WO2012048279A1 - Soupape manchon unique pour piston avec capacité facultative de taux de compression variable - Google Patents

Soupape manchon unique pour piston avec capacité facultative de taux de compression variable Download PDF

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Publication number
WO2012048279A1
WO2012048279A1 PCT/US2011/055457 US2011055457W WO2012048279A1 WO 2012048279 A1 WO2012048279 A1 WO 2012048279A1 US 2011055457 W US2011055457 W US 2011055457W WO 2012048279 A1 WO2012048279 A1 WO 2012048279A1
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WO
WIPO (PCT)
Prior art keywords
valve
cylinder
piston
head
junk head
Prior art date
Application number
PCT/US2011/055457
Other languages
English (en)
Other versions
WO2012048279A4 (fr
Inventor
James M. Cleeves
Simon Jackson
Michael Hawkes
Michael A. Willcox
Original Assignee
Pinnacle Engines, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pinnacle Engines, Inc. filed Critical Pinnacle Engines, Inc.
Priority to CN2011800593105A priority Critical patent/CN103249920A/zh
Priority to EP11779008.9A priority patent/EP2625394B1/fr
Priority to US13/270,200 priority patent/US9650951B2/en
Publication of WO2012048279A1 publication Critical patent/WO2012048279A1/fr
Publication of WO2012048279A4 publication Critical patent/WO2012048279A4/fr

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Classifications

    • 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
    • F01L5/00—Slide valve-gear or valve-arrangements
    • F01L5/04—Slide valve-gear or valve-arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F01L5/06—Slide valve-gear or valve-arrangements with cylindrical, sleeve, or part-annularly shaped valves surrounding working cylinder or piston
    • 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
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/041—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of cylinder or cylinderhead positioning
    • F02B75/042—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of cylinder or cylinderhead positioning the cylinderhead comprising a counter-piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/04—Varying compression ratio by alteration of volume of compression space without changing piston stroke
    • 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
    • F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
    • F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
    • F02B25/08—Engines with oppositely-moving reciprocating working pistons

