Valve operating system for an internal combustion engine

Abstract: In a valve operating system in an internal combustion engine, a swinging support section provided at a base end of a rocker arm is swingably carried on a rocker shaft, and tappet screws are threadedly fitted in a plurality of boss portions formed at a tip end of the rocker arm and arranged in a direction parallel to an axis of the rocker shaft, so that they can be individually put into abutment against upper ends of a plurality of engine valves. Cam abutments are provided on the rocker arm in an intermediate portion between the swinging support section and the boss portions to come into contact with a valve operating cam. The boss portions are interconnected by a connection wall having a plurality of wall portions which intersect each other in a plane perpendicular to the axis of the rocker shaft. Thus, the rigidity of the tip end of the rocker arm is enhanced sufficiently.

Description: BACKGROUND OF THE INVENTION FIELD OF THE INVENTION The present invention relates to a valve operating system for an internal combustion engine, comprising a cylindrical swinging support section provided at a base end of a rocker arm and swingably carried on a rocker shaft mounted in a cylinder head, a plurality of boss portions formed at a tip end of the rocker arm and arranged in a direction parallel to an axis of the rocker shaft, tappet screws being threadedly fitted into the boss portions and capable of being individually put into abutment against upper ends of a plurality of engine valves, and cam abutments provided on the rocker arm in an intermediate portion thereof between the swinging support section and the boss portions to come into contact with a valve operating cam. DESCRIPTION OF THE RELATED ART Such a valve operating system is conventionally known, for example, from Japanese Patent Application Laid-open No.6-185322. In the above known system, however, the plurality of boss portions with the tappet screws threadedly fitted therein are formed at tip ends of a plurality of arms disposed at locations spaced from one another in a direction along the axis of the rocker shaft, and a relatively large load is applied to each of the boss portions during a valve driving operation. Nevertheless, it is not easy to say that the rigidity of each of the boss portions, i.e., the rigidity of the tip end of the rocker arm is sufficient. US-A-4,844,023 only shows one wall portion extending from one boss portion to the other boss portion provided with two or three arms ending in a respective boss portion (Figs. 7, 8, 9). There are no further wall portions of the connecting wall intersecting each other at right angles at a plane perpendicular to the exit of said rocker shaft. JP-A-10-18 823 and EP-A-0 420 159 do not show a plurality of wall portions either. SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a valve operating system in an internal combustion engine, wherein a rigidity of a rocker arm having a plurality of boss portions with a tappet screws threadedly fitted therein can be enhanced sufficiently, while suppressing an increase in weight to the minimum. To achieve the above object, there is provided a valve operating system for an internal combustion engine according to claim 1. With such arrangement, the boss portions are interconnected by the connection wall and hence, the rigidity of the tip end of the rocker arm for driving the plurality of engine valves can be enhanced sufficiently. Moreover, the connection wall has the plurality of wall portions which intersect one another at the right angles in the plane perpendicular to the axis of the rocker shaft, i.e., an axis of swinging movement of the rocker arm. Therefore, it is possible to suppress an increase in weight of the rocker arm due to the connection wall to the minimum, while maintaining a sufficient connecting rigidity. In addition, the connection wall is formed into a substantially L-shape or U-shape in cross-section. With such arrangement, it is possible to suppress an increase in weight due to the connection wall. According to a further aspect of the present invention, the connection wall is provided with a plurality of ribs which intersect each other and which are connected to the wall portions, respectively. With such arrangement of the third feature, it is possible to further enhance the rigidity of the tip end of the rocker arm. According to a further aspect of the present invention, the boss portions are interconnected by the connection wall having the wall portion, an outer surface of which is connected flush to outer peripheral surfaces of the tip ends of the boss portions. With such arrangement, the boss portions can be formed so that they do not protrude, thereby eliminating the concentration of a stress on a connection between the connection wall and each of the boss portions, and it is possible to enhance the durability of the rocker arm, while sufficiently enhancing the rigidity of the tip end of the rocker arm. According to a further aspect of the present invention, the rocker arm is provided with an opening, a portion of a side of which is formed by an inner surface of the connection wall, and a roller which is the cam abutment is accommodated in the opening and rotatably carried on a roller shaft fixed to the rocker arm. With such arrangement of the fifth feature, the connection wall can be disposed in proximity to the roller, whereby the rigidity of supporting of the roller can be enhanced. According to a further aspect of the present invention the rocker arm is provided with first and second support walls, at tip ends of which the tappet screws at axially one end and the axially other end of the rocker shaft are mounted, and the connection wall which interconnects tip ends of the first and second support walls, and the rocker arm has recesses defined at least in an upper surface thereof in an area surrounded by the first and second support walls, the connection wall and the swinging support portion. With such arrangement, the entire outer periphery of the rocker arm is formed by the swinging support section, the pair of support walls and the connection wall, and the recesses are defined at least in the upper surface of the rocker arm. Therefore, it is possible to reduce the weight of the rocker arm, while avoiding a reduction in rigidity of the rocker arm. According to a further aspect of the present invention, the