Valve drive device of four-stroke cycle engine

Abstract: Valve drive device of a four-stroke cycle engine having at least one camshaft with at least one first cam for controlling at least one valve under first operation condition of the engine and at least one second cam for controlling said valve under second operation condition of the engine, wherein said second cam is switchable into a first state to be relatively rotatable with said camshaft and into a second state to be rotatable together with said camshaft, wherein said valve is controllable by the first cam when said second cam is in the first state and said valve is controllable by the second cam when said second cam is in the second state.

Description: This invention relates to a valve drive device of a four-stroke cycle engine according to the preamble of independent claim1. Such a valve drive device of a four-stroke cycle engine can be taken from prior art document JP 62-199915 A. One of conventional valve drive mechanisms for four-stroke cycle engines adapted to be switched to operate with either a low speed cam or a high speed cam is described in a publication of a laid-open Japanese patent application, Tokai Hei-7-133708. That is, the low speed cam is formed integrally with the camshaft while the high speed cam is adapted to be capable of rising or lowering in the height direction of the cam nose portion, and a drive mechanism is provided to raise or lower the high speed cam. The above-described conventional mechanism has problems that the mechanism for raising and lowering the high speed cam is complicated in both constitution and operation. It is an objective of the present invention to provide a valve drive device of a four-stroke cycle engine as indicated above which is simple in structure and provides high engine performance. According to the present invention, said objective is solved by a valve drive device of a four-stroke cycle engine having the features of claim 1. Said valve drive device of a four-stroke cycle engine is capable to be switched to operate with either a low speed cam or a high speed cam while its constitution and operation are made simple. Preferred embodiments of the present invention are laid down in further dependent claims. In the following, the present invention is explained in greater detail with respect to several embodiments thereof in conjunction with the accompanying drawings, wherein: FIG. 1 is a sectional side view of a valve drive mechanism of a four-stroke cycle engine related to an embodiment; FIG. 2 is a sectional front view of the valve drive mechanism; FIG. 3 is a sectional front view of a low speed cam of the valve drive mechanism; FIG. 4 is a sectional side view (section IV-IV in FIG. 3) of the low speed cam; FIG. 5 is a sectional front view of the valve drive mechanism; FIG. 6 is a sectional side view (section VI-VI in FIG. 3) of the high speed cam; FIG. 7 is a sectional side view (section VII-VII in FIG. 3) of the high speed cam; FIG. 8 shows drawings for explaining the operation of the high speed cam; FIG. 9 shows drawings for explaining the operation of the low speed cam; and FIG. 10 shows drawings for explaining the operation of the high speed cam and the low speed cam. Figs. 1 to 9 are drawings for explaining the valve drive mechanism or device for a four-stroke cycle engine according to an embodiment. Figs. 1 and 2 are cross-sectional views of the valve drive mechanism as seen in the direction of camshaft axis and in the direction normal to the camshaft axis, respectively. In these drawings, the symbol 1 denotes a cylinder head of a four-valve engine having intake and exhaust valves, two for each. A valve drive mechanism or device 2 is placed in the cylinder head 1. Intake valve openings 1c' and exhaust valve openings 1d', two for each, of intake ports 1c and exhaust ports 1d are made to be open to a combustion chamber 1b formed in a concave shape on the mating surface 1a on the cylinder block side of the cylinder head 1. These valve openings are opened and closed with valve plates 3a and 4a of intake and exhaust valves 3 and 4 (poppet valves). The above valve drive mechanism 2 is constituted that the intake and exhaust valves 3 and 4 are urged in the closing direction by means of valve springs 6a and 6b interposed between retainers 5a and 5b attached to the upper ends of valve rods 3b and 4b and spring seats, and that the intake and exhaust valves 3 and 4 are press-driven toward opening direction by means of intake and exhaust camshafts 8 and 9 through lifters 7a and 7b attached to the top ends of the valve rods 3b and 4b. The intake camshaft 8 and the exhaust camshaft 9 have low speed cams (first cams) 10 and high speed cams (second cams) 11, respectively two for each cylinder, and adapted that either low speed cams 10 or high speed cams 11 are made to be operative according to the operating state of the engine by means of cam switching means 15 to be described later. Since the low speed cams 10 and high speed cams 11, whether for intake or exhaust, are the same in basic constitution, the following explanation is made concerning the intake cam. The low speed cams 10 are provided two in number for each cylinder corresponding to valve lifters 7a provided two for each cylinder, and moreover, they are slightly displaced outward in the camshaft direction from the axis of the valve lifter 7a. The low speed cam 10 is formed as a single body consisting of a base circle portion 10a having a specified diameter and a