SOHC type internal combustion engine

Abstract: A SOHC type internal combustion engine includes a pair of intake valves V I1 and V I2 and a pair of exhaust valves V E1 ,V E2 . The intake valve driving means 17₁ comprises a plurality of rocker arms 24₁, 25₁, 26₁ disposed adjacent one another, including a pair of driving rocker arms 24₁ 25₁ operatively connected separately to the intake valves and a connection switchover mechanism 50 capable of switching-over the connection and disconnection of the adjacent rocker arms in accordance with the operational condition of the engine. The exhaust valve driving means 18₁ comprises a pair of exhaust valve-side rocker arms 29₁, 30₁ operatively connected separately to the exhaust valves and disposed on opposite sides of the intake valve driving means in positions opposed to the cam shaft 16, respectively. In the intake valve driving means, the opening and closing mode of the intake valves can be changed in accordance with the operational condition of the engine by operation of the connection switchover mechanism, thereby providing an improvement in output from the engine. The intake valve driving means is constructed compactly by disposition of the plurality of rocker arms constituting the intake valve driving means adjacent one another in the positions opposed to the cam shaft, thereby enabling an effective and compact construction of the connection switchover mechanism provided in the intake valve driving means.

Description: This invention relates to a single overhead cam shaft (SOHC) type internal combustion engine comprising an intake valve driving means interposed between a single cam shaft rotatably disposed above a combustion chamber and a pair of intake valves for converting the rotational motion of the cam shaft into the opening and closing motions of the intake valves, an exhaust valve driving means interposed between the cam shaft and a pair of exhaust valves for converting the rotational motion of the cam shaft into the opening and closing motions of the exhaust valves, and a plug-insertion cylindrical portion disposed in a cylinder head for insertion of a spark plug which is to be disposed at a central portion of a ceiling surface of the combustion chamber. Such SOHC type internal combustion engine is conventionally known, for example, from Japanese Patent Application Laid-open No. 57806/88 and the like. In the above prior art, a plurality of intake valve-side rocker arms are interposed between a pair of intake valves and a cam shaft, and a pair of exhaust valve-side rocker arms are interposed between a pair of exhaust valves and the cam shaft, so that the pair of intake valves and the pair of exhaust valves are opened and closed by swingably driving the individual rocker arms by cams provided on the cam shaft. In addition, a connection switchover mechanism is provided in the intake valve-side rocker arms and capable of switching-over the connection and disconnection of the rocker arms, in order to improve the output performance of the engine by varying the opening and closing mode of the intake valves in accordance with the operational condition of the engine. However, the intake valve-side rocker arms are adjacent one another in a location in which the connection switchover mechanism is provided, but the cams for the intake valve-side rocker arms and the cams for the exhaust valve-side rocker arms are provided alternately in an axial direction on the cam shaft, as also seen for example in EP-A-0 187 287, and hence the intake valve-side rocker arms cannot be arranged in a compact manner. This provides an increase in size of the connection switchover mechanism, resulting in an increase in weight of the intake valve-side rocker arm, in a difficulty of improving the dimensional accuracy of the connection switchover mechanism, and in a difficulty of disposing the slide contact portion of the intake valve-side rocker arm with the cam and the operatively connected position of the intake valve-side rocker arm to the intake valve together in a plane perpendicular to the swinging axis of the intake valve-side rocker arm, thereby causing an uneven or eccentric load to act on the intake valve-side rocker arm. JP-A-1 301 909 also illustrates an SOHC type internal combustion engine in which a plurality of intake valve-side rocker arms are interposed between intake valves and a cam shaft, and a pair of exhaust valve-side rocker arms are interposed between a pair of exhaust valves and the cam shaft. The cam shaft is supported at locations between the rocker arms. Viewed from one aspect, the present invention provides a single overhead camshaft type multi-cylinder internal combustion engine having: a plurality of cylinders; a single camshaft rotatably mounted in a cylinder head above combustion chambers for the cylinders, said single camshaft having cams provided thereon; a pair of intake valves for each cylinder mounted in said cylinder head on one side of said camshaft; a plurality of intake valve-side driving rocker arms for operatively connecting said camshaft to said pair of intake valves; a pair of exhaust valves for each cylinder mounted on the cylinder head on the other side of the camshaft; a pair of exhaust valve-side driving rocker arms for operatively connecting said camshaft to said pair of exhaust valves; a structure for rotatably supporting said camshaft on the cylinder head; a spark plug mounting hole in a central portion of a ceiling of each combustion chamber; and a plug pipe which extends to the spark plug mounting hole and is provided in an inclined fashion with its upper portion spaced from the camshaft, said plug pipe being disposed substantially between the camshaft and the axes of the pair of exhaust valves; wherein said plurality of intake valve-side driving rocker arms are positioned between the pair of exhaust valve-side driving rocker arms; characterised in that said supporting structure includes adjacent two holders coupled to the cylinder head, said adjacent two holders are each located between adjacent two cylinders and form adjacent supports for the camshaft, and said plurality of intake valve-side driving rocker arms and said pair of exhaust valve-side driving rocker arms are all disposed between said adjacent two holders at a location substantially above the associated cylinder; said cams for operating the intake and exhaust valve-side driving rocker arms for each cylinder are all disposed between the adjacent two holders with the cams for the exhaust valve-side driving rocker arms being located at opposite outermost positions; and a mechanism is provided for switching over connection and disconnection between adjacent ones of the intake valve-side driving rocker arms. With such construction, in the intake valve driving means, the opening and closing mode of the intake valves can be changed in accordance with the operational condition of the engine by switching-over the connection and disconnection of the plurality of rocker arms by operation of the connection switchover mechanism in accordance with the operational condition of the engine. This can contribute to an improvement in output from the engine. Moreover, the intake valve driving means can be constructed compactly by disposition of the plurality of rocker arms constituting the intake valve driving means adjacent one another in positions along and the cam shaft. As a result, the connection switchover mechanism provided in the intake valve