Abstract:
An improved variable valve lift mechanism that minimizes the number of components and also which permits a more greater latitude of valve lift adjustment including the possibility of no valve lift under some running conditions. This is done without interference with other components of the engine and thus permits a compact engine assembly.

Description:
BACKGROUND OF THE INVENTION  
         [0001]    This invention relates to an internal combustion engine and more particularly to a variable valve drive system for such engines.  
           [0002]    In order to improve the performance of an engine through a wide range of engine running conditions (speed and load), it has been proposed to utilize a system wherein the degree of lift or opening of one or more valves of the engine can be controlled. A number of different types of variable valve lift mechanisms have been employed but, for the most part, the range of valve lift adjustment that is possible is quite limited. This is basically because of the geometry of the systems, which have been proposed, and the operational methods, which they have employed.  
           [0003]    For example, in one form of arrangement, a rocker arm is interposed between the cam lobe and the valve or valve actuating member. This rocker arm has its pivotal axis adjustable so as to in affect change the lever ratio and thus, alter the valve lift. An example of this type of valve lift control is shown in published Japanese Application Hei 7-91217 (U.S. Equivalent 5,501,186).  
           [0004]    As may be seen in this prior art construction, the rocker arm interposed between the cam lobe and the valve tappet has its pivot axis shifted in a transverse direction so as to change the effective lift of the valve. This is because the lever arm ratio is in effect changed. However, there are several disadvantages of this type of construction. First, the shifting of the pivot axis also causes the point of contact between the rocker arm and valve actuator to shift. Thus, the problem of wear in this area is aggravated and uniform wear is also made more difficult. Furthermore, since the shifting must be generally confined to the area immediately adjacent the axis of the actuated valve, the amount of variation in lift possible is restricted.  
           [0005]    Another embodiment is shown in that application wherein different pivot points are utilized by having different pivot arrangements for the valve actuating rocker arm. However, this further limits the degree of adjustment and also causes the problem of having only step wise adjustment rather than adjustment over a range of positions.  
           [0006]    Another type of system for adjusting the valve lift of an engine during running is shown in published Japanese Application Hei 6-307219. In this type of arrangement, the lever ratio of the rocker arm is in effect changed by providing a rolling follower that is interposed between the cam lobe and an upper surface of the rocker arm. This roller follower is shifted transversely to change the effective lever ratio. Again, however, this severely limits the degree of adjustment that can be made and also further complicates the overall structure. Furthermore, this system does not permit zero or not nearly zero lift for the valve actuation. In other words it is not possible to disable the valve operation.  
           [0007]    It is, therefore, a principal object to this invention to provide an improved valve actuating system for an internal combustion engine wherein large degrees of variation in valve lift is possible.  
           [0008]    It is a further object to this invention to provide a relatively simple and yet continuously variable valve lift control mechanism for the valves of an internal combustion engine.  
           [0009]    It is a yet further object to this invention to provide an arrangement for controlling the valve lift an internal combustion engine that is compact in nature, while at the same time, maintains a large effective variation in valve lift.  
         SUMMARY OF INVENTION  
         [0010]    This invention is adapted to be embodied in a variable valve operating system for the valves of an internal combustion engine and specifically one, which is capable of varying the degree of opening in response to the rotation of the cams to a large extent. The valve operating device comprises a rocker arm having a follower portion engaged by the cam. A pivot axis about which the rocker arm pivots in response to the action of the cam on the follower portion is provided. A valve operating portion is operatively engaged with the associated valve for effecting lift of the valve in response to pivotal movement of the rocker arm. A variable lift actuator is effective to change the distance between the point on the valve operating portion that operatively engages the valve without changing the point that is operatively engaged and the distance between that point and the pivot axis of the rocker arm so as to change the degree of lift between substantially no lift to substantially maximum amount of lift. 
       
    
    
     BRIEF DESCRIPTION OF DRAWINGS  
       [0011]    [0011]FIG. 1 is a conventional view taken through a portion of the cylinder head of an internal combustion engine constructed in accordance with an embodiment of the invention.  
         [0012]    [0012]FIG. 2 is an enlarged cross sectional view taken along a plane perpendicular to the plane of FIG. 1.  