Definitions

  • the subject matter described herein relates generally to internal combustion engines and more particularly to those that include sleeve valves that can provide one or more of air and/or fuel intake and exhaust from a cylinder that contains a single piston.
  • a sleeve valve as employed in an internal combustion engine generally includes one or more machined sleeves that fit between a piston and a cylinder wall.
  • Conventional sleeve valves generally rotate and slide to periodically align one or more ports in the sleeve valve body with inlet and/or exhaust ports formed in the cylinder walls in accordance with the cycle requirements of the engine.
  • Sleeve valves have been described for use in opposed piston engines in which two pistons share a single cylinder such that no cylinder head is needed. For example, co-owned U.S. Patent No. 7,559,298, which is incorporated herein by reference, describes such an engine configuration.
  • a system which can be an internal combustion engine, includes a piston that moves, for example with a reciprocating motion within a cylinder of an internal combustion engine, a crankshaft connected to the piston by a connecting rod, a junk head disposed opposite the piston proximate to a first end of the cylinder, and a first sleeve valve associated with a first port connecting to a combustion chamber defined at least in part by a head of the piston, an internal surface of the junk head, and the first sleeve valve.
  • the crankshaft rotates under influence of movement of the piston in the cylinder in accordance with an engine speed commanded by a throttle control.
  • the first sleeve valve at least partially encircles the piston and opens and closes the first port by first movement between a first open position and a first closed position.
  • a first sealing edge of the first sleeve valve is urged into contact with a first valve seat at the first closed position such that the first sealing edge is closer to the first end of the cylinder at the first closed position than at the first open position.
  • the first movement includes the first sleeve valve temporarily ceasing its motion in a direction aligned with an axis of the cylinder at the first closed position and at the first open position.
  • a method includes opening a first sleeve valve associated with a first port connecting to a combustion chamber disposed within a cylinder of an internal combustion engine and defined at least in part by a head of a piston that moves within the cylinder, an internal surface of a junk head disposed proximate to a first end of the cylinder opposite the piston, and the first sleeve valve; closing the first sleeve valve; and rotating a crankshaft connected to the piston by a connecting rod such that the crankshaft rotates under influence of movement of the piston in the cylinder in accordance with an engine speed commanded by a throttle control.
  • the first sleeve valve at least partially encircles the piston.
  • the opening of the sleeve valve includes moving the first sleeve valve to an open position at which the first sleeve valve temporarily ceases its motion in a direction aligned with an axis of the cylinder.
  • the closing of the sleeve valve includes moving the first sleeve valve to a first closed position at which the first sleeve valve temporarily ceases its motion in the direction aligned with the axis of the cylinder and at which a sealing edge of the sleeve valve is urged into contact with a valve seat such that the sealing edge is closer to the first end of the cylinder at the closed position than at the open position.
  • a method includes monitoring operation characteristics of an internal combustion engine to generate engine data, receiving a throttle input from a throttle control of the internal combustion engine, determining a preferred compression ratio within the combustion chamber based on the engine data and the throttle input, and commanding a junk head translation system that varies a distance between a junk head and a top dead center position of a piston from a first cycle of the internal combustion engine to a second, later cycle of the internal combustion engine.
  • the internal combustion engine includes the piston moving in a cylinder and the junk head disposed proximate to a first end of the cylinder opposite the piston.
  • the commanding includes causing the junk head translation system to move the junk head closer to the top dead center position of the piston if the preferred compression ratio is greater than a current compression ratio and away from the top dead center position of the piston if the preferred compression ratio is less than the current compression ratio.
  • any or all of the following features can optionally be included in any feasible combination.
  • the movement of the first sleeve valve between the open position and the closed position can be substantially parallel to the central axis of the cylinder.
  • a coolant circulation system can optionally cause coolant to flow through one or more coolant channels in the junk head to maintain an internal surface of the junk head at or below a target junk head temperature.
  • An ignition source for example one or more spark plugs, can optionally be disposed in the junk head.
  • the system can also optionally include a second valve associated with a second port connecting to the combustion chamber. The second valve can optionally include either a second sleeve valve at least partially encircling the junk head, or one or more poppet valves disposed in the junk head.
  • the second sleeve can open and close the second port by second movement between a second open position and a second closed position.
  • the second closed position can optionally include a second sealing edge of the second sleeve valve being urged into contact with a second valve seat such that the second sealing edge is further from the first end of the cylinder at the second closed position than at the second open position.
  • the second movement can optionally include the second sleeve valve ceasing its motion in the direction aligned with the axis of the cylinder both at the second closed position and at the second open position.
  • the first port can optionally include an intake port through which at least one of intake air and an air-fuel mixture is delivered to the combustion chamber, and the second port can optionally include an exhaust port through which exhaust gases resulting from combustion of a combustion mixture in the combustion chamber are exhausted.
  • the second port can optionally include an intake port through which at least one of intake air and an air-fuel mixture is delivered to the combustion chamber, and the first port can optionally include an exhaust port through which exhaust gases resulting from combustion of a combustion mixture in the combustion chamber are exhausted.
  • An active cooling system associated with at least one of the first sleeve valve and the second valve can optionally be included to maintain the at least one of the first sleeve valve and the second valve at or below a target valve temperature.
