13a is configured so that the roller 23 is periodically pressed as the camshaft 13 rotates. The roller 23 is used as an input portion to drive the intake valve 4 from the drive cam 13a. A driving force necessary for opening the valve is input to the swing lever 15.
[0026]
That is, if the swinging fulcrum A of the swinging lever 15 is moved by the eccentric displacement of the control shaft 12 while the swinging lever 15 is swinging by the drive cam 13a, the tilt angle of the swinging lever 15 changes, and the rocker arm roller The area of the contact surface 16 that contacts the 8 moves.
[0027]
A base circle section corresponding to the base circle of the drive cam 13a is formed on the contact surface 16 on the control shaft 12 side. The base circle section is formed on an arc surface having a base circle radius with the value obtained by subtracting the roller radius from the distance between the swing fulcrum A and the center of the rocker arm roller centered on the swing fulcrum A. On the opposite camshaft 13 side, a lift section formed by an arcuate surface in the opposite direction continuous with the base circle section is formed. This lift section is formed by a circular arc for determining the valve lift amount of the intake valve 4 set in advance, and when the tilt angle of the swing lever 15 changes, the base circle section and the lift section where the rocker arm roller 8 goes and goes Is changed so that the valve lift amount of the intake valve 4 can be continuously varied.
[0028]
That is, if the eccentric cam 13a is rotationally displaced by the control motor 14 so as to give the largest amount of movement as shown in FIG. The swing fulcrum A of the lever 15 moves to the point farthest from the control shaft 12 around the axis of the rocker arm roller 8 when the valve is closed. Then, the swing lever 15 is displaced in the direction in which the roller 23 serving as the input portion and the drive cam 13a are in contact with each other. As a result, the rocker arm roller 8 crosses the region defined by the swing fulcrum of the swing lever 15, that is, the narrowest base circle section and the longest lift section as shown in FIG. Thus, control for ensuring the maximum valve lift amount is performed.
[0029]
When the eccentric cam 13a is rotationally displaced by the control motor 14 so as to have the smallest movement amount as shown in FIG. 5B while the swing lever 15 is swinging, the swing lever 15 swings. The fulcrum A moves to the point closest to the control shaft 12 around the axis of the rocker arm roller 8 when the valve is closed. Then, the swing lever 15 is displaced in a tilting direction while the roller 23 serving as the input portion and the drive cam 13a are in contact with each other. Thereby, the rocker arm roller 8 comes and goes between the region defined by the swing fulcrum of the swing lever 15, that is, the longest base circle section and the shortest lift section as shown in FIG. Thus, control for ensuring the minimum valve lift amount is performed. That is, by the movement of the swing fulcrum A, the maximum valve lift amount is continuously controlled from the minimum valve lift amount.
[0030]
Thus, during the swing of the swing lever 15, the swing support point of the swing lever 15 is fixed by the holding lever 18 on an arc locus centering on the position defining the valve closing state. In both the large lift amount control as shown by X in the diagram and the small lift amount control as shown in Y, the swing displacement is always adjusted based on the valve closing, and the intended opening and closing The intake valve 4 is opened and closed at the time.
[0031]
Moreover, during the swinging of the swinging lever 15, both the swinging lever 15 and the holding lever 18 are always connected from the coil spring member 24 as shown by the two-dot chain line in FIGS. 5 (a) and 5 (b). Since the load (spring force) according to the relative angle is applied, the swing lever 15 and the eccentric cam 12a and the roller 23 of the swing lever 15 and the drive cam 13a can be kept in contact in any situation. Therefore, it is possible to promise (guarantee) the control operation of the normal valve lift amount.
[0032]
Therefore, the valve lift amount can always be stably controlled with high accuracy. In addition, since the load applied to the eccentric cam 12a and the drive cam 13a is determined by the relative angle between the swing lever 15 and the holding lever 18, the behavior that the applied load increases with the high valve lift control is obtained, and the friction is reduced. The increase can be suppressed.
[0033]
In addition, since the rocker arm type intake valve 4 is adopted and the swing fulcrum A of the swing lever 15 is movable around the axis of the rocker arm roller 8, the swing support point A of the swing lever 15 can be moved with high accuracy. Support is possible, and the valve lift can be controlled with higher accuracy.
[0034]
In addition, the structure in which the coil spring 24 is provided around the holding shaft 18 is mounted on the cylinder block 1 because a part of the connecting portion J connecting the swing lever 15 and the holding lever 18 is used as an attachment portion. Thus, the height of the engine can be prevented from being increased, and a separate part for mounting the coil spring 24 is not required.
[0035]
FIG. 8 shows a second embodiment of the present invention.
[0036]
This embodiment is a modification of the first embodiment, and instead of the boss formed at the upper end of the swing lever, a short cylindrical spacer member 28 is provided around the end portion of the holding shaft 17. The coil spring 24 is provided around the slidably inserted portion, and an urging force in a direction extending to the swing lever 15 and the holding lever 18 is applied. Even if it does in this way, there exists an effect similar to 1st Embodiment.
[0037]
The second embodiment employs a structure in which the coil springs 24 are provided on both sides of the oscillating lever 15 in symmetrical directions on both sides, not on one side of the oscillating lever 15. With this structure, it is possible to prevent the eccentric load from being generated in the swing lever 15 and to achieve an effect that the valve lift amount can be controlled with higher accuracy.
[0038]
Of course, also in the first embodiment, the coil spring members 24 may be provided symmetrically on both sides of the swing lever 15 as indicated by the two-dot chain line in FIG.
[0039]
However, in FIG. 8, the same parts as those of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
[0040]
The present invention is not limited to the above-described embodiment, and various modifications may be made without departing from the spirit of the present invention. For example, in the above-described embodiment, the coil spring member is used. However, the present invention is not limited to this, and a torsion spring may be used. In the above-described embodiment, the example in which the coiled spring member is assembled to the connecting portion using the holding shaft that passes between the swing lever and the holding lever has been described. However, a shaft portion different from that is used. A coiled spring member may be assembled to the connected portion. For example, in a structure in which the connecting portion has a shaft portion in one of the swing lever and the holding lever and a through hole for receiving the shaft portion in the other, a coiled spring member is provided around the upper end portion of the swing lever or the holding lever. Just assemble. Of course, a coiled spring member may be assembled around the whole of the upper end of the swing lever to the shaft and the upper end of the holding lever. In short, the upper end of the swing lever, the shaft and the upper end of the holding lever What is necessary is just to assemble a coiled spring member to at least a part of the connecting portion formed by the portion.
[0041]
【The invention's effect】
As described above, according to the first aspect of the present invention, the swinging fulcrum of the swinging lever is always a trajectory based on when the valve is closed by the holding lever regardless of the amount of valve lift set. Fixed on top. In addition, during the swinging of the swing lever, the swing lever and the holding lever are always given a spring force (biasing force) according to the relative angle between them by the coiled spring member. The upper end portion of the moving lever and the eccentric body, the input portion of the swing lever and the drive cam are kept in contact with each other, and a normal valve lift control operation is guaranteed.
[0042]
Therefore, the variation in the opening / closing timing of the reciprocating valve is eliminated, and the valve lift amount can be controlled stably and accurately. In addition, since the coiled spring member is provided at the connecting portion that connects the swing lever and the holding lever, assembly that is not affected by the components on the cylinder head can be realized.
[0043]
According to the second aspect of the invention, in addition to the above effects, the swing fulcrum of the swing lever can be supported with high accuracy, and the valve lift amount can be controlled with high accuracy.
[0044]
According to the invention of claim 3, in addition to the above effect, it is possible to prevent the occurrence of an unbalanced load on the swing lever, and it is possible to promise more accurate valve lift control.
[Brief description of the drawings]
FIG. 1 is a plan view showing a continuously variable valve operating apparatus according to a first embodiment of the present invention.
FIG. 2 is a side sectional view taken along line AA in FIG.
FIG. 3 is a front sectional view taken along line BB in FIG.
4 is a side view taken along line CC in FIG. 1. FIG.
FIG. 5A is a side view showing a state of a movable valve mechanism at the time of maximum lift control.
(B) is a side view showing the state of the movable valve mechanism during the minimum lift control.
FIG. 6 is an exploded perspective view showing the structure of a continuously variable valve gear.
FIG. 7 is a diagram showing control of a valve lift amount performed in the apparatus.
FIG. 8 is a front sectional view showing a continuously variable valve gear according to a second embodiment of the present invention.
[Explanation of symbols]
1 ... Cylinder head 4 ... Intake valve (reciprocating valve)
5 ... Rocker arm 6 ... Rocker shaft (support member)
7 ... Valve 8 ... Rocker arm roller (roller)
10 ... Variable valve mechanism 11 ... Holder (holding part)
12a ... Eccentric cam (Eccentric body)
13a ... Driving cam 15 ... Swing lever 16 ... Contact surface 17 ... Holding shaft (shaft portion)
18: Holding lever 23 ... Roller (input part)
24 ... Coil spring member (coiled spring member)
25: Winding portions 26a, 26b: end portions.

