Abstract:
The present invention relates to a variable valve timing system for an internal combustion engine which cyclically opens and closes a port providing fluid communication between a combustion chamber and a conduit leading thereto and which delays the closure of the port in response to a signal indicative of the power output required of the engine in order to vary the ratio of the mass of fluid inducted into the chamber to the mass of fluid expelled from said chamber during the period the port is open so that the mass of fluid retained in the chamber after closure of the port can be controlled without the use of a throttle valve.

Description:
FIELD OF THE INVENTION 
     The present invention relates to an internal combustion engine and more particularly to a method and apparatus for controlling the induction of said engine. 
     BACKGROUND OF THE INVENTION 
     One major problem plaguing internal combustion engines is the so-called pumping loss which occurs during part throttle operation of the engine. 
     When an internal combustion engine operates at part throttle, a vacuum is developed downstream of the throttle valve. This negative pressure is transmitted to the combustion chamber of the engine during the induction phase of operation thereof. This tends to resist the movement of the piston, in the case of a reciprocating type internal combustion engine, in the direction of bottom dead center (BDC) due to the pressures differential developed across the piston. As a result some of the power developed during the power stroke of the piston is wasted in drawing the piston against the vacuum prevailing in the combustion chamber during the induction stroke thereof. 
     In order to partially overcome this pumping loss problem, a number of so-called &#34;split mode&#34; operation engines have been proposed wherein during part throttle operation, such as cruising and deceleration, some of the cylinders are disabled. However these arrangements, while partially solving the problem have encountered other drawbacks in the form of jolting induced by the sudden torque output changes occurring upon abling and disabling of one or more of the cylinders. Moreover the undue complexity of workable arrangements tends to be prohibitive. 
     Hence there still exists the need for an arrangement which can completely eliminate the pumping loss problem. 
     SUMMARY OF THE INVENTION 
     A first important aspect of the present invention comes in the combination of an internal combustion engine having a combustion chamber which undergoes a volume expansion during one phase of engine operation and contraction during a second phase of operation with an apparatus which opens a port of the chamber during one of said phases and a period overlapping a portion of the other and which varies the period for which the port is open to vary the mass of fluid confined in the chamber. 
     A second important aspect of the invention comes in a method of operating an internal combustion engine wherein a full charge of fluid is inducted into the combustion chamber during one phase of operation of the engine and a portion of the change is discharged or expelled from the chamber during a second phase of operation wherein by controlling the amount of fluid discharged the mass of the fluid retained in the chamber can be controlled. 
     A third important aspect of the present invention comes in the use of a valve actuating apparatus wherein two cams which normally rotate with a given phase difference therebetween are used to reciprocate hydraulic pistons which cooperate to pressurize hydraulic fluid in a cylinder which in turn is used to reciprocate a third piston drivingly connected to a valve. The apparatus also includes an arrangement for varying the phase difference between the cams to vary the period for which the third piston moves the valve. 
     A further important aspect of the present invention comes in the use of intermeshing helical gears which when moved axially with respect to each other induce an angular displacement therebetween in addition to the rotation to rotation translation normally provided. 
     Thus, by way of example, it is possible to control the induction of a combustible charge into the combustion chamber of the engine without the use of a throttle valve and with substantially atmospheric pressure in the induction passage or manifold, by inducting a full charge into the chamber during the induction phase and discharging a controlled portion of said charge back into the induction passage during the initial stage of the compression phase. p It will thus be understood that with the present invention the pumping loss problem can be completely solved. 
     In the case it is desired to employ so-called &#34;external&#34; EGR (exhaust gas recirculation) it is advantageous to provide means by which a predetermined low vacuum can be maintained in the induction passage for facilitating the induction of the exhaust gases from the exhaust conduit or manifold. It is further advantageous to disable the above-mentioned means during given modes of engine operation to obviate the vacuum thus facilitating the cessation of the EGR. 
