FOUR-CYCLE ENGINES WITH TWO-CYCLE COMPRESSION RELEASE BRAKING

Abstract: An internal combustion engine has engine cylinder intake and exhaust valves that are operated by intake and exhaust cams via hydraulic linkages. The hydraulic linkages have selective lost motions that allow selective modification of the openings and closings of the engine cylinder valves. These modifications may also include complete omission of all response to particular lobes on the cams. The hydraulic linkages may be interconnected so that some intake valve openings are produced by an exhaust cam lobe and/or some exhaust valve openings are produced by an intake cam lobe. The linkages and linkage interconnections are preferably controlled electronically. The engine is preferably operable in either four-cycle positive power mode or two-cycle compression release engine braking mode. The intake cam may have plural lobes or only one lobe, while the exhaust cam may only have one lobe.

Description: FOUR-CYCLE ENGINES WITH TWO-CYCLE COMPRESSION RELEASE BRAKING Background of the Invention This invention relates to variable timing valve actuation systems for internal combustion engines, and more particularly to apparatus for controlling, adjusting, or modifying the intake and exhaust valve timing or other related characteristics fay hydraulically linking the timing*- of intake and exhaust systems with high speed electromagnetic valves to achieve compression release retarding effects during every crank shaft revolution. Commonly assigned and copending U.S. patent Application Serial No. 08/512,528 filed Au,gust 8, 1995 shows how lost motion in hydraulic linkages between engine cylinder valves and the mechanical inputs which normally control those valves can be selectively employed to modify the valve openings in relation to the normal inputs. These modifications can be of the timing or amount of valve openings, or the operating mode of the engine can be changed from positive power to compression release braking. However, if the engine is a four-cycle engine in positive power mode, it will also have four cycles in compression release engine braking mode. This means that it is only possible for each engine cylinder to produce one compression release event during every two revolutions of the engine crank shaft. Sickler U.S. Patent No. 4,572,114 shows apparatus for converting a four-cycle engine to two-cycle operation during compression release engine braking. This enables each engine cylinder to produce a compression release event during each revolution of the engine crank shaft, thereby approximately doubling the available compression release braking as compared to fourcycle braking. However, the Sickler apparatus is relatively complicated, employing, for example, two hydraulic connections (e.g., 136 and 212 in Figure 5 or 258 and 212 in Figure 7) to each valve opening mechanism. In view of the foregoing, it is an object of this invention to extend the operating principles of the above-mentioned concurrently filed application to facilitate selective operation of a fourcycle engine in two-cycle compression release engine braking mode. It is another object of this invention to extend the operating principles of the above- mentioned concurrently filed application to facilitate selective operation of a four-cycle engine in two-cycle compression release engine braking mode. Summary of the Invention These and other objects of the invention are accomplished in accordance with the principles of the invention by using hydraulic linkages with selective lost motion between the intake cams and intake valves and between the exhaust cams and exhaust valves of an internal combustion engine. Sufficient lobes may be provided on the cams to produce four-cycle positive power mode openings of the valves and two-cycle compression release engine braking mode operation of the engine, with the lost motion hydraulic linkages being operated to select either the four-cycle lobes or the two-cycle lobes. The hydraulic linkages for intake and exhaust valves may be selectively hydraulically interconnected to allow lobes on one type of cam to produce openings of the other type of valve when two-cycle operation is desired. This may allow the individual cam profiles to be somewhat simplified. The hydraulic linkages and the possible interconnections of those linkages are preferably controlled electronically (e.g., by a suitable programmed microprocessor). This control may be responsive not only to the desired mode of operation of the engine, but also to various engine or vehicle operating conditions so that the timings and/or extent of various valve openings can be adjusted and thereby optimized for current operating conditions in the current mode of operation of the engine. Further features of the invention, its nature and various advances will be more apparent from the accompanying drawings and the following detailed description of the preferred embodiments. Brief Description of the Drawings Figure 1 is a simplified schematic diagram of a representative portion of an illustrative embodiment of an internal combustion engine constructed in accordance with this invention. Figure 2a is a simplified diagram of the lobes on the intake cam in the Figure 1 apparatus. Figures 2b is a simplified diagram of the lobes on the exhaust cam in the Figure 1 apparatus. Figure 2c is a simplified diagram of illustrative engine cylinder valve openings in the Figure I apparatus during two-cycle compression release engine braking mode operation. Figure 2d is a simplified diagram of illustrative engine cylinder valve openings in the Figure 1 apparatus during four-cycle positive power mode operation. Figure 2e is a simplified diagram of illustrative signal traces in the apparatus of Figure 1 for controlling that apparatus to produce operation as shown in Figure 2c. Figure 2f is a simplified diagram of illustrative signal traces in apparatus of Figure 1 for controlling that apparatus to produce operation as shown in Figure 2d. Figure 3 is a view similar to Figure 1, but shows an alternative embodiment of the invention. Figure 4a through 4f are respectively similar to Figures 2a through 2f, but for the alternative embodiment