driving means can be also constructed compactly. A number of embodiments will now be described, by way of example only, with reference to the accompanying drawings, wherein: Figs. 1 to 4 illustrate a first embodiment of the present invention, wherein Fig. 1 is a longitudinal sectional view of an engine body portion, taken along a line I-I in Fig.2; Fig. 2 is a sectional view taken along a line II-II in Fig. 1; Fig. 3 is a sectional view taken along a line III-III in Fig. 1; and Fig. 4 is an enlarged sectional view taken along a line IV-IV in Fig. 1; Figs. 5 and 6 illustrate a second embodiment of the present invention, wherein Fig. 5 is a longitudinal sectional view of an engine body portion, similar to Fig. 1; and Fig. 6 is a sectional view taken along a line VI-VI in Fig. 5; Figs. 7 to 9A illustrate a third embodiment of the present invention, wherein Fig. 7 is a longitudinal sectional view of an engine body portion, similar to Fig. 1; Fig. 8 is a sectional view taken along a line VIII-VIII in Fig. 7; Fig. 9 is a bottom view of a cylinder head, taken along a line IX-IX in Fig. 7; and Fig. 9A is a diagram illustrating the shape of a squish area; Fig. 10 is a bottom view of a cylinder head, similar to Fig. 9, but illustrating a modification of an intake passage; Figs. 11 and 12 illustrate a fourth embodiment of the present invention, wherein Fig. 11 is a longitudinal sectional view of an engine body portion, similar to Fig. 1; and Fig. 12 is a sectional view taken along a line XIl-XII in Fig. 10. Referring first to Fig. 1 illustrating a first embodiment of the present invention, an essential portion of an engine body in an SOHC type multi-cylinder internal combustion engine is comprised of a cylinder block 1 and a cylinder head 2 coupled to an upper surface of the cylinder block 1. A piston 4 having a depression 4a on an upper surface thereof is slidably received in a cylinder 3 provided in the cylinder block 1, and a combustion chamber 5 is defined between the upper surface of the piston 4 and the cylinder head 2. Referring also to Fig. 2, first and second intake valve opening 6 1 and 6 2 and first and second exhaust valve openings 7 1 and 7 2 are provided in the cylinder head 2 and opened into a ceiling surface of the combustion chamber 5. The intake valve openings 6 1 and 6 2 are connected to a single intake port 8 opened in one side surface of the cylinder head 2, and the exhaust valve openings 7 1 and 7 2 are connected to a single exhaust port 9 opened in the other side surface of the cylinder head 2. A first V I1 and a second intake valve V I2 are slidably received in a pair of cylindrical guides 10 disposed in the cylinder head 2, respectively, and adapted to open and close the first and second intake openings 6 1 and 6 2 independently. Coiled valve springs 12, 12 surrounding the intake valves V I1 and V I2 are provided between the cylinder head 2 and retainers 11, 11 fixed to upper ends of the intake valves V I1 and V I2 projecting from the corresponding cylindrical guides 10, respectively, so that the intake valves 12, 12 are biased upwardly, i.e., in valve-closing direction by the valve springs 12, 12. Exhaust valves V E1 and V E2 capable of opening and closing the first and second exhaust valve openings 7 1 and 7 2 independently are slidably received in a pair of cylindrical guides disposed in the cylinder head 2. Coiled valve spring 15, 15 surrounding the exhaust valves V E1 and V E2 are provided between the cylinder head 2 and retainers 14, 14 fixed to upper ends of the exhaust valves V E1 and V E2 projecting from the cylindrical guides 13, respectively, so that the exhaust valves V E1 and V E2 are biased upwardly, i.e., in valve-closing direction by the valve springs 15, 15. An intake valve driving means 17 1 , is interposed between the intake valves V I1 and V I2 and a single cam shaft 16 operatively connected to a crankshaft (not shown) at a reducing ratio of 1/2 for converting the rotational motion of the cam shaft 16 into the opening and closing motions of the intake valves V I1 , and V I2 , and an exhaust valve driving means 18 1 is interposed between the exhaust valves V E1 and V E2 and the cam shaft 16 for converting the rotational motion of the cam shaft 16 into the opening and closing motions of the intake valves V E1 and V E2 . Referring also to Fig. 2, the cam shaft 16 is rotatably carried by the cylinder head 2 and a holder 20 coupled to the cylinder head 2 and has a horizontal axis perpendicular to the axis of the cylinder 3. The cam shaft 16 is integrally provided with a higher speed cam 21 and lower speed cams 22, 22 adjacent to opposite sides of the higher speed cam 21 and further is integrally provided with exhaust valve cams 23, 23 on opposite sides the lower speed cams 22, 22. The higher speed cam 21 has a shape permitting the intake valves V I1 and V I2 to be opened and closed in a higher speed operational region of the engine and includes a base circle portion 21a and a raised portion 2lb projecting radially outwardly from the base circle portion 21a. Each of the lower speed cams 22 has a shape permitting the intake valves V I1 and V I2 to be opened and closed in a lower speed operational region of the engine and includes a base circle portion 22a and a raised portion 22b projecting radially outwardly of the cam shaft 16 by a smaller amount that the raised portion 21b of the higher speed cam 21 and over a region of a central angle smaller than that of the raised portion 21b. Further, the exhaust valve cam 23 has a shape permitting the exhaust valves V E1 and V E2 to be opened and closed in all the operational conditions of the engine. The intake valve driving means 17 1 comprises a first driving rocker arm 24 1 , operatively connected to the first intake valve V I1 , a second rocker arm 25 1 operatively connected to the second intake valve V 12 , and a free rocker arm 26 1 , disposed between the driving rocker arms 24 1 and 25 1 . The rocker arms 24 1 , 25 1 and 26 1 are swingably carried by a rocker arm shaft 27 which is fixedly supported on a holder 20 and has an axis parallel to the cam shaft 16 above the cam shaft 16. The exhaust valve driving means 18 1 comprises a pair of exhaust valve-side rocker arms 29 1 and 30 1 swingably carried on a rocker arm shaft 28 which is fixedly supported on the holder 20 parallel to the rocker arm shaft 27 above the cam shaft 16. In the intake valve driving means 17 1 , a cam slipper 31 is provided at one end of the first driving rocker arm 24 1 and adapted to come into sliding contact with the lower speed cam 22 provided on the cam shaft 16, and a cam slipper (not shown) is provided at one end of the second driving rocker arm 25 1 to come into sliding contact with the lower speed cam 22 provided on the cam shaft 16. A cam slipper (not shown) is provided on the free rocker arm 26 1 to come into sliding contact with the higher speed cam 21 provided on the cam shaft 16. In addition, a cam slipper 34 is provided on one end of each of the exhaust valve-side rocker arms 29 1 and 30 1 to come into sliding contact with corresponding one of the exhaust valve cams 23, 23 provided on the cam shaft 16. A tappet screw 35 is threadedly engaged in the other end of each of the first and second driving arms 24 1 and 25 1 of the intake valve driving means 17 1 for advancing and retreating movement to abut against an upper end of each of the intake valves V I1 and V I2 , so that the intake valves V I1 and V I2 are