nose portion 10b having a specified profile. The low speed cam 10 is secured to the camshaft 8 by means of a lock pin 13 driven into the camshaft 8 from outside at right angles to penetrate the axis of the camshaft 8. Each of the two high speed cams 11 consists of a base circle portion 11 a of the same diameter as that of the base circle portion 10a of the low speed cam and a nose portion 11 b of a specified profile, both joined together through a drum portion 11e. Each high speed cam 11 is placed in alignment with the axis of the lifter 7a and to be between the right and left low speed cams 10 and 10, and is attached for relative rotation with reference to the camshaft 8 through the eccentric bearing 14 (eccentric bushing). The external shape of the eccentric bearing 14 is circular, with the center E of the circular shape is displaced by a dimension t from the axis C of the camshaft 8. The eccentric bearing 14 is rotatably attached to the camshaft 8. Said eccentric bearing is formed like an eccentric sleeve. The length in the axial direction of the eccentric bearing 14 is about half that of the high speed cam 11. Therefore, the nose portions 11 b, 11 b located on both sides of the high speed cam 11 hang over the eccentric bearing 14. Here, the above displacement dimension t is set as follows: When the axis E of the eccentric bearing 14 is on the side of the nose portion 11b of the high speed cam 11, the nose portion 11b of the high speed cam 11 projects radially beyond the nose portion 10b of the low speed cam 10 (See FIG. 10(a)), and conversely when the axis E of the eccentric bearing 14 is on the side opposite the nose portion 11b of the high speed cam 11, the nose portion 11 b of the high speed cam 11 is hidden below the nose portion 10b of the low speed cam 10 (See FIG. 10(e)). A cam switching mechanism or device 15 (coupling device) is disposed between the camshaft 8 and the high speed cam 11 for switching whether to fix the high speed cam 11 to the camshaft 8 so that they rotate together or to make the high speed cam 11 rotatable relative to the camshaft 8. To roughly describe the constitution of the cam switching mechanism 15, a cylinder bore 15a is formed in part of the camshaft 8 corresponding to one of the high speed cams 11 at right angles to the camshaft 8 axis, a piston 15b is placed for reciprocating motion within the cylinder bore 15a, and a connecting pin 15c formed as part of the piston 15b is made capable of sliding into or out of a connecting hole 11c. Here, the open end of the cylinder bore 15a is stopped with a plug 15d, and the piston 15b is urged with a return spring 15e in the sliding out direction of the piston. A hydraulic source communicates through a hydraulic supply hole 15f with an oil chamber (a) formed with the cylinder bore 15a, the piston 15b, and the plug 15. When hydraulic pressure is supplied to the oil chamber (a), the piston 15b causes the connecting pin 15c to slide into the connecting hole 11c. As a result, the high speed cam 11 is fixed to and rotate together with the camshaft 8. Conversely, when the supply of the hydraulic pressure is shut off, the connecting pin 15c slides out of the connecting hole 11c to make the high speed cam 11 movable with reference to the camshaft 8. That is, the high speed cam 11 becomes rotatable relative to the camshaft 8 and also movable in the direction normal to the axis of the camshaft 8 owing to the rotation of the eccentric bearing 14. A guide hole 15g is formed in part of the camshaft 8 corresponding to the other high speed cam 11 in the direction normal to the camshaft axis C. A pressing pin 16 for reciprocating motion is placed in the guide hole 15g and urged outward by means of an urging spring 17. This constitutes urging means which constantly causes, when seen in the camshaft axis direction, the nose portion 11 b of the high speed cam 11 to be in the same position as that of the nose portion 10b of the low speed cam 10 and which urges the high speed cam 11 toward the position in which the high speed cam 11 projects outward to be operative. Incidentally, it may be otherwise constituted as shown in FIG. 6(b), to directly urge the high speed cam 11 by means of an urging spring 17 toward the high speed cam operation position without providing the pressing pin 16. A tip 16a of the pressing pin 16 is formed hemispherical and is stopped as it contacts a contact stop recess 11d sunk-formed in an arcade shape in the high speed cam 11. That is, the high speed cam 11 rotates with reference to the camshaft 8 within a range permitted with the contact stop recess 11d. Here, since the connecting pin 15c and the pressing pin 16 are located on the outer sides in the axial direction of the eccentric bearing 14, they do not restrict the motion of the eccentric bearing 14, so that the eccentric bearing 14 always remains rotatable with reference to the camshaft 8 and the high speed cam 11. The symbol 18 stands for a valve timing adjustment mechanism or device that adjusts opening and closing timing of intake and exhaust valves according to the operating conditions of the engine by causing relative rotation in the direction of advancing or delaying the angular position of the camshaft 8 relative to a cam sprocket 18a attached to one end of the camshaft 8. Next, the motions, functions, and effects of the valve drive mechanism of this embodiment are described. When the engine operates in a high revolution range, hydraulic pressure is supplied through the hydraulic supply