     Further it is not outside the scope of the present invention for use in the case of &#34;internal&#34; EGR wherein exhaust gases are inducted from the exhaust conduit into the combustion chamber via the exhaust valve. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The above and many other aspects, features and advantages of the present invention will become more deeply appreciated as the description of the preferred embodiments is made in conjunction with the attached drawings, in which: 
     FIG. 1 is a sectional view of a hydraulic valve actuating device which forms a part of the preferred embodiment of the present invention; 
     FIG. 2 is a schematic view of a pressure proportioning valve and helical gearing which varies the phasing between the cams shown in FIG. 1; 
     FIG. 3 schematically shows an end elevation of internal combustion engine equipped with the variable valve timing system according to the present invention and depicts the connection between a sprocket driven by the crankshaft of the engine and the sprockets of the variable valve timing system; 
     FIG. 4 and FIG. 5 are graphs showing the valve lift of the inlet valve which occurs when there is zero phase difference between the cams shown in FIG. 1 and a given phase difference between said cams, respectively; 
     FIG. 6 shows a throttle valve arrangement for maintaining a predetermined vacuum within the induction manifold which facilitates the recirculation of exhaust gas from the exhaust conduit to said induction manifold; 
     FIG. 7 is a perspective view of a vehicle equipped with an internal combustion engine having a variable valve timing system according to the present invention; 
     FIG. 8 is a schematic sketch of a second embodiment of the present invention; and 
     FIGS. 9A to 9C are sections taken along section lines I-I, II-II and III-III of FIG. 8, respectively. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     FIG. 1 of the drawings shows a hydraulic valve lifting arrangement 3 of the preferred embodiment of the present invention. With this arrangement two cam shafts 5a and 6a, which by way of example take the form of a twin overhead cam arrangement, carry cams for operating the inlet valve 1 and the exhaust valve 2. In this embodiment the cam shaft 5a carries two sets of cams, tht is cams 4 and 5. As shown the cam 4 induces reciprocation of the exhaust valve 2 while the cam 5 induces reciprocation of a piston 8 via engagement with a tappet portion 8a formed on the end of the piston. As shown the piston 8 is reciprocatively received in an elongate cylinder 7 and biased by biasing means in the form of a spring 10 toward the cam shaft 5a so that the tappet portion 8a remains in sliding contact with the contoured surface of the cam 5. A second piston 9 is received reciprocatively in the cylinder 7 as shown. This piston has a tappet portion 9a which is similar to the tappet portion 8a, and which is maintained in sliding contact with the contoured surface of the cam 6 by spring 11. A third piston 16 is reciprocatively received in a branch like portion 15 of the cylinder 7. This third piston is subject to the bias of a spring 17 which maintains the tappet portion 16a thereof in contact with the top of the valve stem 1a. The common chamber 12 defined within the cylinder 7 is filled with hydraulic fluid supplied from a hydraulic fluid gallery 14 via a check valve 13. 
     Looking now to FIG. 2 we find an arrangement for varying the angular position or phase of cam 6 with respect to cam 5 in response to a demand signal generated in accordance with a demand for a given power output by the internal combustion engine. As shown cam shaft 6a carries a helical gear 18 at one end thereof which is in meshing engagement with a second helical gear 19. The helical gear 19 is slidably received on a rotary shaft 21 and connected thereto via suitable means, which in this case takes the form of splines, for synchronous rotation therewith. Connected to one end of the rotary shaft is a sprocket 20 or similar pulley which is chain or belt driven. Further disclosure to this sprocket will be made later in this disclosure. 
