JP2008190449A - Variable valve gear for engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a parting surface from sliding to a radial direction outward and displacing by separating force acting on a first and a second parting body accompanied by bending stress in reciprocating rocking of a rocking cam without unnecessarily increasing the rigidity of the rocking cam. <P>SOLUTION: The rocking cam 40 is divided into the first parting and the second parting body 41, 45 at a flat surface passing through an axis of a camshaft 3, and a fitting projection part 56 projecting higher than a parting reference surface 55 over a whole body in an axial direction of a pair of cam parts 47, 47 and a cylindrical part 48 is formed on a radial direction outside of the parting surface of the first parting body 41. A fitting depressed part 57 depressed deeper than the parting reference surface 55 corresponding to the fitting projection part 56 is formed on a radially outside of the parting surface of the second parting body 45. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a variable valve operating apparatus for an engine, and more particularly to a technique for preventing first and second divided bodies forming a swing cam from separating radially outward.

  Conventionally, it is generally known to change the opening / closing timing of an intake / exhaust valve of an engine and the valve lift according to the operating state of the engine. As an example of such a variable valve operating apparatus, Patent Document 1 discloses that an outer ring is fitted to an eccentric ring provided on a camshaft, and a swing cam that lifts an intake valve is supported on the camshaft so as to be swingable. The displacement of the outer ring accompanying the rotation of the eccentric ring is transmitted to the swing cam by the link means, and this link means is constituted by a restriction link connected to the outer ring and a link connected to the swing cam, and the swing of the restriction link is configured. There is disclosed a system in which the distance between the fulcrum and the axis of the swing cam is changed according to the operating state of the engine.

According to this variable valve device, when the engine speed is high and the load is high, the control link swing support point is brought closer to the center of the swing cam, so that the valve opening start time is advanced and the valve lift amount is increased, and the engine low speed is reduced. By releasing the swing fulcrum at low load, the valve opening start timing can be delayed to reduce the valve lift amount.
JP 2004-301058 A

  By the way, the rocking cam used for control of the valve drive timing in the internal combustion engine needs to be appropriately replaced in order to maintain the valve opening / closing performance when the cam profile surface becomes heavily worn.

  However, in a multi-cylinder engine, a plurality of rocking cams are provided according to the number of cylinders of the engine. For example, when replacing the rocking cam at the center, the rocking cam is removed from the camshaft. Prior to removal, disassembling work for removing all the swing cams adjacent to the shaft end side was required, and workability was poor. Further, in a multi-cylinder engine, it is preferable to form the eccentric wheel integrally with the camshaft in order to secure the positional accuracy between the cylinders when assembling is taken into consideration.

  Therefore, when the worn rocking cam is replaced or when the rocking cam is attached between the eccentric wheels formed integrally with the camshaft, the rocking cam is composed of the first divided body having the cam profile surface and the cam profile. It is conceivable to divide into a second divided body having no surface and fasten with a fastening bolt.

  However, in the swing cam, the tappet that drives the valve to open and close, the cam follower of the rocker arm, etc. are in contact with the cam profile surface. Acceleration occurs.

  For this reason, when the engine is rotated at a high speed, a large stress acts between the first and second divided bodies, and there is a risk that the divided surface slides radially outward and is displaced.

  In order to solve such a problem, it is conceivable to increase the fastening force between the first and second divided bodies or to make the whole thick, but the size and weight of the entire swing cam Will become bigger. Here, since the rocking cam repeats reciprocating rocking motion, it is preferable to reduce its weight as much as possible.

  The present invention has been made in view of such a point, and an object of the present invention is to provide first and second divided bodies when the swing cam is reciprocally swung without unnecessarily increasing the rigidity of the swing cam. It is to prevent the dividing surface from sliding and displacing radially outward due to the separation force acting with bending stress.

  In order to achieve the above-described object, the present invention forms a fitting convex portion and a fitting concave portion that are fitted to each other on the divided surfaces of the first and second divided bodies obtained by dividing the swing cam into two. The feature is as follows.

  Specifically, the present invention is connected to a drive shaft disposed in parallel with an engine crankshaft, a swing cam pivotally supported by the drive shaft to open and close a valve, and the swing cam. The following solution was taken for a variable valve operating device for an engine having a link mechanism that changes the valve lift characteristics by controlling the swing range of the swing cam according to the operating state of the engine. .

