US20040206331A1 - Engine valve actuator - Google Patents
Engine valve actuator Download PDFInfo
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- US20040206331A1 US20040206331A1 US10/788,431 US78843104A US2004206331A1 US 20040206331 A1 US20040206331 A1 US 20040206331A1 US 78843104 A US78843104 A US 78843104A US 2004206331 A1 US2004206331 A1 US 2004206331A1
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- Prior art keywords
- valve
- actuator
- engine
- fluid
- cylinder
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
- F01L13/065—Compression release engine retarders of the "Jacobs Manufacturing" type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2305/00—Valve arrangements comprising rollers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2800/00—Methods of operation using a variable valve timing mechanism
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2800/00—Methods of operation using a variable valve timing mechanism
- F01L2800/10—Providing exhaust gas recirculation [EGR]
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/32—Miller cycle
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- This disclosure relates generally to internal combustion engines and, more particularly, to engine valve actuators.
- an internal combustion engine requires, among other things, the timed opening and closing of a plurality of valves.
- a typical four-stroke, diesel engine one of ordinary skill in the art will readily recognize such an engine operates through four distinct strokes of a piston reciprocating through a cylinder, with intake and exhaust valves operating in conjunction with the piston.
- intake stroke the piston descends through the cylinder while an intake valve is open.
- the resulting vacuum draws air into the cylinder.
- the piston reverses direction while the intake valve and an exhaust valve are closed, thereby compressing the air within the cylinder.
- the exhaust valve is opened as the piston approaches a top dead center position during the compression stroke to, in effect, increase engine braking operation.
- the engine cylinders draw in air during the intake stroke, compress the air, and then vent the compressed air out of the exhaust valve near top dead center of the piston.
- Miller cycle Another mode of engine operation requiring atypical valve sequencing is known as the Miller cycle.
- the intake valve is held open during the initial stages of the compression stroke. Such operation reduces the effective compression ratio of the engine and results in a more mechanically efficient power producing engine.
- the intake valve is closed prior to completion of a normal intake stroke to provide Miller cycle benefits.
- Exhaust gas recirculation attempts to curtail such drawbacks of conventional engine operation.
- EGR exhaust gas recirculation
- the exhaust gases are expelled through the exhaust valve and reintroduced to the cylinder through the exhaust valve itself.
- Such a process requires that the exhaust valve stay open not only through the exhaust stroke, but also on the intake stroke, after the piston reverses direction, thereby creating a vacuum and drawing a portion of the exhaust gases back into the cylinder through the still open exhaust valve.
- the present disclosure is directed to overcoming one or more of the problems or disadvantages associated with the prior art.
- an engine valve assembly includes a valve seat and an engine valve element adapted to move relative to the valve seat between an open position and a closed position.
- a mechanically driven actuator can be adapted to move the valve element to the open position.
- a fluidically driven actuator can be adapted to prevent the valve element from moving to the closed position.
- the fluidically driven actuator can include an actuator piston reciprocatingly disposed in an actuator cylinder.
- the actuator piston can be adapted to maintain the engine valve element in an intermediate position between the closed position and the open position.
- the actuator cylinder is in fluid communication with a source of pressurized fluid. The source of pressurized is insufficient to move the valve element toward the open position in an internal combustion engine.
- a control valve can be adapted to pass the flow of the pressurized fluid to the actuator cylinder during movement of the valve element toward the open position.
- the valve is operable for maintaining the fluid in the actuator cylinder during movement of the valve element toward the closed position to maintain the valve at the intermediate position.
- a valve assembly includes an engine cylinder and an engine piston reciprocatingly movable relative to the engine cylinder.
- An engine valve element is disposed in a port that is connected to the engine cylinder.
- a source of low pressure fluid is in fluid communication with a fluidically driven valve actuator.
- a force generated by the source of low pressure fluid is sufficient to move the valve element and take up lash associated with the valve element and the valve actuator.
- An engine driven mechanical linkage mounted proximate the engine valve element is adapted to move the engine valve element to an open position.
- a control valve is adapted to control flow of the pressurized fluid from the source of low pressure fluid to the valve actuator.
- a variable valve actuator includes a valve positioned adjacent an engine cylinder and an engine driven mechanical actuator system adapted to move the valve between first and second positions.
- a fluidically driven valve actuator in predetermined intermittent fluid communication with a fluid pressurization source is provided.
- the fluidically driven actuator is adapted to prevent the valve from moving to the second position for a predetermined period of time.
- a control valve is adapted to shut off fluid communication between the fluid pressurization source and the fluidically driven valve actuator and to prevent fluid from back flowing out of the fluidically driven actuator causing the fluidically driven actuator to become hydraulically locked.
- a method of controlling an engine having at least one valve includes moving the valve from a first position to a second position with a mechanically driven actuator, moving the valve from the second position to an intermediate position between the first and second positions, and holding the valve in the intermediate position with a fluidically driven actuator in a hydraulically locked configuration.
- FIG. 1 is a diagrammatic cross-sectional view of an embodiment of an internal combustion engine showing an engine block, cylinder head and engine valve actuator;
- FIG. 2 is cross-sectional view of the engine of FIG. 1, taken along line 2 - 2 of FIG. 1;
- FIG. 3 is a schematic representation of an engine valve actuator shown in a first position
- FIG. 4 is a schematic representation of an engine valve actuator shown in a second position
- FIG. 5 is a schematic representation of an engine valve actuator shown in a third position
- FIG. 6 is a flow chart depicting a sample sequence of steps which may be taken to operate an internal combustion engine valve actuator
- FIG. 7 is a graph plotting valve lift vs. engine crank angle during normal operation
- FIG. 8 is a graph plotting valve lift vs. engine crank angle during internal exhaust gas recirculation operation
- FIG. 9 is a graph plotting valve lift vs. engine crank angle during Miller cycle operation.
