EP2558705B1 - A sliding valve assembly - Google Patents
A sliding valve assembly Download PDFInfo
- Publication number
- EP2558705B1 EP2558705B1 EP10849946.8A EP10849946A EP2558705B1 EP 2558705 B1 EP2558705 B1 EP 2558705B1 EP 10849946 A EP10849946 A EP 10849946A EP 2558705 B1 EP2558705 B1 EP 2558705B1
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- EP
- European Patent Office
- Prior art keywords
- valve
- assembly
- valve body
- sealing
- valve housing
- Prior art date
- Legal status (The legal status 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 status listed.)
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- 238000007789 sealing Methods 0.000 claims description 160
- 239000012530 fluid Substances 0.000 claims description 78
- 230000000903 blocking effect Effects 0.000 claims description 10
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- 230000001965 increasing effect Effects 0.000 claims description 8
- 238000004891 communication Methods 0.000 claims description 7
- 238000002485 combustion reaction Methods 0.000 description 47
- 230000000712 assembly Effects 0.000 description 30
- 238000000429 assembly Methods 0.000 description 30
- 230000006835 compression Effects 0.000 description 12
- 238000007906 compression Methods 0.000 description 12
- 239000007789 gas Substances 0.000 description 12
- 239000000446 fuel Substances 0.000 description 9
- 239000000203 mixture Substances 0.000 description 7
- 230000007246 mechanism Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- 239000004215 Carbon black (E152) Substances 0.000 description 1
- 238000007792 addition Methods 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 229930195733 hydrocarbon Natural products 0.000 description 1
- 150000002430 hydrocarbons Chemical class 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000003534 oscillatory effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
-
- 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
- F01L5/02—Slide valve-gear or valve-arrangements with other than cylindrical, sleeve or part annularly shaped valves, e.g. with flat-type valves
-
- 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
- F01L5/14—Slide valve-gear or valve-arrangements characterised by the provision of valves with reciprocating and other movements
- F01L5/16—Slide valve-gear or valve-arrangements characterised by the provision of valves with reciprocating and other movements with reciprocating and other movement of same valve, e.g. longitudinally of working cylinder and in cross direction
-
- 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
- F01L5/22—Multiple-valve arrangements
-
- 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
- F01L5/24—Component parts, details or accessories, not provided for in preceding subgroups in this group
-
- 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
- F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
- F01L7/06—Rotary or oscillatory slide valve-gear or valve arrangements with disc type valves
-
- 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
- F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
- F01L7/14—Multiple-valve arrangements
-
- 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
- F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
- F01L7/16—Sealing or packing arrangements specially therefor
-
- 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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/36—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle
- F01L1/38—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle for engines with other than four-stroke cycle, e.g. with two-stroke cycle
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G2270/00—Constructional features
- F02G2270/90—Valves
Definitions
- the present invention relates to a valve assembly suitable for use in a pressure system involving a pressure actuator, for example, an energy conversion engine, e.g. an internal combustion engine or a heat engine, e.g. a diesel engine, a Sterling cycle engine, a Miller cycle engine, and an Otto cycle engine. More particularly, the present invention relates to a sliding valve assembly for use in a pressure system and having an improved sealing system configured to reduce friction, heat and wear on the valve and body related sealing components.
- an energy conversion engine e.g. an internal combustion engine or a heat engine, e.g. a diesel engine, a Sterling cycle engine, a Miller cycle engine, and an Otto cycle engine.
- a sliding valve assembly for use in a pressure system and having an improved sealing system configured to reduce friction, heat and wear on the valve and body related sealing components.
- the Otto cycle comprises an intake stroke, in which an intake valve opens and a mixture of air and fuel is directed into the cylinder of the engine.
- a compression stroke then occurs in which the piston compresses the mixture of fuel and air to increase the pressure in the cylinder.
- a spark provided by a spark plug ignites the mixture just before the piston reaches the top of the cylinder, causing the piston to be forced down in the cylinder in the power stroke.
- An exhaust valve then opens in the exhaust stroke, in which burned gases are forced out of the cylinder. The four strokes are repeated continuously during operation of the engine.
- crankshaft is coupled to a timing belt or chain, which in turn is coupled to a camshaft that rotates to open the intake and exhaust valves during the intake and exhaust strokes, respectively.
- a spring associated with each valve closes the valve during the other cycles.
- valves protrude into the cylinder during each cycle, and there is an inherent risk that the piston may contact an open valve at a high force and cause substantial engine damage. Additionally, valve timing events may be limited due to the protrusion of the valve head into the cylinder.
- valve timing events may be limited. For example, there generally is a short time period during which both the intake valve and the exhaust valve are open when conventional poppet valves and stiff springs are employed. During this overlap period, unburned hydrocarbon molecules may remain in the combustion chamber for a subsequent cycle, thereby adversely affecting dynamic compression and reducing engine efficiency.
- sliding valve assemblies which may be used in conjunction with internal combustion engines, have been developed to overcome several of the drawbacks associated with conventional poppet valves.
- One primary advantage of a sliding valve assembly is the capability to have a substantially unobstructed flow path. Specifically, because a conventional poppet valve is not employed, and therefore does not obstruct the flow path through an intake or exhaust port, a sliding valve has the potential to significantly increase airflow capability into a cylinder. Moreover, since the stiff springs used in conjunction with conventional poppet valves may be omitted, sliding valve assemblies may achieve reduced mechanical loads.
- Some sliding valve assemblies have rotating discs, cylinders, sleeves and other spheroidal rotating mechanisms. Such previously known sliding valves may be timed such that their apertures overlap with the cylinder during the intake and exhaust strokes. However, due to their continuous seal contact, these known sliding valves may experience high temperatures and extreme friction, resulting in high rates of wear imposed on the valve and any related sealing mechanisms.
- such sliding valve assemblies generally have fixed aperture sizes, i.e., the size of the aperture in registration with the cylinder may not be varied as the valve is translated or displaced i.e. moved back and forth in a plane as opposed to rotation. Accordingly, the fuel consumption and emissions may be increased by providing a relatively large port aperture, resulting in low gas velocities, which adversely affect engine performance at low engine speeds, particularly during idling conditions.
- sliding valve assemblies are discussed in FR 431248 and GB 246287 and in U.S Patent Nos. 4,201,174 ; 1,922,678 ; 5,003,936 ; 1,722,873 ; 2,074,487 ; and 5,694,890 .
- the present invention has met these needs.
- the present invention provides a sliding valve assembly for introducing and/or exhausting a fluid medium relative to a combustion chamber or cylinder containing a reciprocating piston for an energy conversion engine, for example, an internal combustion engine.