shown in Figure 3. Figure 5 is another view similar to Figure 1, but shows another alternative embodiment of the invention. Figures 6a through 6f are respectively similar to Figures 2a through 2f, but for the alternative embodiment shown in Figure 5. Figure 7 is still another view similar to Figure 1, but shows still another .alternative embodiment of the invention. Figures 8a through 8f are respectively simitar to Figures 2a through 2f, but for the alternative embodiment shown in Figure 7. Figure 9a is a diagram of an illustrative engine cam profile which is useful in explaining certain operating principles of the invention. Figure 9b is a diagram shown several alternative hydraulic valve control signals synchronized with the engine cam profile in Figure 9a in accordance with this invention. Figure 9c is a diagram showing several alternative engine valve openings in response to the engine cam profile in Figure 9a and the hydraulic valve control signals in Figure 9b. Figure 10 is yet another view similar to Figure 1, but shows yet another alternative embodiment of the invention. Figures 11a through 1 If are respectively similar to Figures 2a through 2f, but for the alternative embodiment shown in Figure 10. Figure 12 is still yet another view similar to Figure 1, but shows still yet another alternative embodiment of the invention. Figure 13a through 13f are respectively similar to Figure 12, but for the alternative embodiment shown in Figure 10. Detailed Description of the Preferred Embodiments As shown in Figure 1, an illustrative internal combustion engine 10 constructed in accordance with this invention has an engine cylinder head 20 with intake and exhaust valves 30 and 60 mounted for vertical reciprocation therein. Both of the depicted valves 30 and 60 serve one representative cylinder in engine 10. Intake valve 30 is resiliently biased upwardly toward the depicted closed position by prestressed compression coil springs 32. Exhaust valve 60 is similarly resiliently biased upwardly toward the depicted closed position by prestressed compression coil springs 62. Valve 30 can be pushed down to pen it by downward motion of slave piston 58 Valve 60 can be pushed down to open it by downward motion of slave piston 88. Intake valve 30 has an associated rotating engine cam 40, and exhaust valve 60 similarly has an associated rotating engine cam 70. Intake and exhaust cams 40 and 70 rotate in synchronism with the crank shaft of the engine. Cams 40 and 70 have lobes 42 and 72 for producing openings of valves 30 and 60 as will be described in detail below. Each of cams 40 and 70 is operatively linked to the associated valve 30 and 60 by hydraulic circuitry. Pump 90 supplies pressurized hydraulic fluid to this circuitry from .sump 92. The hydraulic fluid may be engine lubricating oil, engine fuel, or any other suitable fluid. The output pressure of pump 90 is relatively low (e.g., 50 to 100 psi). This pressure is sufficient to fill the hydraulic circuit with fluid via check valves 94, 96, and 98, and to push master pistons 50 and 80 and slave pistons 58 and 88 out into contact with cams 40 and 70 and the tops of valves 30 and 60. However, the output pressure of pump 90 is not high enough to cause slave pistons 58 and 88 to open valves 30 and 60. When an intake cam lobe 42 passes master piston 50, that cam lobe pushes the master piston in. If electronically controlled hydraulic fluid valve 52 is open when this occurs, the hydraulic fluid displaced by master piston 50 escapes from hydraulic subcircuit 54 via valve 52 and is accumulated in hydraulic fluid accumulator 22. Accumulator 22 maintains a quantity of hydraulic fluid at approximately the outlet pressure of pump 90 for immediate refilling of the rest of the hydraulic circuity during return strokes of master pistons 50 and 80 which are not concurrent with return strokes of slave pistons 58 and 88. If accumulator 22 receives too much hydraulic fluid, its plunger moves down far enough to momentarily open a hydraulic fluid drain 24 back to sump 92. If, rather than being open as described immediately above, valve 52 is closed when a cam lobe 42 passes master pitton 50, hydraulic fluid is trapped in subcircuit 54. The pressure in this subcircuit therefore increases significantly, and the hydraulic fluid displaced by master piston 50 causes corresponding hydraulic displacement of slave piston 58. The resulting downward motion of the slave piston opens intake valve 30. When the above-mentioned lobe 42 has passed master piston 50, elements 50, 58, and 30 return to their original positions. Lobes 72 on exhaust cam 70 cooperate with valve 82 (similar to valve 52) to selectively produce openings of exhaust valve 60 in a manner similar to that described above for elements 40, 50, 52, 54, 58, and 30. Thus, if valve 82 is open when an exhaust cam lobe 72 passes master piston 80, the hydraulic fluid displaced by the master piston escapes from hydraulic subcircuit 84 to accumulator 22 via valve 82. This prevents slave piston 88 from opening exhaust valve 60. But if valve 82 is closed when an exhaust cam lobe 72 passes master piston 80, the pressure of the hydraulic fluid trapped in subcircuit 84 increases substantially. This causes slave piston 88 to move down and open valve 60. When the above-mentioned lobe 72 has passed master piston 80, elements 80, 88, .and 60 return to their original positions. The opening and closing of valves 52 and 82 (and other similar valves associated with the engine) is a controlled by electronic control circuit 100. Control circuit 100, which may include a suitably programmed microprocessor, receives inputs from engine and/or vehicle sensors 102. These inputs enable control circuit 100 to maintain basic synchronization with the engine. They also enable the driver of the vehicle to select the mode of operation of the engine (e.g., positive power mode or compression release engine braking mode). These inputs may provide information about various variable engine and/or vehicle operating parameters such as engine and/or vehicle speed. Control circuit 100 responds to its inputs by selecting the openings and closings of valves 52 and 82 that are appropriate to cause valves 30 