That is, in the invention of claim 1, two of the valves are provided for one cylinder,
The swing cam has a pair of cam portions for opening and closing the two valves, and a cylindrical portion connecting the cam portions, and is divided by a plane passing through the axis of the drive shaft. In addition, the first divided body having the cam profile surface and the second divided body not having the cam profile surface are fastened to each other by a fastening bolt and configured integrally.
One of the dividing surfaces of the first and second divided bodies is formed with a fitting convex portion over the entire axial direction of the pair of cam portions and the cylindrical portion, and the other is provided with the fitting convex portion. A fitting recess to be fitted is formed.

The invention of claim 2 is the invention of claim 1, wherein a step is provided between the radially inner side and the outer side of the dividing surfaces of the first and second divided bodies,
The radially inner side of the divided surface forms a divided reference surface that passes through the axis of the drive shaft,
On the radially outer side of one of the divided surfaces of the first and second divided bodies, the fitting convex portion protruding from the divided reference surface is formed,
Of the first and second divided bodies, on the radially outer side of the other divided surface, the fitting concave portion that is recessed from the division reference surface is formed corresponding to the fitting convex portion. It is a feature.

The invention of claim 3 is the invention of claim 2, wherein the fitting convex part is formed on the dividing surface of the first divided body, and the fitting concave part is formed on the dividing surface of the second divided body, respectively.
In the fitting convex portion, a screw hole for screwing the fastening bolt is formed in a direction orthogonal to the dividing surface,
The axial line of the screw hole overlaps with the cam profile surface of the first divided body in the axial direction.

  The invention of claim 4 is the invention of any one of claims 1 to 3, characterized in that the link mechanism is arranged closer to one end side in the axial direction of the swing cam. is there.

  As described above, according to the present invention, the fitting convex portions and the fitting concave portions formed on the dividing surfaces of the first and second divided bodies forming the swing cam are fitted and engaged with each other. Thus, even if a bending stress acts in the direction of separating the first and second divided bodies in accordance with the opening / closing operation of the valve, the divided surface is reliably prevented from sliding and displacing radially outward. Can improve reliability.

  In addition, as a measure for preventing displacement of the split surface to the outside in the radial direction due to such stress, rigidity reinforcement such as increasing the weight by increasing the thickness of the swing cam is not unnecessarily increased. Further downsizing can be achieved without significantly changing the entire structure of the moving cam.

  Moreover, since the fitting convex part was formed in the 1st division body and the screw hole which screwed a fastening bolt was formed in the fitting convex part, it should be understood that the pilot hole of the screw hole penetrates the cam profile surface. This is advantageous in securing the minimum effective depth of the screw hole necessary to obtain a predetermined fastening force, while preventing the swing cam from becoming compact.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. It should be noted that the following description of the preferred embodiment is merely illustrative in nature and is not intended to limit the present invention, its application, or its use.

-Overall configuration-
FIG. 1 is a perspective view showing an overall configuration in which a variable valve device according to an embodiment of the present invention is applied to an intake valve of an engine, and FIG. 2 shows the overall configuration when the variable valve device is viewed from below. FIG.

  As shown in FIGS. 1 and 2, this engine employs a four-valve double overhead cam system having two intake valves 1 (see FIG. 3) and two exhaust valves (not shown) in one cylinder. It is.

  1 and 2, reference numeral 3 denotes a camshaft (drive shaft) that rotates in synchronization with the crankshaft of the engine. The intake valve 1 is driven by a swing cam 40 that is swingably supported by the camshaft 3, and the valve lift amount and valve timing are changed according to the operating state of the engine.

  In order to change the lift amount and timing of the intake valve 1, a plurality of eccentric rings 6 are formed integrally with the camshaft 3 at intervals in the axial direction, and an outer ring 7 is rotatably fitted on each eccentric ring 6. ing. The outer ring 7 and the swing cam 40 are connected by a single connecting link 8 (link mechanism). The swing cam 40 is pivotally supported on the camshaft 3 so as to be swingable. Although not shown, if the cylindrical portion 48 of the swing cam 40 is pivotally supported by a bearing member on an engine cylinder head, a cam carrier or the like, the support can be stabilized while the swing cam 40 is smoothly swung. It is preferable because it can be achieved.

  A rotating shaft 11 is provided in parallel with the camshaft 3, and a plurality of control arms 12 are arranged on the rotating shaft 11 at intervals in the axial direction.

  One end of the rotating shaft 11 is fastened to a screw hole formed in the rotating shaft 11, and the other end of the stud extends through the fitting insertion hole 12 a of the control arm 12 and extends radially outward of the rotating shaft 11. Bolts 17 are attached. The stud bolt 17 is disposed on one end side (right end side in FIG. 1) of the control arm 12.