rocker arm is provided with an opening in which a roller which is the cam abutment is accommodated; a roller shaft rotatably supporting the roller is fixed across the opening; and the recesses are defined in the upper surface of the rocker arm so that oil can be supplied to the roller within the opening. With such arrangement, the oil accumulated in the recesses can be supplied to the roller to lubricate the roller and hence, it is unnecessary to provide a passage for supplying the oil to the roller in the rocker arm, leading to a reduced number of steps of processing the rocker arm. According to a further aspect of the present invention, the rocker arm has a pair of shaft support portions provided thereon between the opening and the first and second support walls for supporting opposite ends of the roller shaft, and the recess is defined in the rocker arm between the shaft support portions and the swinging support section. With such arrangement of the eighth feature, the oil can be accumulated reliably in a portion of the rocker arm which is swung in a relatively small amount, thereby reliably lubricating the roller. According to a further aspect of the present invention, the rocker arm has a pair of shaft support portions provided thereon between the opening and the first and second support walls for supporting opposite ends of the roller shaft, and the recess is defined in the rocker arm between the shaft support portions and the connection wall. With such arrangement of the ninth feature, it is possible to reduce the weight of the tip end side of the rocker arm to alleviate the inertial weight, while performing the lubrication of the roller. The above and other objects, features and advantages of the invention will become apparent from the following description of the preferred embodiment taken in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS Figs.1 to 7 show a first embodiment of the present invention. Fig.1 is a partially vertical sectional view of an internal combustion engine; Fig.2 is a plan view taken in a direction of an arrow 2 in Fig.1; Fig.3 is a plan view of an exhaust-side rocker arm; Fig.4 is a sectional view taken along a line 4-4 in Fig.2; Fig.5 is a sectional view taken along a line 5-5 in Fig.2; Fig.6 is a sectional view taken along a line 6-6 in Fig.5; Fig.7 is a sectional view taken along a line 7-7 in Fig.6; Fig.8 is a sectional view similar to Fig.5, but according to a second embodiment of the present invention; Fig.9 is a sectional view similar to Fig.5, but according to a third embodiment of the present invention; Fig.10 is a sectional view similar to Fig.5, but according to a fourth embodiment of the present invention; and Fig.11 is a view taken in the direction of an arrow 11 in Fig.10. DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to Figs.1 to 7. Referring first to Figs.1 and 2, a multi-cylinder internal combustion engine includes a cylinder block 15, and a cylinder head 16 coupled to an upper portion of the cylinder block 15 through a gasket 17. A piston 19 is slidably received in each of cylinders 18 provided in the cylinder block 15. A combustion chamber 20 is defined in each of the cylinders by the cylinder block 15, the cylinder head 16 and each of the pistons 19. Provided in the cylinder head 16 for every cylinder are a pair of intake valve bores 21 facing one side of a ceiling surface of the combustion chamber 20, an intake port 22 which opens into one side (a right side in Fig.1) of the cylinder head 16 and connected commonly to the intake valve bores 21, a pair of exhaust valve bores 23 facing the other side of the ceiling surface of the combustion chamber 20, and an exhaust port 24 which opens into the other side (a left side in Fig.1) of the cylinder head 16. Stems 25 of intake valves VI, VI capable of opening and closing the intake valve bores 21 are slidably received in guide tubes 26 mounted in the cylinder head 16, and valve springs 28 for biasing the intake valves VI, VI upwards, i.e., in valve closing directions are mounted between the cylinder head 16 and retainers 27, 27 mounted at upper ends of the stems 25 protruding upwards from the guide tubes 26. Stems 29 of exhaust valves VE, VE as engine valves capable of opening and closing the exhaust valve bores 23 are slidably received in guide tubes 30 mounted in the cylinder head 16 , and valve springs 32 for biasing the exhaust valves VE, VE upwards, i.e., in valve closing directions are mounted between the cylinder head 16 and retainers 31, 31 mounted at upper ends of the stems 29 protruding upwards from the guide tubes 30. The intake valves VI, VI are opened and closed by an intake-side valve operating device 33, and the exhaust valves VE, VE are opened and closed by an exhaust-side valve operating device 34. A plug insertion tube 36 is disposed to extend vertically, so that a spark plug 35 mounted in the cylinder head 16 to face a central portion of the combustion chamber 20 is inserted into the plug insertion tube 36. The plug insertion tube 36 is attached at its lower end to the cylinder head 16. The intake-side valve operating device 33 includes a pair of intake-side rocker arms 37 and 38 individually corresponding to the pair of intake valves VI, VI, an intake-side rocker shaft 39 on which the intake-side rocker arms 37 and 38 are swingably carried, and an intake-side camshaft 40 which is rotatable about an axis parallel to the rocker shaft 39. The intake-side rocker shaft 39 is fixedly supported by holder walls 41 provided on the cylinder head 16 between the cylinders, and intake-side rocker arms 37 and 38 are swingably carried at their base ends on the intake-side rocker shaft 39. Tappet screws 42A and 42B are threadedly fitted at tip ends of the intake-side rocker arms 37 and 38 to abut against upper ends of the corresponding intake valves VI, VI, i.e., upper ends of the stems 25, so that their advanced and retracted positions can be adjusted. The intake-side camshaft 40 is operatively connected at a reduction ratio of 1/2 to a crankshaft (not shown) and rotatably carried by the holder walls 41 and cam holders 43 fastened to upper ends of the holder walls 41. The intake-side camshaft 40 is provided with a high-speed valve operating cam 44 corresponding to one of the intake-side rocker arms 37, and a low-speed valve operating cam 45 corresponding to the other intake-side rocker arm 38. A roller 46 supported on the one intake-side rocker