         [0013]    [0013]FIG. 3 is a view looking in the same direction as FIG. 2 but only showing the valve operating mechanism.  
         [0014]    [0014]FIG. 4 is a cross sectional view taken along the line  4 - 4  of FIG. 3.  
         [0015]    [0015]FIG. 5 is a cross sectional view taken along the line  5 - 5  of FIG. 3.  
         [0016]    [0016]FIGS. 6, 7 and  8  are views, in part similar to FIG. 3, and show, respectively, maximum valve lift, middle variation in valve lift and small or no valve lift. 
     
    
     DETAILED DESCRIPTION  
       [0017]    Referring now in detail to the drawings and initially primarily to FIG. 1, a portion of an overhead valve type internal combustion engine is illustrated. The engine is identified generally by the reference numeral  11 . Although the invention is described in conjunction with overhead valve engines, it should be apparent that the invention can be utilized also with types of engines not having overhead valves.  
         [0018]    Since the invention deals primarily with the valve operating mechanism and particularly the individual variable valve lift mechanisms, indicated generally by the reference numerals  12 , only the cylinder head portion of the engine  11  is depicted. The cylinder head is identified generally by the reference numeral  13 .  
         [0019]    The cylinder head  13  includes a main body portion  14  that have upstanding walls  15  that form one-half of the bearing surfaces for a camshaft, indicated by the reference numeral  16 . In the illustrated embodiment, the camshaft  16  can be either or both of an intake and/or an exhaust camshaft of the engine  11 . The camshaft  16  has bearing portions that are journalled between the upstanding walls  15  of the cylinder head and by bearing caps  17  that are detachably affixed thereto.  
         [0020]    In the illustrated embodiment, each of the variable valve lift mechanisms  12  operate a pair of valves for the same cylinder of the enginel  1 . The valves of the pairs each being indicated by the reference numerals  18 .  
         [0021]    As is typical with internal combustion engine practice, the valves  18  are poppet type valves, which are urged toward their closed positions by coil compression springs  19 . These coil compression springs  19  encircle the stems  21  (see FIG. 2) of the valves  18 . The springs  19  are loaded between engagement with suitable machined surfaces of the cylinder head and keeper retainer assemblies  22  fixed to the valve stems  21  in a well known manner.  
         [0022]    The stems  21  carry adjusting shims  23 , which form the actuating members for the valves  18 . Although directly operated valves are shown, the invention can be also utilized in conjunction with arrangement wherein thimble tappets are interposed between the valves  18  and the cam lobes of the associated camshaft  16 , to be described.  
         [0023]    The camshaft  16  is rotatably driven by a camshaft drive mechanism, which may be of any known type. This may include, by way of example, a timing chain  24  that is driven either directly or through a transmission mechanism at one-half crankshaft speed from the crankshaft of the associated engine  11 . This timing chain  24  is engaged with a variable valve timing mechanism  25  which may be of any known type and which is capable of shifting the timing phase of the camshaft  16  relative to the engine crankshaft.  
         [0024]    Referring now primarily to FIG. 2, the valve actuating mechanism including the variable valve lift mechanisms  12  will be described in detail. Each variable valve lift mechanisms  12  includes a cylindrical member  26 , which has a slotted opening  27  for a purpose to be described. This cylindrical member  26  has an inner diameter that is larger than the diameter of the cam lobes  28  formed on the camshaft  16 . The rotational axis of the camshaft  16  is indicated by the line C in FIG. 2.  
         [0025]    Adjacent the slotted opening  27  and on one side thereof, the cylindrical member  26  has a lug like projection  29  that receives a pivot pin  31 . The pivot pin  31 , in turn, journals a valve actuating rocker arm assembly  30 . The rocker arm assembly  30  is comprised of paired rocker arms  32  that are suitably connected to each other. These rocker arms  32  extend through the slotted openings  27  and carry roller followers  33  that are engaged with the cam lobes  28  so as to effect pivotal movement of the rocker arm  32  about the pivot axis formed by the pivot pin  31 .  
         [0026]    Each of these pair of rocker arms  32  also are provided with a valve actuating or contacting section  34  that has an arcuate shape with its center lying concentric with the rotational axis C of the camshaft  16 .  