- the sliding valve assembly includes: a valve housing having a first fluid conducting passage and a second fluid conducting passage separated by a valve cavity; a valve body contained in the valve cavity of the valve housing and having a fluid conducting port adjacent to a fluid impervious surface; an actuator for translating movements of the valve body within the valve cavity of the valve housing into a fluid conducting position wherein the fluid conducting port of the valve body allows a fluid conducting relationship between the first fluid conducting passage and the second fluid conducting passage of the valve housing and into a fluid blocking position where the fluid impervious surface of the valve body obstructs a fluid conducting relation between the first fluid conducting passage and the second fluid conducting passage of the valve housing; cooperating surfaces on the valve body and the valve housing for constraining the valve body during the translating movements of the valve body within the valve cavity of
- the first sealing assembly and the second sealing assembly include a primary seal ring, a secondary seal ring surrounding the periphery of the primary seal ring, and a resilient member, e.g. tension spring arranged to apply a resilient force between the primary seal ring and its respective sealing surface for loading the primary seal ring against its respective sealing surface.
- the sealing surface may include a wall of the seal cavity of the valve body; whereas with regard to the second sealing assembly, the sealing surface may include a wall of the seal cavity of the valve housing.
- the first sealing assembly and the second sealing assembly and its primary seal ring may have one of many shapes, e.g. cylindrical or non-cylindrical, for example, obloid and D-shape, and the secondary seal ring is freely moveable relative to the primary seal ring within its respective seal cavity.
- the valve housing also includes a cap mounted within an annular member of the upper valve housing.
- This cap may include a plurality of parallel ports or channels, each forming a passage for the fluid medium and/or pressure in the system for delivering pressure to at least the second sealing assembly located within the valve housing for increasing its sealing effectiveness against the sealing surface of the valve housing.
- This arrangement of the ports or channels for directing high pressure in a combustion chamber of a cylinder to the sealing assembly acts to enhance the sealing effect of this second sealing assembly.
- the pressure within the system travels within the seal cavity containing the first and/or second sealing assembly to force or pressure the primary seal ring and the secondary seal ring of the first and/or second sealing assembly against one or more sealing surfaces of the seal cavity containing the first and/or second sealing assembly to force or further pressure the primary seal ring and the secondary seal ring of the first and/or second sealing assembly against one or more sealing surfaces of the valve body or the valve housing.
- the cooperating surfaces may include one or more cams and cam followers responsive to the valve body actuator. These cooperating surfaces of the cams and cam followers may act to constrain the valve body during its translating movements within the valve housing for opening and closing the valve assembly.
- the cams may include surfaces located in housings on either side of the valve body or in the valve body itself, with the followers attached to the lateral sides of the valve body for engagement with the cam surfaces.
- the cam surfaces may be straight or they may have an inclined portion. If the cam surfaces have an inclined portion, the followers will be raised thereby raising the valve body away from the valve housing during the translational movement of the valve body thereby effectively separating the valve body from the valve housing and thus moving at least the first sealing assembly away from the lower portion of the valve housing.
- a further embodiment includes a front cam follower and a rear cam follower mounted along the width of the valve body wherein these cam followers cooperate with cam surfaces of the valve housing for reducing the friction between the contact and/or sealing surfaces of the sealing system of the sliding valve assembly.
- valve body is forced away from the sealing surface of the valve housing by the linear cam and cam followers during the translational movement or oscillations of the valve body relative to the valve housing by the actuator, the friction, heat and wear on the valve, the valve body and related sealing components may be substantially reduced compared to conventional sliding valves.
- the valve body is disposed substantially within the valve cavity or bore of the valve housing.
- the valve body is configured to translate or oscillate within the valve housing via a cam and actuator system according to the timing of the rotation of the camshaft and crankshaft, thereby selectively enabling or preventing fluid communication between the passageway of the valve body and a cylinder of an internal combustion engine.
- translational movement of the valve body in a first direction enables fluid communication
- translational movement of the valve body in an opposing direction prevents fluid communication with the cylinder.
- the pressure in the system e.g. cylinder pressure and the resilient member, e.g. spring of the sealing assembly or sealing assemblies provide an effective seal for the pressure system.
- actuators may be used for the translational movement of the valve body.
- camshafts, solenoids, rocker arms, chains, gears, belts, and hydraulic, pneumatic, electric actuators, and/or other means may be employed to cause translational movement of the valve body.
- the present invention further allows considerable flexibility with respect to the different types of actuators that may be employed, particularly compared to prior art sliding valve assemblies that rely solely on conventional mechanisms to provide the translational movement of the valve.
- Such design flexibility provides various advantages in addition to the translational movement of the valve body, for example, the attainment of variable aperture sizes and timing events, as generally described herein below.
- a first sliding valve assembly of the present invention would be employed as an intake valve, and a second sliding valve assembly of the invention would be employed as an exhaust valve.
- valve assembly of the invention may also be used effectively in any number of pressure systems.
- the valve assembly may be any one of a number of valve assemblies, for example, a sliding valve assembly, a rotating valve assembly, a semi-rotating valve assembly, or an oscillating valve assembly.
- an object of the present invention to provide a valve assembly with an improved sealing system for use in a pressure system, such as an energy conversion engine or heat engine, for example, in internal combustion engines.
- the valve assembly including an improved sealing system of the present invention may be a sliding valve assembly, a rotary valve assembly, a semi-rotary valve assembly or an oscillatory valve assembly for use in a pressure system which may or may not include a pressure actuator, for example, an energy conversion engine, e.g. an internal combustion engine or a heat engine, for example, a diesel engine, a Sterling cycle engine, a Miller cycle engine, and an Otto cycle engine.
- a pressure actuator for example, an energy conversion engine, e.g. an internal combustion engine or a heat engine, for example, a diesel engine, a Sterling cycle engine, a Miller cycle engine, and an Otto cycle engine.
- the sliding valve assembly 30, 130 of the present invention may be used as an intake valve and/or an exhaust valve in a standard internal combustion engine.
- the configurations of the intake valve and the exhaust valve are substantially identical.
- an intake valve of the present invention will be referred to generally as an intake valve 30 while an exhaust valve will be referred to generally as an exhaust valve 130, although each valve preferably is provided in accordance with the sliding valve assembly 30 of FIG. 2 .
- the intake valve 30 and the exhaust valve 130 are broken away for clarity purposes so as to more clearly see the location of the sealing system within the sliding valve assembly of the invention.
- a standard internal combustion engine 31 comprises a cylinder 33, a combustion chamber 35 and a piston 37, which is coupled to a crankshaft via a connecting rod (not shown) in a manner known to those skilled in the art.
- Intake valve 30 and exhaust valve 130 may be provided as separate modular components that are disposed atop cylinder head 43 or within the head 43 or, alternatively, intake valve 30 and exhaust valve 130 may be formed as single units within cylinder head 43, as illustrated in FIG. 4 .
- the valve assemblies 30 and 130 because of their compact nature, may be combined with the engine block 43, thus eliminating the need for a separable cylinder head.