and 60 to ope and close as required for the desired engine operating mode. Control circuit 100 may also respond to these inputs by adjusting the timing and duration of the openings and closings of valves 52 and 82 so that the openings and closings of valves 30 and 60 are modified (e.g., with respect to timing, duration and/or height) to optimize engine performance for current engine and/or vehicle operating conditions. Examples of the foregoing principles will now be discussed in connection with Figures 2a through 2f. Figure 2a shows the profile of intake cam 40 plotted against engine crankangle. (The same crankangle scale shown in Figure 2a applies for all of the Figure 2 group. Top dead center of the compression stroke of the associated engine cylinder in four-cycle positive power mode is at O° and again at 720 β .) Figure 2b shows the profile of exhaust cam 70. Figure 2c .shows the openings of valves 30 and 60 that are produced during two-cycle compression release engine braking mode. (In Figure 2c, and other similar figures, each opening of valve 30 is identified by the reference number 30, and each opening of valve 60 is identified by the reference number 60. The suffix letters "a" or "b" are used in Figure 2c and similar figures to indicate whether the valve opening is due to the "a" or "b" lobe on the associated cam 40/70.) Figure 2c shows that intake valve 30 opens during each downward stroke of the associated engine piston in order to admit air to the associated engine cylinder. Figure 2c further shows that exhaust valve 60 is opened near the end of each upward stroke of the associated engine piston to produce a release of compressed air to the exhaust manifold of the engine. A compression release event is therefore produced during each 360 degrees of rotation of the engine crank shaft, thereby producing two-cycle compression release engine braking. With compression release events thus occurring twice as frequently as in the case of four-cycle engine braking, approximately twice as much engine and vehicle retarding horsepower is available as compared to four-cycle compression release engine braking. Figure 2d shows the openings of valves 30 and 60 that are produced during four-cycle positive power mode operation of the engine. Figure 2e shows the signal traces produced by control circuit 100 for controlling valves 52 (lower signal trace t52) and 82 (upper signal trace t82) during compression release engine braking mode operation of the engine. In these (and other similar signal traces) the valve 52 or 82 is closed when the associated signal trace is low, and the valve is open when the signal trace is high. In Figure 2e the signal for controlling valve 52 is low at all times. Valve 52 is therefore closed at all times during compression release engine braking, and intake valve 30 opens in response to both of intake cam lobes 42a and 42b. The signal for controlling valve 82, on the other hand, is high during the initial portion of exhaust cam lobe 72a and low during a trailing portion of that cam lobe (which includes an additional prominence 72a') and at all other times. Valve 82 is therefore open during the initial portion of cam lobe 72a but closed during additional prominence 72a' and during lobe 72b. Exhaust valve 60 accordingly remains closed during the initial portion of lobe 72a' and during lobe 72b. Exhaust valve 60 accordingly remains closed during the initial portion of lobe 72a, but opens (as at 60a in Figure 2c) in response to additional prominence 72a'. Exhaust valve 60 also opens (as at 60b in Figures 2c) in response to lobe 72b. Figure 2f shows the signal traces produced by control circuit 100 for controlling valves 52 (lower signal trace t52) and 82 (upper signal trace t82) during positive power-mode operation of the engine. The signal for controlling valve 52 is high during intake cam lobe 42a but low during intake cam lobe 42b. Valve 52 is therefore open during lobe 42a but closed during lobe 42b. This allows intake valve 30 to completely ignore lobe 42a by remaining closed during that lobe. Valve 30 does, however, open (as at 30b in Figure 2d) in response to lobe 42b. The signal for controlling valve 82 in Figure 2f is high during exhaust cam lobe 72b and the latter portion of exhaust cam lobe 72a. At other times this signal is low. Valve 82 is therefore open during lobe 72b and the latter portion of lobe 72a but closed during the initial portion of lobe 72a. This allows exhaust valve 60 to remain closed during lobe 72b, thereby completely ignoring that lobe. Exhaust valve 60 opens (as at 60a in Figure 2d) in response to the initial portion of lobe 72a, but it ignores the trailing prominence 72a' on that lobe and instead closes by about crank angle 360°. In addition to opening and closing valves 52 and 82 as described above in connection with Figure 2 to select which cam lobes engine cylinder valves 30 and 60 respond to, control circuit 100 can m.ake more subtle modifications in the timings of the operation of valves 52 and 82 to produce more subtle changes in the openings and closings of valves 30 and 60. For example, the staπ of a compression release event such as 60a or 60b in Figure 2c can be delayed, relative to the stan of the associated cam feature by delaying the closing of valve 82 somewhat relative to the stan of that cam feature. Similarly, a valve 30 or 60 can be closed early by opening the associated valve 52 or 82 before the end the cam feature that produced that engine valve opening. The distance that a valve 30 or 60 opens can also be selectively reduced by, for example, opening the associated valve 52 or 82 briefly before or as the peak of a cam feature is reached. It may be desirable to make these kinds of changes in engine valve operation to optimize the engine for various engine and/or vehicle operating conditions (e.g., changes in engine and/or vehicle speed). For example, such changes may optimize the amount of engine braking produced for various engine speeds or, in positive power mode, may optimize fuel consumption and/or engine emissions for various engine speeds. Control circuit 100 may be programmed to perform various algorithms or look up table operations to determine the precise