opened and closed in response to the swinging movement of the driving rocker arms 24 1 and 25 1 . A tappet screw 36 is also threadedly engaged in the other end of each of the rocker arms 29 1 and 30 1 in the exhaust valve driving means 18 1 to abut against an upper end of each of the exhaust valves V E1 and V E2 , so that the exhaust valves V E1 and V E2 are opened and closed in response to the swinging movement of the rocker arms 29 1 and 30 1 . Referring again to Fig. 1, a support plate 37 is fixedly mounted on the holder 20 above the cylinder head 2 in a position corresponding to between adjacent cylinders 3 to cover the rocker arm shafts 27 and 28. The support plate 37 is provided with a lost motion mechanism 38 for resiliently biasing the free rocker arm 26 1 toward the higher speed cam 21. The lost motion mechanism 38 comprises a bottomed cylindrical guide member 39 fitted in the support plate 37, a piston 40 slidably received in the guide member 39 and having an abutment portion shaped convergently at an end closer to the free rocker arm 26 1 for abutment against the free rocker arm 26 1 , a stopper 41 detachably secured to an inner surface of the guide member 39 closer to an opened end to engage the piston 40, and a first spring 42 and a second spring 43 interposed between the piston 40 and the guide member 39 to resiliently bias the piston 40 in a direction to abut against the free rocker arm 26 1 . The support plate 37 is provided with a bottomed cylindrical portion 37a opened downwardly in a location corresponding to the free rocker arm 26 1 , and the guide member 39 is fitted into the bottomed cylindrical portion 37a with its opened end turned downwardly. A spring chamber 44 is defined between the piston 40 and the guide member 39. The first spring 42 has a relatively small spring constant and is provided in a compressed manner between a retainer 45 contained in the spring chamber 44 and the piston 40, and the second spring 43 has a relatively large spring constant and is provided in a compressed manner between the retainer 45 and a closed end of the guide member 39. The bottomed small hole 40b is made coaxially in an inner surface of a closed end of the piston 40, and the first spring 42 having a relatively small spring constant is contained in the small hole 40b, whereby falling of the first spring is prevented. The abutment portion 40a of the piston 40 also has an air vent hole 46 made therein into a cross-shape opening in an outer surface of the abutment portion 40a and communicating with the outside of the spring chamber 44, in order to prevent the interior of the spring chamber 44 from being pressurized and depressurized during sliding movement of the piston 40. Further, an oil groove 47 is provided on the support plate 37 to extend in parallel to the cam shaft 16 adjacent a base end of the bottomed cylindrical portion 37a, and an oil passage 48 is provided in the base end of the bottomed cylindrical portion 37a and the guide member 39 for conducting an oil flowing through the oil groove 47 into the spring chamber 44. Thus, lubricating oil can be supplied between the piston 40 and the guide member 39 by flowing of the lubricating oil through the oil groove 47. Referring to Fig. 4, the intake valve driving means 17 1 is provided with a connection switchover mechanism 50 capable of switching-over the connection and disconnection of the rocker arms 24 1 to 26 1 in accordance with the operational condition of the engine. The connection switchover mechanism 50 comprises a first connecting piston 51 capable of connecting the first driving rocker arm 24 1 and the free rocker arm 26 1 , a second connecting piston 52 capable of connecting the free rocker arm 26 1 and the second driving rocker arm 25 1 , a restricting member 53 for restricting the movement of the first and second connecting pistons 51 and 52, and a return spring 54 for biasing the pistons 51 and 52 and the restricting member 53 toward a disconnection position. A first bottomed guide hole 55 is provided in the first driving rocker arm 24 1 in parallel to the rocker arm shaft 27 and opened toward the free rocker arm 26 1 . The first connecting piston 51 is slidably received in the first guide hole 55, and a hydraulic pressure chamber 56 is defined between one end of the first connecting piston 51 and a closed end of the first guide hole 55. A communication passage 57 is also provided in the first driving rocker arm 24 1 to communicate with the hydraulic pressure chamber 56, and a hydraulic pressure supply passage 58 is provided in the rocker shaft 27 and leads to a hydraulic pressure supply source which is not shown. The hydraulic pressure supply passage 58 continually communicates with the communication passage 57 and the hydraulic pressure chamber 56 despite the swinging condition of the first driving rocker arm 24 1 by means of an internal groove (not numbered) in the first driving rocker arm 24 1 . A guide hole 59 corresponding to the first guide hole 55 is provided in the free rocker arm 26 1 to extend between opposite side surfaces thereof in parallel to the rocker arm shaft 27, and the second connecting piston 52 abutting at one end thereof against the other end of the first connecting piston 51 is slidably received in the guide hole 59. A second bottomed guide hole 60 corresponding to the guide hole 59 is provided in the second driving rocker arm 25 1 in parallel to the rocker arm shaft 27 and is open toward the free rocker arm 26 1 . The bottomed cylindrical restricting member 53 abuts against the other end of the second connecting piston 52 and is slidably received in the second guide hole 60. The restricting member 53 is disposed with its open end turned to the closed end of the second guide hole 60, and a collar 53a projecting radially outwardly is in sliding contact with an inner surface of the second guide hole 60 at such open end. The return spring 54 is mounted in a compressed manner between the closed end of the second guide hole 60 and a closed end of the restricting member 53, so that the pistons 51 and 52 and the restricting member 53 abut against one another and are biased toward the hydraulic pressure chamber 56 by the spring force of the return spring 54. Moreover, a communication hole 61 for venting air and oil is provided at the closed end of the second guide hole 60. A retaining ring 62 is fitted on an inner surface of the second guide hole 60 and is capable of engaging the collar 53a of the restricting member 53, so that the restricting member 53 is inhibited from slipping out of the second guide hole 60 by the retaining ring 62. Moreover, the fitted position of the retaining ring 62 is determined to inhibit the further movement of the restricting member 53 toward the free rocker arm 26 1 from a state in which it is in abutment against the free rocker arm 26 1 in a location corresponding to a plane between the free rocker arm 26 1 and the second driving rocker arm 25 1 . In the connection switchover mechanism 50, a swing pin 63 is embedded in the side surface of each of the first and second driving rocker arms 24 1 and 25 1 which is facing the free rocker arm 26 1 to engage the free rocker arm 26 1 while permitting the relatively swinging movement of the driving rocker arms 24 1 and 25 1 with the free rocker arm 26 1 . Referring again to Figs. 1 and 2, a spark plug 64 is disposed at a central portion of a ceiling surface of the combustion chamber 5. A plug pipe 65 is