- FIG. 10 is a schematic representation of an alternative engine valve actuator configuration.
- an embodiment of an internal combustion engine is generally referred to by reference numeral 20 . While the engine 20 is depicted and will be described in further detail herein with reference to a four stroke, internal combustion diesel engine, it is to be understood that the teachings of the disclosure can be, employed in conjunction with any other type of engine as well.
- the engine 20 may include a plurality of engine cylinders 22 in each of which is reciprocatingly mounted an engine piston 24 .
- an engine piston 24 In the depicted embodiment, six such engine cylinders 22 and six engine pistons 24 are depicted in aligned fashion, but it is to be understood that a greater or lesser number are possible, and that engine cylinder orientations other than in-line, such as, for example, a “V” configuration, are possible as well.
- a connecting rod 26 may be connected to each engine piston 24 , and in turn be connected to a crank shaft 27 so as to capitalize on the motion of the engine piston 24 to produce useful work in a machine (not shown) with which the engine 20 is associated.
- Each engine cylinder 24 may be provided within an engine block 28 having a cylinder head 30 , and may further include at least one intake valve 32 , and an exhaust valve 34 .
- FIGS. 2-5 the cylinder head 30 , and a pair of exhaust valves 34 are shown in greater detail for one of the engine cylinders 22 .
- a pair of exhaust ports 38 may be provided in the cylinder head 30 to allow for fluid communication into and out of the engine cylinder 22 .
- FIG. 1 depicts only one intake port 36 per cylinder 22 , it is to be understood that a pair of intake ports 36 are typically provided in each cylinder 22 in a manner similar to the exhaust ports 38 depicted in FIG. 2.
- air may be allowed to enter the engine cylinder 22 through the intake ports 36
- combustion or exhaust gases may be allowed to exit the engine cylinder 22 through the exhaust ports 38 .
- An intake valve element 40 may be provided within each intake port 36
- an exhaust valve element 42 may be provided within each exhaust port 38 .
- Each of the valve elements 40 , 42 may include a valve head 44 from which a valve stem 46 extends.
- the valve head 44 includes a sealing surface 48 adapted to seal against a valve seat 50 about a perimeter 52 of the valve ports 36 , 38 .
- the valve elements 40 , 42 further include a bridge 54 adapted to contact the valve stems 46 associated with each engine cylinder 22 .
- a valve spring 56 imparts force between the top of each valve stem 46 and the cylinder head 30 , thereby biasing the stem 46 away from the cylinder head 30 and thus biasing the valve head 44 into seating engagement with the corresponding valve seats 50 to close the intake and exhaust valves 32 , 34 .
- movement of the valve elements 40 , 42 is controlled not only by the springs 56 , but by a cam assembly 58 as well.
- rotation of the cam 60 periodically causes a push rod 62 to rise, thereby causing a rocker arm 64 , connected thereto, to pivot about a pivot 66 .
- an end 68 of the rocker arm 64 is caused to move downwardly and thereby open the exhaust valve element 42 .
- the cam 60 imparts sufficient force to the valve stem 46 to overcome the biasing force of the spring 56 and thereby push the valve head 44 away from the valve seat 50 , to open the exhaust valves 34 (or intake valve 32 ).
- Further rotation of the cam 60 allows the spring 56 to push the end 68 of the rocker arm 64 upward and the push rod 62 downward until the cam 60 completes another revolution.
- valve actuator 70 may be used to so hold the intake valve 32 and/or exhaust valve 34 open.
- the valve actuator 70 includes an actuator cylinder 72 in which an actuator piston 74 is reciprocatingly disposed.
- the actuator cylinder 72 may include an opening 79 , through which an actuator rod 78 may extend in the direction of the rocker arm 64 and the valve stem 46 as well.
- the actuator cylinder 72 may also include a port 80 providing access to an actuation chamber 82 .
- the port 80 is adapted to place the actuation chamber 82 into fluid communication with a low pressure fluid source 84 .
- the pressurized fluid may be lubrication oil of the engine 20 (typically at a pressure level less than one hundred pounds per square inch, for example, on the order of sixty to ninety pounds per square inch (413.7 KPa to 620.5 KPa)).
- Placement of the fluid source 84 into fluid communication with the actuation chamber 82 may be provided through a fluid passage 85 and be controlled by a control valve 88 .
- the control valve 88 may include an inlet 92 and an outlet 94 .
- the control valve 88 may be biased into a first position connecting the port 80 to the low pressure fluid source 84 and be actuated by a solenoid 95 to a second position disconnecting the port 80 from the low pressure fluid source 84 .
- the solenoid 95 may itself be actuated upon receipt of a control signal or the like from a main control or processor 96 (FIG. 1) of the engine 20 .
- the fluid source 84 may be in fluid communication with an oil drain, sump, or accumulator 97 , for example, via a check valve.
- the low pressure fluid source 84 when the control valve 88 is in the first position (FIG. 4), is able to fill the actuator chamber 82 sufficiently to move the actuator piston 74 so as to take up any lash 98 (FIG. 3) existing in the system, such as that between the actuator rod 78 and the valve stem 46 or between the actuator rod 78 and the rocker arm 64 .