arm 37 is in rolling contact with the high-speed valve operating cam 44, and a roller (not shown) supported on the other intake-side rocker arm 38 is in rolling contact with the low-speed valve operating cam 45. Moreover, an interlocking-motion switchover means (not shown) is provided between the intake-side rocker arms 37 and 38 and capable of switching over the interlocking motion of the rocker arms 37 and 38 and the releasing of the interlocking motion one from another, so that the rocker arms 37 and 38 are swung independently from each other during operation of the engine at a low speed and the rocker arms 37 and 38 are swung operatively from each other in an interlocking motion during operation of the engine at a high speed. Therefore, during operation of the engine at the low speed, the one intake-side rocker arm 37 is swung to open and close one of the intake valves VI in an operational characteristic corresponding to a cam profile of the high-speed valve operating cam 44, while the other intake-side rocker arm 38 is swung to open and close the other intake valves VI in an operational characteristic corresponding to a cam profile of the low-speed valve operating cam 45. During operation of the engine at the high speed, both of the intake-side rocker arms 37 and 38 are swung to open and close the intake valves VI, VI in the operational characteristic corresponding to the high-speed valve operating cam 44. The exhaust-side valve operating device 34 includes a single exhaust-side rocker arm 50 which is common to the pair of exhaust valves VE and VE, an exhaust-side rocker shaft 51 serving as an arm support portion on which the exhaust-side rocker arm 50 is swingably carried and an exhaust-side cam shaft 52 which is rotatable about an axis parallel to the rocker shaft 51. The exhaust-side rocker shaft 51 has an axis parallel to the intake-side rocker shaft 39 and is fixedly supported by the holder wall 41, as is the intake-side rocker shaft 39. The exhaust-side rocker arm 50 is swingably carried at its base end on the exhaust-side rocker shaft 51, and first and second tappet screws 53A and 53B are threadedly fitted at tip ends of the exhaust-side rocker arm 50 to abut against upper ends of the corresponding exhaust valves VE, VE, i.e., upper ends of the stems 29, so that their advanced and retracted positions can be adjusted. The exhaust-side camshaft 52 is operatively connected at a reduction ratio of 1/2 to the crankshaft (not shown) rotatably carried by the holder walls 41 and cam holders 54 fastened to the upper ends of the holder walls 41. A valve operating cam 55 is provided on the exhaust-side camshaft 52 in correspondence to the exhaust-side rocker arm 50, and a roller 56 as a cam abutment axially supported on the exhaust-side rocker arm 50 is in rolling contact with the valve operating cam 55. Referring to Fig.3, the exhaust-side rocker arm 50 is provided at its base end with a cylindrical swinging support section 57 through which the exhaust-side rocker shaft 51 is inserted and which is swingably carried on the rocker shaft 51. The exhaust-side rocker arm 50 is further provided with first and second support walls 58 and 59, and a connection wall 60 connecting tip ends of the first and second support walls 58 and 59 to each other. First and second boss portions 58a and 59a each having a circular outer peripheral surface are integrally formed on respective tip ends of the first and second support walls 58 and 59, so that they are arranged parallel to the axis of the exhaust-side rocker shaft 51. It is preferable that the first and second support walls 58 and 59 are provided to extend from opposite ends of the swinging support section 57 along a plane perpendicular to the axis of the exhaust-side rocker shaft 51, and that the first and second boss portions 58a and 59a and the swinging support section 57 are interconnected by the first and second support walls 58 and 59 perpendicular to the axis of the exhaust-side rocker shaft 51. The boss portions 58a and 59a are provided with threaded bores 61A and 61B into which the first and second tappet screws 53A and 53B are threadedly engaged. The roller 56 is supported on the exhaust-side rocker arm 50 in a location intermediate between the swinging support section 57 and the tappet screws 53A and 53B, i.e., at a location displaced from the axis of the exhaust-side rocker shaft 51. A first straight line L1 extends through (1) the center of one 53A of the first and second tappet screws 53A and 53B which is disposed on axially one side (a lower end side in Fig.3) of the exhaust-side rocker shaft 51, i.e., the center of the threaded bore 61A in the first boss portion 58a, and (2) an area of contact (an area indicated by intersecting oblique lines in Fig.3) of the valve operating cam 55 with the roller 56. A second straight line L2 extends through (1) the center of the other 53B of the first and second tappet screws 53A and 53B which is disposed on the axially other side (an upper end side in Fig.3) of the exhaust-side rocker shaft 51, i.e., the center of the threaded bore 61B in the second boss portion 59a, and (2) an area of contact of the valve operating cam 55 with the roller 56. The first and second straight lines L1 and L2 and the axis C of the exhaust-side rocker shaft 51 intersect together at intersection points P1 and P2 as viewed in the plane of the exhaust-side rocker arm 50. The intersection points P1 and P2 are disposed at locations inside axially opposite sides of the swinging support section 57. In other words, the swinging support section 57 is formed to have such a length that their opposite ends faces are disposed outside the first and second intersection points P1 and P2. It is desirable that the first and second straight lines L1 and L2 pass through the center of the area of contact of the valve operating cam 55 with the roller 56. Moreover, the swinging support section 57 is formed at a length longer than a distance between the centers of the first and second tappet screws 53A and 53B, and third and fourth straight lines L3 and L4 passing through the centers of the first and second tappet screws 53A and 53B and intersecting the axis C of the exhaust-side rocker shaft 51 at right angles are disposed inside the axially opposite ends of the swinging support section 57. Referring also to Figs.4 to 6, a rectangular opening 62 for accommodation of the roller 56 is provided in the exhaust-side