hole 15f to the oil chamber (a) of the cam switching mechanism 15, the piston 15b slides so that its connecting pin 15c slides into and stopped with the connecting hole 11c of the high speed cam 11, and the high speed cam 11 rotates together with the camshaft 8 simultaneously like a single body (See FIG. 7(b)). At this time, since the high speed cam 11 is press-urged with the pressing pin 16 and the urging spring 17, the center E of the eccentric bearing 14 is displaced by a dimension t toward the side where the nose portion 11 b of the high speed cam 11 becomes the highest. As a result, the nose portion 11 b of the high speed cam 11 projects outward beyond the nose portion 10b of the low speed cam 10 (See Figs. 10(a) and 8(a)). Along with the rotation of the camshaft 8 in this state, the lifter 7a and further the intake or exhaust valve 3 or 4 are driven to open and close according to valve opening-closing characteristics determined with the cam profile of the nose portion 11 b of the high speed cam 11 (See Figs. 8(a) to 8(f)). When the engine operates in a low revolution range, supply of hydraulic pressure to the oil chamber (a) of the cam switching mechanism 15 is shut off, the piston 15b is pushed back with the return spring 15e, the connecting pin 15c of the piston 15b retracts inside, and the high speed cam 11 is disengaged from the camshaft 8 (See FIG. 7(a)). At this time, since the high speed cam 11 is press-urged with the pressing pin 16 and the urging spring 17, the center E of the eccentric bearing 14 is displaced on the side where the nose portion 11b of the high speed cam 11 becomes the highest. As a result, the nose portion 11b of the high speed cam 11 projects outward beyond the nose portion 10b of the low speed cam 10 (See Figs. 9(a) and 10(a)). In this state, when the camshaft 8 rotates counterclockwise as seen in Figs. 8 and 9 to cause the cam nose portion 11 b of the high speed cam 11 to begin contacting the lifter 7a (See FIG. 9(b) and FIG. 10(b)), a force in the direction opposite the camshaft rotation (clockwise) acts on the high speed cam 11. As a result, the eccentric bearing 14 rotates clockwise as seen in Figs. 9 and 10, and the axis E of the eccentric bearing 14 shifts toward the side (opposite the nose portion) to decrease the lift amount of the high speed cam 11 (See FIG. 9(b) to 9(d) and Figs. 10(b) to 10(d)), the nose portion 10b of the low speed cam 10 begins to press the valve lifter 7a (FIG. 9(c)), the intake valve 3 begins to open along with the rotation of the camshaft 8 (FIG. 9(d)), and the intake valve 3 is opened by a low cam lift L of the nose portion 10b of the low speed cam 10 (FIG. 9(e)). At this time, the axis E of the eccentric bearing 14 is located opposite by 180 degrees to the nose portion 11b (See FIG. 10(e)), and the nose portion 11b of the high speed cam 11 is hidden within the nose portion 10b of the low speed cam 10. When the camshaft 8 further rotates, the axis E of the eccentric bearing 14 moves toward the nose portion 11b side (See Figs. 10(f) and 10(g)), the nose portions 10b and 11b move away from the lifter 7a, and the nose portion 11b of the high speed cam 11 projects outward beyond the nose portion 10b of the low speed cam 10 (Figs. 9(f) and 9(g)). In effect, this embodiment is constituted as follows: The eccentric bearing 14 is interposed between the high speed cam 11 and the camshaft 8. The high speed cam 11 is adapted to be switched either to the state of being fixed to the camshaft 8 or to the state capable of making relative motion with reference to the camshaft 8. To make the low speed cam 10 operative, the high speed cam 11 is switched to the state capable of making relative motion with reference to the camshaft 8. In this way, it is possible to switch cams between the high speed cam 11 and the low speed cam 10 according to the operating state of the engine by means of a simple constitution. As a result, it is possible during the low speed operation to provide the valve opening-closing characteristics of low lift and narrow opening angle with improved combustion stability and low speed torque, and during the high speed operation to provide the valve opening-closing characteristics of high lift and wide opening angle with improved output. Since the high speed cam 11 is urged with the pressing pin 16 and the urging spring 17 in the direction passing the center of the nose portion 11b radially outward, it is possible to automatically and smoothly bring the high speed cam 11 to the state in which the high speed cam 11, as seen in the camshaft axis direction, is in the same position as the low speed cam 10 and the nose portion 11b of the high speed cam 11 projects radially beyond the nose portion 10b of the low speed cam 10. The above embodiment is constituted that the eccentric bearing 14 is in the state of constantly capable of making relative rotation, the high speed cam 11 is switched either to the state of being fixed to the camshaft 8 or to the state capable of making relative motion, and the high speed cam 11 is fixed to the camshaft 8 during the high speed cam operation. However, it may be alternatively constituted that the eccentric bearing 14 is immovable with reference to the camshaft 8 during the high speed cam operation and the high speed cam 11 is fixed to the eccentric bearing 14. The embodiment shows the low and high speed cam and the cam switching device adapted to a 4-valve engine, wherein said cams are provided for controlling a pair of intake