engine valve timings that are most appropriate for the current values of the inputs 102 it is receiving. Control circuit 100 then produces the signals applied to valves 52 and 82 that are required to produce those engine valve timings. The various kinds of more subtle modification of engine valve operation in relation to engine cam features that have just been described are further described and illustrated in above- mentioned Application Serial No. 08/512,528, which is incorporated by reference herein. It will be seen from the foregoing that the apparatus of this invention provides a simple and effective way to operate an internal combustion engine in either four-cycle positive power mode or two-cycle compression release engine braking mode, as well as to make more subtle modifications of valve timing relative to cam features. Figure 3 shows .an alternative embodiment of the invention in which pan of an intake cam lobe is used during compression release engine braking to produce a compression-releasing exhaust valve opening. The apparatus 10a shown in Figure 3 has many similarities to the Figure 1 apparatus, and the same reference numbers are used for basically similar elements in both Figures. In addition to electronically controlled hydraulic fluid valves 52 and 82, the apparatus shown in Figure 3 has another electronically controlled hydraulic fluid divener or valve 110 which can be switched to hydraulically connect either its ports A and B or its ports A and C. Port C is connected to hydraulic subcircuit 84 via conduit 112. Like valves 52 and 82, valve 110 is controlled by electronic control circuit 100. The operation of the apparatus showα in Figure 3 will now be explained with reference to Figures 4a through 4f (respectively similar to Figures 2a through 2f). Figure 4a shows the profile of intake cam 40 in Figure 3. Note that, as is often the case in conventional engines, intake cam lobe 42b begins somewhat before top dead center of the exhaust stroke (i.e., somewhat before crankangle 360"). Figure 4b shows the profile of exhaust cam 70 in Figure 3. Note that exhaust cam lobe 72a in Figure 4 does not require die additional trailing prominence 72a' shown in Figure 2b. Figure 4c shows the openings of intake and exhaust valves 30 and 60 during two-cycle compression release engine braking operation of engine 10a. This pattern is very similar to the pattern shown in Figure 2c, except that exhaust valve opening 60x (which takes the place of exhaust valve opening 60a in Figure 2c) is produced by an initial portion of intake cam lobe 42b as will be more fully described in connection with Figure 4e. Figure 4d shows the openings of intake and exhaust valves 30 and 60 during four-cycle positive power mode operation of engine 10a. Figure 4e shows the signal traces produced by control circuit 100 during two-cycle compression release engine braking mode operation of engine 10a to control valve 52 (bottom signal trace t52), valve 82 (middle signal trace t82), and valve 110 (top signal trace tl 10). As in similar Figure 2e, each of the lower signal traces in Figure 4e is low when the associated valve 52 or 82 is closed, and high when the associated valve is open. The top signal trace in Figure 4e is low when valve 110 hydraulically connects its ports A and B, and high when valve 110 hydraulically connects its ports A and C. The bottom signal trace is low at all times in Figure 4e. The middle signal trace is low except during the initial portion of exhaust cam lobe 72a. The top signal trace causes valve 110 to connect its A and B ports at all times except during an initial portion of intake cam lobe 42 b. Figure 4f shows the signal traces produced by control circuit 100 during four-cycle positive power mode operation of engine 10a. Again, the bottom signal t52 in Figure 4f controls valve 52, the middle signal t82 controls valve 82, and the top signal tl 10 controls valve 110. The bottom signal trace is high during intake cam lobe 42a, which causes intake valve 30 to completely ignore intake cam lobe 42a. However, this signal is low during lobe 42b so that intake valve 30 opens in response to that lobe as shown at 30b in Figure 4d. The middle signal trace in Figure 4f is low except during exhaust cam lobe 72b. This causes exhaust valve 60 to open (as shown at 60a in Figure 4d) in response to exhaust cam lobe 72a, but to remain closed during lobe 72b. The top signal trace in Figure 4f is low at all times so that valve 110 connects its A and B gprts at all times. As a result of the signals shown in Figure 4e, intake valve 30 opens (as at 30a in Figure 4c) in response to intake cam lobe 42a and (as at 30b in Figure 4c) in response to at least a latter portion of intake cam lobe 42b. Also as a result of the signals shown in Figure 4d, exhaust valve 60 opens (as at 60b in Figure 4c) in response to exhaust cam lobe 72b. Exhaust valve 60 does not open during exhaust cam lobe 72a because valve 82 is open during the forward stroke of master piston 80 in response to that cam lobe. However, toward the end of lobe 72a valve 82 closes and valve 110 switches to its port A-C position. This allows high pressure hydraulic fluid propelled by master piston 50 at the start of intake cam lobe 42b to flow to slave piston 88, thereby opening exhaust valve 60 as shown at 60x in Figure 4c. As soon as an adequate exhaust valve opening 60x has been produced, valve 110 switches back to its port A-B position. This allows exhaust valve 60 to close and causes the remainder of the forward stroke of master piston 50 to produce the opening of intake valve 30 which is shown at 30b in Figure 4c. From the foregoing it will be seen that the apparatus of Figure 3 provides an alternative way of operating an engine in either four-cycle positive power mode or two-cycle compression release engine braking mode. In addition, any of the above-described more subtle types of modifications of engine valve response to cam features can also be implemented in the apparatus shown in Figure 3. Figure 5 shows another alternative embodiment of the invention in which part of an exhaust cam lobe is used during compression release engine braking to produce an extra intake valve opening. Once