Abstract:
A camshaft phaser wherein camshaft oscillatory torque resulting from opening and closing of an associated engine valve is employed to controllably adjust the degree of advance or retard of the rotor. All advance chambers communicate with a first annular passage, and all retard chambers communicate with a second annular passage. Valve means connecting the first and second annular passages are controllable by a solenoid-actuated piston to permit selective flow of oil between the advance and retard chambers to alter the angular position of the rotor with respect to the stator. The solenoid windings are selectively actuable in response to an engine control module. Preferably, the phaser is a sealed unit, filled with oil at manufacture and requires no oil connection with the oil recirculation system of an engine upon which the phaser is mounted. The phaser is independent of engine oil pressure for actuation.

Description:
TECHNICAL FIELD 
     The present invention relates to camshaft phasers for internal combustion engines; more particularly, to means for controlling the actuation of such camshaft phasers; and most particularly, to method and apparatus for controlling such actuation through camshaft oscillatory torque. 
     BACKGROUND OF THE INVENTION 
     Camshaft phasers for varying the valve timing of internal combustion engines are well known. A phaser typically comprises a rotor element that is attached to the end of a camshaft and is variably displaceable rotationally within a stator element driven by the engine crankshaft. Prior art phasers typically are actuated by pressurized oil that is derived from the engine&#39;s main oil supply and is selectively directed by electrically-controlled valving to chambers within the phaser to alter the phase relationship between the rotor and stator, and, hence, between the camshaft and crankshaft. Providing oil from the engine can require extensive and undesirable modification of the engine block and/or the camshaft and/or the forward camshaft bearing. Such modifications can be expensive and difficult to implement and are known to be important considerations when adapting a camshaft phaser to an existing engine design. It is highly desirable, therefore, in the art to provide a camshaft phaser requiring little or no modification to the receiving engine. 
     Further, prior art phasers experience a delay in oil pressure and flow upon start-up of a phaser-equipped engine, which prevents immediate phaser operation. To prevent uncontrolled phaser motion during this delay, vane phasers typically are equipped with additional locking devices to prevent rotor movement. Further, engine oil pressure decreases significantly for hot idle conditions, limiting phaser response rate. Further, oil quality and air entrainment may vary with time and operating conditions, which can also affect phaser torsional stiffness, resulting in unwanted holding position variation. Further, oil viscosity may vary over several orders of magnitude within the normal range of engine operating temperatures, causing a temperature-dependent variation in phaser response rate. And finally, it is difficult to achieve phase change rates greater than about 100 crank degree/second with engine-oil motivated phasers; faster phaser rates require significantly larger engine oil pumps, larger oil flow passages, and higher system pressures. Such changes are expensive in manufacture and adversely affect fuel economy. 
     A typical cam phaser in good working order exhibits a characteristic level of torque-imposed instability as a result, in part, of the rotor of the cam phaser being mounted directly to the engine camshaft. In opening an engine valve, the valve follower leaves the base circle portion of the cam lobe and begins to climb the rising edge of the eccentric portion, imposing a resistive (negative) torque on the camshaft. At some further position of the cam rotation, the resistive torque reaches a maximum, then declines to zero, and then becomes an assistive (positive) torque in the opposite direction as the follower descends the falling edge of the eccentric portion as the valve closes. Thus, for each rotation of the camshaft lobe, an oscillatory torque is imposed on the camshaft. For a multiple cylinder engine, this cycle is repeated several times for each revolution of the camshaft. 
     U.S. Pat. No. 6,453,859 B1 discloses a multi-mode control system for variable camshaft devices wherein torque-induced phaser oscillatory motion is employed for providing pressurized engine oil and/or phaser chamber oil to the advance and retard chambers of the phaser via a spool valve. A first drawback of the invention is that an engine oil supply is still required for actuation of the phaser, requiring modification of the associated engine block or head. A second drawback is that an adequate spool valve is relatively cumbersome and therefore has a relatively low reaction rate. A third drawback is that the system requires both a spool valve and a plurality of check valves, as does the apparatus disclosed in U.S. Pat. No. 5,645,017. 
     What is needed is method and apparatus for controlling actuation of a camshaft phaser without reliance on engine oil supply or pressure. 
     What is further needed is such method and apparatus wherein flow-controlling check valves are directly actuated without resort to an additional spool valve. 
     It is a principal object of the present invention to provide actuation control of a camshaft phaser without reliance on engine oil supply or pressure. 
     It is a further object of the present invention to provide a camshaft phaser which may be installed into an existing engine without a requirement for a real-time supply of engine oil to actuate the phaser. 
     It is a still further object of the invention to provide a camshaft phaser wherein flow-controlling check valves are directly actuated by a solenoid without requiring an additional spool valve. 