or exhaust valves, respectively. According to an other embodiment which is not shown the low and high speed cam and the cam switching device can be adapted to control a single intake or exhaust valve, respectively. Said single valves may be the valves of a 2-valve engine or a multi-valve engine, e.g. a 3-, 4- or 5-valve engine. Furthermore, the embodiment shows the low and high speed cams and the cam switching devices controlling the intake and exhaust valves of the engine. According to an other embodiment which is not shown the low and high speed cams and the cam switching devices may control the intake or exhaust valves, while the respective other valves may be controlled by a conventional valve drive device. The embodiments described above are teaching an internal combustion engine having a combustion chamber, at least one gas flow passage communicating with said combustion chamber through a valve seat, a poppet valve for controlling the flow through said valve seat, a camshaft journalled for rotation about a camshaft axis, a first cam having a first lift characteristic fixed for rotation with said camshaft, a second cam associated with said camshaft for relative rotation, said second cam has a second lift characteristic different from said first lift characteristic of said first cam, a valve actuator associated with said first and said second cams for transmitting their rotational movements to reciprocation of said poppet valve, and a coupling device 15 for selectively permitting relative movement between said camshaft and said second cam so that said first cam controls the entire opening and closing cycle of said poppet valve and for coupling said second cam for rotation with said camshaft about said camshaft axis so that said second cam controls at least a part of the opening and closing cycle of said poppet valve. The coupling device 15 maintains the angular phase positions of the first and second cams regardless of which cam is controlling the opening and closing cycle of the poppet valve. The maximum valve lift provided by the second cam is greater than that of the first cam. The coupling device 15 shifts the axis about which the second cam rotates when the first cam controls the entire opening and closing cycle of the poppet valve so that the second cam does not control the opening and closing cycle of said poppet valve. As can be taken from the embodiment, the coupling device comprises an eccentric bushing having a cylindrical bore coaxially received on the camshaft and an cylindrical outer surface eccentrically disposed to said cylindrical bore and received in a complimentary bore formed in the second cam and a selectively operable lock for coupling one of said eccentric bushing and said second cam for rotation with said camshaft so that both said second cam and said eccentric bushing rotate in unison with said camshaft. The selectively operable lock fixes the second cam for rotation with the camshaft. The portion of the coupling device 15 that maintains the angular phase positions of the first and second cams regardless of which cam is controlling the opening and closing cycle of the poppet valve comprises a resiliently biased member engaged between the camshaft and said second cam. The selectively operable lock is operative to axially limit the movement of the eccentric bushing relative to the camshaft in at least one axial direction. The resiliently biased member is operative to axially limit the movement of the eccentric bushing relative to the camshaft in an axial direction opposite to the axial direction controlled by the selectively operable lock. The embodiments are teaching a valve drive mechanism of a four-stroke cycle engine adapted to be switched to operate with either a low speed cam of a cam profile suited for low speed operation or a high speed cam of a cam profile suited for high speed operation, characterized in that the low speed cam is adapted to rotate together with a camshaft, that the high speed cam is adapted to be switched to either rotate together with the camshaft or make relative movement with reference to the camshaft, and that the high speed cam, when switched to make relative movement, is substantially hidden within the cam profile of the low speed cam along with the rotation of the camshaft, so that the valves are opened and closed with the low speed cams. Thus, when the engine is to be operated with the low speed cam, the high speed cam is switched to the state capable of making relative movement, so that the high speed cam is automatically hidden within the cam profile of the low speed cam along with the rotation of the camshaft, namely by utilizing the rotation of the camshaft. As a result, valves are driven to open and close by means of the low speed cams. With such simple constitution and simple operation, the mechanism can be switched to operate with either the high speed cam or the low speed cam. An eccentric bearing with its axis off the camshaft axis is attached for relative rotation to the camshaft, that the high speed cam is attached for relative rotation to the eccentric bearing, and that cam switching means is provided to connect the high speed cam to the camshaft in the state of being either capable or incapable of making relative motion with reference to the camshaft. Thus, when the engine is to be operated with the low speed cam, the high speed cam is switched to the state capable of making relative movement. Then, the high speed cam rotates relative to the camshaft