- “Taking up any lash in the system” is defined herein to mean removing any space between movable components. In so doing, when it is desired to hold the exhaust valve 34 in an open position, the control valve 88 can be moved to the second position (FIG. 5) thereby disconnecting the inlet 92 and hydraulically locking the actuator 70 .
- the engine 20 can be used in a variety of applications.
- the engine 20 may be provided on board a prime-mover, vehicle or the like, or any type of machine requiring the provision of mechanical or electrical energy.
- Such machines may include, but are not limited to, earth moving machines, backhoes, graders, rock crushers, pavers, skid-steer loaders, cranes, trucks, and the like.
- the engine 20 can be operated so as to open an engine valve and hold an engine valve open in the following manner.
- a typical four-stoke, diesel cycle, internal combustion engine operates through four distinct strokes of the piston 24 through the cylinder 22 .
- FIG. 7 depicts the intake valve 32 and exhaust valve 34 lift of a typical diesel cycle engine wherein engine operation is plotted as seven hundred and twenty degrees of engine crank angle, and with each of the four strokes representing 180° of rotation of the crank shaft 27 . In so doing, air is drawn into the engine cylinder 22 , as indicated in a step 102 .
- step 116 This can be accomplished by allowing the cam assembly 58 to open the exhaust valve 34 according to a normal exhaust stroke as indicated above (step 116 ), and then using the actuator 70 to maintain the exhaust valve 34 in an open position. More specifically, as the cam assembly 58 moves to open the exhaust valve 34 , the rocker arm 64 pivots downwardly compressing the spring 56 . With the spring pressure overcome by the cam assembly 58 , the pressurized fluid flowing from the low pressure source 84 and filling the actuation chamber 82 is able to move the piston 74 . The piston 74 moves through the lash 98 until the actuator rod 78 engages the rocker arm 64 . This step is indicated by reference numeral 118 in FIG. 6.
- a “hydraulically locked” device is defined as a device having substantially no fluid flow and substantially no fluid leakage, and “backflow” is defined as fluid flow from the actuator 70 to the low pressure fluid source 84 .
- the actuator 70 may be hydraulically locked using any number of other devices including, but not limited to, check valves.
- a check valve 121 can be provided between the actuator 70 and the low pressure source 84 .
- the check valve allows the fluid from source 84 to enter the actuator cylinder 72 and move the actuator piston 74 , but not flow back to the source 84 .
- a normally closed control valve 122 may be provided also in communication with the low pressure source 84 (or drain 97 or atmosphere).
- solenoid 123 of the control valve 122 Upon actuation of solenoid 123 of the control valve 122 , the fluid pressure with the actuator cylinder 72 is able to flow to the low pressure source 84 or drain 97 . In so doing, the actuator piston 74 is able to move up, closing the valve 32 , 34 .
- the exhaust valve 34 is held open as the engine piston 24 ascends to a top dead center position, and remains open after the engine piston 24 reverses and descends while the intake valve 32 is opened, as indicated by steps 124 and 126 , respectively. A portion of the exhaust gases vented from the engine cylinder 22 through the exhaust valve 34 are thereby reintroduced to the engine cylinder 22 by the resulting pressure differential. This step is indicated by reference numeral 128 . After a predetermined stroke length (e.g., ninety degrees of a seven hundred and twenty degree four stroke cycle as shown in FIG. 8), the exhaust valve 34 is closed as indicated by a step 130 , while the intake valve 32 remains open to complete the intake stroke as explained above.
- a predetermined stroke length e.g., ninety degrees of a seven hundred and twenty degree four stroke cycle as shown in FIG. 8
- the exhaust valve 34 can be closed by switching the control valve 88 back to the first position (shown in FIG. 4) and thereby enabling the spring 56 to push the actuator piston 74 up, and the pressurized fluid out of, the actuator cylinder 72 . Normal engine operation may then resume, beginning with the compression stroke as indicated in FIG. 6.
- the intake valve 32 (or exhaust valve 34 ) may be held open during the initial stages of the compression stroke to thereby reduce the compression ratio of the engine and provide the engine efficiencies of the Miller cycle as well known by those of ordinary skill in the art.
- the intake valve 32 could be so held by employing the actuator 70 after the cam assembly 58 opens the intake valve during the intake stroke. More specifically, as the intake valve 32 is about to be closed by the spring 56 at the conclusion of a normal intake stroke, the control valve 88 could be actuated so as to prevent fluid flow from the actuator 72 back to the low pressure fluid source 84 . In so doing, the actuator piston 74 is locked in position, as is the intake valve 32 as depicted in FIG. 9.
Abstract
An engine with a lockable valve actuator and method of controlling an engine with such an actuator are disclosed. The actuator may include an actuator cylinder with an actuator piston reciprocatingly disposed therein. The actuator piston may be moved by directing pressurized fluid into the actuator cylinder, and locked into a given position by maintaining the pressurized fluid in the actuator cylinder. The actuator may be used in conjunction with a mechanically driven actuator used to move a valve, with the fluidically driven actuator being used to maintain the valve into a desired position.
Description
- This application is a continuation of U.S. patent application Ser. No. 10/067,030, which was filed on Feb. 4, 2002.
- This disclosure relates generally to internal combustion engines and, more particularly, to engine valve actuators.
- The operation of an internal combustion engine requires, among other things, the timed opening and closing of a plurality of valves. For example, with a typical four-stroke, diesel engine, one of ordinary skill in the art will readily recognize such an engine operates through four distinct strokes of a piston reciprocating through a cylinder, with intake and exhaust valves operating in conjunction with the piston. In an intake stroke, the piston descends through the cylinder while an intake valve is open. The resulting vacuum draws air into the cylinder. In a subsequent compression stroke, the piston reverses direction while the intake valve and an exhaust valve are closed, thereby compressing the air within the cylinder. This is followed by a combustion or power stroke wherein fuel is injected into the compressed air and thereby ignited, with the resulting force pushing the piston again in the descending direction while both the intake and exhaust valves are closed. Finally, the piston reverses direction with the exhaust valve open, thereby pushing the combustion gases out of the cylinder.