- a single-piece head/block arrangement has several advantages.
- the head bolts may be eliminated or the number of head bolts may be reduced.
- the engine block may be of a stronger and sturdier construction.
- the head gaskets and attaching hardware may be eliminated, thus allowing easy access for maintenance, i.e. service, and access, and, thus reduced manufacturing and maintenance costs.
- FIG. 2 shows one sliding valve assembly of the present invention for use in an internal combustions engine wherein as stated herein above the sliding valve assembly 30, 130 may be used as an intake valve 30 and an exhaust valve 130. Therefore, two sliding valve assemblies of the invention will be provided relative to cylinder 33.
- Sliding valve assembly 30, 130 includes a valve housing which is comprised of an upper valve housing 45 and a lower valve housing 47; a valve body 49 which is housed in the valve housing; and a sealing system including a sealing assembly 51 which includes a primary seal ring 53, a secondary seal ring 55 and a resilient member or spring 57 and a sealing assembly 59 which includes a primary seal ring 59a, a secondary seal ring 59b, and a resilient member or spring 59c. As shown in FIG.
- the lower valve housing 47 is a single plate extending over the combustion chamber 35 of cylinder 33.
- the upper valve housing 45 for each sliding valve assembly 30, 130 is about half the length of the lower valve housing plate 47.
- the upper valve housing 45 is fixedly connected to the lower valve housing plate 47 through suitable means such as welding.
- the lower valve housing plate 47 and the cylinder 33 are connected together by fasteners (not shown) such as screws received in apertures 47a in the lower valve housing plate 47 and apertures 33a of cylinder 33.
- sliding valve assembly 30, 130 further includes a valve actuating rod 61; linear cams 63, 65 and roller bearings or cam followers 67, 69, 71 and 73 mounted to the lateral sides 49a and 49b of valve body 49.
- Linear cam 63 has cooperating cam surfaces 63a and 63b which are engaged by cam followers 67, 69 respectively
- linear cam 65 has cooperating cam surfaces 65a and 65b which are engaged by cam followers 71 and 73.
- Cam followers 67, 69, 71 and 73 travel on cam surfaces 63a, 63b, 65a and 65b when valve body 49 is translated or oscillated within the valve housing via actuation of actuator rod 61.
- Actuator rod 61 is received in aperture 49c of valve body 49 wherein it is retained via retaining pin 74. It is to be appreciated that the arrangement of the valve actuating rod 61 within aperture 49c via retaining pin 74 is such that actuating rod 61 is permitted to freely move or toggle relative to valve body 49 during movement of the valve body 49 within the valve housing. This toggle feature becomes particularly important when linear cams 63 and 65 and followers 67, 69, 71 and 73 are used, and particularly if the cam surfaces 63a, 63b, 65a and 65b of cams 63, 65 are inclined.
- valve body 49 has an opening or fluid conducting port 75
- the upper valve housing 45 has an opening or a first fluid conducting passage 79
- the lower valve housing plate 47 has an opening or a second fluid conducting passage 77.
- the upper valve housing 45 has an annular member 45a which receives a cap 45b defining the first fluid conducting passage 79.
- the upper valve housing 45 also includes two channels 45c and 45d which receive cams 63, 65 respectively when valve body 49 is assembled within the upper valve housing 45.
- cap 45b is mounted within the annular member 45a of the upper valve housing 45 and forms a seal cavity 45e for retaining the sealing assembly 51, the latter of which is shown best in FIG. 2 .
- the valve body 49 has a lower fluid impervious surface 49d that is adjacent to or juxtaposed relative to the fluid conducting port 75 of the valve body 49.
- the valve body 49 further includes a seal cavity 49e for retaining the sealing assembly 59, the latter of which is shown best in FIG. 2 .
- the fluid conducting port 75 of the valve body 49, the first fluid conducting passage 79 of upper valve housing 45 and the second fluid conducting passage 77 of the lower valve housing plate 47 cooperate to open the sliding valve assembly 30 when the fluid conducting port 75 of the valve body 49 is aligned with the passages 79 and 77.
- This alignment of port 75 with passages 77 and 79 of the sliding valve assembly 30 is referred to as being the fluid conducting position or the opened position of the sliding valve assembly 30.
- the sealing assembly 51 is received in a recessed portion or seal cavity 45e of the upper valve housing 45 and the sealing assembly 59 is received in a recessed portion or seal cavity 49e in the lower fluid impervious surface 49d of the valve body 49, as discussed herein above.
- the intake valve 30 is illustrated as being in a fluid conducting position or in its intake stroke position wherein the intake valve 30 opens and a mixture of air and fuel is directed into cylinder 33 to force the piston 37 downwardly as indicated by the arrow.
- the exhaust valve 130 is in its fluid blocking position or closed position wherein the valve body 49 totally blocks the fluid conducting passage 79 of the upper valve housing 45 and the fluid conducting passage 77 of the lower valve housing plate 47.
- the sealing assembly 59 in the seal cavity 49e of the valve body 49 becomes the primary seal and the sealing assembly 51 in the upper valve housing 45 becomes the secondary seal, which is commonly referred to as an "apron seal".
- the pressurized air or gas is caused to flow into the seal cavity 49e of the valve body 49 as shown by the arrows and to act against sealing assembly 59, particularly against the second sealing ring 59b to force the sealing assembly 59 against a wall surface of the seal cavity 49e to increase the effectiveness of the sealing assembly 59 for both valve sliding assemblies 30 and 130.
- the mixture of air and fuel is directed into the combustion chamber 35 upon the intake stroke of the sliding valve assembly 30 and is prevented from seeping out of the exhaust valve assembly 130 in view of its respective sealing assemblies 51 and 59 and particularly due to the added performance of the sealing assembly 59 within valve body 49 and the pressure acting upon the sealing assembly 59 as illustrated in FIG. 3 .
- the sealing assembly 59 is constructed similarly to that disclosed herein above with reference to FIGS. 1A through 2 . That is, the sealing assembly 59 of FIG. 3 includes a primary seal ring 59a, a secondary seal ring 59b positioned around the periphery of the primary seal ring 59a, and a resilient member 59c. In FIG. 3 , the resilient member 59c is not shown for clarity purposes so as to more clearly indicate the path the pressure travels from chamber 35.
- FIG. 1B shows a compression stroke or power stroke for a standard internal combustion engine 31.
- the intake valve 30 and the exhaust valve 130 are both closed.
- piston 37 compresses the air and fuel to increase the pressure in cylinder 33.
- a spark ignites the mixture before piston 37 reaches the top of cylinder 33 causing the piston 37 to be forced downwardly in the cylinder 33 in its power stroke as indicated by the arrow.
- sealing assembly 59 of each sliding valve assembly 30 and 130 acts as a primary seal and sealing assembly 51 in the upper valve housing 45 acts as a secondary seal or "apron seal".