disposed in the cylinder head 2 and serves as a cylindrical plug-insertion portion for insertion of the spark plug 64. The pair of exhaust valve-side rocker arms 29 1 and 30 1 constituting the exhaust valve driving means 18 1 are disposed for sliding contact with the exhaust valve cams 23, 23 of the cam shaft 16 on opposite sides of the intake rocker arms 24 1 , 25 1 and 26 1 which are disposed adjacent one another to constitute the intake valve driving means 17 1 . This ensures that a relatively wide space is provided between the exhaust valve rocker arms 29 1 and 30 1 and the exhaust valves V E1 and V E2 can be disposed at a relatively wide distance apart from each other. Therefore, the plug pipe 65 is positioned in the cylinder head 2 in such a manner that the axis thereof is disposed between the exhaust valves V E1 and V E2 , i.e., located between the exhaust valves V E1 and V E2 as well as between the exhaust valve-side rocker arms 29 1 and 30 1 . The plug pipe 65 is inclined so that the upper portion thereof is spaced from the cam shaft 16. The spark plug 64 inserted into the plug pipe 65 is threadedly mounted in the cylinder head 2 at the central portion of the ceiling surface of the combustion chamber 5. The operation of the first embodiment will be described. When the engine is in a lower speed operation, the hydraulic pressure in the hydraulic pressure chamber 56 in the connection switchover mechanism 50 is released, and the pistons 51 and 52 and the restricting member 53 are in their disconnected states in which they have been moved to the maximum extent toward the hydraulic pressure chamber 56 by the spring force of the return spring 54. In such condition, the abutment surfaces of the first and second connecting pistons 51 and 52 are in positions between the first driving rocker arm 24 1 and the free rocker arm 26 1 , while the abutment surfaces of the second connecting piston 52 and the restricting member 53 are in positions between the free rocker arm 26 1 and the second driving rocker arm 25 1 . Therefore, the rocker arms 24 1 , 25 1 and 26 1 are in a disconnected state to allow relative angular displacement. In such disconnected condition, the rotation of the cam shaft 16 causes the first and second driving rocker arms 24 1 and 25 1 to be swung in response to the sliding contact with the lower speed cams 22, 22, so that the intake valves V I1 and V I2 are opened and closed at a timing and a lift amount corresponding to the shape of the lower speed cams 22, 22. During this time, the free rocker arm 26 1 is swung in response to the sliding contact with the higher speed cam 21, but the swinging movement thereof exerts no influence on the first and second driving rocker arms 24 1 and 25 1 . In addition, the exhaust valves V E1 and V E2 are opened and closed at a timing and a lift amount corresponding to the shape of the exhaust valve cams 23, 23. During a higher speed operation of the engine, a higher hydraulic pressure is supplied to the hydraulic pressure chamber 56. This causes the first and second connecting pistons 51 and 52 as well as the restricting member 53 in the connection switchover mechanism 50 of the intake valve driving means 17 1 to be moved toward the connecting positions against the spring force of the return spring 54, so that the first connecting piston 51 is fitted into the guide hole 59, while at the same time, the second connecting piston 52 is fitted into the second guide hole 60, thereby connecting the rocker arms 24 1 , 25 1 and 26 1 . At this time, the amount of swinging movement of the free rocker arm 26 1 in sliding contact with the higher speed cam 21 is largest and therefore, the first and second driving rocker arms 24 1 and 25 1 are swung with the free rocker am 26 1 , and the intake valves V I1 and V I2 are opened and closed at a timing and a lift amount corresponding to the shape of the higher speed cam 21. During this higher speed operation, the exhaust valve-side rocker arms 29 1 and 30 1 still open and close the exhaust valves V E1 and V E2 at a timing and a lift amount corresponding to the shape of the exhaust valve cams 23, 23, as during the lower speed operation. It is possible to provide an improvement in output from the engine with a valve operating characteristic adapted for the operational condition of the engine by changing the opening and closing mode of the intake valves V I1 and V I2 between the higher and lower speed operations in this manner. In such an internal combustion engine, in the position corresponding to the cam shaft 16, the rocker arms 24 1 , 25 1 and 26 1 constituting the intake valve driving means 17 1 are disposed adjacent one another and can be arranged together in a compact manner. It follows that the connection switchover mechanism 50 is also arranged in a compact manner. This enables not only an easy improvement in dimensional accuracy of the components of the connection switchover mechanism 50 in order to provide a smooth operation of the connection switchover mechanism 50, but also contributes to a reduction in the weight of the rocker arms 24 1 , 25 1 and 26 1 . Moreover, the sliding contact positions of the first and second driving rocker arms 24 1 and 25 1 with the lower speed cams 22, 22 and the operatively connected positions of these rocker arms to the intake valves V I1 and V I2 can be established within a plane substantially perpendicular to the axis of the rocker arm shaft 27, thereby avoiding the action of an uneven or eccentric load on the first and second rocker arms 24 1 and 25 1 . The plug pipe 65 is disposed in the cylinder head 2 with its axis located between the exhaust valves V E1 and V E2 thereby effectively utilizing the space produced by positioning the exhaust valve-side rocker arms 29 1 and 30 1 on opposite sides of the intake valve driving means 17 1 . Therefore, it is possible to make the entire arrangement more compact. Figs. 5 and 6 illustrate a second embodiment of the present invention, wherein parts that are similar or identical to those in the previously described first embodiment are identified by the same reference characters. A cam shaft 16 is rotatably carried by the cylinder head 2 and a cam holder 71 coupled to the cylinder head 2. Integrally provided on the cam shaft 16 in an arrangement similar to that shown in Fig. 3 illustrating the first embodiment are a higher speed cam 21, lower speed cams 22, 22 on opposite sides of the higher speed cam 21, and exhaust valve-side cams 23, 23 on opposite sides of the lower speed cams 22, 22. A rocker arm shaft 70 parallel to the cam shaft 16 is fixedly supported in the cylinder head 2 below the cam shaft 16. An intake valve driving means 17 2 is provided between the intake valves V I1 and V I2 and the cam shaft 16 for converting the rotational motion of the cam shaft 16 to the opening and closing motions of the intake valves V I1 and V I2 , and an exhaust valve driving means 18 2 is provided between the exhaust valves V E1 and V E2 and the cam shaft 16 for converting the rotational motion of the cam shaft 16 to the opening and closing motions of the exhaust valves V E1 and V E2 . The intake valve driving means 17 2 comprises a first driving rocker arm 24 2 operatively connected to the first intake valve V I1 , a second driving rocker arm 25 2 operatively connected to the second intake valve V I2 , and a free rocker arm 26 2 disposed between the driving rocker arms 24 2 and 25 2 . The rocker arms 24 2 , 25 2 and 26 