     A shift fork 24 is operatively arranged with the helical gear 19 so that the gear may be moved along the shaft 21. A power cylinder arrangement 40 is operatively connected to the shift fork 24. This arrangement consists of a cylinder 42 in which a piston 44 is slidably received to define a variable volume hydraulic chamber 46. The piston is connected to the shift fork 24 and biased in a direction against the hydraulic pressure prevailing in the chamber 46 by a spring 48. With this arrangement as the pressure in the chamber 46 decreases the spring will bias the piston and shift fork 24 in a direction to move the helical gear 19 to the right (as seen in the figure) and vice versa. It will be appreciated that as the helical gear 19 is moved axially along the helical gear 18 a positive angular displacement between the rotary shaft 21 and the cam shaft 6a occurs in addition to the rotation to rotation translation normally provided between the meshing gears. Hence for any given relative axial movement between the two helical gears 18 and 19 a corresponding change in phase or angular position between the cams 5 and 6 will occur. This will be made clearer with reference to FIG. 3 of the drawings. 
     In order to readily control the pressure prevailing in the hydraulic chamber 46 a pressure proportioning valve 50 is provided. The function of this valve is to proportion the degree of pressure permitted to be transmitted from a pump 52 to the chamber 46. As shown the proportioning valve 50 has a valve member 54 which is movable with respect to a valve seat 56 so as to variable restrict the flow of pressurized hydraulic fluid from the pump therepast. As shown the chamber 46 and a sump 58 from which the pump 52 draws hydraulic fluid fluidly communicate with a valve chamber 60 located downstream of the valve seat 56. A relief valve 62 interconnects the feed line interconnecting the pump and the proportioning valve and the drain line interconnecting the proportioning valve and the sump. Hence upon a predetermined pressure prevailing in the feed line as will occur when the valve member 54 seats on the valve seat 56 hydraulic fluid will be relieved through the valve 62 back to the sump 58. 
     The proportioning valve 50 has a bore formed therein in which two pistons 64 and 66 are reciprocatively disposed. The first piston 64 defines a variable volume hydraulic chamber 68 in said bore. As shown the chamber 68 is communicated with the valve chamber 60 via a small diameter passage 70. The second piston is received in the open end of the bore to define an atmospheric chamber 72. The second piston 66 has a small diameter through bore (no numeral) formed therein to establish constant communication between said atmospheric chamber 72 and the atmosphere. Springs (no numerals) are disposed in hydraulic chamber 68 and the atmospheric chamber respectively. A lever arrangement generally denoted by the numeral 74 is operatively connected to the accelerator pedal of the vehicle to which the variable valve timing system according to the present invention is provided. This lever is arranged to urge the piston 66 against the bias of the spring disposed in the atmospheric chamber 72 to in turn apply a load to the first piston 68 in response to an increase in the magnitude of the demand signal. However the generation of this signal is not limited to the movement or depression of the previously mentioned accelerator pedal and may be generated by other suitable means. As shown the first piston is fixedly connected to the valve member 54. Thus if the accelerator pedal is depressed the piston and spring arrangement will tend to open the valve 50 to permit an increased hydraulic pressure to prevail in the hydraulic chamber 46. This increased pressure will also be transmitted to the hydraulic chamber 68 of the proportioning valve. An equilibrium is therefor established between the piston and spring arrangement and the pressure in the chamber 68. 
     With the just described arrangement upon depression of the accelerator pedal the pressure in the hydraulic chamber 46 increases driving the helical gear 19 toward the left (as seen in the drawings). It is to be noted however, that any other suitable mechanical hydraulic or electrical arrangement for achieving the just mentioned movement of the helical gear falls within the perview of the present invention and accordingly can be substituted for the just described arrangement. 
     Turning now to FIG. 3 of the drawings we find a schematic representation of an internal combustion engine 100 which is equipped with the preferred embodiment of the present invention. As shown the cam shaft 5a and shaft 21 are equipped with sprockets or pulleys 26 and 20 respectively. The connection between the shaft 21 and the cam shaft 6a has already been set forth. A chain 29 or suitable belt is provided about sprockets 26 and 20 and arranged in drive connection with the crankshaft 27 of the engine through suitable means such as a sprocket 28. Hence both sprockets 26 and 20 rotate in synchronism with crankshaft of the engine. Preferably for ease of manufacture and design the sprockets 20 and 26 are of the same diameter (with the same number of teeth) and the meshing helical gears are likewise so selected that the cam shaft 6a rotates at the same rotational speed as the cam shaft 5a. 