  The insertion hole 12a of the control arm 12 is formed in a long hole shape having a long axis in the circumferential direction, and spacers 18 and 18 are fitted in the gap between the stud bolt 17 and the insertion hole 12a. When the rotation shaft 11 and the control arm 12 are assembled, the spacer 18 is selected and fitted with a size that fits the gap after adjusting the relative angle of the control arm 12 with respect to the rotation shaft 11. . The upper end portion of the spacer 18 projects upward from the outer peripheral surface of the control arm 12.

  With the spacer 18 fitted in the fitting insertion hole 12 a of the control arm 12, a washer 16 having an inner circumferential surface having a curvature radius substantially the same as the curvature radius of the outer circumferential surface of the control arm 12 is placed on the control arm 12. Here, the inner peripheral surface of the washer 16 is formed with a fitting groove 16a formed in a long hole shape having a long axis in the circumferential direction at a position corresponding to the fitting insertion hole 12a of the control arm 12, and a spacer. The upper end of 18 is fitted in the fitting groove 16 a, and the other end of the stud bolt 17 protruding from the through hole 16 b of the washer 16 is fastened by a fastening nut 19. Note that the washer 16 removed from the control arm 12 in FIG. 1 is shown upside down for explanation. The washer 16 is also fastened by a fastening bolt 14 that is spaced from the fastening nut 19 in the axial direction. The distal end portion of the fastening bolt 14 passes through the control arm 12 and is fastened to the rotating shaft 11. As a result, the control arm 12 is fastened to the rotating shaft 11.

  In addition, a washer 15 having an inner peripheral surface having a curvature radius substantially the same as the curvature radius of the outer peripheral surface of the control arm 12 is attached to the other end side (left end side in FIG. 1) of the control arm 12 by a fastening bolt 14. . The distal end portion of the fastening bolt 14 passes through the control arm 12 and is fastened to the rotating shaft 11. As a result, the control arm 12 is fastened to the rotating shaft 11.

  Each control arm 12 and the outer ring 7 are connected by a restriction link 13 that restricts the displacement of the outer ring 7 accompanying the rotation of the eccentric ring 6 so that the swing cam 40 swings.

  The rotating shaft 11 operates a motor (not shown) according to the operating state of the engine to rotate the control arm 12 and changes the position of the restriction link 13 to change the lift amount and timing of the intake valve 1. It is like that. In this case, the control arm 12 is controlled so that the valve lift amount increases as the engine load increases. Hereinafter, the change of the valve lift characteristic of the variable valve operating device will be specifically described.

-Change of valve lift characteristics of variable valve system-
As shown in FIG. 3, a direct acting tappet 21 is provided at the upper end of the stem of the intake valve 1, and a swing cam 40 is in contact with the tappet 21. The intake valve 1 is urged in a direction to close the intake port 25 by a valve spring 24 provided between a retainer 22 provided in the tappet 21 and a retainer 23 provided in the cylinder head.

  One end of the connecting link 8 is rotatably connected to the swing cam 40 by a connecting pin 31, and one end of the regulating link 13 is rotatably connected to the tip of the control arm 12 by a connecting pin 32. Thus, the connecting link 8 and the regulation link 13 are linked with the outer ring 7 in the middle. In other words, the other end of each of the connection link 8 and the regulation link 13 is coaxially and rotatably connected by a connection pin 33 to a protruding portion formed by partially protruding the outer ring 7 outward. The connecting pins 31 to 33 all extend in parallel with the camshaft 3.

  The rotation direction of the camshaft 3 (eccentric wheel 6) is set to the clockwise direction (clockwise) in FIG.

  The connecting pin 33 connected to the outer ring 7 and the connecting link 8 is disposed above the camshaft 3, and the rotating shaft 11 of the control arm 12 is disposed on the side of the connecting point. The connecting pin 32 at the tip of the control arm 12 is the rotation center of the restriction link 13. As shown in FIG. 3, when the connecting pin 32 is moved upward by the rotation of the control arm 12 and positioned above the camshaft 3, a small lift control state is established.

  3 and 4, the position of the outer ring 7 changes with the rotation of the eccentric ring 6, and the swing cam 40 is in a state where the lift amount of the intake valve 1 is zero as shown in FIG. As shown in FIG. 4, the intake valve 1 is largely lifted through the direct acting tappet 21 (the swing cam 40 has greatly lifted the intake valve 1 through the direct acting tappet 21). Swing between.