without driving the lifter. Along with this, the eccentric bearing rotates with reference to the camshaft and causes relative movement of the high speed cam in the direction of reducing its nose portion height. As a result, the high speed cam retracts within the profile of the low speed cam. As a result, valves are driven with the low speed cams. In this way, switching between the low speed cam and the high speed cam is accomplished with the simple constitution of providing the eccentric bearing between the high speed cam and the camshaft and the simple action of moving the high speed cam in the nose portion height direction by the relative rotation of the eccentric bearing with reference to the camshaft. When the high speed cams are in operation, valves are driven to open and close by connecting the high speed cam and the camshaft by means of a pin or the like. The cam switching means is constituted to either make or brake interconnection between the camshaft and the eccentric bearing. Thus, the cam switching means is constituted to either make or brake interconnection between the camshaft and the high speed cam, so that the high speed cam is operative when the camshaft is connected to the high speed cam and that the low speed cam is operative when the connection is released. As a result, switching between the low speed cam and the high speed cam is accomplished with simple constitution and operation. The high speed cam switching means is constituted to either make or brake interconnection between the camshaft and the eccentric bearing and further to either make or brake interconnection between the eccentric bearing and the high speed cam. Thus, the cam switching means is constituted to either make or brake interconnection between the camshaft and the eccentric bearing and further to either make or brake interconnection between the eccentric bearing and the high speed cam. As a result, also in this case, switching between the low speed cam and the high speed cam is accomplished with simple constitution and simple operation. An urging means is provided to urge the high speed cam toward the apex of the cam nose portion. Since urging means is provided to urge the high speed cam toward the apex of the cam nose portion, it is possible, in the state of the high speed cam being capable of making relative movement, to move the high speed cam smoothly to the high speed cam operation position in which the high speed cam projects from the low speed cam. The embodiments described above are teaching a valve drive device of a four-stroke cycle engine having at least one camshaft 8,9 with at least one first cam 10 for controlling at least one valve 3,4 under first operation condition of the engine and at least one second cam 11 for controlling said valve 3,4 under second operation condition of the engine, wherein said second cam 11 is switchable into a first state to be relatively rotatable with said camshaft 8,9 and into a second state to be rotatable together with said camshaft 8,9, wherein said valve 3,4 is controllable by the first cam 10 when said second cam 11 is in the first state and said valve 3,4 is controllable by the second cam 11 when said second cam 11 is in the second state. Said first cam 10 is provided with a cam profile suited for low speed operation and said second cam 11 is provided with a cam profile suited for high speed operation. In the first state of the second cam 11 the cam profile of the second cam 11 is substantially hidden within the cam profile of the first cam 10, so that the valve 3,4 is controllable with the cam profile of the first cam 10, and in the second state of the second cam (11) the cam profile of the second cam 11 is substantially projecting from the cam profile of the first cam 10, so that the valve 3,4 is controllable with the cam profile of the second cam 11. A cam switching means 15 is provided for connecting the second cam 11 to the camshaft 8,9 to be in the second state and for disconnecting the second cam 11 from the camshaft 8,9 to be in the first state. An eccentric bearing means 14 is provided for rotatably supporting said second cam 11 on the camshaft 8,9. An axis E of said eccentric bearing means 14 is set off with regard to an axis C of the camshaft 8,9. Said eccentric bearing means 14 comprises an eccentric bearing sleeve rotatably having an inner circular surface supported on the camshaft 8,9 and an outer circular surface supporting said second cam 11. Said inner circular surface is eccentric with said outer circular surface. An urging means 16,17 is provided between said camshaft 8,9 and said second cam 11 for urging the second cam 11 in direction of an apex of a cam nose portion of the second cam 11. Said urging means 16,17 engages the camshaft 8,9 and a contact stop means 11d provided on the second cam 11 for restricting the relative rotation of the second cam 11 with the camshaft within a predetermined range. According to the embodiment, said first cam 10 comprises two cam portions for controlling two valve 3,4 associated to on cylinder of the engine, wherein said second cam 11 for controlling said two valve 3,4 is provided between said two cam portions of said first cam 10. The embodiment described above shows an intake camshaft 8 and an exhaust camshaft 9 each provided with at least one first cam 10 and at least one second cam 11. According to the embodiments, a valve timing adjustment device 18 is attached to said camshaft 8,9 for adjusting a phase angle of said camshaft 8,9.