  • the active cooling system can optionally include an oil supply tube inserted into a valve stem of the poppet valve to deliver oil near a valve head of the poppet valve and thereby maintain an internal surface valve head at or below the target valve head temperature.
  • a junk head translation system can optionally cause movement of the junk head in the cylinder such that a distance of the junk head from a top dead center position of the piston is variable from a first cycle of the internal combustion engine to a second, later cycle of the internal combustion engine.
  • a controller can be configured to perform operations that can include monitoring operation characteristics of the internal combustion engine to generate engine data, receiving a throttle input from the throttle control, determining a preferred compression ratio within the combustion chamber based on the engine data and the throttle input, and commanding the junk head translation system to cause movement of the junk head parallel to the central axis of the cylinder to provide the preferred compression ratio.
  • the command can cause the junk head translation system to move the junk head closer to the top dead center position of the piston if the preferred compression ratio is greater than a current compression ratio and away from the top dead center position of the piston if the preferred compression ratio is less than the current compression ratio.
  • the engine data can optionally include at least one of a current engine speed, a current engine load, a detection of a premature detonation within the combustion chamber, and a current operation of a turbocharger or a supercharger that pressurizes and therefore adds heat to inlet air delivered to the combustion chamber.
  • the junk head translation system can vary the distance between the junk head and the top dead center position of the piston on a time scale that is substantially longer than a single engine cycle of the internal combustion engine.
  • an elastic rebound mechanism can optionally bias the junk head against a stop with a preload force directed away from the first end of the cylinder.
  • the preload force can be sufficient to retain the junk head against the stop up to a threshold combustion chamber pressure such that the junk head moves toward the first end of the cylinder to increase a combustion chamber volume during an engine cycle when the threshold combustion chamber pressure is exceeded.
  • the controller unit can optionally be implemented in hardware or software or a combination of both.
  • the moving of the junk head can cause an increase or decrease in a compression ratio within the cylinder, for example in response to throttle commands.
  • a lower compression ratio can be provided when the engine is operating at a low speed under high loads.
  • a turbocharger or supercharger can optionally be used in conjunction with an engine that includes one or more of the features described herein. Boosting of the intake air pressure for high power operation can coincide with a reduction in the compression ratio, for example to reduce incidence of uncontrolled detonation or "knocking" in the cylinder.
  • the compression ratio can be high.
  • Systems and methods consistent with this approach are described as well as articles that comprise a tangibly embodied machine-readable medium operable to cause one or more machines (e.g., computers, etc.) to result in operations described herein.
  • machines e.g., computers, etc.
  • computer systems are also described that may include a processor and a memory coupled to the processor.
  • the memory may include one or more programs that cause the processor to perform one or more of the operations described herein.
  • FIG. 1 shows a cross-sectional diagram showing components of a single piston engine with sleeve valves
  • FIG 2A and FIG. 2B show cross-sectional diagrams showing components of a single piston engine with a sleeve valve and a poppet valve;
  • FIG. 3 shows a top elevation view of a poppet valve actuator with coolant oil flows
  • FIG. 4 shows a cross-sectional diagram showing components of a single piston engine with two sleeve valves and a moveable junk head
  • FIG. 5 shows a process flow diagram illustrating aspects of a method having one or more features consistent with implementations of the current subject matter
  • FIG. 6 shows an isometric diagram illustrating an example of a junk head translation system
  • FIG. 7 shows an isometric diagram illustrating another example of a junk head translation system
  • FIG. 8 shows a cross-sectional diagram illustrating yet another example of a junk head translation system
  • FIG. 9 shows a process flow chart illustrating aspects of a method having one or more features consistent with implementations of the current subject matter.
  • Implementations of the current subject matter provide methods, systems, articles or manufacture, and the like that can, among other possible advantages, provide engines in which a sleeve valve is used in conjunction with a cylinder containing a single piston.
  • sleeve valves consistent with one or more implementations of the current subject matter can move intermittently such that a stop in motion occurs at a closed position as a leading or sealing edge of the sleeve valve is urged into contact with a valve seat and a reversal in motion occurs as the leading or sealing edge disengages from the valve seat to cause the valve to open.
  • the term "junk head” is used to refer to a structure that can have one or more physical features that are similar to a traditional piston (e.g. one or more compression or oil-sealing piston rings, positioning in a cylinder opposite a traditional piston as in an opposed piston engine, etc.), but that is not attached to a crankshaft or other means of transferring combustion energy to useful work.
  • the junk head can be movable, for example in accordance with one or more throttle conditions of the engine, to vary the cylinder geometry and thereby enable variable compression ratio operation of the engine.
  • a sleeve valve consistent with implementations of the current subject matter may move in a reciprocating path between a first position, where at least one port is open, and a second position, where the sleeve valve closes the first port.
  • FIG. 1 shows a cross-sectional view illustrating features of an engine 100 consistent with one or more implementations of the current subject matter.
  • a first, active piston 102 is connected by a connecting rod 104 to a crankshaft 106.
  • the active piston 102 is located within a cylinder (not shown in FIG. 1) and has positioned at least partially around its circumference a sleeve valve 110 that moves in an intermittent manner from an open position to a closed position under the influence of one or more springs (not shown), rocker arms 1 14, cams 116, push rods connecting the rocker arm and the cam (not shown in FIG. 1), and the like to control flow of air, air and fuel, or exhaust through a port (not shown in FIG. 1) which can be an intake port or an exhaust port depending on the specific engine configuration.