2 are swingably carried at their base ends on the rocker arm shaft 70. The exhaust valve driving means 18 2 comprises exhaust valve-side rocker arms 29 2 and 30 2 swingably carried at their base ends on the rocker arm shaft 70 and operatively connected separately to the exhaust valves V E1 and V E2 . In the intake valve driving means 17 2 , a cam slipper 72 is provided at an intermediate and upper portion of the first driving rocker arm 24 2 to come into sliding contact with the lower speed cam 22 (see Fig. 3); a cam slipper 73 is provided at an intermediate and upper portion of the second driving rocker arm 25 2 to come into sliding contact with the lower speed cam 22 (see Fig. 3), and a cam slipper 74 is provided on the free rocker arm 26 2 to come into sliding contact with the higher speed cam 21 (see Fig. 3). In addition, cam slippers 75 and 76 are provided on intermediate and upper portions of the exhaust valve-side rocker arms 29 2 and 30 2 to come into sliding contact with the exhaust valve cams 23, 23 (see Fig. 3). A lost motion mechanism 38' having the basically same construction as the lost motion mechanism 38 in the first embodiment is provided in the cylinder head 2 to resiliently bias the free rocker arm 26 2 in the intake valve driving means 17 2 toward the cam shaft 16. Further, a connection switchover mechanism (not shown) having the basically same construction as the connection switchover mechanism 50 in the first embodiment is provided in the intake valve driving mechanism 17 2 to switchover the connection and disconnection of the rocker arms 24 2 , 25 2 and 26 2 in accordance with the operational condition of the engine. A lubricating oil supply passage 77 is provided in the rocker arm shaft 70 parallel to the hydraulic pressure supply passage 58, and injecting nozzles 78 are provided at base portions of the rocker arms 24 2 , 25 2 , 26 2 , 29 2 and 30 2 respectively to communicate with the lubricating oil supply passage 77 in accordance with the swing positions of the rocker arms 24 2 , 25 2 , 26 2 , 29 2 and 30 2 in order to eject a lubricating oil from the lubricating oil supply passage 77 toward their sliding contact portions with the cam shaft 16. It should be noted that the pair of rocker arms 29 2 and 30 2 constituting the exhaust valve driving means 18 2 are disposed on opposite sides of the intake valve driving means 17 2 in their positions opposed to the cam shaft 16. Therefore, it is possible to insure a relatively wide space between the exhaust valve-side rocker arms 29 2 and 30 2 as in the previous first embodiment and it is also possible to dispose the exhaust valves V E1 and V E2 at a relatively wide distance spaced from each other, so that the plug pipe 65 may be disposed in the cylinder head 2 between the exhaust valves V E1 and V E2 as well as between the exhaust valve-side rocker arms 29 2 and 30 2 . Thus, with such second embodiment, it is possible to ensure a space for the plug pipe 65 with a compact entire arrangement, notwithstanding the provision of the connection switchover mechanism in the intake valve driving means 17 2 . Figs. 7 to 9A illustrate a third embodiment of the present invention, wherein parts similar or identical to those in the previous embodiments are identified by the same reference characters. Referring first to Figs. 7 and 8, a cam shaft 16 is rotatably carried by a cylinder head 2 and a holder 20 coupled to the cylinder head 2. An intake valve driving means 17 3 is provided between the cam shaft 16 and the intake valves V I1 and V I2 for converting the rotational motion of the cam shaft 16 into the opening and closing motions of the intake valves V I1 and V I2 , and an exhaust valve driving means 18 3 is provided between the exhaust valves V E1 and V E2 and the cam shaft 16 for converting the rotational motion of the cam shaft 16 into the opening and closing motions of the exhaust valves V E1 and V E2 . The intake valve driving means 17 3 comprises a first driving rocker arm 24 3 operatively connected to the first intake valve V I1 , and a second driving rocker arm 25 3 operatively connected to the second intake valve V I2 and disposed adjacent the first driving rocker arm 24 3 . The rocker arms 24 3 and 25 3 are swingably carried at their intermediate portions by the rocker shaft 27. The exhaust valve driving means 18 3 comprises exhaust valve rocker arms 29 3 and 30 3 which are operatively connected separately to the exhaust valves V E1 and V E2 and swingably carried at their intermediate portions by the rocker arm shaft 28. A connection switchover mechanism 50' is provided in the intake valve driving means 17 3 for switching-over the connection and disconnection of the rocker arms 24 3 and 25 3 and comprises a connection piston 83 movable in response to a hydraulic pressure from the hydraulic pressure supply passage 58 provided in the rocker arm shaft 27 between a position in which the first and second driving rocker arms 24 3 and 25 3 are connected and a position in which such connection is released, a restricting member 84 slidably received in the second driving rocker arm 25 3 and abutting against the connecting piston 83, and a return spring 85 interposed between the restricting member 84 and the second driving rocker arm 25 3 to bias the connecting piston 83 and the restricting member 84 toward a disconnecting side. In the intake valve driving means 17 3 , a roller 81 is pinned at one end of the first driving rocker arm 24 3 to come into rolling contact with the cam 79 integrally provided on the cam shaft 16, and a slipper 82 is provided at one end of the second driving rocker arm 25 3 to come into sliding contact with a raised portion 80 integrally provided on the cam shaft 16 adjacent the cam 79. The raised portion 80 is basically formed to have an outer surface that is circular about the axis of the cam shaft 16, but also to have a shape such that the second intake valve V I2 is slightly operated in an opening direction while being in a substantially closed state, when the first intake valve V I1 is opened by the first driving rocker arm 24 3 in a condition in which the second driving rocker arm 25 3 is not connected with the first driving rocker arm 24 3 . Moreover, the width of the raised portion 80 in a direction along the axis of the cam shaft 16 is relatively small, and the width of the slipper 82 provided on the second driving rocker arm 25 3 is also small in correspondence to the raised portion 80 because very little force is transmitted therebetween. Rollers 86 and 87 are pinned at one end of each of the exhaust valve-side rocker arms 29 3 and 30 3 in the exhaust valve driving means 18 3 to come into rolling contact with the exhaust valve-side cams 23, 23 provided on the cam shaft 16 on opposite sides of the cam 79 and the raised portion 80 provided on the cam shaft 16 adjacent each other, respectively. Thus, the pair of the exhaust valve-side rocker arms 29 3 and 30 3 constituting the exhaust valve driving means 18 3 are disposed on opposite sides of the intake valve driving means 17 3 in their position opposed to the cam shaft 16, and therefore, it is possible to ensure a relatively wide space between the exhaust valve rocker arms 29 3 and 30 3 . It is also possible to dispose the exhaust valves V E1 and V E2 at a relatively wide distance spaced apart from each other, so that the plug pipe 65 may be disposed in the cylinder head 2 between the exhaust valves V E1 and V E2 as well as