- In certain variations on the typical diesel or Otto cycle, it is desirable to open or close one of the intake and/or exhaust valves at alternative times. For example, in a compression release braking mode, the exhaust valve is opened as the piston approaches a top dead center position during the compression stroke to, in effect, increase engine braking operation. In so doing the engine cylinders draw in air during the intake stroke, compress the air, and then vent the compressed air out of the exhaust valve near top dead center of the piston.
- Another mode of engine operation requiring atypical valve sequencing is known as the Miller cycle. During the Miller cycle, the intake valve is held open during the initial stages of the compression stroke. Such operation reduces the effective compression ratio of the engine and results in a more mechanically efficient power producing engine. Alternatively, the intake valve is closed prior to completion of a normal intake stroke to provide Miller cycle benefits.
- One other situation modifying typical valve operation is internal exhaust gas recirculation. One disadvantage of diesel or Otto cycle engine operation is that all of the fuel brought into the cylinder and compressed may not entirely combust. Among other things, this phenomenon may be undesirable due to an unacceptably high level of pollutants, such as nitrous oxide (NOx) and particulates, being released during the exhaust stroke.
- Exhaust gas recirculation (hereinafter referred to as “EGR”) attempts to curtail such drawbacks of conventional engine operation. With EGR, at least a portion of the exhaust gases is not exhausted to the atmosphere, but rather is introduced back into the engine cylinder to be combusted in subsequent power or combustion strokes of the engine. With typical internal EGR, the exhaust gases are expelled through the exhaust valve and reintroduced to the cylinder through the exhaust valve itself. Such a process requires that the exhaust valve stay open not only through the exhaust stroke, but also on the intake stroke, after the piston reverses direction, thereby creating a vacuum and drawing a portion of the exhaust gases back into the cylinder through the still open exhaust valve.
- One of ordinary skill in the art will readily appreciate that a substantial force is required to open the exhaust valve and maintain the valve in an open position as the piston reciprocates through the cylinder toward the top dead center position. A valve actuator employing highly pressurized oil may be used to apply this force to open the exhaust valve.
- However, holding an exhaust valve in an open position by a valve actuator employing highly pressurized oil requires, for example, pressurized oil on the order of fifteen hundred to five thousand pounds per square inch (10.34 to 34.4 MPa). The engine or machine in which the engine has been mounted therefore has had to provide a high pressure source or high pressure rail and be able to supply the high pressure oil to the actuator when desired. Such a requirement has, among other things, the disadvantage, at least with respect to Miller cycle and EGR operation, of decreasing the engine efficiency in that the engine must continually direct usable work to the high pressure rail to maintain such pressures even though the high pressure oil is only required for a relatively short duration during the engine operation. Not only is the provision of such pressurized fluid taxing on the efficiency of the engine, but with certain machines the provision of such a high pressure rail is simply not available or desirable.
- The present disclosure is directed to overcoming one or more of the problems or disadvantages associated with the prior art.
- In accordance with one aspect of the disclosure, an engine valve assembly includes a valve seat and an engine valve element adapted to move relative to the valve seat between an open position and a closed position. A mechanically driven actuator can be adapted to move the valve element to the open position. A fluidically driven actuator can be adapted to prevent the valve element from moving to the closed position. The fluidically driven actuator can include an actuator piston reciprocatingly disposed in an actuator cylinder. The actuator piston can be adapted to maintain the engine valve element in an intermediate position between the closed position and the open position. The actuator cylinder is in fluid communication with a source of pressurized fluid. The source of pressurized is insufficient to move the valve element toward the open position in an internal combustion engine. A control valve can be adapted to pass the flow of the pressurized fluid to the actuator cylinder during movement of the valve element toward the open position. The valve is operable for maintaining the fluid in the actuator cylinder during movement of the valve element toward the closed position to maintain the valve at the intermediate position.
- In accordance with another aspect of the disclosure, a valve assembly includes an engine cylinder and an engine piston reciprocatingly movable relative to the engine cylinder. An engine valve element is disposed in a port that is connected to the engine cylinder. A source of low pressure fluid is in fluid communication with a fluidically driven valve actuator. A force generated by the source of low pressure fluid is sufficient to move the valve element and take up lash associated with the valve element and the valve actuator. An engine driven mechanical linkage mounted proximate the engine valve element is adapted to move the engine valve element to an open position. A control valve is adapted to control flow of the pressurized fluid from the source of low pressure fluid to the valve actuator.
- In accordance with another aspect of the disclosure, a variable valve actuator includes a valve positioned adjacent an engine cylinder and an engine driven mechanical actuator system adapted to move the valve between first and second positions. A fluidically driven valve actuator in predetermined intermittent fluid communication with a fluid pressurization source is provided. The fluidically driven actuator is adapted to prevent the valve from moving to the second position for a predetermined period of time. A control valve is adapted to shut off fluid communication between the fluid pressurization source and the fluidically driven valve actuator and to prevent fluid from back flowing out of the fluidically driven actuator causing the fluidically driven actuator to become hydraulically locked.