  • a junk head 120 Positioned opposite the piston head 1 18 in the cylinder is a junk head 120. Unlike the first piston 102, the junk head 120 is not attached, either directly or via a connecting rod, to a crankshaft for power output. In some implementations discussed in greater detail below, the junk head 120 can be connected to a crank or some other junk head translation mechanism or system that allows the position of the junk head 120 in the cylinder to be adjusted. Also unlike the first piston 102, in at least some implementations the junk head 120 does not experience cyclical movement during an engine cycle. In other implementations however, the junk head can be coupled to an elastic rebound mechanism such as a spring or other device that facilitates a peak pressure limitation mode of operation.
  • an elastic rebound mechanism such as a spring or other device that facilitates a peak pressure limitation mode of operation.
  • the junk head 120 can be stationary or otherwise fixed in position in the cylinder such that the compression ratio within the cylinder remains constant.
  • the junk head 120 can be moved or otherwise translated along the central axis of rotation of the cylinder to increase or decrease the size of the combustion volume or chamber 122 within the cylinder, for example from one cycle to the next, and thereby enable an engine to provide variable compression ratios through changes in the geometry of the combustion chamber 122.
  • a second sleeve valve 1 19 can also be positioned at least partially around the junk head 120 to control flow through a second port (not shown), which can be an intake port or an exhaust port.
  • This second sleeve valve 121 can have associated with it a rocker arm 1 14 as well as one or more springs 112, cams (not shown in FIG. 1), etc.
  • either or both of the sleeve valves 110 and 121 can experience substantially linear, reciprocating motion parallel to a central axis of rotation of the cylinder such that a seal is provided by urging a sealing edge of each sleeve valve 1 10, 121 against a respective valve seat in a closed position of the sleeve valve 1 10, 121.
  • one or more spark plugs or other ignition sources 124 can be positioned at or near the center of the combustion chamber 122 through the junk head 120.
  • the junk head 120 can also be directly cooled with flow through coolant, for example through one or more coolant channels 126, such that it can be maintained at an optimized temperature.
  • coolant for example through one or more coolant channels 126, such that it can be maintained at an optimized temperature.
  • a relatively reduced temperature of internal surfaces of the junk head 120 contacting a combustion mixture within the combustion chamber 122 can therefore be maintained so that the compression ratio of the engine 100 can be raised and the knock resistance can be improved.
  • an engine 200 includes a junk head that includes a poppet valve assembly 202 positioned centrally in the junk head 120 and one or more spark plugs or other ignition sources 124 positioned off the center axis also in the junk head 120.
  • the one or more spark plugs or other ignition sources 124 can be offset from the center of the combustion chamber 122 (i.e. the volume between the piston head 1 18 and the junk head 120 as further defined at least by cylinder walls of the engine body 204, and, in some implementations, by at least one sleeve valve 110.
  • More than one spark plug or other ignition source 124 can be included to enhance the burn rate of the mixture independent of the turbulence type or magnitude generated within the combustion chamber (e.g. by air or other gas flows via the intake and/or exhaust valves, by motion of the piston 102, by the shape of the piston head 1 18, or the like). Implementations of the current subject matter can also include more than one poppet valve disposed in the junk head. For example, two or more poppet valves can be positioned offset from the cylinder centerline. One or more spark plugs or other ignition sources 124 can be positioned either offset from the cylinder centerline as shown in FIG 2, or on or near the cylinder centerline if the poppet valve or valves 202 are offset from the cylinder centerline.
  • FIG. 2A and FIG. 2B use of one or more poppet valves 202 mounted in a moveable junk head is also within the scope of the current subject matter.
  • the poppet valve 202 in the movable junk head 120 can be actuated by a traditional valve train that moves with the moveable junk head 120, or by a hydraulic actuation similar to that used in the Fiat Multiair system that allows a valve actuation cam etc. to be stationary while the hydraulic connection to the poppet valve 202 is maintained by a slidable connection.
  • the poppet valve 202 can, in one implementation, be used to open and close an exhaust port 206 while a sleeve valve 1 10 opens and closes an intake port 208. Such a configuration can be used to reduce heat losses out of the combustion chamber.
  • the first port 206 can be an intake port controlled by operation of the poppet valve 202 while the sleeve valve 1 10 controls flow of exhaust gases through the second port 208.
  • This second configuration can enhance the knock resistance of the engine as a sleeve valve 110 used as an exhaust valve is generally easier to maintain at a lower temperature than is a poppet valve used for controlling an exhaust port.
  • a sleeve valve 110 as the intake valve can enable high flow rates and low restrictions for either tumble or swirl styles of mixture motion enhancement, for example as described in co-pending and co-owned international patent application no. PCT/US201 1/027775 ("Multi-Mode High Efficiency Internal Combustion Engine"), the disclosure of which is incorporated by reference herein.
  • PCT/US201 1/027775 Multi-Mode High Efficiency Internal Combustion Engine
  • the engine is run as a diesel, resistance to knock (e.g. premature detonation of the air-fuel mixture) can be a lesser concern, so an exhaust poppet valve may not require active cooling.
  • a spark ignited engine designed for high efficiency can merit ensuring that the valve is well cooled.
  • the poppet valve 202 can optionally be of larger diameter than a conventional poppet valve and can also have a large-diameter stem 210 to conduct heat away from the valve head 220 more effectively than a smaller conventional valve.
  • a valve can optionally also be made of a highly conductive material, such as for example a high-strength aluminum alloy.
  • the valve stem 210 and/or body can be filled with a cooling fluid, for example sodium in a steel valve.
  • valve stem 210, actuator 212, and keeper 214 can have access holes such that an oil supply tube 216 can be inserted into the valve stem 210.
  • the oil supply tube 216 can deliver oil near the valve head 220 inside the valve stem 210 and the clearance between the oil supply tube 216 and the valve stem 210 can allow the oil flow to exit.
  • the oil supply tube 216 can optionally be rigid and fixed to the block, for example such that the differential motion between the valve and the engine/oil tube creates a volume change in the valve oil passages so that oil is drawn into the valve as the valve opens and ejected it as the valve closes.