again, the apparatus 10b shown in Figure 5 has many similarities to the Figure 1 apparatus, and the same reference numbers are used for similar elements in both Figures. Apparatus 10b has an additional electronically controlled hydraulic fluid divener or valve 120 which can be switched to hydraulically connect either its ports A and B or its ports A and C. Port C is connected to hydraulic subcircuit 54 via conduit 122. Valve 120 is controlled by electronic control circuit 100. The operation of apparatus 10b will be explained with references to Figures 6a through 6f, which are respectively similar to Figures 2a through 2f or Figures 4a through 4f. Figures 5 and 6a show that intake cam 40 has only one lobe 42. Figures 5 and 6b show that exhaust cam 70 has two lobes 72a and 72b. Figure 6c shows that during two-cycle compression release engine braking, exhaust valve 60 opens at 60b in response to exhaust cam lobe 72b. Exhaust valve 60 also opens at 60a in response to an additional trailing prominence 72a' on lobe 72a. Intake valve 30 opens at 30x in response to an initial portion of exhaust cam lobe 72a and at 30b in response to intake cam lobe 42. Figure 6d shows that during four-cycle positive power mode, exhaust valve 60 opens at 60a in response to the initial portion of exhaust cam lobe 72a. Intake valve 30 opens at 30b in response to intake cam lobe 42. In Figures 6e and 6f the top signal trace tl20 controls valve 120. This trace is low for connection of valve port A to valve port B. This trace is high for connection of valve port A to valve port G- (In Figure 6f this trace is low at all times.) The bottom trace t52 in Figures 6e and 6f controls valve 52 (high for open; low for clo.sed). This trace is low at all times in both Figures 6e and 6f, but valve 52 could be opened momentarily to make the more subtle .adjustments of intake valve response as described above in connection with the other embodiments. The middle trace t82 in Figures 6e and 6f controls valve 82 (high for open; low for closed). As shown by the top trace 1120 in Figure 6e, valve 120 is switched to connect port A to port C during an initial portion of exhaust cam lobe 72a. This causes the initial portion of the forward stroke of master piston 80 in response to that lobe to open intake valve 30 as shown at 30x in Figure 6c. After a suitable opening 30x has been produced, valve 82 is opened to suppress the intermediate portion of lobe 72a and to allow valve 30 to re-close. Valve 120 is then returned to the condition in which it connects port A to port B. Valve 82 is re-closed when additional prominence 72a' is about to begin. Accordingly, additional prominence 72a' causes exhaust valve 60 to open as shown at 60a in Figure 6c. In Figure 6f the middle signal trace t82 shows that valve 82 is open during exhaust cam lobe 60b and the addition^ prominence 72a' on lobe 72a. This allows exhaust valve 60 to ignore these exhaust cam features during positive power mode operation of engine I0b. Once again, the more subtle timing modifications described above in connection with the other embodiments can also be employed in die embodiment shown in Figure 5. Figures 6e .and 6f show valve 52 remaining closed at all times during both modes of operation of engine 10b. Valve 52 and d e hydraulic circuit path through that valve can therefore be eliminated from engine 10b if desired. On die other hand, it may be desired to retain valve 52 for the purpose of making certain of the more subtle timing modifications mentioned in the preceding paragraph. Still anoώer embodiment is shown in Figure 7. Elements that are similar to elements in previously described embodiments are again identified by die same reference numbers. Figures 8a through 8f relate to the embodiment shown in Figure 7 and are respectively similar to Figures 2a through 2f, Figures 4a through 4f, or Figures 6a through 6f. Figure 8a shows the profile of intake cam 40. Figure 8b shows the profile of exhaust cam 70. In the two-cycle compression release engine braking mode operation shown in Figure 8c exhaust valve opening 60b is produced by exhaust cam lobe 72b, while exhaust valve opening 60x is produced by an initial portion of intake cam lobe 42. Also in Figure 8c intake valve opening 30x is produced by d e initial portion of exhaust cam lobe 72a, while intake valve opening 30b is produced by die latter portion of intake cam lobe 42. In the four-cycle positive power mode operation shown in Figure 8d exhaust valve opening 60a is produced by exhaust cam lobe 72a, while intake valve opening 30b is produced by intake cam lobe 42. The signal traces shown in Figure 8e are for two-cycle engine braking, while Figure 8f shows these signal traces for four-cycle positive power mode operation. In Figures 8e and 8f the top trace t!20 is for control of valve 120 and the second trace tl 10 is for control of valve 110. In each case the trace is low for connection of valve ports A .and C. The third and fourth traces are for control of valves 82 and 52, respectively. In each case d e trace is low for closing the associated valve, and high for opening the associated valve. In order for exhaust cam lobe 72b to produce exhaust valve opening 60b in two-cycle compression release engine braking mode (Figure 2c), valve 82 is closed and valve 120 is in its A-B position during lobe 72b. In order for the initial portion of exhaust cam lobe 72a to produce intake valve opening 30x, valve 82 is closed and valve 120 is in its A-C position during tiiis portion of lobe 72a. This causes pressurized hydraulic fluid to flow from master piston 80 through valve 120 (ports A-C) and conduit 122 to slave piston 58, thereby opening intake valve 30. As soon as an adequate opening 30x of the intake valve has been produced, valve 82 is opened to release further hydraulic fluid pressure from master piston 80 to accumulator 22. Valve 120 may also then be restored to its A-B position. Valve 82 can be re-closed at any time after exhaust cam lobe 72a. In order for the initial portion of intake cam lobe 42 to produce exhaust valve opening 60x, valve 52 is closed and valve 110 is in its A-C position during this portion of lobe 42. This causes pressurized hydraulic fluid from