     It is a still further object of the invention to provide an improved camshaft phaser wherein inherent oil pressure differences within a stator are harnessed to alter the rotational position of a rotor within the stator. 
     SUMMARY OF THE INVENTION 
     For simplicity, in the discussion herein below, only vane type phasers are addressed specifically. However, principles in accordance with the invention for controlling the advance and retard positions of a camshaft phaser should be understood as being applicable by one of ordinary skill in the art to either vane-type or spline-type phasers. 
     Briefly described, a camshaft phaser includes a conventional stator having a generally cylindrical shape and having a plurality of angularly spaced-apart radial lobes extending inwardly into a central chamber. The stator is adapted to be driven rotationally by the crankshaft assembly of an internal combustion engine. Concentrically disposed within the central chamber of the stator is a rotor having a plurality of radial vanes extending outwardly from a central hub, the vanes being interspersed with the lobes such that first and second chambers are formed on either side of each vane. All first and second chambers are filled with oil. When either the first or second chambers becomes biasedly pressurized, as by oscillatory camshaft torque, for example, the rotor is urged angularly in either a first rotational direction or an opposite second rotational direction within the stator. All first chambers mutually communicate with a first annular passage, preferably formed in an insert disposed in a central assembly bolt therein, and all second chambers mutually communicate with a similarly-disposed second annular passage. Valve means connecting the first and second annular passages are directly actuable by a solenoid-actuated piston to permit selective flow of oil between the first and second chambers to alter the angular position of the rotor with respect to the stator. Rotational torque of the rotor by oscillatory actuating torque resulting from opening and closing actuation of an associated engine valve provides the force for displacing oil from the first to the second chambers or from the second to the first chambers, as desired, to advance or retard the rotor position within the stator. Preferably, the solenoid is selectively actuable in response to an electronic control module that integrates various programmed engine status parameters to permit flow directly between the first and second chambers. 
     In a currently preferred embodiment, the phaser is a sealed unit, filled with oil at manufacture and requiring no oil connection with the oil recirculation system of an engine upon which the phaser is mounted. In an alternative embodiment, a small flow of oil may be provided to the phaser from the engine to flush out any particles which may form with use, to purge bubbles, and to compensate for any leaks in the phaser. However, in no embodiment in accordance with the present invention is the phaser dependent upon engine oil pressure for actuation, as in prior art phasers. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The present invention will now be described, by way of example, with reference to the accompanying drawings, in which: 
     FIG. 1 is a graphical representation of the variation in valve opening distance, oscillatory variation in camshaft torque, and resulting variation in camshaft torque instability as a function of engine crankshaft angle; 
     FIG. 2 is an elevational cross-sectional view of a currently preferred first embodiment of a camshaft phaser in accordance with the invention; 
     FIG. 3 is a cross-sectional view of the phaser shown in FIG. 2, taken along line  3 — 3  therein; and 
     FIG. 4 is a second embodiment of a camshaft phaser in accordance with the invention. 
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     Referring to FIG. 1, several simultaneous engine functions are shown as a function of the rotation of an engine crankshaft coupled to an engine camshaft via an improved camshaft phaser assembly in accordance with the invention. Exemplarily, the camshaft functions shown in FIG. 1 relate to a three-lobe intake valve camshaft for one bank of a V-6 engine. Recall that in a four-stroke engine, the crankshaft rotates twice for each rotation of the camshaft; thus, in the example shown, each lobe has an actuation domain of 240 crank angle degrees. 
     Curve  10  shows the lift in millimeters of a typical engine valve through opening and closing by a cam lobe. Curve  12  shows the torque in Newton-meters imposed on a camshaft by actuation of the valve cam follower for the cam lobe. Note that the initial torque value is negative (counter to camshaft rotation) as the follower begins to ascend the opening flank of the lobe, reaching a minimum of approximately −17 Nm when the valve is about half-open; then becomes increasingly positive (in the direction of camshaft rotation), passing through 0 just ahead of the peak opening of the valve; reaches a maximum value in excess of +10 Nm when the follower is descending the closing flank of the lobe and the valve is about half-closed; and remains positive through the remainder of the valve cycle until the follower is once again on the base circle portion of the cam lobe. 