Claims: Valve drive device of a four-stroke cycle engine having at least one camshaft (8,9) with at least one first cam (10) for controlling at least one valve (3,4) under first operation condition of the engine and at least one second cam (11) for controlling said valve (3,4) under second operation condition of the engine, wherein said second cam (11) is switchable into a first state to be relatively rotatable with reference to said camshaft (8,9) and into a second state to be rotatable together with said camshaft (8,9), wherein said valve (3,4) is controllable by the first cam (10) when said second cam (11) is in the first state and said valve (3,4) is controllable by the second cam (11) when said second cam (11) is in the second state, characterized by an eccentric bearing means (14) provided for rotatably supporting said second cam (11) on the camshaft (8,9), wherein an axis (E) of said eccentric bearing means (14) is offset with regard to an axis (C) of the camshaft (8,9), and said second cam (11) is radial displaceable with regard to said axis (C) of the camshaft (8,9). Valve drive device according to claim 1, characterized in that said first cam (10) is provided with a cam profile suited for low speed operation and said second cam (11) is provided with a cam profile suited for high speed operation, wherein in the first state of the second cam (11) the cam profile of the second cam (11) is substantially hidden within the cam profile of the first cam (10), so that the valve (3,4) is controllable with the cam profile of the first cam (10), and in the second state of the second cam (11) the cam profile of the second cam (11) is substantially projecting from the cam profile of the first cam (10), so that the valve (3,4) is controllable with the cam profile of the second cam (11). Valve drive device according to claim 1 or 2, characterized in that cam switching means (15) is provided for connecting the second cam (11) to the camshaft (8,9) to be in the second state and for disconnecting the second cam (11) from the camshaft (8,9) to be in the first state. Valve drive device according to at least one of the claims 1 to 3, characterized in that said eccentric bearing means (14) comprises an eccentric bearing sleeve rotatably having an inner circular surface supported on the camshaft (8,9) and an outer circular surface supporting said second cam (11), wherein said inner circular surface is eccentric with said outer circular surface. Valve drive device according to at least one of the claims 1 to 4, characterized in that an urging means (16,17) is provided between said camshaft (8,9) and said second cam (11) for urging the second cam (11) in direction of an apex of a cam nose portion of the second cam (11). Valve drive device according to claim 5, characterized in that urging means (16,17) engages the camshaft (8,9) and a contact stop means (11d) provided on the second cam (11) for restricting the relative rotation of the second cam (11) with the camshaft within a predetermined range. Valve drive device according to at least one of the claims 1 to 6, characterized in that said first cam (10) comprises two cam portions for controlling two valve (3,4) associated to on cylinder of the engine, wherein said second cam (11) for controlling said two valve (3,4) is provided between said two cam portions of said first cam (10). Valve drive device according to at least one of the claims 1 to 7, characterized by an intake camshaft (8) and an exhaust camshaft (9) each provided with at least one first cam (10) and at least one second cam (11). Valve drive device according to at least one of the claims 1 to 8, characterized by a valve timing adjustment device (18) attached to said camshaft (8,9) for adjusting a phase angle of said camshaft (8,9).

Inventors: SUZUKI ATSUSHI, SUZUKI, ATSUSHI
Applicants: YAMAHA MOTOR CO LTD, YAMAHA HATSUDOKI KABUSHIKI KAISHA
Application year: 2001
Main classification: F01L13
IPC codes: F01L13, F01L1