- the pressure in the cylinder 33 travels into the seal cavity 49e as shown in FIG. 3 to force the sealing assembly 59 against a wall of the seal cavity 49e for enhancing the performance of the sealing assembly 59 for both sliding valve assemblies 30 and 130.
- FIG. 1C shows an exhaust stroke for a standard internal combustion engine 31.
- the intake valve 30 is closed while the exhaust valve 130 is opened.
- the burned gases are forced through the exhaust valve 130 and out of cylinder 33.
- the fluid conducting port 75 is aligned with the first fluid conducting passage 79 of the upper valve housing 45 and with the second fluid conducting passage 77 of lower valve housing plate 47.
- the pressure in cylinder 33 travels into the seal cavity 49e of valve body 49 as shown in FIG. 3 to enhance the performance of the sealing assembly 59 of both the intake valve 30 and the exhaust valve 130.
- the enhanced performance of sealing assembly 59 aids in directing the burned gases out through the first fluid conducting passage 79 of upper valve housing 45.
- the secondary seal ring 55 is positioned around the periphery of the primary seal ring 53 which has an external groove (shown in FIG.2 at reference numeral 53a) for receiving the secondary seal ring 55.
- the sealing assembly 51 is housed in the recessed groove or seal cavity 45e of upper valve housing 45. There is preferably a sufficient clearance provided in the seal cavity 45e to allow at least the secondary seal ring 55 to move freely within the seal cavity 45e.
- the resilient member 57 in the form of a hoop spring is arranged in the seal cavity 45e to apply a resilient force between the primary seal ring 53 and the wall of the seal cavity 45e to load the primary seal ring 53 against the wall of the seal cavity 45e in the upper valve housing 45.
- the resilient member 57 of the spring assembly 51 is shown as having a cylindrical shape it is to be appreciated that the resilient member 57 may have other shapes, for example, a non-cylindrical shape, for example, an obloid shape, a D-shape, or variations of a circle shape.
- the primary seal ring 53 and the secondary seal ring 55 preferably are split rings and that they may have a shape corresponding to the resilient member 57.
- the primary seal ring 53, the secondary seal ring 55 and the resilient member 57 of the sealing assembly 51 may have other shapes, for example, a non-cylindrical shape, for example, an obloid shape, a D-shape, or variations of a circle shape.
- the secondary seal ring 59b is positioned around the periphery of the primary seal ring 59a which has an external groove (shown in FIG.2 at reference numeral 59d) for receiving the secondary seal ring 59b.
- the sealing assembly 59 is housed in the recessed groove or seal cavity 49e of the valve body 49. There is preferably a sufficient clearance provided in the seal cavity 49e to allow at least the secondary seal ring 49b to move freely within the seal cavity 49e.
- the resilient member 59c in the form of a hoop spring is arranged in the seal cavity 49e to apply a resilient force between the primary seal ring 59a and the wall of the seal cavity 49e to load the primary seal ring 59a against the wall of the seal cavity 49e in the valve body 49.
- the resilient member 59c of the spring assembly 59 is shown as having a cylindrical shape it is to be appreciated that the resilient member 59c may have other shapes, for example, a non-cylindrical shape, for example, an obloid shape, a D-shape, or variations of a circle shape.
- the primary seal ring 59a and the secondary seal ring 59b preferably are split rings.
- the primary seal ring 59a and the secondary seal ring 59b may have other shapes corresponding to the resilient member 59c. It is also to be appreciated that the primary seal ring 59a, the secondary seal ring 59b, and the resilient member 59c of the sealing assembly 59 may have other shapes, for example, a non-cylindrical shape, for example, an obloid shape, a D-shape, or variations of a circle shape.
- FIG. 4 shows an example of the intake valve 30 and the exhaust valve 130 in an internal combustion engine 78 wherein a cylinder head 43 is integrated into an engine block containing a piston 37.
- This concept of a single-piece head block concept has several advantages such as a decrease in the number of engine parts, for example, head bolts and/or head gaskets, and therefore, a stronger engine block and reduced manufacturing costs.
- a further advantage would be easy access to the modular valve mechanisms for their service and/or replacement.
- FIG. 5 shows the sliding valve assembly of the invention as used in an internal combustion engine which may be similar to that disclosed in U.S. Patent Application Publication No. 2007/0289562 A1
- engine 81 has a compression cylinder 82 and an expansion cylinder 83 which communicate with opposite ends of a combustion chamber 84, with reciprocating pistons 85, 86 in the two cylinders forming compression chambers of variable volume.
- the pistons 85, 86 are connected to a crankshaft 87 by connecting rods 88, 89 for movement in concert between top dead center (TDC) and bottom dead center (BDC) positions in the cylinders, with each of the pistons 85, 86 making one upstroke and one downstroke during each revolution of the crankshaft 87.
- TDC top dead center
- BDC bottom dead center
- Compression cylinder 82 receives fresh air through an intake conduit 90 and intake valve 91 and communicates with the inlet end of combustion chamber 84 through an outlet valve 92. Fuel is injected into the combustion chamber 84 through a fuel injector 93 or other suitable fuel inlet, where it is mixed with the air from the compression cylinder 82. The mixture burns and expands in the combustion chamber 84, and the expanding gas flows into the expansion cylinder 83 from the outlet end of the combustion chamber 84 through an inlet valve 95. Exhaust gas is discharged from the expansion cylinder 83 through an outlet valve or exhaust valve 96 and through exhaust conduit 97.
- Intake valve 91, outlet valve 92, inlet valve 95, and exhaust valve 96 of FIG. 5 may be sliding valve assemblies of the invention similar to those discussed with reference to FIGS. 1A , 1B , 1C and 2 .
- the intake valve 91, the outlet valve 92, and the exhaust valve 96 preferably will have an upper valve housing 45 similar to that disclosed hereinabove with reference to FIGS. 1A , 1B , 1C and 2 , wherein the cap 45b is configured as shown in these figures and the pressure within the compression cylinder 82 of FIG. 5 acts primary on the sealing assembly 51 making this sealing assembly 51 the primary seal and the sealing assembly 59 the secondary or apron seal. Referring to FIGS.
- the upper valve housing 98 ( FIGS. 6A and 6B ) of the sliding valve assembly 95 will have a configuration such as that illustrated in FIGS. 6A and 6B wherein the expanding gas from the combustion chamber 84 of FIG. 5 acts upon the sealing assembly 51 contained within the upper valve housing 98 of the intake sliding valve assembly 95.
- FIG. 6A illustrates, as indicated by the downward pointing arrow, an intake stroke for the expansion cylinder 83 and the reciprocating piston 86 of engine 81 of FIG. 5
- FIG. 6B illustrates, as indicated by the upwardly pointing arrow, an exhaust stroke for the reciprocating piston 86 and the expansion cylinder 83 of FIG. 5
- the sliding valve assembly 95 is opened wherein the fluid conducting passages 98c and 77 and the fluid conducting port 75 of valve body 49 are in alignment.