- In accordance with yet another aspect of the disclosure, a method of controlling an engine having at least one valve includes moving the valve from a first position to a second position with a mechanically driven actuator, moving the valve from the second position to an intermediate position between the first and second positions, and holding the valve in the intermediate position with a fluidically driven actuator in a hydraulically locked configuration.
- FIG. 1 is a diagrammatic cross-sectional view of an embodiment of an internal combustion engine showing an engine block, cylinder head and engine valve actuator;
- FIG. 2 is cross-sectional view of the engine of FIG. 1, taken along line2-2 of FIG. 1;
- FIG. 3 is a schematic representation of an engine valve actuator shown in a first position;
- FIG. 4 is a schematic representation of an engine valve actuator shown in a second position;
- FIG. 5 is a schematic representation of an engine valve actuator shown in a third position;
- FIG. 6 is a flow chart depicting a sample sequence of steps which may be taken to operate an internal combustion engine valve actuator;
- FIG. 7 is a graph plotting valve lift vs. engine crank angle during normal operation;
- FIG. 8 is a graph plotting valve lift vs. engine crank angle during internal exhaust gas recirculation operation;
- FIG. 9 is a graph plotting valve lift vs. engine crank angle during Miller cycle operation; and
- FIG. 10 is a schematic representation of an alternative engine valve actuator configuration.
- Referring now to the drawings, and with specific reference to FIG. 1, an embodiment of an internal combustion engine is generally referred to by
reference numeral 20. While theengine 20 is depicted and will be described in further detail herein with reference to a four stroke, internal combustion diesel engine, it is to be understood that the teachings of the disclosure can be, employed in conjunction with any other type of engine as well. - The
engine 20 may include a plurality ofengine cylinders 22 in each of which is reciprocatingly mounted anengine piston 24. In the depicted embodiment, sixsuch engine cylinders 22 and sixengine pistons 24 are depicted in aligned fashion, but it is to be understood that a greater or lesser number are possible, and that engine cylinder orientations other than in-line, such as, for example, a “V” configuration, are possible as well. A connectingrod 26 may be connected to eachengine piston 24, and in turn be connected to a crankshaft 27 so as to capitalize on the motion of theengine piston 24 to produce useful work in a machine (not shown) with which theengine 20 is associated. Eachengine cylinder 24 may be provided within anengine block 28 having acylinder head 30, and may further include at least oneintake valve 32, and anexhaust valve 34. - Referring now to FIGS. 2-5, the
cylinder head 30, and a pair ofexhaust valves 34 are shown in greater detail for one of theengine cylinders 22. As shown therein, a pair ofexhaust ports 38 may be provided in thecylinder head 30 to allow for fluid communication into and out of theengine cylinder 22. In addition, while FIG. 1 depicts only oneintake port 36 percylinder 22, it is to be understood that a pair ofintake ports 36 are typically provided in eachcylinder 22 in a manner similar to theexhaust ports 38 depicted in FIG. 2. In normal engine operation, air may be allowed to enter theengine cylinder 22 through theintake ports 36, while combustion or exhaust gases may be allowed to exit theengine cylinder 22 through theexhaust ports 38. Anintake valve element 40 may be provided within eachintake port 36, while anexhaust valve element 42 may be provided within eachexhaust port 38. - Each of the
valve elements valve head 44 from which avalve stem 46 extends. Thevalve head 44 includes a sealingsurface 48 adapted to seal against avalve seat 50 about aperimeter 52 of thevalve ports valve elements bridge 54 adapted to contact the valve stems 46 associated with eachengine cylinder 22. Avalve spring 56 imparts force between the top of eachvalve stem 46 and thecylinder head 30, thereby biasing thestem 46 away from thecylinder head 30 and thus biasing thevalve head 44 into seating engagement with the corresponding valve seats 50 to close the intake andexhaust valves - As shown best in FIG. 2, movement of the
valve elements springs 56, but by acam assembly 58 as well. As one of ordinary skill in the art will readily recognize, rotation of thecam 60 periodically causes apush rod 62 to rise, thereby causing arocker arm 64, connected thereto, to pivot about apivot 66. In so doing, anend 68 of therocker arm 64 is caused to move downwardly and thereby open theexhaust valve element 42. Under normal engine operation, thecam 60 imparts sufficient force to thevalve stem 46 to overcome the biasing force of thespring 56 and thereby push thevalve head 44 away from thevalve seat 50, to open the exhaust valves 34 (or intake valve 32). Further rotation of thecam 60 allows thespring 56 to push theend 68 of therocker arm 64 upward and thepush rod 62 downward until thecam 60 completes another revolution. - In certain modes of engine operation, such as with the compression release braking, Miller cycle operation, and EGR referenced above, it is desirable for the intake and/or
exhaust valves cam 60. In such situations, avalve actuator 70 may be used to so hold theintake valve 32 and/orexhaust valve 34 open. As shown in FIGS. 3-5, one example of thevalve actuator 70 includes anactuator cylinder 72 in which anactuator piston 74 is reciprocatingly disposed. Theactuator cylinder 72 may include anopening 79, through which anactuator rod 78 may extend in the direction of therocker arm 64 and thevalve stem 46 as well. - The
actuator cylinder 72 may also include aport 80 providing access to anactuation chamber 82. Theport 80 is adapted to place theactuation chamber 82 into fluid communication with a lowpressure fluid source 84. In one embodiment, the pressurized fluid may be lubrication oil of the engine 20 (typically at a pressure level less than one hundred pounds per square inch, for example, on the order of sixty to ninety pounds per square inch (413.7 KPa to 620.5 KPa)). Placement of thefluid source 84 into fluid communication with theactuation chamber 82 may be provided through afluid passage 85 and be controlled by acontrol valve 88. Thecontrol valve 88 may include aninlet 92 and anoutlet 94. Thecontrol valve 88 may be biased into a first position connecting theport 80 to the lowpressure fluid source 84 and be actuated by asolenoid 95 to a second position disconnecting theport 80 from the lowpressure fluid source 84. Thesolenoid 95 may itself be actuated upon receipt of a control signal or the like from a main control or processor 96 (FIG. 1) of theengine 20. Thefluid source 84 may be in fluid communication with an oil drain, sump, oraccumulator 97, for example, via a check valve. - The low