master piston 50 to flow through valve 110 (ports A-C) and conduit 112 to slave piston 88, thereby opening exhaust valve 60 as shown at 60x in Figure 8c. As soon as an adequate opening of the exhaust valve has been produced, valve 52 opens briefly to vent some hydraulic fluid to accumulator 22. This allows exhaust valve 60 to re-close. Valve 110 is then returned to its A-B position and valve 52 is re- closed so that the remaining portion of intake cam lobe 42 causes intake valve 30 to open as shown at 30b in Figure 8c. In Figure 8f valves 110 and 120 remain in tiieir A-B positions at all times. Similarly, valve 52 remains closed at all times. Valve 82 is closed at all times except during exhaust cam lobe 72b when valve 82 is opened so tiiat exhaust valve 60 will not open in response to that lobe. Still anodier embodiment is shown in Figure 10. Elements that are similar to elements in previously described embodiments are again identified by die same referenced numbers. Figures 11a dirough 1 lb relate to die embodiment shown in Figure 10 and are respectively similar to Figures 2a dirough 2f, Figures 4a dirough 4f, Figures 6a dirough 6f, or Figures 8a dirough 8f. Figure 1 la shows die profile of intake cam 40. Figure 1 lb shows the profile of exhaust cam 70. In the two-cycle compression release engine braking mode operation shown in Figure 1 lc, exhaust valve opening 60b is produced by intake cam lobe 42b, while exhaust valve opening 60x is produced by an initial portion of intake cam lobe 42. Also in FIG 1 lc, intake valve opening 30x is produced by die initial portion of exhaust cam lobe 72a, while intake valve opening 30b is produced by die latter portion of intake cam lobe 42. In the four-cycle positive power mode operation shown in Figure l id, exhaust valve opening 60a is produced by exhaust cam lobe 72a, while intake vale opening 30b is produced by intake cam lobe 42. The signal traces shown in Figure 1 le are for two-cycle engine braking, while Figure 1 If shows tiiese signal traces for four-cycle positive power mode operation. In Figures 1 le and I If the top trace tl20 is for control of valve 120 and die second trace tllO is for control of valve 110. In each case the trace is low for connection of valve ports A and B, and die trace is high for connection of valve ports A and C. The third and fourth traces are for control of valves 82 and 52, respectively. In each case the trace is low for closing the .associated valve, and high for opening the associated valve. In order for intake cam lobe 42b to produce exhaust valve opening 60b in two-cycle compression release engine braking mode (Figure 1 lc), valve 52 is closed and valve 110 is in its A-C position during lobe 42b. In order for the initial portion of exhaust cam lobe 72a to produce intake valve opening 30x, valve 82 is closed and valve 120 is in its A-C position during this portion of lobe 72a. This causes pressurized hydraulic fluid to flow from master piston 80 through valve 120 (ports A-C) and conduit 122 to slave piston 58, thereby opening intake valve 30. As soon as an adequate opening 30x of the intake valve has been produced, valve 82 is opened to release further hydraulic fluid pressure from master piston 80 to accumulator 22. Valve 120 may also then be restored to its A-B position. Valve 120 may also then be restored to its A-B position. Valve 82 can be re-closed at any time after exhaust cam lobe 72a. In order for the initial portion of intake cam lobe 42a to produce exhaust valve opening 60x, valve 52 is closed and valve 110 is in its A-C position during this portion of lobe 42a. This causes pressurized hydraulic fluid from master piston 50 to flow through valve 110 (ports A-C) and conduit 112 to slave piston 88, thereby opening exhaust valve 60 as shown as 60x in FIG 1 lc. As soon as an adequate opening of the exhaust valve has been produced, valve 52 opens briefly to vent some hydraulic fluid to accumulator 22. This allows exhaust valve 60 to re-close. Valve 110 is then returned to its A-B position and valve 52 is re-closed so that the remaining portion of intake cam lobe 42a causes intake valve 30 to opening as shown at 30b in FIG 1 lc. In Figure 1 If valves 110 and 120 remain in their A-B positions at all times. Similarly, valve 82 remains closed at all times. Valve 52 is closed at all times except during intake cam lobe 42b when valve 52 is opened so that intake valve 30 will not open in response to that lobe. Control of valves 52, 82, 110, and 120 shown in Figure 10 may be carried out by control circuit 100, which may be a similar circuit as that described in the other embodiments of the invention. Still yet another embodiment is shown in Figure 12. Elements that are similar to elements in previously described embodiments are again identified by the same reference numbers. Figures 13a through 13f relate to the embodiment shown in Figure 12 and are respectively similar to Figures 2a through 2f, Figures 4a through 4f, Figures 6a through 6f, Figures 8a through 8f, and Figures 1 la through 1 If. Figure 13a shows the profile of intake cam 40 with lobe 42. Figure 13b shows the profile of exhaust cam 70 with lobe 72a. Superimposed on Figures 13a and 13b, respectively, in dashed lines, are remote intake and exhaust cam profiles, 242 and 272, respectively. Profiles 242 and 272 may originate with cams associated with other cylinders of the same engine 10c. In the two-cycle compression release engine braking mode operation shown in Figure 13c, exhaust valve opening 60b may be produced by a remote intake of exhaust cam lobe 242 or 272, while exhaust valve opening 60x may be produced by an initial portion of intake cam lobe 42. Also in Figure 13c intake valve opening 30x may be produced by the initial portion of exhaust cam lobe 72a, while intake valve opening 30b is produced by the latter portion of intake cam lobe 42. With renewed reference to opening 60b of Figure 13c, it should be noted that opening 60b may be alternatively opened by any energy source capable of providing the necessary energy to open the exhaust valve at the proper time. For example, with reference to Figure 12, opening 60b could be produced by hydraulic force stored in a common rail system