- the sliding valve assembly 96 is closed wherein the fluid conducting passages 99c and 77 and the fluid conducting port 75 of valve body 49 are not in alignment.
- FIG. 6B illustrates the exhaust stroke for the reciprocating piston 86 and the expansion cylinder 83 of FIG. 5 , wherein the sliding valve assembly 95 is closed while the sliding valve assembly 96 is opened.
- the intake sliding valve assembly 95 includes the upper valve housing 98 having an annular member 98a, a cap 98b mounted in the annular member 98a and having a first fluid conducting passage 98c and a seal cavity 98d for retaining a sealing assembly 51. It is to be appreciated that the upper valve housing 95 further includes cams similar to cams 63 and 65 of FIG. 2 and cam followers 67, 69, 71 and 73, wherein cam follower 67 is shown in FIG. 6A . Additionally, the sliding valve assembly 95 further includes a valve body 49 having a sealing assembly 59 and a lower valve housing 47.
- the upper valve housing 98, the sealing assembly 51, the valve body 49, the sealing assembly 59 in the valve body 49, and the valve housing 47 are constructed similarly to that shown in FIGS. 1A through 2 .
- cap 98b has at least six ports or channels 98e, four of which are shown in FIGS. 6A and 6B . These ports 98e extend parallel to the first fluid conducting passage 98c of cap 98b.
- the expanding gas from the combustion chamber 84 of FIG. 5 will enter ports 98e to act upon sealing assembly 51 to enhance the performance of the sealing assembly 51.
- the sealing assembly 51 becomes the primary seal whereas the sealing assembly 59 in the valve body 49 becomes the secondary seal or "apron seal" in the system.
- the exhaust sliding valve assembly 96 of FIG. 5 includes an upper valve housing 99 having an annular member 99a and a cap 99b mounted in the annular member 99a, a first fluid conducting passage 99c in cap 99b, a seal cavity 99d formed within the annular member 99a, and a sealing assembly 51 retained in the annular member 99a of the upper valve housing 99.
- the exhaust sliding valve assembly 99 with its valve body 49, the sealing assembly 51, and sealing assembly 59 within the valve body 49 are constructed similarly to the sliding valve assemblies 91 and 92 of FIG. 5 , which in turn, are constructed similarly to the sliding valve assemblies 30 and 130 of FIGS. 1A through 2 . That is, the pressure in the expansion cylinder 83 of FIGS.
- valve assemblies 30, 130 also include cams 63 and 65 that have surfaces that cooperate with the surfaces of cam followers 67, 69, 71 and 73. These cooperating surfaces are responsive to the actuating rod 61 which arrangement, in effect, is designed to perform one or more functions.
- cams 63 and 65 and cam followers 67, 69, 71 and 73 upon the oscillation of valve body 49 within the valve housing by actuating rod 61 act to: 1) constrain the valve body 49 during its translating movements within the valve housing for opening and closing the valve assembly 30, 130 and 2) release the sealing pressure of the sealing assembly 59 against the top sealing surface of the lower valve housing or plate 47 when in a closed or blocking position of valve assembly 30, 130.
- the cams 63 and 65 preferably include surfaces located in housings on either sides 49a and 49b of the valve body 49 with the followers 67, 69, 71 and 73 rotatably attached to the lateral sides 49a, 49b of the valve body for engagement with the cam surfaces.
- the cam surfaces may be straight or they may have an inclined portion. If the cam surfaces have an inclined portion, then cam followers 67, 69, 71 and 73 will raise the valve body 49 away from the valve housing during the translational movement of the valve body 49 thereby effectively separating the valve body 49 from the valve housing and thus spacing at least the sealing assembly 59 from the lower valve housing 47.
- the movement of the valve body 49 and the sealing assembly 59 away from the lower valve housing 47 reduces the friction which otherwise may exist between the two sealing surfaces if the sealing assembly 59 still engages the fluid impervious surface 49a of the valve body 49.
- the linear cams 63 and 65 and cam followers 67, 69, 71 and 73 are designed to ramp the valve body 49 with its sealing assembly 59 from the sealing surfaces and to break contact between the sealing ring assembly 59 and the sealing surfaces thereby reducing friction between the two surfaces, and to break free of the frictional contact between the valve body 49 and the sealing assembly 51 and thereby allowing a more effective opening and/or closing of the sliding valve assembly of the present invention.
- the sealing assemblies 51 and 59 of the sealing system of the sliding valve assemblies of the invention are configured to seal the sliding valve assembly 30, 130 in at least a radial direction.
- the sealing assemblies 51 and 59 employ relatively fewer sealing components compared to previously known sliding valve assemblies.
- the characteristics of the sealing assemblies 51 and 59 and their location within its respective sliding valve assembly are expected to further improve the sealing effect of the sliding valve assembly 30, 130.
- actuating the actuating rod 61 to control actuation of intake valve 30 and exhaust valve 130 during operation of the engine illustrated in FIGS. 1A -1C may be employed.
- camshafts, solenoids, rocker arms, chains, gears, belts, and hydraulic, pneumatic, electric actuators, and/or other means may be employed to cause translational movement of the valve body 49 by actuator 61.
- engine 31 when used in conjunction with the sliding intake and exhaust valves 30 and 130 of the present invention, may be similar to that disclosed in U.S. Patent No. 6,976,464 B2 issued on December 20, 2005 , the teachings of which are incorporated by reference herein in their entirety.
- the intake and exhaust valves 20 and 120 are semi-rotating valve assemblies instead of sliding valve assemblies.
- engine 31 and sliding valve assemblies 30 and 130 of the present invention as depicted FIGS. 1A-1C appear in the environment of a four stroke Otto cycle, it will be apparent to one skilled in the art that sliding valve assemblies 30 and 130 of the present invention may be employed in other engines that operate on other cycles, such as a two-stroke cycle.
- FIGS. 7, 8 and 9 show a further embodiment for a valve body of a sliding valve assembly of the present invention.
- the valve body 100 includes a front cam follower 101 and a rear cam follower 103 both of which extend substantially across the width of the valve body 100.
- valve body 100 includes a fluid conducting port 105 and an actuator rod 107 for translating movement of valve body 100 within a valve housing similar to that discussed hereinabove with reference to FIGS. 1A through 2 .
- Valve body 100 further includes a sealing assembly 109 on its lower surface 111 wherein sealing assembly 109 is constructed and functions similarly to that of sealing assembly 59 of FIGS. 1A through 2 .
- Valve body 100 operates within the valve housing similar to that discussed herein above wherein the fluid conducting port 105 comes into and out of alignment with first fluid conducting passage and the second fluid conducting passage of the valve housing.