pressure fluid source 84, when thecontrol valve 88 is in the first position (FIG. 4), is able to fill theactuator chamber 82 sufficiently to move theactuator piston 74 so as to take up any lash 98 (FIG. 3) existing in the system, such as that between theactuator rod 78 and thevalve stem 46 or between theactuator rod 78 and therocker arm 64. “Taking up any lash in the system” is defined herein to mean removing any space between movable components. In so doing, when it is desired to hold theexhaust valve 34 in an open position, thecontrol valve 88 can be moved to the second position (FIG. 5) thereby disconnecting theinlet 92 and hydraulically locking theactuator 70. Pressure within theengine cylinder 22 imparts force on theexhaust valve 34, and in turn theactuator rod 78, but the fluid within theactuator cylinder 72, being incompressible and locked, holds theactuator piston 74, and thus the exhaust valve 34 (or intake valve 32), in the open position. - In operation, the
engine 20 can be used in a variety of applications. For example, theengine 20 may be provided on board a prime-mover, vehicle or the like, or any type of machine requiring the provision of mechanical or electrical energy. Such machines may include, but are not limited to, earth moving machines, backhoes, graders, rock crushers, pavers, skid-steer loaders, cranes, trucks, and the like. - Referring now to FIG. 6, in conjunction with FIGS. 2-5, the
engine 20 can be operated so as to open an engine valve and hold an engine valve open in the following manner. By way of background, one of ordinary skill in the art will understand that a typical four-stoke, diesel cycle, internal combustion engine operates through four distinct strokes of thepiston 24 through thecylinder 22. - In a first or intake stroke, the
engine piston 24 descends through theengine cylinder 22 away from thecylinder head 30 while theintake valve 32 is opened by thecam assembly 58, as indicated insteps intake valve 32 andexhaust valve 34 lift of a typical diesel cycle engine wherein engine operation is plotted as seven hundred and twenty degrees of engine crank angle, and with each of the four strokes representing 180° of rotation of thecrank shaft 27. In so doing, air is drawn into theengine cylinder 22, as indicated in astep 102. - In a second or compression stroke, the
engine piston 24 reverses its motion, at the direction of therod 26, while theintake valve 32 andexhaust valve 34 are closed withsprings 56. Such steps are indicated byreference numerals engine piston 24 ascends through theengine cylinder 22 toward thecylinder head 30, air is compressed (as indicated by a step 110). - In a third or combustion stroke, fuel is injected directly into the compressed air and thereby is ignited, as indicated by a
step 112. The resulting explosion and expanding gases push theengine piston 24 again in a descending direction (as indicated by a step 113) through theengine cylinder 22, while the intake andexhaust valves - In a fourth or exhaust stroke, the
engine piston 24 again reverses and ascends through theengine cylinder 22, but with theexhaust valve 34 open by thecam assembly 58, thereby pushing the combustion gases out of theengine cylinder 22. Such steps are indicated in FIG. 6 assteps - With certain engine operation variations, such as compression release braking, Miller cycle operation, and EGR, it may be desirable to alter the above valve timing and hold one or more valves open against substantial cylinder pressures. The teachings of the present disclosure enable such operation, without resort to highly pressurized oil rails, thereby preserving engine efficiency and simplicity. Taking internal EGR as an example, it is necessary in such operation for the exhaust valve34 (or intake valve 32) to remain open throughout not only the exhaust stroke, but during an interim period between when the
exhaust valve 34 is normally closed and when theintake valve 32 opens to conduct the intake stroke. FIG. 8 depicts such altered valve timing in graphical form. - This can be accomplished by allowing the
cam assembly 58 to open theexhaust valve 34 according to a normal exhaust stroke as indicated above (step 116), and then using theactuator 70 to maintain theexhaust valve 34 in an open position. More specifically, as thecam assembly 58 moves to open theexhaust valve 34, therocker arm 64 pivots downwardly compressing thespring 56. With the spring pressure overcome by thecam assembly 58, the pressurized fluid flowing from thelow pressure source 84 and filling theactuation chamber 82 is able to move thepiston 74. Thepiston 74 moves through thelash 98 until theactuator rod 78 engages therocker arm 64. This step is indicated byreference numeral 118 in FIG. 6. - In order to hold the
exhaust valve 34 in such a position even after thecam 60 rotates to another position, thecontrol valve 88 is switched from the first position (shown in FIG. 4) to the second position (shown in FIG. 5), as indicated by astep 120. In so doing, the fluid is locked from escaping theactuation chamber 82 and, due to its incompressibility, prevents theactuator piston 74 from moving and, thus, prevents theexhaust valve 34 from closing. As used herein, a “hydraulically locked” device is defined as a device having substantially no fluid flow and substantially no fluid leakage, and “backflow” is defined as fluid flow from theactuator 70 to the lowpressure fluid source 84. - In addition to the above example, the
actuator 70 may be hydraulically locked using any number of other devices including, but not limited to, check valves. For example, as shown in FIG. 10, acheck valve 121 can be provided between the actuator 70 and thelow pressure source 84. The check valve allows the fluid fromsource 84 to enter theactuator cylinder 72 and move theactuator piston 74, but not flow back to thesource 84. In conjunction with such structure, a normally closedcontrol valve 122 may be provided also in communication with the low pressure source 84 (or drain 97 or atmosphere). Upon actuation of solenoid 123 of thecontrol valve 122, the fluid pressure with theactuator cylinder 72 is able to flow to thelow pressure source 84 ordrain 97. In so doing, theactuator piston 74 is able to move up, closing thevalve - Continuing with the example of EGR, the