rocker arm 50 between the first and second support walls 58 and 59. A roller shaft 63, which has a length shorter than a distance between the first and second support walls 58 and 59 and has an axis parallel to the exhaust-side rocker shaft 51, extends across the opening 62 and is fixed to the exhaust rocker arm 50, and the roller 56 is rotatably carried on the roller shaft 63 with a needle bearing 64 interposed therebetween. A pair of shaft support portions 65, 65 which are formed into a cylindrical shape are provided over the first and second support walls 58 and 59 and the opening 62 respectively to extend in parallel to the exhaust-side rocker shaft 51. Shaft insertion bores 66, 66 are coaxially provided in the shaft support portions 65, 65, respectively, with its inner end opening into the opening 62 and with its outer end opening outwards and sideways of the exhaust-side rocker arm 50, i.e., outwards and sideways of the first and second support walls 58, 59. The shaft insertion bore 66 comprises a first insertion bore portion 66a adjacent the opening 62, a second insertion bore portion 66b connected at its inner end to an outer end of the first insertion bore portion 66a, and a step 66c formed between the outer end of the first insertion bore portion 66a and the inner end of the second insertion bore portion 66b and facing on a side opposite from the opening 62. It is desirable that the first and second insertion bore portions 66a and 66b are formed as coaxial circular bores, so that the annular step 66c is formed between both of the insertion bore portions 66a and 66b. If the first and second insertion bore portions 66a and 66b are formed as described above, it is easy to carry out a boring for forming them. Alternatively, the first insertion bore portion 66a may be circular in cross section, while the second insertion bore portion 66b may be non-circular in cross section. Namely, the second insertion bore portion 66b may be of any cross-sectional shape, if the step 66c is formed between the first and second insertion bore portions 66a and 66b to face on the side opposite from the opening 62. The roller shaft 63 is fitted in and fixed to inner ends of the shaft insertion bores 66, 66 with each of portions of the shaft insertion bores 66 axially outer than opposite ends of the roller shaft 63 being left in a hollow form. For such fitting and fixing, outer peripheral edges of the opposite ends of the roller shaft 63 fitted in the first insertion bore portions 66a, 66a are brought into caulked engagement with the steps 66c, 66c. Thus, wall-removed portions 67, 67 are formed in the exhaust-side rocker arm 50 at locations axially outside the opposite ends of the roller shaft 63 in a state in which the roller shaft 63 has been fixed to the exhaust-side rocker arm 50. The cylindrical swinging support section 57 comprises a thinner cylindrical portion 57a surrounding the exhaust-side rocker shaft 51, and thicker cylindrical portions 57b, 57b thicker than the thinner cylindrical portion 57a and continuously and integrally formed at opposite ends of the thinner cylindrical portion 57a, respectively. The first and second support walls 58 and 59 are formed continuously with the thicker cylindrical portions 57b, 57b. Referring also to Fig.7, grooves 68, 68 capable of accumulation of an oil between the grooves and the outer surface of the exhaust-side rocker shaft 51 are provided in an arcuate shape in lower portions of inner surfaces of the thicker cylindrical portions 57b, 57b corresponding to connections of the first and second support walls 58 and 59, respectively. Recesses 69 and 70 capable of supplying the oil to the roller 56 within the opening 62 are defined in portions of the upper surface of the exhaust-side rocker arm 50, which are surrounded by the first and second support walls 58 and 59, the connection wall 60 and the swinging support section 57. One of the recesses 69 is defined in the exhaust-side rocker arm 50 between the shaft support portions 65, 65 and the swinging support section 57, and the other recess 70 is defined in the exhaust-side rocker arm 50 between the shaft support portions 65, 65 and the connection wall 60. An axially central portion of the swinging support section 57, i.e., an axially intermediate portion of the thinner cylindrical portion 57a is disposed at a location corresponding to the plug insertion tube 36. Notches 71 and 72 connected to each other are provided in the swinging support section 57 and the exhaust-side rocker shaft 51 at the location corresponding to the plug insertion tube 36 and formed into such an arcuate shape that they are recessed on a side opposite to the plug insertion tube 36, and a portion of the plug insertion tube 36 is accommodated in the notch 71. Moreover, the notches 71 and 72 are provided in the swinging support section 57 and the exhaust-side rocker shaft 51 between connections of the first and second support walls 58 and 59 to the swinging support section 57. An oil injection bore 73 is provided, with its outer end opening into the opening 62, in the swinging support section 57 on a side opposite to the notch 71 with respect to the axis C of the exhaust-side rocker shaft 51. An oil supply passage 74 is provided in the exhaust-side rocker shaft 51 to extend along the axis C of the exhaust-side rocker shaft 51, and an oil supply bore 75 is also provided in the exhaust-side rocker shaft 51 to communicate with the oil supply passage74, and is capable of communicating at its outer end with an inner end of the oil injection bore 73. The oil supply passage 74 is connected to an oil supply source which is not shown. Therefore, it is possible to supply the oil through the oil supply passage 74 within the exhaust-side rocker shaft 51 via the oil supply bore 75 and the oil injection bore 73 to the roller 56 to lubricate the roller 56. The communication between the oil supply bore 75 and the oil injection bore 73 may be cut off depending on a swung state of the exhaust-side rocker arm 50, but in the cut-off state, the oil supplied from the oil supply bore 75 is used for the lubrication between the swinging support section 57 and the exhaust-side rocker shaft 51, and the oil is also supplied to the grooves 68, 68 in the inner surface of the swinging support section 57. The connection wall 60 interconnecting the tip ends of the first and second support walls 58 and 59, i.e., the first and second