- the front cam follower 101 and the rear cam follower 103 cooperate with cam surfaces 112, 114 respectively, to raise and lower the valve body 100 within the valve housing and to reduce the frictional forces between the contact surfaces to enhance the life of the sealing assembly 109 and to allow the valve to effectively open and close.
- Cam surfaces 112, 114 may also have straight profiles.
- the sealing assemblies 51, 59 and 109 of the sliding valve assembly of the invention may be considered as being a dynamic seal, that is, a pressure energized seal.
- An advantage of a dynamic seal is that a relatively small area is in contact with the dynamic surface, thereby producing little friction, resulting in long life of the engine and improved sealing especially at high speeds of the engine.
- the sealing assemblies 51, 59, and 109 of the invention have a continuous load from its respective resilient member or tension spring to provide a sealing line. As the system pressure increases, these sealing assemblies 51, 59 and 109 are compressed against the sealing surface by the additional pressure in the system, thereby maintaining and/or improving the effectiveness of the seal.
- the sealing assembly 59 is generally in communication with a combustion chamber wherein pressure is increased in the system and this increased pressure acts on the sealing assembly 59 to increase its sealing effectiveness.
- pressure is directed from the combustion chamber 84 and into the ports or channels 98e of the cap 98b and against the sealing assembly 51.
- the cap mounted in the upper valve housing may be removable and interchangeable depending on whether pressure is received relative to the upper valve housing or relative to the lower valve housing. That is, if the pressure in the system is available from the combustion chamber 84 of FIGS.
- cap 98b with channels 98e for delivering the pressure directly against the sealing assembly 51 may be provided in the upper valve housing 98; however if the pressure in the system is available from the compression cylinder 82 of FIG. 5 , then a cap without channels may be provided in the upper valve housing such as cap 45b of the upper valve housing 45 of FIGS. 1A through 1C .
- valve assembly of the invention may be a rotary valve assembly, a semi-rotating valve assembly, an oscillating valve assembly or any other type of valve assembly used in various applications especially pressure systems for effectively operating the sealing assembly of the present invention.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Sealing With Elastic Sealing Lips (AREA)
- Mechanically-Actuated Valves (AREA)
- Sliding Valves (AREA)
- Taps Or Cocks (AREA)
Description
- The present invention relates to a valve assembly suitable for use in a pressure system involving a pressure actuator, for example, an energy conversion engine, e.g. an internal combustion engine or a heat engine, e.g. a diesel engine, a Sterling cycle engine, a Miller cycle engine, and an Otto cycle engine. More particularly, the present invention relates to a sliding valve assembly for use in a pressure system and having an improved sealing system configured to reduce friction, heat and wear on the valve and body related sealing components.
- Most modem internal combustion engines utilize a four stroke operating sequence known as the Otto cycle. The Otto cycle comprises an intake stroke, in which an intake valve opens and a mixture of air and fuel is directed into the cylinder of the engine. A compression stroke then occurs in which the piston compresses the mixture of fuel and air to increase the pressure in the cylinder. A spark provided by a spark plug ignites the mixture just before the piston reaches the top of the cylinder, causing the piston to be forced down in the cylinder in the power stroke. An exhaust valve then opens in the exhaust stroke, in which burned gases are forced out of the cylinder. The four strokes are repeated continuously during operation of the engine.
- Internal combustion engines operating on the Otto cycle principal generally utilize spring-loaded poppet valves that selectively open and close the intake and exhaust ports during each cycle. In most engines, a crankshaft is coupled to a timing belt or chain, which in turn is coupled to a camshaft that rotates to open the intake and exhaust valves during the intake and exhaust strokes, respectively. A spring associated with each valve closes the valve during the other cycles.
- There are several drawbacks associated with the use of such spring-loaded poppet valves. One drawback is that the valves protrude into the cylinder during each cycle, and there is an inherent risk that the piston may contact an open valve at a high force and cause substantial engine damage. Additionally, valve timing events may be limited due to the protrusion of the valve head into the cylinder.
- Another disadvantage with the use of poppet valves in conventional internal combustion engines is that a relatively stiff spring is used to close the valves. Therefore, a relatively strong force is required to overcome the resistive force of the spring to open each valve during each cycle, reducing the efficiency of the engine. Moreover, due to the stiff resistive force provided by the springs, valve timing events may be limited. For example, there generally is a short time period during which both the intake valve and the exhaust valve are open when conventional poppet valves and stiff springs are employed. During this overlap period, unburned hydrocarbon molecules may remain in the combustion chamber for a subsequent cycle, thereby adversely affecting dynamic compression and reducing engine efficiency.
- Yet a further disadvantage associated with the use of conventional poppet valves is that energy is lost as a result of an obstruction of the orifice, i.e., because a portion of a poppet valve protrudes through the orifice and into the cylinder. Moreover, flow into the cylinder through the intake port is disrupted when it contacts the head of the poppet valve, i.e., the portion of the valve that seals the orifice in the closed state. The intake valve head may cause turbulence and dead air space within the cylinder, which in turn reduces the efficiency of the engine. Furthermore, when the head of the exhaust valve protrudes into the cylinder during the exhaust stroke, burned gases may not efficiently flow out of the cylinder, which further reduces combustion capabilities.
- Various sliding valve designs, which may be used in conjunction with internal combustion engines, have been developed to overcome several of the drawbacks associated with conventional poppet valves. One primary advantage of a sliding valve assembly is the capability to have a substantially unobstructed flow path. Specifically, because a conventional poppet valve is not employed, and therefore does not obstruct the flow path through an intake or exhaust port, a sliding valve has the potential to significantly increase airflow capability into a cylinder. Moreover, since the stiff springs used in conjunction with conventional poppet valves may be omitted, sliding valve assemblies may achieve reduced mechanical loads.
- Some sliding valve assemblies have rotating discs, cylinders, sleeves and other spheroidal rotating mechanisms. Such previously known sliding valves may be timed such that their apertures overlap with the cylinder during the intake and exhaust strokes. However, due to their continuous seal contact, these known sliding valves may experience high temperatures and extreme friction, resulting in high rates of wear imposed on the valve and any related sealing mechanisms.
- Moreover, such sliding valve assemblies generally have fixed aperture sizes, i.e., the size of the aperture in registration with the cylinder may not be varied as the valve is translated or displaced i.e. moved back and forth in a plane as opposed to rotation. Accordingly, the fuel consumption and emissions may be increased by providing a relatively large port aperture, resulting in low gas velocities, which adversely affect engine performance at low engine speeds, particularly during idling conditions.
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- Another drawback associated with some of the sliding valve systems of the prior art is the complexity of the sealing system employing a significant number of seals. It would be desirable to provide an effective sealing system for a sliding valve system that employs significantly fewer components.
- There is a need therefore to provide a sliding valve assembly that is configured to be easily incorporated into a pressure system, for example, energy conversion engines, e.g. internal combustion engines.