     The alternating negative and positive torque exerted on the camshaft causes a slight oscillatory instability in the instantaneous angular position of the rotor during valve actuation by a cam lobe, as shown in curve  14  in FIG. 1 wherein instability is expressed in angular deviation from nominal (0) during actuation by a single lobe. For the three-lobe camshaft described above, such oscillatory instability occurs identically three times with each rotation of the camshaft/rotor. The nominal position is the angular holding position of the phaser rotor with respect to the phaser stator as intended by the phaser electronic control system. In the example shown, the instability curve  14  nearly mirrors the valve opening curve  10 , reaching a minimum value  16  of about −2.5 degrees near the valve opening peak and a maximum value  18  of about +1.5 degrees when the valve is nearly closed again. Such oscillatory instability of the rotor is to be expected and is used advantageously in accordance with the invention to controllably adjust the angular position of a rotor within a stator, and hence the advance or retard position of valve timing in an associated internal combustion engine. 
     Referring to FIGS. 2 and 3, an improved and currently preferred embodiment of a camshaft phaser system  20  in accordance with the invention includes a conventional camshaft phaser  21  having a stator  22  having a generally cylindrical shape and having a plurality of angularly spaced-apart radial lobes  24  extending inwardly. Stator  22  is adapted to be driven rotationally by the crankshaft assembly (not shown) of an internal combustion engine  40  via a conventional sprocket wheel  26 . Concentrically disposed within stator  22  is a rotor  28  having a plurality of conventional radial vanes  30  extending outwardly from a central hub  32 , vanes  30  being interspersed with lobes  24  such that conventional first and second chambers  34 , 36  are formed on either side of each vane  30  for either advancing or retarding the position of the rotor with respect to the stator. Chambers  34 , 36  are closed axially by sprocket wheel  26  and cover plate  38 . All first and second chambers  34 , 36  are filled with oil. Phaser assembly  21  may optionally include a locking pin subassembly  39  disposed in a vane  30  for rotationally immobilizing the rotor with respect to the stator at a specific predetermined relative angle, for example, full retard of the valve timing. 
     In internal combustion engine  40 , a camshaft bearing  42  supports a conventional camshaft  44 . Bearing  42  extends beyond engine  40  for also supporting sprocket wheel  26  and rotor hub  32 . Camshaft  44  is hollow at its outer end and is threaded for receiving phaser assembly bolt  46 . Rotor  28  is fixed to an end of and rotates with camshaft  44  via assembly bolt  46 . Thus, lobes on camshaft  44  operate to open and close respective engine valves (not shown). 
     Bolt  46  is provided with a well  48  for receiving a valving insert  50 . Insert  50  includes first and second check valves  52 , 54  opening into a central bore  56 , which valves, when selectively opened as described below, permit unidirectional flow of oil in either of two opposite directions between first and second chambers  34 , 36 . 
     Check valves  52 , 54  are disposed in insert  50  such that first and second valve balls  58 , 60  extend into central bore  56  when the valves are fully closed. Bolt  46  is provided with first and second annular passages  62 , 64  spaced apart axially and communicating with valves  52 , 54  via passages  66 , 68 , respectively. First passage  62  communicates with each first chamber  34  via radial passages  70  in hub  32  (FIG.  3 ). Second passage  64  communicates with each second chamber  36  via radial passages  72  in hub  32 . 
     A piston  74  slidably disposed in central bore  56  includes connector channel  77 , and first and second ramps  76 , 78  for selectively engaging first and second balls  58 , 60 , respectively. Piston  74  is preferably connected to and is axially positionable by a solenoid armature  80  disposed within a non-ferromagnetic cap  82  sealably attached to bolt  46 . A solenoid spring  84  is disposed, preferably in compression, between armature  80  and cap  82  to urge armature  80  and piston  74  to the right in FIG.  2 . Solenoid windings  86  and pole piece  88  surround armature  80  and are mounted on a phaser cover or other non-rotational surface. An air gap  90  exists between pole piece  88  and cap  82  such that, when electrically energized, the solenoid windings are magnetically coupled to the armature through cap  82 . 
     In operation, when either the first or second chambers become biasedly pressurized by oscillatory torque, the rotor is urged angularly in either a first rotational direction or an opposite second rotational direction within the stator, as described above. When a change in rotor position is needed, such as retarding or advancing of the rotor as may be desired for a specific application, ECM  100  controls the voltage and current sent to windings  86 , as required. As for example, in a first direction change of the angular position of the rotor, voltage and current to the solenoid windings are turned off causing the magnetic field around the solenoid to collapse, and the magnetic force imposed in the armature to dissipate. The force of spring  84  pushing the armature and piston remains and slides piston  74  to a position such that ramp  76  displaces ball  58 , opening check valve  52 . In this condition, torque instability creates oscillatory pressure to displace oil from first chambers  34  through opened valve  52  and channel  77 , and back through valve  54  (after unseating ball  60  against its bias spring) into second chambers  36 . With the completion of one or a few oscillatory cycles, the rotor is driven to its desired angular position. Piston  74  then returns to its neutral position via a signal from ECM  100  whereby both valves  52  and  54  are permitted to close. 