associated with the engine 10c. The hydraulic force to open the exhaust valve for opening 60b may be provided through valve 140 from a hydraulic source 150 into hydraulic conduit 112. While the foregoing discussion identifies hydraulic source 150 as providing the necessary energy to open the exhaust valve 60 for opening 60b. it should be appreciated that alternate energy sources may be used without transgressing the intended scope of the invention. In the four-cycle positive power mode operation shown in Figure 13d, exhaust valve opening 60a is produced by exhaust cam lobe 72a, while intake valve opening 30b is produced by intake cam lobe 42. The signal traces shown in Figure 13e are for two-cycle engine braking, while Figure 13f shows these signal traces for four-cycle positive power mode operation. In Figures 13e and 13f the top trace 1140 is for control of valve 140, trace 1120 is for control of valve 120 and the trace tl 10 is for control of valve 110. In each case the trace is low for connection of valve ports A and B, and the trace is high for connection of valve ports A and C. The fourth and fifth traces are for control of valves 82 and 52, respectively. In each case the trace is low for closing the associated valve, and high for opening the associated valve. In order for remote cam lobe 272 to produce exhaust valve opening 60b in two-cycle compression release engine braking mode (Fig. 13c), valves 82, 52 and 110 are closed, valve 140 is open and valve 120 is in its A-C position. In order for the initial portion of exhaust cam lobe 72a to produce intake valve opening 30x, valve 82 is closed and valve 120 is in its A-C position during this portion of lobe 72a. This causes pressurized hydraulic fluid to flow from master piston 80 through valve 120 (ports A-C) and conduit 122 to slave piston 58, thereby opening intake valve 30. As soon as an adequate opening 30x of the intake valve has been produced, valve 82 is opened to release further hydraulic fluid pressure from master piston 80 to accumulator 22. Valve 120 may also then be restored to its A-B position. Valve 82 can be re- closed at any time after exhaust cam lobe 72a. In order for the initial portion of intake cam lobe 42 to produce exhaust valve opening 60x, valves 52 and 140 are closed and valve 110 is in its A-C position during this portion of lobe 42. This causes pressurized hydraulic fluid from master piston 50 to flow through valve 110 (ports A-C) and conduit 112 to slave piston 88, thereby opening exhaust valve 60 as shown at 60x in Figure 13c. As soon as an adequate opening of the exhaust valve has been produced, valve 52 opens briefly to vent some hydraulic fluid to accumulator 22. This allows exhaust valve 60 to re-close. Valve 110 is then returned to its A-B position and valve 52 is re-closed so that the remaining portion of intake cam lobe 42 causes intake valve 30 to open as shown at 30b in Figure 8c. It has been mentioned several times in the foregoing discussion that control of valves such as 52, 82, etc. can also be used to produce more subtle variations in engine valve timing, amount of engine valve opening, etc. The aforementioned Application Serial No. 08/512,528, which shows and describes this principle in somewhat related apparatus, has been incorporated by reference herein. Figures 9a-c herein also provide several examples of this principle. An illustrative engine cam profile is shown in Figure 9a. Various possible signals lor controlling trigger valves like 52, 82, etc. are shown in Figure 9b, which is synchronized with Figure 9a. These signals are respectively identified as a, b, c, and d. The various openings of an engine valve such as 30 or 60 in response to the Figure 9a cam profile and an associated, trigger valve controlled by the Figure 9b control signals are shown in Figure 9c. For example, the engine valve opens as shown at a in Figure 9c when the associated trigger valve is controlled by signal a in Figure 9b. Signal . keeps the trigger valve closed throughout the entirety of the engine cam, thereby causing the engine valve opening to follow the full engine cam profile. As shown at b. in Figure 9c, the engine valve opens by a lesser amount and closes earlier when the associated trigger valve is opened before the engine cam profile reaches its peak as shown by signal b_ in Figure 9b. As shown at c in FIG 9c, these trends are even more pronounced when the associated trigger valve is opened even earlier as shown by signal c in Figure 9b. As shown at d in FIG 9c, the opening of the engine valve can be delayed relative to the start of the engine cam profile by leaving the associated trigger valve open until after the cam profile has begun (see signal d in Figure 9b). Still other examples of these kinds of engine valve opening modifications are shown and described in the aforementioned Application Serial No. 08/512,528, which has been incorporated by reference herein. The systems of this invention can have an number of additional advantages. Use of the hydraulic lost motion to modify or eliminate certain positive cam motions and ".hereby alter engine valve timing and displacement may be useful to improve fuel economy in positive power mode. By closing certain engine valves earlier in cold weather in positive power mode, the system can be used as an engine warm-up device. During two-stroke engine braking mode operation the engine exhaust valves may be opened to allow reverse flow from the exhaust manifold into the engme cylinders. This supercharges the engine cylinders to increase engine braking performance. Changing exhaust valve timing in positive power mode operation of the engine can also be used to recirculate some exhaust gas and thereby reduce particle emissions. It will be understood that the foregoing is only illustrative of the principles of this invention and that various modifications can be made by those skilled in the art For example, Figures 1, 3, 5, 7, 10 and 12 all suggest that the engine has one intake and one exhaust valve 30 and 60 per engine cylinder. It is quite common for engines to have two intake and two exhaust valves per cylinder, and it will be readily apparent that this invention is equally applicable to such engines.