between the exhaust valve-side rocker arms 29 3 and 30 3 . Referring also to the Fig. 9, an intake passage 97 1 provided in the cylinder head 2 in communication with the first intake valve opening 6 1 and an intake passage 97 2 provided in the cylinder head 2 in communication with the second intake valve opening 6 2 are commonly connected to an intake port 8 provided in one side surface of the cylinder head 2 for each cylinder 3. One of the intake passages, such as passage 97 1 , is formed in an inwardly expanded and curved fashion to extend along the inner surface of the combustion chamber 5 just in front of the first intake valve opening 6 1 , in order to provide a swirl suction of the gas from the first intake valve opening 6 1 into the combustion chamber 5, when the second intake valve V I2 has become substantially inoperative. A recess 2a is provided on a lower surface of the cylinder head 2 to form a ceiling surface of the combustion chamber 5, and a squish area 98 is provided between an opened edge of the recess 2a and a top surface of the piston 4 at the top dead center point. The opened edge of the recess 2a is shaped such that the following edge portions are connected together: a first peripheral edge 2a 1 corresponding to an inner periphery of the cylinder extending from the first intake valve opening 6 1 to the first exhaust valve opening 7 1 in a direction 99 of swirl suction from the first intake valve opening 6 1 into the combustion chamber 5; a second peripheral edge portion 2a 2 corresponding to a peripheral edge of the circular depression 4a in the piston 4 between the first and second exhaust valve openings 7 1 and 7 2 ; a third peripheral edge portion 2a 3 irregularly connected between an inner periphery of the cylinder and the peripheral edge of the depression 4a between the second exhaust valve opening 7 2 and the second intake valve opening 6 2 ; and a fourth peripheral edge portion 2a 4 corresponding to the peripheral hedge of the depression 4a between the second and first intake valve opening 6 2 and 6 1 . Therefore, the squish area 98 has a shape as shown by the cross-hatched region in Fig. 9A and is not formed in a section extending from the first intake valve opening 6 1 to the first exhaust valve opening 7 1 in the direction 99 of swirl suction. In those portions of the squish area 98 which correspond to between the intake valve openings 6 1 and 6 2 and between the exhaust valve openings 7 1 and 7 2 , the inner periphery of the squish area 98 is opposed to the peripheral edge of the recess 4a at the upper and central portion in the piston 4. With such third embodiment, in a higher speed operation condition of the engine, the first and second driving rocker arms 24 3 and 25 3 can be interconnected, so that the intake valves V I1 and V I2 can be opened and closed at a timing and a lift amount suitable for higher speed operation by the shape of the cam 79. On the other hand, in a lower speed operational condition of the engine, the connection of the first and second driving rocker arms 24 3 and 25 3 can be released, so that the first intake valve V I1 can be opened and closed at the timing and lift amount corresponding to the shape of the cam 79 by the first driving rocker arm 24 3 in slide contact with the cam 79, while the second driving rocker arm 25 3 in slide contact with the raised portion 80 can be brought into a substantially inoperative state to put the second intake valve V I2 substantially out of operation. However, the second intake valve V I2 is not completely inoperative and can be slightly operated in the opening direction when the first intake valve V I1 is opened. This makes it possible to prevent sticking of the second intake valve V I2 to the valve seat which may be otherwise produced when a completely closed state is maintained. In the lower speed operational condition of the engine in which the second intake valve V I2 is substantially inoperative and only the first intake valve V I1 is opened and closed, a fuel-air mixture from the intake port 8 is supplied via the intake passage 97 1 and the first intake valve opening 6 1 into the combustion chamber 5, so that a swirl is produced in the combustion chamber 5. Moreover, the intake passage 97 1 is formed in a curved fashion to extend tangentially along the inner surface of the combustion chamber 5 just in front of the first intake valve opening 6 11 , so that the fuel-air mixture is drawn into the combustion chamber 5 while being whirled, enabling a swirl to be produced effectively. The fuel-air mixture introduced into the combustion chamber 5 through the first intake valve opening 6 1 flows within the combustion chamber 5 in the direction of swirl suction, but because the squish area 98 is not formed in the section from the first intake valve opening 6 1 to the first exhaust valve opening 7 1 in the direction 99 of swirl suction, a squish flow can be prevented from acting on the whirled flow just introduced into the combustion chamber 5 through the first intake valve opening 6 1 in a direction that otherwise would disturb the whirling of such flow, thereby effectively forming a swirl in the combustion chamber 5. Further, the inner periphery of the squish area 98 is formed in opposition to the peripheral edge of the depression 4a at the central portion of the upper surface of the piston 4 between the intake valve openings 6 1 and 6 2 as well as between the exhaust valve openings 7 1 and 7 2 and therefore, a whirled flow is easily produced along the inner surface of the combustion chamber 5, which makes it possible to form a more effective swirl within the combustion chamber 5. It is possible to provide an improvement in burning property by forming a powerful swirl within the combustion chamber 5 in this manner. It should be noted that the first driving rocker arm 24 3 which is in operation in a lower speed region in which the component, in the valve operating system, of the friction loss in the entire engine constitutes a larger proportion is in rolling contact with the cam 79 through the roller 81, and this can contribute to a reduction in friction loss due to the valve operating system in the lower speed region and thus a reduction in friction loss in the entire engine. Moreover, because the exhaust valve-side rocker arms 29 3 and 30 3 constituting the exhaust valve driving means 18 3 is also in rolling contact with the exhaust valve cams 23, 23 through the rollers 86 and 87, it is possible to further reduce the friction loss in the lower speed region. Further, the second driving rocker arm 25 3 is in slide contact with the raised portion 80 through the slipper 83 and this ensures that the width of the slipper 83 can be smaller than that of the roller 81. Moreover, because the intake valve driving means 17 3 is comprised of the pair of driving rocker arms 24 3 and 25 3 , such intake valve driving means 17 3 can be constructed more compactly along the axis of the cam shaft 16, as compared with the intake valve driving means constructed of three rocker arms as in the previously described first and second embodiments. Moreover, as in the previous embodiments, the entire construction can be made compact, notwithstanding the provision of the connection switchover mechanism 50' in the intake valve driving means 17 3 . In the above third embodiment, the intake passage 97 1 has been formed in the curved fashion just in front of the first intake valve opening 6 1 , but it will be