  FIG. 5 is a cross-sectional view showing the large lift control state. As shown in FIG. 5, when the connecting pin 32 is moved downward by the rotation of the control arm 12 and brought close to the camshaft 3, a large lift control state is established.

  In FIG. 5, when the eccentric ring 6 rotates, the outer ring 7 is displaced accordingly, but the displacement is regulated by the regulation link 13. That is, since the restriction link 13 rotates around the connection pin 32 disposed below the rotation shaft 11, the connection pin 33 of the outer ring 7 is centered on the connection pin 32 every time the eccentric ring 6 makes one rotation. As a reciprocating arc motion.

  Along with this reciprocating arc motion, the swing cam 40 connected to the outer ring 7 by the connecting link 8 is in a state where the lift amount of the intake valve 1 is zero as shown in FIG. 5 and a direct acting type as shown in FIG. And the state where the intake valve 1 is largely lifted via the tappet 21 (the state where the swing cam 40 is largely lifted via the direct acting tappet 21).

  In the state shown in FIG. 5, the base surface of the swing cam 40 is in contact with the tappet 21, and the valve lift is zero (the intake valve 1 is closed). In the state shown in FIG. 6, the cam nose side end of the cam surface of the swing cam 40 is in contact with the tappet 21 and has a valve lift peak (the intake valve 1 is open).

  As described above, since the connecting link 8 and the regulating link 13 link the outer ring 7 in the middle, the position of the regulating link 13 is largely changed by the control arm 12 and the valve lift amount by the swing cam 40 is greatly changed. Since it is possible to obtain an optimum intake amount corresponding to the engine operating state only by controlling the valve lift amount, it is possible to reduce pumping loss as a throttleless and intake air during large lift control. Filling efficiency can be improved.

-Configuration of swing cam-
FIG. 7 is a perspective view showing the configuration of the swing cam, and FIG. 8 is a perspective view showing the configuration when the swing cam is viewed from the opposite direction to FIG. As shown in FIGS. 7 and 8, the swing cam 40 has a pair of cam portions 47, 47 for opening and closing two intake valves 1, 1 (see FIG. 3) provided for one cylinder, respectively. A first divided body 41 having a cam profile surface on a plane passing through the axis of the camshaft 3 and a cam profile surface having no cam profile surface. It is divided into two divided bodies 45. The first and second divided bodies 41 and 45 are integrally configured by being fastened to each other by a fastening bolt 44. A through hole 49 for inserting the camshaft 3 is formed in both cam portions 47 and 47 and the cylindrical portion 48 forming the swing cam 40 so as to penetrate in the axial direction.

  The cam profile surfaces of the cam portions 47 and 47 of the swing cam 40 have a base circle surface (base circle region) in which the curvature radius is constant within a predetermined angle range, and the curvature radius gradually follows the base circle region. A large cam surface (cam nose region) is formed (see FIG. 12).

  One end portion of the connection pin 31 connected to the connection link 8 is supported on one end side in the axial direction of the first divided body 41 and extending outward in the axial direction from the second divided body 45. An extension 43 having a first pin support 42 is formed.

  The second divided body 45 is formed with a second pin support portion 46 that faces the first pin support portion 42 and supports the other end portion of the connection pin 31.

  FIG. 9 is a plan view for explaining the attachment of the connecting pin to the swing cam. As shown in FIG. 9, the connecting pin 31 includes a head portion 31a, a base end side shaft portion 31b having a smaller diameter than the head portion 31a and having a screw portion, and a connection link having a smaller diameter than the base end side shaft portion 31b. 8 includes a connecting shaft portion 31c serving as a rotation center, and a distal end side shaft portion 31d having a smaller diameter than the connecting shaft portion 31c.

  The first pin support portion 42 has a screw hole 42a that is screwed with a screw portion of the base end side shaft portion 31b of the connecting pin 31, and a fitting hole 42b that is fitted with the head portion 31a. The through hole 49 is formed in parallel with the axial direction. The fitting hole 42b has a diameter larger than that of the screw hole 42a and is formed on the front side (left side in FIG. 9) of the connecting pin 31 in the insertion direction.

  The second pin support portion 46 has a fitting hole 46a that is coaxial with the screw hole 42a of the first pin support portion 42 and fits with the distal end side shaft portion 31d of the connecting pin 31, and a hole diameter larger than the fitting hole 46a. A small relief hole 46b is formed.