         [0027]    Referring back to FIG. 1, it will be seen that each of the cylindrical member  26  of the variable valve lift mechanisms  12  is provided with a lug  35  is diametrically opposed to the slotted opening  27 . A coupling rod  36  extends through openings in the lugs  35  of each of the variable valve lift mechanisms  12  so that their cylindrical members  26  all rotate in unison. This rotation is achieved in a manner, which will be described shortly.  
         [0028]    The roller followers  33  are supported on the rocker arms  32  by means of a roller follower pin  37 , which further serve to couple the rocker arms  32  to each other (see FIG. 4).  
         [0029]    Referring now to FIG. 1 it will be seen that at one end of the cylinder head  13 , there is provided a drive sleeve  38  which, like the cylindrical members  26  of the variable valve lift mechanisms  12  is journalled between the cylinder head upstanding walls  15  and the bearing caps  17 . The coupling rod  36  extends into a projection  39  on this drive sleeve  38 .  
         [0030]    The drive sleeve  38  is also provided with an integral gear  41  that is enmeshed with a driving pinion  42  of an electrical stepping motor  43 , which can be mounted externally of the cylinder head assembly and thus, isolated from the heat of the engine.  
         [0031]    At this point, it might be in order to indicate that the conventional variable valve lift mechanisms are normally operated by hydraulic motors that are supplied with pressure from the lubricating system of the engine. This has a number of disadvantages and does not easily permit the same engine to be utilized with or without a variable valve lift mechanism. In addition, heat is a factor in the operation of these systems and thus, by utilizing an electrical motor externally positioned, heat problems are substantially avoided.  
         [0032]    It has been previously noted that the valve actuating portion  34  of each rocker arm  32  is curved in shape and the curvature is about the axis of rotation C of the camshaft  16 . Thus, in one extreme position of valve lift, the maximum valve lift as shown in FIGS. 2 and 6, the contact point A between this valve actuating portion  34  and the valve shim  23  is in line with the axis of the valve stem  21  and also is in line with the rotational axis R of the roller followers  33  and the camshaft rotational axis C. This is the point when the maximum valve lift is obtained.  
         [0033]    If less lift is required, the variable valve lift mechanisms  12  are rotated in a counter clockwise direction as shown in FIGS. 2 and 6 through  8  to an intermediate position as shown in FIG. 7.  
         [0034]    In this position, the contact point A has moved to an intermediate portion along the curve length of the curved valve actuating portion  34 . At the same time the pivot axis B of the rocker arms  32  is also moved in the same direction so as to shorten the effective lift length to the distance between the points B and A as seen in this figure.  
         [0035]    If the actuating motor  43  is energized further to rotate the cylindrical member  26  of the variable valve lift mechanism  12  to a further point as shown in FIG. 8, the valve lift can be substantially minimized. In fact, if there is a spherical end formed on the shim  23 , which is preferred, then the point A will be in line with the camshaft rotational axis C and the center of the valve stem  21  so that the contact point A is on the center of the shim  23  and, accordingly, there will be no lift because there will in essence be no significant pivotal movement of the rocker arms  32 .  
         [0036]    That is, the rocker arm  32  may pivot slightly, but this will merely result in sliding movement of the valve actuating or contacting section  34  of the rocker arm across the valve shim  23  without its opening. Because of this operation the engine  11  can be operated without any throttle valves in the induction system. The engine speed can be controlled by varying the valve lift to control the induction air flow, thus simplifying the engine construction and improving transient response.  
         [0037]    Thus, from the foregoing description, it should be readily apparent that the described embodiment of the invention provides a very wide range of valve lift adjustments without unduly complicated physical structure and without otherwise jeopardizing the valve actuation. In fact, this mechanism also reduces the necessity for subsequent valve adjustment due to wear since wear will be minimized. This mechanism also permits reduction in hydrocarbon emissions particularly during engine starting and even may eliminate the utilization of a throttle valve is used in conjunction with the intake valves because they can be retained from opening.  
         [0038]    In the foregoing description, it has been disclosed that the variable valve lift mechanisms are all operated simultaneously. Of course, it would be possible to actuate them each independently. The invention has also been described in conjunction with an arrangement wherein the valve stem axis intersects the camshaft rotational axis but that need not be the case. Various other changes and modifications may be made without departing from the spirit and scope of the invention, as defined by the appended claims.