  • a check valve can optionally be included in or upstream of the oil supply tube or passage 216 to ensure that this pumping action produces flow of the cooling oil through the valve passages.
  • Pumping action can also be obtained by varying the valve section where the valve stem 210 passes through a fixed cavity supplied with oil. Oil can additionally be fed from a pressurized cavity 222 without valve-induced pumping action, for example as shown in FIG. 2B.
  • FIG. 3 shows a top view of an actuator assembly 300 for an implementation having a poppet valve that includes active cooling as described above in reference to FIG. 2.
  • the actuator 212 can include a forked rocker end 302 that is urged against the keeper 214 as it pivots upon a pivot point or block 304 due to the influence of a follower 306 on a rotating cam 310. If more than one poppet valve is employed, a pair of such rockers can be used, or alternatively a single rocker can actuate multiple valves.
  • the compression ratio, CR, for an internal combustion engine is defined as
  • the compression ratio can be increased by reducing the clearance volume and decreased by enlarging the clearance volume.
  • changes in the clearance volume can be achieved by incorporation of a moveable junk head 120 that can be translated within the cylinder at a rate that is determined by the current throttle condition rather than by the speed at which the engine is operating.
  • FIG. 4 shows a cross-sectional view of an engine 400 in which a cylinder includes a junk head 120 that is moveable such that a compression ratio within the cylinder can be varied from one engine cycle to another, subsequent engine cycle.
  • the junk head 120 can be translated in a direction parallel to the central axis 402 of the cylinder - moving the junk head 120 to the left in the view shown in FIG. 4 reduces the clearance volume and thereby increases the compression ratio, while moving the junk head 120 to the right enlarges the clearance volume and thereby decreases the compression ratio.
  • motion of the junk head occurs on substantially longer time scales and with a slower frequency than the reciprocating motion of the piston in the cylinder.
  • a first sleeve valve 404 and a second sleeve valve 406 are included to control the opening and closing of an intake port 410, and an exhaust port 412, respectively.
  • Either or both of the intake port 410 and the exhaust port 412 can be a swirl or tumble port such as those described in co-pending and co-owned U.S. patent application no. 12/860,061 ("High Swirl Port”) and co-pending and co-owned international patent application no. PCT/US201 1/027775 ("Multi-Mode High Efficiency Internal Combustion Engine”), the disclosure of each of which is incorporated by reference herein.
  • Either or both of these ports may wrap entirely or at least partially about the circumference of the cylinder (as is shown in FIG. 4). Sealing edges of the sleeve valves 404, 406 can form a seal at valve seats 414. As shown in FIG. 4, the exhaust port 412 is located closer to the junk head 120. However, a reversed configuration, in which the intake port is closer to the junk head 120, is also within the scope of the current subject matter.
  • Both of the junk head 120 and the piston 102 are moveable within the cylinder, albeit at differing frequencies.
  • the first sleeve valve 404 and the second sleeve valve 406 also move within the cylinder relative to the piston 102 and junk head 120.
  • one or more compression piston rings 416 and oil sealing piston rings 420 can be provided about the circumference of each of the piston 102 and the junk head 120.
  • the oil sealing ring 420 can optionally be replaced by a polymer seal with the addition of a blow-by gas vent between the compression ring and the polymer seal.
  • the piston 102 moves in accordance with the engine cycle within the cylinder to drive the connecting rod to turn the crankshaft as discussed above.
  • the junk head 120 in contrast, can be controlled to move according to a throttle setting or engine operating condition.
  • a controller device (not shown in FIG. 4), which can include one or more programmable processors, can send commands to a junk head translation system to cause the junk head 120 to translate within the cylinder according to a currently required compression ratio.
  • the required compression ratio can be determined by the controller device based on one or more factors, including current engine speed, current engine load, detection of premature detonation within the cylinder (e.g. engine "knocking"), current operation of a turbocharger or supercharger that pressurizes and accordingly adds heat to the intake gases, and the like.
  • motion of the junk head generally occurs on substantially longer time scales and with a slower frequency than the reciprocating motion of the piston in the cylinder.
  • the piston 102 may make one or more complete cycles between a bottom dead center (BDC) and a top dead center (TDC) position and back during each engine cycle (e.g. one cycle between BDC and TDC and back to BDC for a two-stroke engine, two cycles between BDC and TDC and back to BDC for a four-stroke engine, etc.), the junk head 120 tends to move substantially more slowly.
  • a complete cycle of the junk head 120 for example between a first, lower compression ratio position to a second, higher compression ratio position and back to the first, lower compression ratio position can occur during operation of the engine, albeit over many engine cycles rather than during a single engine cycle
  • FIG. 5 shows a process flow chart 500 illustrating method features, one or more of which are consistent with at least one implementation of the current subject matter.
  • the engine data can include, but are not limited to, one or more of a current engine load, a current engine speed, an intake temperature, a richness of a fuel mixture being delivered to a combustion chamber of the engine, an amount of pre-compression of intake air, and the like.
  • a controller device receives a throttle input for an internal combustion engine at 504. Based on the throttle input and one or more of the other data, the controller device can, at 506 determine a preferred compression ratio within a cylinder of the internal combustion engine.
  • the controller device can send a command to a junk head translation system to cause a junk head in the cylinder to move to change a current compression ratio in the cylinder to match the preferred compression ratio.
  • the preferred compression ratio can optionally be determined and applied to each cylinder in a multi-cylinder engine.
  • the controller device can determine a preferred compression ratio for each cylinder individually.
  • Such an approach can be useful, particularly in a dynamic load regime, in which one portion of the engine has warmed up more quickly and become more knock prone than another.
  • This approach can provide significant advantages for an engine running in a homogeneous charge compression ignition (HCCI) mode, in which well-mixed fuel and air (or some other oxidizer) are compressed to the point of auto- ignition. In such an engine, control over the factors influencing the ignition timing can be quite important.