  The connecting pin 31 is inserted through the fitting hole 42b and the screw hole 42a of the first pin support portion 42, and the distal end side shaft portion 31d is fitted into the fitting hole 46a. Then, the screw portion of the base end side shaft portion 31b is screwed into the screw hole 42a, so that the connecting pin 31 straddles the first and second pin support portions 42 and 46 and both ends thereof are supported.

  Thus, since the connecting pin 31 is disposed closer to one end side in the axial direction of the swing cam 40, the connecting link 8 connected to the swing cam 40 via the connection pin 31 is similarly the swing cam 40. It is arrange | positioned near one end side (left side in FIG. 1).

  Hereinafter, the fitting convex part 56 and the fitting concave part 57 formed on the dividing surfaces of the first and second divided bodies 41 and 45, which are characteristic parts of the present invention, will be described.

  FIG. 10 is a perspective view showing the configuration of the dividing surface of the first divided body, and FIG. 11 is a perspective view showing the configuration of the dividing surface of the second divided body. FIG. 12 is a side view showing the configuration when the swing cam is viewed from the axial direction.

  As shown in FIGS. 10 to 12, a step is provided between the radially inner side and the outer side of the divided surface of the first and second divided bodies 41 and 45, and the radially inner side of the divided surface is A division reference plane 55 that passes through the axis of the camshaft 3 is formed. Then, on the radially outer side of the dividing surface of the first divided body 41, a fitting convex portion 56 that protrudes from the dividing reference surface 55 over the entire axial direction of the pair of cam portions 47, 47 and the cylindrical portion 48 is provided. Is formed. Further, on the radially outer side of the dividing surface of the second divided body 45, a fitting concave portion 57 that is recessed from the division reference surface 55 is formed corresponding to the fitting convex portion 56.

  As shown in FIGS. 12 and 13, the first and second divided bodies 41 and 45 are fastened together by fastening bolts 44. Specifically, the first divided body 41 is formed with an insertion hole 51 through which the shaft portion of the fastening bolt 44 is inserted, and the second divided body 45 is coaxial with the insertion hole 51 and screwed with the tip screw portion of the fastening bolt 44. The screw holes 52 to be joined are formed in a direction orthogonal to the division reference surface 55.

  The screw hole 52 of the second divided body 45 is a position where the axial line overlaps the cam profile surface of the cam portions 47, 47 of the swing cam 40 in the axial direction and faces the through hole 49 (total). 4 places). The lower hole 53 of the screw hole 52 formed on the cam surface (cam nose region) side in which the radius of curvature gradually increases is formed as a bottomed hole so as not to penetrate the cam nose region. .

  On the other hand, the lower hole 54 of the screw hole 52 formed on the base circle surface (base circle region) side where the radius of curvature is constant by a predetermined angle range following the cam nose region is not penetrated into the base circle region. It opens in a direction perpendicular to the axis of the screw hole 52 and outside the region of the cam profile surface. The opening of the lower hole 54 is formed in a long hole shape having a long axis in the axial direction as shown in FIG.

  Further, the screw hole 52 is not formed only below the division reference surface 55 of the first divided body 41, but is also formed in the fitting convex portion 56 of the first divided body 41, The minimum effective depth of the screw hole 52 required to obtain a predetermined fastening force is ensured without penetrating the lower hole 54 of the screw hole 52 into the cam profile surface.

  As described above, according to the variable valve operating apparatus for an engine according to the present embodiment, the fitting convex portion 56 formed on the dividing surface of the first and second divided bodies 41 and 45 forming the swing cam 40 is fitted. Since the mating recess 57 is fitted and engaged with each other, even if a bending stress acts in the direction of separating the first and second divided bodies 41 and 45 in accordance with the opening / closing operation of the intake valve 1, It is possible to reliably prevent the surface from sliding and displacing radially outward, thereby improving reliability.

  Further, as a measure for preventing the displacement of the dividing surface due to such stress to the outside in the radial direction, the rigidity reinforcement such as increasing the weight by increasing the thickness of the rocking cam 40 is not unnecessarily increased. Further downsizing can be achieved without significantly changing the entire structure of the swing cam 40.

  Further, since the fitting convex portion 56 is formed in the first divided body 41 and the screw hole 52 into which the fastening bolt 44 is screwed is formed in the fitting convex portion 56, the lower hole 54 of the screw hole 52 is a cam. It is advantageous in securing the minimum effective depth of the screw hole 52 necessary for obtaining a predetermined fastening force while preventing the profile cam from penetrating, and the swing cam 40 can be made compact.