- There is a still further need to provide a sliding valve assembly that is configured to reduce friction, heat and wear on the valve body and related sealing components.
- There is yet a further need to provide a sliding valve assembly having an improved sealing system configured to effectively seal the valve and/or the combustion chambers of the piston cylinder assemblies associated with energy conversion engines or having an improved sealing system configured to effectively seal the valve and/or the pressure chambers associated with pressure systems.
- The present invention has met these needs. The present invention provides a sliding valve assembly for introducing and/or exhausting a fluid medium relative to a combustion chamber or cylinder containing a reciprocating piston for an energy conversion engine, for example, an internal combustion engine. The sliding valve assembly includes: a valve housing having a first fluid conducting passage and a second fluid conducting passage separated by a valve cavity; a valve body contained in the valve cavity of the valve housing and having a fluid conducting port adjacent to a fluid impervious surface; an actuator for translating movements of the valve body within the valve cavity of the valve housing into a fluid conducting position wherein the fluid conducting port of the valve body allows a fluid conducting relationship between the first fluid conducting passage and the second fluid conducting passage of the valve housing and into a fluid blocking position where the fluid impervious surface of the valve body obstructs a fluid conducting relation between the first fluid conducting passage and the second fluid conducting passage of the valve housing; cooperating surfaces on the valve body and the valve housing for constraining the valve body during the translating movements of the valve body within the valve cavity of the valve housing between the fluid conducting position and the fluid blocking position of the valve body; and a sealing system including a first sealing assembly located within the fluid impervious surface of the valve body for forming a sealing relationship between the valve body and the valve housing, said first sealing assembly in communication with the pressure in the system and adapted to receive the pressure in the system thereby increasing the effectiveness of the first sealing assembly. The sealing system also includes a second sealing assembly located within the valve housing for forming a second sealing relationship between the valve housing and the valve body.
- The first sealing assembly and the second sealing assembly include a primary seal ring, a secondary seal ring surrounding the periphery of the primary seal ring, and a resilient member, e.g. tension spring arranged to apply a resilient force between the primary seal ring and its respective sealing surface for loading the primary seal ring against its respective sealing surface. With regard to the first sealing assembly, the sealing surface may include a wall of the seal cavity of the valve body; whereas with regard to the second sealing assembly, the sealing surface may include a wall of the seal cavity of the valve housing.
- The first sealing assembly and the second sealing assembly and its primary seal ring may have one of many shapes, e.g. cylindrical or non-cylindrical, for example, obloid and D-shape, and the secondary seal ring is freely moveable relative to the primary seal ring within its respective seal cavity.
- The valve housing also includes a cap mounted within an annular member of the upper valve housing. This cap may include a plurality of parallel ports or channels, each forming a passage for the fluid medium and/or pressure in the system for delivering pressure to at least the second sealing assembly located within the valve housing for increasing its sealing effectiveness against the sealing surface of the valve housing. This arrangement of the ports or channels for directing high pressure in a combustion chamber of a cylinder to the sealing assembly acts to enhance the sealing effect of this second sealing assembly. Absent these ports, the pressure within the system travels within the seal cavity containing the first and/or second sealing assembly to force or pressure the primary seal ring and the secondary seal ring of the first and/or second sealing assembly against one or more sealing surfaces of the seal cavity containing the first and/or second sealing assembly to force or further pressure the primary seal ring and the secondary seal ring of the first and/or second sealing assembly against one or more sealing surfaces of the valve body or the valve housing.
- The cooperating surfaces may include one or more cams and cam followers responsive to the valve body actuator. These cooperating surfaces of the cams and cam followers may act to constrain the valve body during its translating movements within the valve housing for opening and closing the valve assembly. The cams may include surfaces located in housings on either side of the valve body or in the valve body itself, with the followers attached to the lateral sides of the valve body for engagement with the cam surfaces. The cam surfaces may be straight or they may have an inclined portion. If the cam surfaces have an inclined portion, the followers will be raised thereby raising the valve body away from the valve housing during the translational movement of the valve body thereby effectively separating the valve body from the valve housing and thus moving at least the first sealing assembly away from the lower portion of the valve housing.
- A further embodiment includes a front cam follower and a rear cam follower mounted along the width of the valve body wherein these cam followers cooperate with cam surfaces of the valve housing for reducing the friction between the contact and/or sealing surfaces of the sealing system of the sliding valve assembly.
- Advantageously, because the valve body is forced away from the sealing surface of the valve housing by the linear cam and cam followers during the translational movement or oscillations of the valve body relative to the valve housing by the actuator, the friction, heat and wear on the valve, the valve body and related sealing components may be substantially reduced compared to conventional sliding valves.
- The valve body is disposed substantially within the valve cavity or bore of the valve housing. The valve body is configured to translate or oscillate within the valve housing via a cam and actuator system according to the timing of the rotation of the camshaft and crankshaft, thereby selectively enabling or preventing fluid communication between the passageway of the valve body and a cylinder of an internal combustion engine. Specifically, translational movement of the valve body in a first direction enables fluid communication, while translational movement of the valve body in an opposing direction prevents fluid communication with the cylinder. In this latter or closed position of the valve assembly, the pressure in the system, e.g. cylinder pressure and the resilient member, e.g. spring of the sealing assembly or sealing assemblies provide an effective seal for the pressure system.
- Any number of types of actuators may be used for the translational movement of the valve body. For example, camshafts, solenoids, rocker arms, chains, gears, belts, and hydraulic, pneumatic, electric actuators, and/or other means may be employed to cause translational movement of the valve body. Thus, the present invention further allows considerable flexibility with respect to the different types of actuators that may be employed, particularly compared to prior art sliding valve assemblies that rely solely on conventional mechanisms to provide the translational movement of the valve. Such design flexibility provides various advantages in addition to the translational movement of the valve body, for example, the attainment of variable aperture sizes and timing events, as generally described herein below.
- If used in a conventional internal combustion engine, a first sliding valve assembly of the present invention would be employed as an intake valve, and a second sliding valve assembly of the invention would be employed as an exhaust valve.
- The valve assembly of the invention may also be used effectively in any number of pressure systems. The valve assembly may be any one of a number of valve assemblies, for example, a sliding valve assembly, a rotating valve assembly, a semi-rotating valve assembly, or an oscillating valve assembly.
- It is therefore, an object of the present invention to provide a valve assembly with an improved sealing system for use in a pressure system, such as an energy conversion engine or heat engine, for example, in internal combustion engines.
- It is a further object of the present invention to provide a valve assembly such as a sliding valve assembly having an improved sealing system that is configured to reduce friction, heat and wear on the valve and body related sealing components.
- It is still a further object of the present invention to provide a valve assembly such as a sliding valve assembly having an improved sealing system such that as the system pressure increases, the pressure causes the seal to be compressed against a sealing surface thereby increasing the effectiveness of the sealing system.