understood that the intake passage 97 1 may be disposed with the position of the intake port 8 being displaced toward the second intake valve opening 6 2 , as compared with Fig. 9, so as to extend substantially along the inner surface of the combustion chamber 5 over the entire length of the passage from the connection with the intake port 8 to the first intake valve opening 6 1 . Fig. 11 and 12 illustrate a fourth embodiment of the present invention, wherein parts that are similar or identical to those in the previous embodiments are identified by the same reference characters. An intake valve driving means 17 4 is provided between the cam shaft 16 and the intake valves V I1 and V I2 for converting the rotational motion of the cam shaft 16 into the opening and closing motions of the intake valves V I1 and V I2 , and an exhaust valve driving means 18 4 is provided between the exhaust valves V E1 and V E2 and the cam shaft 16 for converting the rotational motion of the cam shaft 16 into the opening and closing motions of the exhaust valves V E1 and V E2 . The intake valve driving means 17 4 comprises a first driving rocker arm 24 4 operatively connected to the first intake valve V I1 , a second driving rocker arm 25 4 operatively connected to the second intake valve V I2 , and a free rocker arm 26 4 disposed between the driving rocker arms 24 4 and 25 4 and capable of becoming free from the intake valves V I1 and V I2 . The rocker arms 24 4 , 25 4 and 26 4 are swingably carried at their intermediate portions by the rocker arm shaft 27. The exhaust valve driving means 18 4 comprises exhaust valve-side rocker arms 29 4 and 30 4 which are operatively connected separately to the exhaust valves V E1 and V E2 and swingably carried at their intermediate portions by the rocker arm shaft 28. A connection switchover mechanism 50 is provided in the intake valve driving means 17 4 and is capable of switching-over the connection and disconnection of the rocker arms 24 4 , 25 4 and 26 4 . Integrally provided on the cam shaft 16 are a higher speed cam 21 formed so that it is operative primarily during a higher speed operation of the engine, a lower speed cam 22 as a second cam formed adjacent the higher speed cam 21, so that it is operative primarily during a lower speed operation of the engine, and a raised portion 80 adjacent the higher speed cam 21 on the opposite side from the lower speed cam 22. Further, in the intake valve driving means 17 4 , a roller 89 is pinned at one end of the first driving rocker arm 24 4 to come into rolling contact with the lower speed cam 22; a slipper 90 is provided at one end of the free rocker arm 26 4 to come into sliding contact with the higher speed cam 21, and a slipper 91 is provided at one end of the second driving rocker arm 25 4 to come into sliding contact with the raised portion 80. Moreover, the width of the raised portion 80 in a direction along the axis of the cam shaft 16 is relatively small, and the width of the slipper 91 provided on the second rocker arm 25 4 is also small in correspondence to the raised portion 80. Rollers 86 and 87 are pinned at one end of each of the exhaust valve-side rocker arms 29 4 and 30 4 in the exhaust valve driving means 18 4 to come into rolling contact with the exhaust valve cams 23, 23 provided on the cam shaft 16 on opposite sides of the lower speed cam 22 and the raised portion 80, respectively. Thus, the pair of exhaust valve-side rocker arms 29 4 and 30 4 constituting the exhaust valve driving means 18 4 are disposed on opposite sides of the intake valve driving means 17 4 in positions opposed to the cam shaft 16 and therefore, it is possible to insure a relatively wide space between the exhaust valve rocker arms 29 4 and 30 4 . In addition, the exhaust valves V E1 and V EZ can be disposed at a relatively large distance apart from each other, so that the plug pipe 65 may be positioned in the cylinder head 2 between the exhaust valves V E1 and V E2 as well as between the exhaust valve-side rocker arms 29 4 and 30 4 . With such fourth embodiment, in a higher speed operational condition of the engine, the first and second driving rocker arms 24 4 and 25 4 and the free rocker arm 26 4 are interconnected, so that the intake valves V I1 and V I2 can be opened and closed at a timing and a lift amount corresponding to the shape of the higher speed cam 21. In a lower speed operational condition of the engine, the connection of the first driving rocker arm 24 4 and the free rocker arm 26 4 as well as the connection of the free rocker arm 26 4 and the second driving rocker arm 25 4 can be released, so that the first intake valve V I1 can be opened and closed at a timing and a lift amount corresponding to the shape of the lower speed cam 22 by the first driving rocker arm 24 4 which is in rolling contact with the lower speed cam 22, while the second driving rocker arm 25 4 in sliding contact with the raised portion 80 can be brought into a substantially inoperative state to put the second intake valve V I2 substantially out of operation. The first driving rocker arm 24 4 operative in a lower speed region is in rolling contact with the lower speed cam 22 through the roller 89, which can contribute to a reduction in friction loss in the valve-operating system in the lower speed region and thus a reduction in friction loss in the entire engine. In addition, because the exhaust valve-side rocker arms 29 4 and 30 4 are also in rolling contact with the exhaust valve cam 23, 23 through the rollers 86 and 87, it is possible to provide a further reduction in friction loss in the lower speed region. Further, the second driving rocker arm 25 4 is in sliding contact with the raised portion 80 through the slipper 91 and therefore, the width of the slipper 91 can be smaller than that of the roller 89. This ensures that the intake valve driving means 17 4 can be constructed more compactly along the axis of the cam shaft 16, as compared with those in the previous first and second embodiments. Moreover, the entire arrangement can be made compact as in the previous embodiments, notwithstanding the provision of the connection switchover mechanism 50 in the intake valve driving means 17 4 . In the foregoing embodiments, the connection switchover mechanism has been described as being provided in the rocker arms constituting the intake valve driving means for switching-over the connection and disconnection of all the rocker arms, but it will be understood that the connection switchover mechanism may be constructed to switch-over the connection and disconnection of only a pair of adjacent rocker arms. Thus, in at least preferred embodiments there is provided an SOHC type internal combustion engine including a pair of intake valves and a pair of exhaust valves, wherein the intake valve driving means can be constructed compactly, whereby the opening and closing mode of the intake valves can be changed in accordance with the operational condition of the engine; and there is ensured a space for disposition of the plug insertion cylindrical portion, while providing a compact entire valve-operating system; and there is provided a reduction in friction loss in the lower speed region in which the component, in the valve-operating system, of the friction loss in the entire engine constitutes a larger proportion and thus a reduction in friction loss in the entire engine, and to provide a compact construction of the intake valve driving means.