exhaust valve 34 is held open as theengine piston 24 ascends to a top dead center position, and remains open after theengine piston 24 reverses and descends while theintake valve 32 is opened, as indicated bysteps engine cylinder 22 through theexhaust valve 34 are thereby reintroduced to theengine cylinder 22 by the resulting pressure differential. This step is indicated byreference numeral 128. After a predetermined stroke length (e.g., ninety degrees of a seven hundred and twenty degree four stroke cycle as shown in FIG. 8), theexhaust valve 34 is closed as indicated by astep 130, while theintake valve 32 remains open to complete the intake stroke as explained above. Theexhaust valve 34 can be closed by switching thecontrol valve 88 back to the first position (shown in FIG. 4) and thereby enabling thespring 56 to push theactuator piston 74 up, and the pressurized fluid out of, theactuator cylinder 72. Normal engine operation may then resume, beginning with the compression stroke as indicated in FIG. 6. - The teachings of the present disclosure can also be used to provide Miller cycle benefits. As illustrated in FIG. 9, the intake valve32 (or exhaust valve 34) may be held open during the initial stages of the compression stroke to thereby reduce the compression ratio of the engine and provide the engine efficiencies of the Miller cycle as well known by those of ordinary skill in the art. The
intake valve 32 could be so held by employing theactuator 70 after thecam assembly 58 opens the intake valve during the intake stroke. More specifically, as theintake valve 32 is about to be closed by thespring 56 at the conclusion of a normal intake stroke, thecontrol valve 88 could be actuated so as to prevent fluid flow from theactuator 72 back to the lowpressure fluid source 84. In so doing, theactuator piston 74 is locked in position, as is theintake valve 32 as depicted in FIG. 9. - One of ordinary skill in the art will understand that significant force is required to open the intake and
exhaust valves engine cylinder 22 and thus against thevalves actuator 70, and its ability to become hydraulically locked, is able to hold thevalves - Other aspects and features of the present disclosure can be obtained from a study of the drawings, the disclosure, and the appended claims.
Claims (20)
1. An engine valve assembly, comprising:
a valve seat;
an engine valve element adapted to move relative to the valve seat between an open position and a closed position;
a mechanically driven actuator being adapted to move the valve element to the open position;
a fluidically driven actuator being adapted to prevent the valve element from moving to the closed position, the fluidically driven actuator including an actuator piston reciprocatingly disposed in an actuator cylinder, the actuator piston adapted to maintain the engine valve element in an intermediate position between the closed position and the open position, the actuator cylinder being in fluid communication with a source of pressurized fluid, the source of pressurized being insufficient to move the valve element toward the open position in an internal combustion engine; and
a control valve adapted to pass the flow of the pressurized fluid to the actuator cylinder during movement of the valve element toward the open position, and maintain the fluid in the actuator cylinder during movement of the valve element toward the closed position to maintain the valve at the intermediate position.
2. The engine valve assembly of claim 1 , including a spring connected to the engine valve element and biasing the engine valve element toward the closed position.
3. An engine valve assembly, comprising:
an engine valve element disposed in a port connected to an engine cylinder;
a fluidically driven valve actuator;
a source of low pressure fluid in fluid communication with the valve actuator, a force generated by the source of low pressure fluid being sufficient to move the valve element and take up lash associated with the valve element and the valve actuator;
an engine driven mechanical linkage mounted proximate the engine valve element and adapted to move the engine valve element to an open position; and
a control valve adapted to control flow of the pressurized fluid from the source of low pressure fluid to the valve actuator.
4. The engine valve assembly of claim 3 , wherein the valve actuator includes an actuator cylinder and an actuator plunger reciprocatingly disposed in the actuator cylinder.
5. The engine valve assembly of claim 3 , wherein the valve actuator includes an actuator piston reciprocatingly disposed in an actuator cylinder, the actuator piston having a rod operatively associated therewith and being adapted to maintain the engine valve element in an intermediate position between a closed position and the open position.
6. The valve assembly of claim 3 , including a coil spring mounted about the valve element to bias the valve element toward a closed position.
7. The valve assembly of claim 3 , wherein the source of low pressure fluid is a lubrication oil system of the engine.
8. The valve assembly of claim 3 , wherein the mechanical linkage is actuated by a cam shaft.
9. A variable valve actuator system, comprising:
a valve positioned adjacent an engine cylinder;
an engine driven mechanical actuator system adapted to move the valve between first and second positions;
a fluid pressurization source;
a fluidically driven valve actuator in predetermined intermittent fluid communication with the fluid pressurization source, the fluidically driven actuator adapted to prevent the valve from moving to the second position for a predetermined period of time;
a control valve adapted to shut off fluid communication between the fluid pressurization source and the fluidically driven valve actuator and to prevent fluid from back flowing out of the fluidically driven actuator causing the fluidically driven actuator to become hydraulically locked.
10. The variable valve actuator system of claim 9 , wherein the source of pressurized fluid is a lubrication oil system for an engine.