     Referring once more to FIG. 1 of the drawings it will be understood that when the demand for power is minimal viz. the accelerator pedal is not depressed, that the cams 5 and 6 rotate with the maximum phase difference therebetween. This of course induces the maximum duration of pressure generation within the cylinder 7 whereby the lift of the inlet valve is such that the valve remains open for the maximum of a predetermined period into the compression stroke. This situation can be best understood from FIG. 5 wherein the broken lines indicate the individual lifts L 1  and L 2  provided by pistons 8 and 9 respectively and the solid line curve indicates the addition of the individual lifts and indicates the actual or resultant lift of the inlet valve. 
     Thus as the accelerator is depressed the phase difference between the cams 5 and 6 tends to zero whereupon the pistons 8 and 9 tend to reciprocate toward each other simultaneously. Maximum pressure of minimum duration tends to be generated inducing the piston 16 to undergo maximum lit and minimum overlap of the compression stroke. This situation is clearly depicted in FIG. 4 of the drawings. 
     Thus as the demand for power increases viz. as the accelerator pedal is depressed the amount of combustible charge discharged back into the induction manifold reduces thereby increasing the mass of charge retained in the combustion chamber at the point of ignition. At full depression of the accelerator pedal the same effect as wide open throttle operation occurs viz, the maximum amount of charging of air and/or air-fuel mixture into the combustion chamber occurs. However throughout all of the operation of the engine it will be appreciated that atmospheric or close to atmospheric pressure will prevail within the induction manifold eliminating any work necessary to draw air around a partially closed throttle valve and eliminating the retardation of the movement of the piston (in the case of a reciprocating type internal combustion engine) toward BDC due to the presence of a partial vacuum during stroking thereof. 
     However in the case it is desired to recirculate exhaust gases from the exhaust manifold to the induction manifold it is preferable to create a predetermined vacuum within the induction manifold. This vacuum may be of the order of -100 mmHg within the induction manifold. Thus, to this end it is possible to dispose a throttle valve 30 or the like in the passage leading to the induction manifold of the engine. This arrangement is clearly shown in FIG. 6 of the drawings. As seen a vacuum motor for controlling the throttle valve consists of a housing containing therein a flexible diaphragm 34 which partitions the housing into a vacuum chamber 33 and an atmospheric chamber 32. The vacuum chamber 33 is fluidly communicated with the induction passage 31 at a point downstream of the throttle valve 30 so as to be exposed to the vacuum generated thereby. The diaphragm is operatively connected to the throttle valve 30 through a linkage indicated by 36. Hence with this arrangement as the vacuum increases in the induction passage downstream of the throttle valve the diaphragm will respond to the vacuum increase to move the throttle valve to a positon wherein an increased amount of air is permitted into the induction passage accodingly reducing the vacuum prevailing therein. Automatic maintenance of the preselected or predetermind vacuum (e.g. -100 mmHg) is thus achieved. As indicated the EGR conduct is arranged to open into the induction passage 31 at a location downstream of the throttle valve 30 so as to be exposed to the vacuum. 
     In addition to the just described arrangement it is possible to add, as indicated in phantom, further control means 37 which disables or induces the throttle valve to take a wide open position under predetermined modes of engine operation when EGR is not required, such as full load operation, high speed low load operation and idling. This of course facilitates the termination of the supply of EGR gas into the induction manifold under these conditions. It will be noted that this removes partial throttle in the induction system under full load condition. The control means can take the form of a solenoid clutch or the like. Although not clear from the schematic drawing the control means (in phantom) and the linkage 36 are located externally of the induction passage 31 in a well known manner. 