Claims: A single overhead camshaft type multi-cylinder internal combustion engine having: a plurality of cylinders (3); a single camshaft (16) rotatably mounted in a cylinder head (2) above combustion chambers (5) for the cylinders, said single camshaft (16) having cams (21, 22, 23) provided thereon; a pair of intake valves (V I1 , V I2 ) for each cylinder (3) mounted in said cylinder head (2) on one side of said camshaft (16); a plurality of intake valve-side driving rocker arms (24 1 , 25 1 , 26 1 ; 24 2 , 25 2 , 26 2 ; 24 3 , 25 3 ; 24 4 , 25 4 , 26 4 ) for operatively connecting said camshaft (16) to said pair of intake valves (V I1 , V I2 ) ; a pair of exhaust valves (V E1 , V E2 ) for each cylinder (3) mounted on the cylinder head (2) on the other side of the camshaft (16); a pair of exhaust valve-side driving rocker arms (29 1 , 30 1 ; 29 2 , 30 2 ; 29 3 , 30 3 ; 29 4 , 30 4 ) for operatively connecting said camshaft (16) to said pair of exhaust valves (V E1 , V E2 ); a structure for rotatably supporting said camshaft (16) on the cylinder head (2); a spark plug mounting hole in a central portion of a ceiling of each combustion chamber (5); and a plug pipe (65) which extends to the spark plug mounting hole and is provided in an inclined fashion with its upper portion spaced from the camshaft (16), said plug pipe (65) being disposed substantially between the camshaft (16) and the axes of the pair of exhaust valves (V E1 , V E2 ) ; wherein said plurality of intake valve-side driving rocker arms (24 1 , 25 1 , 26 1 ; 24 2 , 25 2 , 26 2 ; 24 3 , 25 3 ; 24 4 , 25 4 , 26 4 ) are positioned between the pair of exhaust valve-side driving rocker arms (29 1 , 30 1 ; 29 2 , 30 2 ; 29 3 , 30 3 ; 29 4 , 30 4 ); characterised in that said supporting structure includes adjacent two holders (20; 71) coupled to the cylinder head (2), said adjacent two holders (20; 71) are each located between adjacent two cylinders (3) and form adjacent supports for the camshaft (16), and said plurality of intake valve-side driving rocker arms (24 1 , 25 1 , 26 1 ; 24 2 , 25 2 , 26 2 ; 24 3 , 25 3 ; 24 4 , 25 4 , 26 4 ) and said pair of exhaust valve-side driving rocker arms (29 1 , 30 1 ; 29 2 , 30 2 ; 29 3 , 30 3 ; 29 4 , 30 4 ) are all disposed between said adjacent two holders (20; 71) at a location substantially above the associated cylinder (3); said cams (21, 22, 23) for operating the intake and exhaust valve-side driving rocker arms (24 1 , 25 1 , 26 1 ; 24 2 , 25 2 , 26 2 ; 24 3 , 25 3 ; 24 4 , 25 4 , 26 4 and 29 1 , 30 1 ; 29 2 , 30 2 ; 29 3 , 30 3 ; 29 4 , 30 4 ) for each cylinder are all disposed between the adjacent two holders (20; 71) with the cams (23) for the exhaust valve-side driving rocker arms being located at opposite outermost positions; and a mechanism (50; 50') is provided for switching over connection and disconnection between adjacent ones of the intake valve-side driving rocker arms (24 1 , 25 1 , 26 1 ; 24 2 , 25 2 , 26 2 ; 24 3 , 25 3 ; 24 4 , 25 4 , 26 4 ). A single overhead camshaft type multi-cylinder internal combustion engine according to claim 1, characterised in that a rocker arm shaft (28) for carrying the exhaust valve-side driving rocker arms (29 1 , 30 1 ; 29 3 , 30 3 ; 29 4 , 30 4 ) is disposed in the cylinder head (2) so as to lie substantially parallel to the camshaft (16) at a location closer to the pair of exhaust valves (V E1 , V E2 ), said plug pipe (65) being located between the rocker arm shaft (28) and the axes of the exhaust valves (V E1 , V E2 ). A single overhead camshaft type multi-cylinder internal combustion engine according to claim 1 or 2, characterised in that said plurality of intake valve-side driving rocker arms include a free rocker arm (26 1 ; 26 2 ; 26 4 ) which is operable during certain engine operation, and a lost motion mechanism (38; 38') is provided in operative association with said free rocker arm on a member (37) which is carried over the adjacent two holders (20; 71).

Inventors: AOKI TAKATOSHI, IWATA TAKESHI, SUGIMOTO CHIHAYA, AOKI, TAKATOSHI, IWATA, TAKESHI, SUGIMOTO, CHIHAYA, AOKI, TAKATOSHI, C/O KABUSHIKI KAISHA HONDA, IWATA, TAKESHI, C/O KABUSHIKI KAISHA HONDA, SUGIMOTO, CHIHAYA, C/O KABUSHIKI KAISHA HONDA
Applicants: HONDA MOTOR CO LTD, HONDA GIKEN KOGYO KABUSHIKI KAISHA
Application year: 1991
Main classification: F01L1
IPC codes: F01L1, F02B1, F02F1