  • HCCI homogeneous charge compression ignition
  • FIG. 6 shows an illustrative example of a junk head translation system 600.
  • a junk head 120 can include a threaded region 602 that is configured to engage with a similarly tapped section of the engine block within a cylinder.
  • a motor 604 which can be electric, hydraulic, belt driven, or the like, can rotate a worm drive 606 on command from the controller device.
  • the worm drive 606 can engage with a series of teeth 610 on the junk head 120 to cause rotation of the junk head.
  • Rotation of the junk head 120 in a first direction can cause the junk head 120 to move further into the cylinder by interaction of the threaded region 602 with the tapped section of the engine block.
  • Rotation of the junk head 120 in a second direction opposite to the first direction can cause the junk head 120 to move back out of the cylinder by interaction of the threaded region 602 with the tapped section of the engine block.
  • FIG. 6 shows an example in which a threaded region 602 of the junk head engages with a tapped section of the engine block
  • the scope of the current subject matter also includes an alternative implementation in which the junk head 120 includes a tapped section that interacts with a threaded region of the ending block, a threaded adjustment assembly between the block and the junk head, or the like, which can allow the junk head to remain rotationally fixed relative to the main body of the engine.
  • FIG. 7 shows an illustrative example of another junk head translation system 700.
  • a junk head 120 can be connected via a connecting rod 702 to a cam shaft 704 than can be rotated on command from the controller device, for example by a motor, which can be electric, hydraulic, belt-driven, etc.
  • the cam shaft 704 can include an eccentric or off-center cam lobe 706 that is mounted to the cam shaft 704 at a rotation point that is not at the central axis of rotation of the cam lobe 706 such that when the cam shaft 704 is rotated, the cam lobe 706 acts on the end 710 of the connecting rod 702 to result in lifting or dropping the junk head within the cylinder.
  • FIG. 8 shows an illustrative example of yet another junk head translation system 800.
  • a wedge 802 can be driven between a fixed block 804 or other feature in the engine block and the junk head 120 such that as the wedge 802 is moved in one direction, the junk head 120 is caused to move along another axis.
  • the wedge can be driven by a hydraulic drive 806 as shown in FIG. 8, or alternatively by other types of drives (e.g. a threaded drive, a belt drive, etc.).
  • the junk head 120 is neither fixed to the main engine assembly nor rigidly coupled to a junk head translation system 700 that controls movement on times scales longer than an engine cycle.
  • an elastic junk head rebound mechanism such as for example a backing spring or the like, can hold the junk head 120 against a stop with a certain preload force applied. The applied preload force can hold the junk head 120 stationary against the stop until the pressure in the combustion chamber acting against the junk head 120 overcomes the preload force provided by the spring or other elastic junk head rebound mechanism.
  • Adjusting the spring or other elastic junk head rebound mechanism preload force to set the peak pressure allows a degree of control over peak temperatures in the combustion process, such as at full power operation, at which the combustion event can be susceptible to knock due to high peak pressures and temperatures. Gas loads on the valves and other components can also be reduced by limiting the peak pressure.
  • an elastic junk head rebound mechanism as described above can be used in conjunction with either an otherwise fixed junk head position or with a junk head translation mechanism that can translate the location of the stop from one engine cycle to a later engine cycle.
  • FIG. 9 shows a process flow chart 900 illustrating method features, one or more of which are consistent with at least one implementation of the current subject matter.
  • a first sleeve valve associated with a first port connecting to a combustion chamber is opened.
  • the combustion chamber is disposed within a cylinder of an internal combustion engine and defined at least in part by a head of a piston that moves within the cylinder, an internal surface of a junk head disposed at a first end of the cylinder opposite the piston, and the first sleeve valve, which at least partially encircles the piston.
  • the opening includes moving the first sleeve valve to an open position at which the first sleeve valve temporarily ceases its motion in a direction aligned with an axis of the cylinder.
  • the first sleeve valve is closed by moving the first sleeve valve to a first closed position at which the first sleeve valve temporarily ceases its motion in the direction aligned with the axis of the cylinder and at which a sealing edge of the sleeve valve is urged into contact with a valve seat such that the sealing edge is closer to the first end of the cylinder at the closed position than at the open position.
  • a crankshaft connected to the piston by a connecting rod rotates under influence of movement of the piston in the cylinder in accordance with an engine speed commanded by a throttle control.
  • One or more aspects or features of the subject matter described herein can be realized in digital electronic circuitry, integrated circuitry, specially designed application specific integrated circuits (ASICs), field programmable gate arrays (FPGAs) computer hardware, firmware, software, and/or combinations thereof.
  • ASICs application specific integrated circuits
  • FPGAs field programmable gate arrays
  • These various aspects or features can include implementation in one or more computer programs that are executable and/or interpretable on a programmable system including at least one programmable processor, which can be special or general purpose, coupled to receive data and instructions from, and to transmit data and instructions to, a storage system, at least one input device, and at least one output device.
  • the programmable system or computing system may include clients and servers.
  • a client and server are generally remote from each other and typically interact through a communication network. The relationship of client and server arises by virtue of computer programs running on the respective computers and having a client-server relationship to each other.
  • machine-readable signal refers to any signal used to provide machine instructions and/or data to a programmable processor.
  • the machine-readable medium can store such machine instructions non-transitorily, such as for example as would a non-transient solid- state memory or a magnetic hard drive or any equivalent storage medium.
  • the machine-readable medium can alternatively or additionally store such machine instructions in a transient manner, such as for example as would a processor cache or other random access memory associated with one or more physical processor cores.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