  In the present embodiment, the fitting convex portion 56 is formed on the dividing surface of the first divided body 41 and the fitting concave portion 57 is formed on the dividing surface of the second divided body 45. The fitting concave portion 57 may be formed on the dividing surface 41 and the fitting convex portion 56 may be formed on the dividing surface of the second divided body 45. Further, a fitting convex portion 56 and a fitting concave portion 57 are formed so as to face the dividing surface of the first divided body 41 with the through hole 49 interposed therebetween, and the first divided body 41 is formed on the dividing surface of the second divided body 45. The fitting concave portion 57 and the fitting convex portion 56 corresponding to the fitting convex portion 56 and the fitting concave portion 57 may be formed.

  In the present embodiment, the variable valve operating apparatus for the intake valve has been described.However, the present invention can also be adopted as a variable valve operating apparatus for the exhaust valve, and the valve operating form is not limited to the tappet type. It can also be used for rocker arm models.

  As described above, the present invention provides a separation force that acts on the first and second divided bodies with bending stress when the swing cam is reciprocally swung without unnecessarily increasing the rigidity of the swing cam. Therefore, it is possible to prevent the split surface from sliding and displacing radially outward, and thus a highly practical effect is obtained. Therefore, it is extremely useful and has high industrial applicability.

It is a perspective view which shows the variable valve apparatus which concerns on embodiment of this invention. It is A arrow line view which shows the whole structure of a variable valve apparatus. It is sectional drawing which shows the state at the time of valve lift amount zero at the time of small lift control. It is sectional drawing which shows the state at the time of valve lift peak at the time of small lift control. It is sectional drawing which shows the state at the time of valve lift amount zero at the time of large lift control. It is sectional drawing which shows the state at the time of the valve lift peak at the time of large lift control. It is a perspective view which shows the structure of a rocking cam. It is a perspective view which shows a structure when a rocking cam is seen from another angle. It is a top view explaining attachment to a rocking cam of a connecting pin. It is a perspective view which shows the structure of a 1st division body. It is a perspective view which shows the structure of a 2nd division body. It is a side view which shows a structure when a rocking cam is seen from an axial direction. It is a front view which shows the structure of a rocking cam.

Explanation of symbols

1 Intake valve 3 Camshaft (drive shaft)
8 Link (link mechanism)
40 oscillating cam 41 first divided body 44 fastening bolt 45 second divided body 47 cam portion 48 cylindrical portion 52 screw hole 55 division reference surface 56 fitting convex portion 57 fitting concave portion

Claims (4)

A drive shaft arranged parallel to the crankshaft of the engine;
A swing cam pivotally supported by the drive shaft to open and close the valve;
A variable valve operating apparatus for an engine comprising a link mechanism coupled to the swing cam and controlling a swing range of the swing cam according to an operating state of the engine to change a valve lift characteristic;
Two valves are provided for one cylinder,
The swing cam has a pair of cam portions for opening and closing the two valves, and a cylindrical portion connecting the cam portions, and is divided by a plane passing through the axis of the drive shaft. In addition, the first divided body having the cam profile surface and the second divided body not having the cam profile surface are fastened to each other by a fastening bolt and configured integrally.
One of the dividing surfaces of the first and second divided bodies is formed with a fitting convex portion over the entire axial direction of the pair of cam portions and the cylindrical portion, and the other is provided with the fitting convex portion. A variable valve operating apparatus for an engine, wherein a fitting recess for fitting is formed. In claim 1,
A step is provided between the radially inner side and the outer side of the dividing surfaces of the first and second divided bodies,
The radially inner side of the divided surface forms a divided reference surface that passes through the axis of the drive shaft,
On the radially outer side of one of the divided surfaces of the first and second divided bodies, the fitting convex portion protruding from the divided reference surface is formed,
Of the first and second divided bodies, on the radially outer side of the other divided surface, the fitting concave portion that is recessed from the division reference surface is formed corresponding to the fitting convex portion. The variable valve operating device of the engine characterized by the above. In claim 2,
The fitting convex part is formed on the dividing surface of the first divided body, and the fitting concave part is formed on the dividing surface of the second divided body, respectively.
In the fitting convex portion, a screw hole for screwing the fastening bolt is formed in a direction orthogonal to the dividing surface,
The variable valve operating apparatus for an engine according to claim 1, wherein an axis of the screw hole overlaps with a cam profile surface of the first divided body in an axial direction. In any one of Claims 1 thru | or 3,
The variable valve operating apparatus for an engine, wherein the link mechanism is disposed closer to one end side in the axial direction of the swing cam.

Images