     When a second rotor position change is desired, the solenoid windings  86  and armature  80  are actuated axially as a result of signals received from ECM  100  to engage second ramp  78  with second ball  60 , thus allowing oil to flow in a reverse direction from second chambers  36  into first chambers  34  under pressure from oscillatory torque during the opposite phase of the torque cycle. Again, the completion of one or a few oscillatory cycles may be required to provide a sufficient number of successive torque pulses to move the rotor through a sufficient angle. The torque oscillation is rectified during this time so that back flow of oil cannot occur through the positive portion of the oscillation because check valve  52  is closed to flow in that direction. 
     First and second ramps  76 , 78  are spaced apart axially such that both first and second check valves  52 , 54  may be closed simultaneously, effectively locking the rotor in a predetermined, desired holding position of advance/retard. A Pulse Width Modulated (PWM) voltage signal applied by the ECM to the solenoid actuator in known fashion can readily control the piston at such an intermediate position. 
     With both check valves closed while piston  74  is in an intermediate position, the phaser is hydraulically stiffer than prior art vane-type camshaft phasers because the ratio of vane area to trapped oil chamber volume is relatively large. Conversely, conventional cam phasers having a control valve located within the engine cylinder head have a much larger trapped oil volume and therefore have a greater positional fluctuation for a given torque fluctuation. Since the present improved phaser is significantly stiffer than prior art phasers, a prior art lock pin assembly  39  used to hold the rotor in a predetermined angular position may be eliminated in some applications. 
     Referring to FIG. 4, in a second embodiment  20 ′ of a phaser system having camshaft phaser  21 ′ in accordance with the invention, engine oil is shown being provided into and out of the phaser assembly, which is otherwise identical to first embodiment  20 . An oil feed passage  120  through camshaft bearing  42  connects an oil gallery  122  in engine  40  with an annular reservoir  124  between bearing  42  and bolt  46 . Reservoir  124  communicates with a passage  126  in insert  50  for supplying oil as needed to check valves  52 , 54 . Oil returns to an engine sump  128  via a central passage  130  in bolt  46  and a weep hole  132  in camshaft  44 . Preferably, the rate of oil flow is very low, being restricted by a restriction orifice  134 . Where strict engine oil independence is a requirement, as may be imposed for a specific application, the oil supply and drain passages shown in FIG. 4 may be eliminated, as shown in currently-preferred phaser assembly  20  in FIG.  2 . However, there are some positive attributes to accessing engine oil, such as for purging bubbles from the phaser, enabling constant changing and renewing of oil within the phaser so that contaminants are purged, enabling lock pin disengagement by oil pressure, and the like. As noted above, however, in no instance is engine oil pressure the actuating force for rotation of the rotor, as in prior art phasers. 
     The actuation method disclosed hereinabove employs a magnetic field generated in a solenoid coil mounted in a timing chain cover. There is no mechanical contact between this coil and the rotating phaser, only a magnetic coupling, allowing the phaser to be oil-tight with no actuator sliding or rotating seals, as may be desired for some applications such as belt-driven engines. However, this is only one actuation embodiment. Another embodiment (not shown) includes an electromagnetic coil connected to the piston via a rotatable coupling. Yet another embodiment (not shown) includes the activation coil within the phaser so that it also rotates with the phaser. The electrical signal to the coil is supplied through slip-rings similar to those used for conventional alternators. In a further embodiment (not shown), one coil may be employed per check valve, defining each check valve as a directly-actuated solenoid check valve similar to an engine fuel injector. These may be relatively small coils, since the force they provide must move only the ball in the check valve. 
     While ramps  76  and  78  are shown as positioned to the outside of check balls  58 ,  60 , it is understood that the ramps may be positioned to the inside of the check balls to reverse the operation of piston  74  relative to the direction of oil flow through valves  52 ,  54 . Means for connecting the fluid flow between the valves, such as for example a longitudinal flute, would also be provided. 
     The mechanical adaptations required for these embodiments would be obvious to one of ordinary skill in the art and need not be elaborated here. However, all such embodiments and adaptations are comprehended by the present invention. 
     Further, the check valves employed in embodiments in accordance with the invention may be other than the ball and socket configuration shown and described above. They may also be flat plate or reed designs, as are well known in the valve arts. All such valves are comprehended by the invention, provided that they may be selectively engaged and disengaged as described to provide the desired function. 
     While the invention has been described by reference to various specific embodiments, it should be understood that numerous changes may be made within the spirit and scope of the inventive concepts described. Accordingly, it is intended that the invention not be limited to the described embodiments, but will have full scope defined by the language of the following claims.