boss portions 58a and 59a comprises first and second wall portions 60a and 60b intersecting each other at right angles in a plane perpendicular to the axis C of the exhaust-side rocker shaft 51, i.e., the swinging axis of the exhaust-side rocker arm 50. The wall portions 60a and 60b intersect each other to form, for example, a substantially L-shape in such plane. Moreover, the second wall portion 60b is formed to extend in parallel to the axis of the exhaust-side rocker shaft 51 with its outer surface connected flush to outer surfaces of the first and second boss portions 58a and 59a at their tip ends. One side of the opening 62 is defined by a portion of an inner surface of the first wall portion 60a. The operation of the first embodiment will be described below. In the exhaust-side rocker arm 50, the intersection points P1 and P2, at which (a) the first straight line L1 extending through (1) the center of one 53A of the first and second tappet screws 53A and 53B arranged in parallel to the axis C of the exhaust-side rocker shaft 51, which is disposed on the axially one side of the exhaust-side rocker shaft 51 and (2) the area of contact of the valve operating cam 55 with the roller 56, preferably the center of such area, (b) the second straight line L2 extending through (1) the center of the other 53B of the first and second tappet screws 53A and 53B which is disposed on the axially other side (an upper end side in Fig.3) of the exhaust-side rocker shaft 51 and (2) the area of contact of the valve operating cam 55 with the roller 56, preferably the center of such area, and (c) the axis C of the exhaust-side rocker shaft 51 intersect together as viewed in the plane of the exhaust-side rocker arm 50, are disposed inside the axially opposite ends of the cylindrical swinging support section 57 swingably carried on the exhaust-side rocker shaft 51. Therefore, even if a difference is produced between the tappet clearances in the first and second tappet screws 53A and 53B, and a large load is produced on the first or second straight line L1, L2 to act so as to incline the exhaust-side rocker arm 50, the exhaust-side rocker arm 50 can be supported stably, because the swinging support section 57 is supported on the exhaust-side rocker shaft 51 on the first and second straight lines L1 and L2. As a result, it is also possible to prevent an uneven wear from being produced in the swinging support section 57 and the roller 56. In addition, the swinging support section 57 is formed at the length longer than the distance between the centers of the first and second tappet screws 53A and 53B, and the third and fourth straight lines L3 and L4 passing the centers of the first and second tappet screws 53A and 53B and intersecting the axis C of the exhaust-side rocker shaft 51 at the right angles are disposed inside the axially opposite ends of the swinging support section 57. Therefore, the exhaust-side rocker shaft 52 is supported on the exhaust-side rocker shaft 52 over the length longer than the distance between the tappet screws 53A and 53B, and the exhaust-side rocker arms 50A is supported more stably. The roller shaft 63 is fitted and fixed in the exhaust-side rocker arm 50, and the roller 56 in rolling contact with the valve operating cam 55 is rotatably carried on the roller shaft 63. However, the roller shaft 63 is shorter than the distance between the first and second support walls 58 and 59 provided to extend from the opposite ends of the swinging support section 57, and is fitted and fixed at the inner ends of the pair of shaft insertion bores 66, 66 which are coaxially provided in the exhaust-side rocker arm 50 with their portions axially outer than opposite ends of the roller shaft 63 being left as the hollow wall-removed portions 67, 67. Thus, the portions of the shaft insertion bores 66 which are axially outer than the opposite ends of the roller shaft 63 are left in the hollow forms and hence, the weight of the entire exhaust-side rocker arm 50 can be reduced, and it is also possible to confirm, from the opposite sides of the exhaust-side rocker arm 50, the state of the roller shaft 63 fixed to the rocker arm 50. Moreover, the roller shaft 63 can be formed at a relatively small length, whereby the assembling of the roller shaft 63 to the exhaust-side rocker arm 50 is facilitated. In addition, the roller shaft 63 can be formed so that it is difficult to deform, thereby ensuring a proper swinging movement of the exhaust-side rocker arm 50. Loads from the exhaust valves VE, VE are applied to the first and second support walls 58 and 59, but the roller 56 can be supported by the roller shaft 63 disposed at the location kept away from the load-applied portions and hence, the rigidity of supporting of the roller 56 can be enhanced. The shaft insertion bore 66 comprises the first insertion bore portion 66 adjacent to the opening 62 with the roller 56 accommodated therein, and the second insertion bore portion 66b connected at its inner end to the outer end of the first insertion bore portion 66 to form the step 66c facing on the side opposite from the opening 62 between the first and second insertion bore portions 66a and 66b. The opposite ends of the roller shaft 63 fitted in the first insertion bore portions 66a, 66a of the shaft insertion bores 66, 66 are in caulked engagement with the steps 66c, respectively, whereby the roller shaft 63 is fitted and fixed in the shaft insertion bores 66, 66. Therefore, the portions of the shaft insertion bores 66, 66 left in the hollow forms, i.e., the wall-removed portions 67, 67 can be formed at large areas as the second insertion bore portions 66b, 66b, and the weight of the entire exhaust-side rocker arm 50 can be further reduced. Further, since the roller shaft 63 is fixed in the caulked manner to the exhaust-side rocker arm 50, the assembling of the roller shaft 63 to the exhaust-side rocker arm 50 is further facilitated. Further, the pair of cylindrical shaft support portions 65, 65 defining the shaft insertion bores 66, 66 respectively are provided on the exhaust-side rocker arm 50 over the first and second support walls 58 and 59 and the opening 62, and the pair of cylindrical shaft support portions 65, 65 interconnected through the roller shaft 63 are connected to the support walls 58 and 59. Therefore, the rigidity of the support walls 58 and 59 and the rigidity of supporting of the roller 56 can be further