Moteur à combustion interne pouvant comprendre un piston se déplaçant dans un cylindre et une culasse de cylindre disposée en face de la tête de piston dans le cylindre. La culasse de cylindre peut facultativement être mobile entre une position de taux de compression plus élevé, plus proche du point mort haut du piston, et une position de taux de compression plus faible, plus éloignée du point mort haut du piston. Au moins un orifice d'admission peut fournir un fluide comprenant de l'air d'admission à une chambre de combustion à l'intérieur du cylindre. Les gaz de combustion peuvent être dirigés hors de la chambre de combustion par au moins un orifice d'échappement. L'orifice d'admission et/ou l'orifice d'échappement peuvent être ouverts ou fermés par le fonctionnement d'une soupape manchon qui entoure au moins partiellement le piston. L'invention décrit les articles, systèmes et procédés qui s'y rapportent.
PCT/US2011/055457 2010-10-08 2011-10-07 Soupape manchon unique pour piston avec capacité facultative de taux de compression variable WO2012048279A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN2011800593105A CN103249920A (zh) 2010-10-08 2011-10-07 具有可变压缩比的单活塞套筒阀
EP11779008.9A EP2625394B1 (fr) 2010-10-08 2011-10-07 Piston unique à soupape du type fourreau et préférablement capable de taux de compression variable
US13/270,200 US9650951B2 (en) 2010-10-08 2011-10-10 Single piston sleeve valve with optional variable compression ratio capability