     Thus by way of summary the operation of the preferred embodiment of the present invention is as follows: As demand for power output by the engine increases, the proportioning valve 50 feeds an increased amount of hydraulic pressure to the chamber 46, driving the helical gear 19 along the rotary shaft 21. This movement in addition to the rotation to rotation translation constantly occurring between the two helical gears 18 and 19 during operation of the engine, drives the helical gear 18 to rotate through an additional degree of rotation with respect to the gear 19. Thus as the sprockets 20 and 26 rotate synchronously with the crankshaft 27 of the engine, the cam shaft 6a undergoes a relative rotation with respect to the cam shaft 5a in and this case in a sense to reduce the phase difference between the cams 5 and 6. Thus as the phase difference between the cams 5 and 6 decreases the pistons 8 and 9 tend to reciprocate toward each other simultaneously. 
     It will be understood that with the maximum delay between pistons 8 and 9 being urged into the cylinder 7 by the action of cams 5 and 6 respectively, the maximum period of pressure generation within the chamber 12 defined between the three pistons 8, 9 and 16 will occur. Hence piston 16 will tend to hold the inlet valve 1 open for the maximum period. However upon the phase difference between the two cams being reduced the time of pressure generation will decrease and reach a minimum value upon simultaneous reciprocation of the pistons 8 and 9. The maximum peak pressure in the chamber 12 will also occur at this time. 
     Thus in operation as the phase difference between the cams decreases the time for which the valve is open decreases reducing the amount of overlap of the compression phase of engine operation. Less charge is permitted to be returned to the induction passage or manifold thus increasing the amount or mass of charge retained in the combustion chamber. A proportional increase in power output is thus achieved. 
     It will be appreciated that the means by which the demand signal is generated is not limited to the depression of an accelerator pedal and will, in the case of an aircraft or boat, be generated via manipulation of a hand operated lever or the like. The demand signal may also be generated by a suitable electronic or hydraulic circuit if the situation demands. 
     Turning now to FIGS. 8 and 9A to 9C we find another embodiment of the present invention. In this case the proportioning valve 50, discussed previously in connection with FIG. 2, is connected to a hydraulic cylinder 80 in which one end of a cam shaft 84 is slidably received. As shown the cam shaft 84 carries a cam 82 which is formed with a given profile which will be discussed later in connection with FIGS. 9A to 9C. The other end of the cam shaft is slidably received in an axial bore of a sprocket or pulley 86. A spring 88 is disposed in the bore to bias the cam shaft in a direction against the bias of the hydraulic pressure prevailing in the hydraulic cylinder 80. As shown the cam shaft 84 and the sprocket 86 are splined together via splines 90 and 92 formed in the axial bore and on the end of the cam shaft 84 respectively. The sprocket 86 and the sprocket 28 (referred to in FIG. 3) driven directly by the crankshaft of the engine are operatively connected to synchronous rotation. 
     The profile of the cam 82 can best be appreciated from FIGS. 9A to 9C. FIG 9A shows a cross-section of camming having a narrow peak which induces valve lift similar to that depicted by the curve of FIG. 4 while FIG. 9C shows a cross-section of camming which induces lift similar to that shown in FIG. 5. 
     The operation of the second embodiment is basically the same as that of the first wherein upon increased hydraulic fluid prevailing in the hydraulic cylinder 80 the cam shaft 84 is moved axially from a first axial position in which the narrow peak cams or lifts the inlet valve, toward a second axial position in which the wide peak (FIG. 9C) lifts said valve. 
     Of course this arrangement can also be applied to the exhaust valve in the case it is desired to control internal EGR. 
     It is also possible to employ other means than the hydraulic systems set forth hereinbefore, which may take the form of solenoids or the like controlled by electronic circuits in the form of microcomputers and the like. 
     It is also possible to apply various pieces of apparatus, such as the valve lifting apparatus shown in FIG. 2, to applications other than internal combustion engines since the arrangement inherently has the function of adding two mechanical inputs to provide a variable output.