enhanced. The cylindrical swinging support section 57 provided at the base end of the exhaust-side rocker arm 50 so that it is swingably supported by the exhaust-side rocker shaft 51, comprises the thinner cylindrical portion 57a surrounding the exhaust-side rocker shaft 51, and the thicker cylindrical portions 57b, 57b thicker than the thinner cylindrical portion 57a surrounding the exhaust-side rocker shaft 51 and integrally connected to the axially opposite ends of the thinner cylindrical portion 57a, respectively. Therefore, the central portion of the swinging support section 57 can be formed at a smaller thickness to avoid an increase in weight of the exhaust-side rocker arm 50, while the opposite ends of the swinging support section 57 having a possibility that a large load may be applied, can be formed at a larger thickness to enhance the rigidity of supporting of the exhaust-side rocker arm 50 and the durability of the latter. In addition, the grooves 68, 68 capable of accumulation of an oil between the grooves and the outer surface of the exhaust-side rocker shaft 51 are provided in the inner surfaces of the opposite ends of the swinging support section 57 along the axis of the exhaust-side rocker shaft 51, i.e., in the inner surfaces of the thicker cylindrical portions 57b, 57b, respectively. Therefore, the oil can be accumulated between the opposite ends of the swinging support section 57 and the exhaust-side rocker shaft 51, and even if the exhaust-side rocker arm 50 is inclined, an uneven wear can be prevented to the utmost from being produced, leading to an enhanced durability. Moreover, the grooves 68, 68 are merely provided in the inner surface of the swinging support section 57 at its opposite ends and hence, the weight of the exhaust-side rocker arm 50 cannot be increased, and a reduction in rigidity of the swinging support section 57 can be inhibited. Furthermore, the first and second support walls 58 and 59, at the tip ends of which the first and second tappet screws 53A and 53B are mounted to abut against the upper end of the exhaust valves VE, VE, are provided to extend from the opposite ends of the swinging support section 57 at the locations corresponding to the grooves 68, 68. Therefore, a slight reduction in rigidity of the opposite ends of the swinging support section 57 due to the provision of the grooves 68, 68 can be made up for by the first and second support walls 58 and 59. The outer periphery of the exhaust-side rocker arm 50 is formed by the swinging support section 57, the first support wall 58, the second support wall 59 and the connection wall 60, and the recesses 69 and 70 are defined at least in the upper surface of the exhaust-side rocker arm 50 by the portions surrounded by the swinging support section 57, the first support wall 58, the second support wall 59 and the connection wall 60. Therefore, it is possible to provide a reduction in weight of the exhaust-side rocker arm 50, while avoiding a reduction in rigidity of the exhaust-side rocker arm 50. Moreover, one of the recesses 69 is disposed between the pair of shaft support portions 65, 65 and the swinging support section 57, and the oil can be supplied to the roller 56 accommodated in the opening 62. Therefore, the oil scattered within the valve operating chamber can be reliably accumulated at a portion of the exhaust-side rocker arm 50 which is swung in a relatively small amount, thereby lubricating the roller 56, and hence, it is unnecessary to provide a passage for supplying the oil to the roller 56 in the exhaust-side rocker arm 50, thereby reducing the number of steps of processing the exhaust-side rocker arm 50. The other recess 70 is defined in the exhaust-side rocker arm 50 between the shaft support portions 65, 65 and the connection wall 60 to enable the supplying of the oil to the roller 56 and hence, the weight of the tip end of the exhaust-side rocker arm 50 can be reduced to alleviate the inertial weight, while performing the lubrication of the roller 56. The axially central portion of the swinging support section 57 in the exhaust-side rocker arm 50 is disposed at the location corresponding to the plug insertion tube 36 mounted in the cylinder head 16, and the notches 71 and 72 connected smoothly to each other and formed into the arcuate shape recessed on the side opposite to the plug insertion tube 36 are provided in the swinging support section 57 and the exhaust-side rocker shaft 51 at the location corresponding to the plug insertion tube 36. Therefore, it is possible not only to reduce the weight of the exhaust-side rocker arm 50, but also the exhaust-side rocker shaft 51 and the plug insertion tube 36 can be disposed in the proximity to each other in such a manner that a portion of the plug insertion tube 36 is accommodated in the notch 71, and the limitation of the layout of the exhaust-side rocker arm 50 within the valve operating chamber can be moderated to contribute to the compactness of the entire engine. Moreover, the notches 71 and 72 are provided in the swinging support section 57 and the exhaust-side rocker shaft 51 between the connections of the first and second support walls 58 and 59 to the swinging support section 57 and hence, the notches 71 and 72 can be disposed at the portions to which a relatively small stress is applied during driving of the exhaust valves VE, VE, thereby reducing the influence to the rigidity due to the provision of the notch 71 in the exhaust-side rocker arm 50 to reduce the weight of the exhaust-side rocker arm 50. The oil is supplied from the oil supply passage 74 in the exhaust-side rocker shaft 51 through the oil supply bore 75 and the oil injection bore 73 to the roller 56, and the oil injection bore 73 is provided in the swinging support section 57 on the side opposite to the notch 71, with respect to the axis C of the exhaust-side rocker shaft 51, which notch is provided in the swinging support section 57 in such a manner that an outer surface of a portion of the exhaust-side rocker shaft 71 provided with the notch 72 faces the notch 71. Therefore, it is possible to conduct a boring for the oil injection bore 73 from the side of the notch 71, thereby facilitating the boring for the oil injection bore 73. The first and second boss portions 58a and 59a, in which the first and second tappet screws 53A and 53B are threadedly fitted to abut against the upper ends of the exhaust valves VE, VE, are disposed