11. The variable valve actuator system of claim 9 , wherein the mechanical actuation system includes a cam shaft to move the valve from the first position to the second position; and
a compression spring to move the valve from the second position to the first position when the fluidically driven actuator is not hydraulically locked.
12. A method of controlling an engine having at least one valve, comprising:
moving the valve from a first position to a second position with a mechanically driven actuator;
moving the valve from the second position to an intermediate position between the first and second positions; and
holding the valve in the intermediate position with a fluidically driven actuator in a hydraulically locked configuration.
13. The method of claim 12 , wherein holding the valve in the intermediate position comprises:
transporting pressurized fluid from a fluid pressurization source to the fluidically driven actuator;
removing fluid communication between the fluid source and the fluidically driven actuator; and
hydraulically locking the fluid in the fluidically driven actuator by preventing fluid backflow from the fluidically driven actuator.
14. The method of claim 13 , wherein preventing backflow is performed by a control valve.
15. The method of claim 12 , including holding an intake valve in the intermediate position with the hydraulically locked actuator.
16. The method of claim 12 , including holding an exhaust valve in the intermediate position with the hydraulically locked actuator.
17. The method of claim 12 , wherein moving the valve from the first position to the second position includes using a mechanical linkage.
18. The method of claim 12 , wherein moving the valve from the first position to the second position includes the step of using a mechanical linkage having a cam.
19. The method of claim 12 , wherein holding the valve in the intermediate position includes using a hydraulically locked actuator having an actuator cylinder and an actuator piston reciprocatingly disposed in the actuator cylinder, and wherein holding the valve in the open position includes directing fluid to the actuator cylinder, and preventing backflow of the fluid out of the actuator cylinder.
20. The method of claim 12 , wherein the pressurized fluid is lubrication oil of the engine.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US10/788,431 US20040206331A1 (en) | 2002-02-04 | 2004-02-27 | Engine valve actuator |
US10/992,137 US20050247286A1 (en) | 2002-02-04 | 2004-11-19 | Combustion engine including fluidically-controlled engine valve actuator |
US11/504,774 US20070062193A1 (en) | 2002-02-04 | 2006-08-16 | Combustion engine including fluidically-controlled engine valve actuator |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/067,030 US6732685B2 (en) | 2002-02-04 | 2002-02-04 | Engine valve actuator |
US10/788,431 US20040206331A1 (en) | 2002-02-04 | 2004-02-27 | Engine valve actuator |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/067,030 Continuation US6732685B2 (en) | 2002-02-04 | 2002-02-04 | Engine valve actuator |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
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US10/933,300 Continuation-In-Part US7178492B2 (en) | 2002-02-04 | 2004-09-03 | Air and fuel supply system for combustion engine |
US10/992,137 Continuation-In-Part US20050247286A1 (en) | 2002-02-04 | 2004-11-19 | Combustion engine including fluidically-controlled engine valve actuator |
Publications (1)
Publication Number | Publication Date |
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US20040206331A1 true US20040206331A1 (en) | 2004-10-21 |
Family
ID=27658792
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
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US10/067,030 Expired - Lifetime US6732685B2 (en) | 2002-02-04 | 2002-02-04 | Engine valve actuator |
US10/788,431 Abandoned US20040206331A1 (en) | 2002-02-04 | 2004-02-27 | Engine valve actuator |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
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US10/067,030 Expired - Lifetime US6732685B2 (en) | 2002-02-04 | 2002-02-04 | Engine valve actuator |
Country Status (5)
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US (2) | US6732685B2 (en) |
EP (1) | EP1472437B1 (en) |
JP (1) | JP4404638B2 (en) |
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WO (1) | WO2003067036A1 (en) |
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US20050279301A1 (en) * | 2003-06-10 | 2005-12-22 | Caterpillar Inc. | System and method for actuating an engine valve |
US7055472B2 (en) | 2003-06-10 | 2006-06-06 | Caterpillar Inc. | System and method for actuating an engine valve |
US20050279329A1 (en) * | 2003-06-25 | 2005-12-22 | Caterpillar Inc. | Variable valve actuation control for operation at altitude |
US20060016413A1 (en) * | 2004-07-20 | 2006-01-26 | Denso Corporation | Engine controller for starting and stopping engine |
US20090199796A1 (en) * | 2006-06-30 | 2009-08-13 | Komatsu Ltd. | Engine valve device |
US20110214631A1 (en) * | 2008-11-20 | 2011-09-08 | Komatsu Ltd. | Variable valve device and method of controlling the same |
US20150204250A1 (en) * | 2012-09-25 | 2015-07-23 | Renault Trucks | Valve actuation mechanism and automotive vehicle equipped with such a valve actuation mechanism |
US9512786B2 (en) * | 2012-09-25 | 2016-12-06 | Renault Trucks | Valve actuation mechanism and automotive vehicle equipped with such a valve actuation mechanism |
Also Published As
Publication number | Publication date |
---|---|
JP4404638B2 (en) | 2010-01-27 |
US20030145812A1 (en) | 2003-08-07 |
JP2005517110A (en) | 2005-06-09 |
WO2003067036A1 (en) | 2003-08-14 |
US6732685B2 (en) | 2004-05-11 |
DE60336118D1 (en) | 2011-04-07 |
EP1472437B1 (en) | 2011-02-23 |
EP1472437A1 (en) | 2004-11-03 |
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Owner name: CATERPILLAR INC., ILLINOIS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:LEMAN, SCOTT A.;REEL/FRAME:015492/0967 Effective date: 20040605 |
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STCB | Information on status: application discontinuation |
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