Claims (3)

An eccentric body that can be moved eccentrically and a drive cam that can be rotationally driven are arranged in parallel on the upper part of a cylinder head having a reciprocating valve, and a rocking lever that extends along between the eccentric body and the drive cam. It has, and the rocking lever has a front Symbol reciprocating valve abutting abutment surface and the eccentric member receives an eccentric displacement of the eccentric rocking fulcrum to move between said drive cam, becomes an input unit for inputting a driving force for opening said reciprocating valve before SL drive cam Furthermore, when moving the swing support point, wherein the change in the tilt angle of the swing lever reciprocating valve and those A variable valve mechanism that continuously varies the valve lift amount of the reciprocating valve by moving a region of the abutting contact surface;
Wherein provided on the side of the swing lever, which one end is connected freely rotating the swing fulcrum of the swing lever and the other end defining a state when the valve is closed in the reciprocating valve operating The swinging fulcrum of the swinging lever is located between the eccentric body and the drive cam, with the position of the reciprocating valve being pivotally supported at the position that defines the closed state of the reciprocating valve. A holding lever for swinging along
One end of the wire forming the winding portions supported on the swing lever, and supports the other end to said holding lever is provided between the holding lever and the rocking lever, before KiYurado A continuously variable valve for an internal combustion engine, comprising: a coiled spring member that applies an urging force in a direction that expands to the lever and the holding lever, and the urging force changes according to the variable valve lift amount. apparatus. The holding lever is provided on both sides of the swing lever,
2. The continuously variable valve operating apparatus according to claim 1, wherein the coiled spring member is provided on both sides of the swing lever in a symmetric direction about the swing lever. The reciprocating valve is supported by a rocker arm having one end supported by a support member in a swingable manner, and a pivotable roller that is in contact with the contact surface at an intermediate portion, and swinging the other end of the rocker arm. It is composed of a rocker arm type having a valve body that is opened and closed,
Said holding lever is one end connected freely rotating the swing fulcrum of the swing lever, the holding portion second end portion is formed in the cylinder head in the axial position of the roller when closing The continuously variable valve operating apparatus for an internal combustion engine according to claim 1, wherein the continuously variable valve operating apparatus is configured by a lever member rotatably supported on the internal combustion engine.

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