at the tip ends of the exhaust-side rocker arm 50 and arranged in the direction along the axis C of the exhaust-side rocker shaft 51, but they are interconnected by the connection wall 60. Therefore, the rigidity of the tip end of the exhaust-side rocker arm 50 driving the pair of exhaust valves VE, VE can be enhanced sufficiently and moreover, the connection wall 60 comprises the first and second wall portions 60a and 60b intersecting each other at the right angles in the plane perpendicular to the axis C of the exhaust-side rocker shaft 51, i.e., the swinging axis of the exhaust-side rocker arm 50. Therefore, it is possible to suppress the increase in weight of the exhaust-side rocker arm 50 due to the connection wall 60 to the minimum, while maintaining the sufficient connection rigidity. In addition, the second wall portion 60b of the connection wall 60 is formed to extend in parallel to the axis of the exhaust-side rocker shaft 51, so that its outer surface is connected flush to the outer surfaces of the tip ends of the first and second boss portions 58a and 59a. Therefore, it is possible to eliminate the concentration of a stress on the connections between the connection wall 60 and the boss portions 58a and 59a, thereby enhancing the durability of the exhaust-side rocker arm 50, while sufficiently enhancing the rigidity of the tip end of the exhaust-side rocker arm 50. Further, one side of the opening 62 provided in the exhaust-side rocker arm 50 to accommodate the roller 56 is formed by the inner surface of the first wall portion 60a of the connection wall 60, and the connection wall 60 can be disposed in proximity to the roller 56, thereby enhancing the rigidity of supporting of the roller 56. Fig.8 shows a second embodiment of the present invention. A connection wall 90 interconnecting the tip ends of the first and second support walls 58 and 59 of the exhaust-side rocker arm 50, i.e., the first and second boss portions 58a and 59a, comprises a first wall portion 90a and a pair of second wall portions 90b, 90b which intersect each other at right angles in a plane perpendicular to the axis C of the exhaust-side rocker shaft 51. The second wall portions 90b, 90b are continuously provided at right angles at upper and lower ends of the first wall portion 90a which defines one side of the opening 62 by its inner surface, whereby the connection wall 90 is formed into a substantially U-shape to open on a side opposite to the roller 56. Tip end faces of the second wall portions 90b, 90b are connected flush to the outer peripheral surfaces of the tip ends of the first and second boss portions 58a and 59a. Even according to the second embodiment of the present invention, as in the first embodiment, the rigidity of the tip end of the exhaust-side rocker arm 50 can be enhanced sufficiently, and the increase in weight of the exhaust-side rocker arm 50 due to the connection wall 90 can be suppressed to the minimum. In addition, the concentration of a stress on the connection of the connection wall 90 and each of the boss portions 58a and 59a can be eliminated, and it is possible to enhance the durability of the exhaust-side rocker arm 50, while sufficiently enhancing the rigidity of the tip end of the exhaust-side rocker arm 50. Fig.9 shows a third embodiment of the present invention. According to a further embodiment, a connection wall 91 interconnecting the tip ends of the first and second support walls 58 and 59 of the exhaust-side rocker arm 50, i.e., the first and second boss portions 58a and 59a, comprises a pair of first wall portions 91a, 91a and a second wall portion 91b which intersect each other at right angles in a plane perpendicular to the axis C of the exhaust-side rocker shaft 51. Lower ends of the pair of first wall portions 91a, 91a extending vertically at a distance from each other are continuously provided at right angles by the second wall portion 91b, whereby the connection wall 91 is formed into a substantially U-shape to open upwards. Moreover, inner one of the first wall portions 91a defines one side of the opening 62 by its inner surface, while outer one of the first wall portions 91a extends in parallel to the axis C of the exhaust-side rocker shaft 51 to have the same height as the boss portions 58a and 59a, and is connected flush to the outer peripheral surfaces of the tip ends of the boss portions 58a and 59a. According to this embodiment, an effect similar to that in the second embodiment can be provided. Figs.10 and 11 show a fourth embodiment of the present invention. A connection wall 92 interconnecting the tip ends of the first and second support walls 58 and 59 of the exhaust-side rocker arm 50, i.e., the first and second boss portions 58a and 59a, is formed into a substantially U-shape to open on a side opposite to the roller 56 by a first wall portion 90a and a pair of second wall portions 90b, 90b, and is provided with a plurality of ribs 93, 93 which are connected to the wall portions 90a, 90b, 90b and intersect one another. According to the fourth embodiment, the rigidity of the tip ends of the exhaust-side rocker arm 50 can be further enhanced. Although the embodiments of the present invention have been described in detail, it will be understood that the present invention is not limited to the above-described embodiments, and various modifications in design may be made without departing from the spirit and scope of the invention defined in claims. For example, the present invention is applicable to a valve operating system for an intake valve. In a valve operating system in an internal combustion engine, a swinging support section provided at a base end of a rocker arm is swingably carried on a rocker shaft, and tappet screws are threadedly fitted in a plurality of boss portions formed at a tip end of the rocker arm and arranged in a direction parallel to an axis of the rocker shaft, so that they can be individually put into abutment against upper ends of a plurality of engine valves. Cam abutments are provided on the rocker arm in an intermediate portion between the swinging support section and the boss portions to come into contact with a valve operating cam. The boss portions are interconnected by a connection wall having a plurality of wall portions which intersect each other in a plane perpendicular to the axis of the rocker shaft. Thus, the rigidity of the tip end of the rocker arm is enhanced sufficiently.