Claims: WE CLAIM: 1. An internal combustion engine comprising; an intake valve associated with a cylinder of safti engine; an exhaust valve associated with said cylinder; an intake cam having one lobe synchronized with possible openings of said intake valve; an exhaust cam having one lobe synchronized with possible openings of said exhaust valve; a first hydraulic linkage containing hydraulic fluid operatively coupled between said intake cam and said intake valve for selectively responding to said intake cam lobes by causing said intake valve to open; a second hydraulic linkage containing hydraulic fluid operatively coupled between said exhaust cam and said exhaust valve for selectively responding to said exhaust cam lobe by causing said exhaust valve to open; a first hydraulic fluid control for selectively controlling hydraulic fluid pressure in said first hydraulic linkage to selectively modify the openings of said intake valve in response to said intake cam lobes; and a second hydraulic fluid control for selectively controlling hydraulic fluid pressure in said second hydraulic linkage to selectively modify the openings of said exhaust valve in response to said exhaust cam lobes. 2. The apparatus defined in claim 1 wherein at least one of said hydraulic fluid controls comprises a valve for selec t ively releasing hydraulic fluid from the hydraulic linkage associated with that hydraulic fluid control. 3. The apparatus defined in claim 2 wherein said valve is an electrically operated valve controlled by electronic control circuity. 4. The apparatus defined in claim 1 further comprising: a sensor for monitoring an operating parameter of said engine and for producing an output signal indicative of said parameter, which output signal is appUed to one of said hydraulic fluid control circuitry for causing said hydrauUc fluid control to modify operation of one of said hydraulic linkages in accordance with said parameter. 5. The apparatus defined in claim 4 wherein said parameter includes an indica ti on of whether said engine is to be in positive power mode or compression release engine braking mode. 6. The apparatus defined in claim 5 wherein said hydraulic fluid control is responsive to said output signal of said sensor (1) by operating said valves to produce four-cycle posi t ive power mode operation of said engine when said signal indicates that said engine is to be in positive power mode, and (2) by operating said valves to produce two-cycle compression release engine braking mode operation of said engine when said signal indicates that said engine is to be in compression release engine braking mode. 7. The apparatus defined in claim 1 wherein at least one of said hydraulic linkages comprises: a master piston that reciprocates in response to the lobe or lobes on the cam to which that hydraulic linkage is operatively coupled; and a slave piston that selectively reciprocates in response to hydrauUc fluid pressure and flow in said hydraulic linkage in order to selectively open the valve to which the hydrauUc linkage is operatively coupled. 8. The apparatus defined in claim 1 wherein said second hydrauUc fluid control is selectively operable to allow said exhaust valve to remain completely closed in response to said lobe on said exhaust cam. 9. The apparatus defined in claim 1 wherein said first hydraulic fluid control is selectively operable to allow said intake valve to remain completely closed in response to any first one of said lobes on said intake cam and to open in response to any second one of said lobes on said intake cam. 10. The apparatus defined in claim 1 wherein said intake cam has a plurality of lobes and said exhaust cam has a single lobe. 11. The engine of claim 1 further comprising One or more additional lobes on said intake cam. 12. The apparatus defined in claim 11 wherein at least one of said hydrauUc fluid controls comprises a valve for selectively releasing hydraulic fluid from the hydraulic linkage associated with that hydraulic fluid control. 13. The apparatus defined in claim 12 wherein said valve is an electricaUy operated valve controlled by electronic control circuitry. 14. The apparatus defined in claim 11 further comprising: a sensor for monitoring an operating parameter of said engine and for producing na output signal indicative of said parameter which output signal is applied to none of said hydraulic fluid controls for causing .said hydrauUc fluid control to modify operation of one of said hydraulic linkages in accordance with said parameter. 15. The apparatus defined in claim 14 wherein said parameter includes an indication of whether said engine is to be in positive power mode or compression release engine braking mode. 16. The apparatus defined in claim 15 wherein said hydraulic fluid control is responsive to said output signal of said sensor (1) by operating said valves to produce four-cycle positive power mode operation of said engine when said signal indicates that said engine is to be in positive power mode, and (2) by operating said valves to produce two-cycle compression release engine braking mode operation of said engine when said signal indicates that said engine is to be in compression release engine braking mode. 17. The apparatus defined in claim 11 wherein at least one of said hydraulic linkages comprises: a master piston that reciprocates in response to the lobe or lobes on the « * τn to which that hydraulic linkage is operatively coupled; and a slave piston that selectively reciprocates in response to hydrauUc fluid pressure and flow in said hydrauUc linkage in order to selectively open the valve to which that hydraulic linkage is operatively coupled. 18. The apparatus defined in claim 1 wherein said second hydrauUc fluid control is selectively operable to allow said exhaust valve to remain completely closed in response to said lobe on said exhaust cam ad to open in response to said lobe on said exhaust cam. 19. The apparatus defined in claim 11 wherein said first hydraulic fluid control is selectively operable to allow said intake valve to remain completely closed in response to any first one of said lobes on said intake cam and to open in response to any second one of said lobes on said intake cam. 20. The apparatus defined in claim 1 1 further comprising a remote cam synchronized with possible openings of said intake and exhaust valves.

Inventors: HAORAN HU, HAORAN, HU
Applicants: DIESEL ENGINE RETARDERS INC, DIESEL ENGINE RETARDERS, INC.
Application year: 1997
Main classification: F01L9
IPC codes: F01L9, F01L13, F02B69, F02B75, F02D13