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US39152510P 2010-10-08 2010-10-08
US61/391,525 2010-10-08
US201161501462P 2011-06-27 2011-06-27
US61/501,462 2011-06-27

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WO2012048279A1 true WO2012048279A1 (fr) 2012-04-12
WO2012048279A4 WO2012048279A4 (fr) 2012-05-31

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CN (1) CN103249920A (fr)
WO (1) WO2012048279A1 (fr)

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Publication number Priority date Publication date Assignee Title
CN105569905B (zh) * 2016-03-07 2018-04-13 吉林大学 一种发动机循环点火节能装置和发动机及其循环点火方法
CN106837457B (zh) * 2017-03-22 2019-04-09 北京理工大学 用于对置活塞发动机的可变配气相位机构
CN112678499B (zh) * 2021-01-27 2024-02-20 青岛华泰电力设备有限公司 一种进度可调节式机械下料装置

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FR348575A (fr) * 1903-12-05 1905-04-17 Francis Lyst Machine à combustion interne et moteur à pétrole
US860061A (en) 1906-12-29 1907-07-16 Heinrich Roesner Carpenter's bench.
GB190902015A (en) * 1909-01-27 1909-08-05 Eugene Guy Euston Beaumont Improved Method of and Means for Automatically Varying the Volume of the Compression Chamber in Internal Combustion Engines.
FR497282A (fr) * 1918-04-04 1919-12-02 Georges Rene Eugene Briens Moteur à explosions sans soupapes
US1502291A (en) * 1920-09-07 1924-07-22 George E Conway Valve for motors
GB382670A (en) * 1930-08-09 1932-10-31 Adolphe Kegresse Improvements in or relating to the feeding of two- or more-cylinder internal combustion engines
FR805866A (fr) * 1935-04-06 1936-12-02 United Aircraft Corp Perfectionnements relatifs aux moteurs du type à fourreau de distribution
DE643470C (de) * 1935-02-06 1937-04-08 Ernst Schmid Brennkraftmaschine
GB542009A (en) * 1940-06-18 1941-12-22 Arthur John Rowledge Improvements in or relating to liquid-cooling systems for sleevevalve internal-combustion engines
GB635664A (en) * 1948-01-23 1950-04-12 George Urban Leonard Sartoris Improvements in high-speed air and gas compressors
GB1516982A (en) * 1975-09-15 1978-07-05 Jones R Reciprocating piston heat engines
WO1979000650A1 (fr) * 1978-02-22 1979-09-06 Caterpillar Tractor Co Soupape de moteur refroidie, avec transfert de chaleur ameliore
GB2432398A (en) * 2005-11-18 2007-05-23 Lotus Car Reciprocating piston sleeve valve engine with variable valve timing
WO2007083159A1 (fr) * 2006-01-23 2007-07-26 Lotus Cars Limited Moteur a combustion interne a deux temps a taux de compression variable et volet d'orifice d'echappement
US7559298B2 (en) 2006-04-18 2009-07-14 Cleeves Engines Inc. Internal combustion engine
US20110027775A1 (en) 2009-07-21 2011-02-03 Arbor Vita Corporation Detection of influenza virus

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US1823770A (en) * 1928-11-26 1931-09-15 Tartrais Eugene Henri Engine of the two-stroke type
US2686507A (en) * 1952-03-06 1954-08-17 Lombardi Leo Sleeve valve system
GB2376503A (en) * 2001-04-27 2002-12-18 Martin Leonard Stanley Flint Automatically variable compression ratio device with adjustable cylinder head portion

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR348575A (fr) * 1903-12-05 1905-04-17 Francis Lyst Machine à combustion interne et moteur à pétrole
US860061A (en) 1906-12-29 1907-07-16 Heinrich Roesner Carpenter's bench.
GB190902015A (en) * 1909-01-27 1909-08-05 Eugene Guy Euston Beaumont Improved Method of and Means for Automatically Varying the Volume of the Compression Chamber in Internal Combustion Engines.
FR497282A (fr) * 1918-04-04 1919-12-02 Georges Rene Eugene Briens Moteur à explosions sans soupapes
US1502291A (en) * 1920-09-07 1924-07-22 George E Conway Valve for motors
GB382670A (en) * 1930-08-09 1932-10-31 Adolphe Kegresse Improvements in or relating to the feeding of two- or more-cylinder internal combustion engines
DE643470C (de) * 1935-02-06 1937-04-08 Ernst Schmid Brennkraftmaschine
FR805866A (fr) * 1935-04-06 1936-12-02 United Aircraft Corp Perfectionnements relatifs aux moteurs du type à fourreau de distribution
GB542009A (en) * 1940-06-18 1941-12-22 Arthur John Rowledge Improvements in or relating to liquid-cooling systems for sleevevalve internal-combustion engines
GB635664A (en) * 1948-01-23 1950-04-12 George Urban Leonard Sartoris Improvements in high-speed air and gas compressors
GB1516982A (en) * 1975-09-15 1978-07-05 Jones R Reciprocating piston heat engines
WO1979000650A1 (fr) * 1978-02-22 1979-09-06 Caterpillar Tractor Co Soupape de moteur refroidie, avec transfert de chaleur ameliore
GB2432398A (en) * 2005-11-18 2007-05-23 Lotus Car Reciprocating piston sleeve valve engine with variable valve timing
WO2007083159A1 (fr) * 2006-01-23 2007-07-26 Lotus Cars Limited Moteur a combustion interne a deux temps a taux de compression variable et volet d'orifice d'echappement
US7559298B2 (en) 2006-04-18 2009-07-14 Cleeves Engines Inc. Internal combustion engine
US20110027775A1 (en) 2009-07-21 2011-02-03 Arbor Vita Corporation Detection of influenza virus

Also Published As

Publication number Publication date
CN103249920A (zh) 2013-08-14
WO2012048279A4 (fr) 2012-05-31
EP2625394B1 (fr) 2017-06-21
EP2625394A1 (fr) 2013-08-14

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