Claims: A valve operating system for an internal combustion engine, comprising a cylindrical swinging support section (57) provided at a base end of a rocker arm (50) and swingably carried on a rocker shaft (51) mounted in a cylinder head (16), a plurality of boss portions (58a and 59a) formed at a tip end of said rocker arm (50) and arranged in a direction parallel to an axis (C) of said rocker shaft (51), tappet screws (53a and 53b) being threadedly fitted into said boss portions (58a and 59a) and capable of being individually put into abutment against upper ends of a plurality of engine valves (VE), and a cam abutment (56) provided on said rocker arm (50) in an intermediate portion between said swinging support section (57) and said boss portions (58a and 59a) to come into contact with a valve operating cam (55), wherein said boss portions (58a and 59a) are interconnected by a connection wall (60, 90, 91, 92) having a plurality of wall portions (60a, 60b; 90b, 90a, 90b; 91a, 91b, 91a) extending from one boss portion (58a) to the other boss portion (58b) and intersecting each other at right angles in a plane perpendicular to the axis (C) of said rocker shaft (51), forming said connection wall into a substantially L-shape or U-shape in this plane. A valve operating system for an internal combustion engine according to claim 1, wherein said connection wall (92) is provided with a plurality of ribs (93) which intersect each other and which are connected to said wall portions (90a, 90b), respectively. A valve operating system for an internal combustion engine according to claim 1, wherein said boss portions (58a and 59a) are interconnected by the connection wall (60, 90, 91, 92) having the wall portion (60b, 90b, 91a), an outer surface of which is connected flush to outer peripheral surfaces of the tip ends of said boss portions (58a and 59a). A valve operating system for an internal combustion engine according to claim 1, wherein said rocker arm (50) is provided with an opening (62), a portion of a side of which is formed by an inner surface of said connection wall (60, 90, 91, 92), and a roller (56) which is said cam abutment is accommodated in said opening (62) and rotatably carried on a roller shaft (63) fixed to said rocker arm (50). A valve operating system for an internal combustion engine according to claim 1, wherein said rocker arm (50) is provided with first and second support walls (58 and 59), at tip ends of which the tappet screws (53A and 53B) at axially one end and the axially other end of said rocker shaft (51) are mounted, and the connection wall (60) which interconnects tip ends of said first and second support walls (58 and 59), and said rocker arm (50) has recesses (69 and 70) defined at least in an upper surface thereof in an area surrounded by said first and second support walls (58 and 59), said connection wall (60) and said swinging support portion (57). A valve operating system for an internal combustion engine according to claim 5, wherein said rocker arm (50) is provided with an opening (62) in which a roller (56) which is said cam abutment is accommodated; a roller shaft (63) rotatably supporting said roller (56) is fixed across said opening (62); and said recesses (69 and 70) are defined in the upper surface of said rocker arm (50) so that oil can be supplied to the roller within said opening (62). A valve operating system for an internal combustion engine according to claim 6, wherein said rocker arm (50) has a pair of shaft support portions (65) provided thereon between said opening (62) and said first and second support walls (58 and 59) for supporting opposite ends of said roller shaft (63), and said recess (69) is defined in said rocker arm (50) between said shaft support portions (65) and said swinging support section (57). A valve operating system for an internal combustion engine according to claim 6, wherein said rocker arm (50) has a pair of shaft support portions (65) provided thereon between said opening (62) and said first and second support walls (58 and 59) for supporting opposite ends of said roller shaft (63), and the recess (70) is defined in said rocker arm (50) between said shaft support portions (65) and said connection wall (60).

Inventors: IWAMOTO JUNICHI, TANAKA CHIKARA, YAMADA NORIYUKI, IWAMOTO, JUNICHI, TANAKA, CHIKARA, YAMADA, NORIYUKI, Iwamoto, Junichi, c/o Kabushiki Kaisha PSG, Tanaka, Chikara, c/o K.K. Honda Gijutsu Kenkyusho, YAMADA, NORIYUKI, C/O K.K. HONDA GIJUTSU KENKYUSHO
Applicants: HONDA MOTOR CO LTD, HONDA GIKEN KOGYO KABUSHIKI KAISHA
Application year: 2000
Main classification: F01L1
IPC codes: F01L1, F01L13