- It is yet a further object of the present invention to provide a valve assembly such as a sliding valve assembly that may be actuated using any number of means thereby affording more design flexibility.
- These and other advantages and objects of the present invention will be better appreciated and understood when read in light of the accompanying drawings.
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FIG. 1A is a perspective, partially cut-away view of a sliding valve assembly according to the present invention used as an intake valve and an exhaust valve during an intake stroke of a standard internal combustion engine. -
FIG. 1B is a perspective, partially cut-away view of the sliding valve assembly according to the present invention used as an intake valve and an exhaust valve during a compression or power stroke of a standard combustion engine. -
FIG. 1C is a perspective, partially cut-away view of the sliding valve assembly according to the present invention used as an intake and exhaust valve during an exhaust stroke of a standard internal combustion. -
FIG. 2 is an exploded perspective view of the sliding valve assembly of the present invention. -
FIG. 3 is a schematic, cross-sectional, enlarged view illustrating the path of pressurized gas as it enters a seal cavity containing a sealing assembly in a valve body of the sliding valve assembly of the present invention relative to a compression cylinder. -
FIG. 4 is a perspective view of a standard internal combustion engine wherein a cylinder head is integrated into an engine block and incorporating the sliding valve assembly of the present invention as an intake valve and an exhaust valve. -
FIG. 5 is an elevational sectional view of a design for an internal combustion engine which may incorporate one or more sliding valve assemblies of the present invention. -
FIG. 6A is a perspective, partially cut-away view of the sliding valve assembly according to the present invention used as an intake valve and an exhaust valve during an intake stroke of the internal combustion engine ofFIG. 5 . -
FIG. 6B is a perspective, partially cut-away view of the sliding valve assembly according to the present invention used as an intake valve and an exhaust valve during an exhaust stroke of the internal combustion engine ofFIG. 5 . -
FIG. 7 is a perspective view of a further embodiment of a sliding valve assembly according to the teachings of the present invention. -
FIG. 8 is a bottom elevational view of the sliding valve assembly ofFIG. 7 . -
FIG. 9 is a side elevational view of the sliding valve assembly ofFIG.7 . - The valve assembly including an improved sealing system of the present invention may be a sliding valve assembly, a rotary valve assembly, a semi-rotary valve assembly or an oscillatory valve assembly for use in a pressure system which may or may not include a pressure actuator, for example, an energy conversion engine, e.g. an internal combustion engine or a heat engine, for example, a diesel engine, a Sterling cycle engine, a Miller cycle engine, and an Otto cycle engine.
- Referring to
FIGS. 1A ,1B ,1C and2 , the slidingvalve assembly FIGS. 1A - 1C , an intake valve of the present invention will be referred to generally as anintake valve 30 while an exhaust valve will be referred to generally as anexhaust valve 130, although each valve preferably is provided in accordance with the slidingvalve assembly 30 ofFIG. 2 . InFIGS. 1A through 1C , theintake valve 30 and theexhaust valve 130 are broken away for clarity purposes so as to more clearly see the location of the sealing system within the sliding valve assembly of the invention. - In
FIGS. 1A - 1C , a standardinternal combustion engine 31 comprises acylinder 33, acombustion chamber 35 and apiston 37, which is coupled to a crankshaft via a connecting rod (not shown) in a manner known to those skilled in the art.Intake valve 30 andexhaust valve 130 may be provided as separate modular components that are disposed atopcylinder head 43 or within thehead 43 or, alternatively,intake valve 30 andexhaust valve 130 may be formed as single units withincylinder head 43, as illustrated inFIG. 4 . Thevalve assemblies engine block 43, thus eliminating the need for a separable cylinder head. A single-piece head/block arrangement has several advantages. For example, the head bolts may be eliminated or the number of head bolts may be reduced. The engine block may be of a stronger and sturdier construction. The head gaskets and attaching hardware may be eliminated, thus allowing easy access for maintenance, i.e. service, and access, and, thus reduced manufacturing and maintenance costs. -
FIG. 2 shows one sliding valve assembly of the present invention for use in an internal combustions engine wherein as stated herein above the slidingvalve assembly intake valve 30 and anexhaust valve 130. Therefore, two sliding valve assemblies of the invention will be provided relative tocylinder 33. Slidingvalve assembly upper valve housing 45 and alower valve housing 47; avalve body 49 which is housed in the valve housing; and a sealing system including a sealingassembly 51 which includes aprimary seal ring 53, asecondary seal ring 55 and a resilient member orspring 57 and a sealingassembly 59 which includes aprimary seal ring 59a, asecondary seal ring 59b, and a resilient member orspring 59c. As shown inFIG. 2 , thelower valve housing 47 is a single plate extending over thecombustion chamber 35 ofcylinder 33. Also, as shown inFIG. 2 , theupper valve housing 45 for each slidingvalve assembly valve housing plate 47. Theupper valve housing 45 is fixedly connected to the lowervalve housing plate 47 through suitable means such as welding. The lowervalve housing plate 47 and thecylinder 33 are connected together by fasteners (not shown) such as screws received inapertures 47a in the lowervalve housing plate 47 andapertures 33a ofcylinder 33. - Still referring to
Figure 2 slidingvalve assembly valve actuating rod 61;linear cams cam followers lateral sides valve body 49.Linear cam 63 has cooperating cam surfaces 63a and 63b which are engaged bycam followers linear cam 65 has cooperating cam surfaces 65a and 65b which are engaged bycam followers Cam followers cam surfaces valve body 49 is translated or oscillated within the valve housing via actuation ofactuator rod 61.Actuator rod 61 is received inaperture 49c ofvalve body 49 wherein it is retained via retainingpin 74. It is to be appreciated that the arrangement of thevalve actuating rod 61 withinaperture 49c via retainingpin 74 is such thatactuating rod 61 is permitted to freely move or toggle relative tovalve body 49 during movement of thevalve body 49 within the valve housing. This toggle feature becomes particularly important whenlinear cams followers cams - As further shown in
FIG. 2 ,valve body 49 has an opening orfluid conducting port 75, theupper valve housing 45 has an opening or a firstfluid conducting passage 79, and the lowervalve housing plate 47 has an opening or a secondfluid conducting passage 77. Theupper valve housing 45 has anannular member 45a which receives acap 45b defining the firstfluid conducting passage 79. Theupper valve housing 45 also includes twochannels cams valve body 49 is assembled within theupper valve housing 45. - As best shown in
FIGS. 1A ,1B and1C pertaining to a standard internal combustion engine,cap 45b is mounted within theannular member 45a of theupper valve housing 45 and forms aseal cavity 45e for retaining the sealingassembly 51, the latter of which is shown best inFIG. 2 . As also shown inFIGS. 1A ,1B and1C , thevalve body 49 has a lower fluidimpervious surface 49d that is adjacent to or juxtaposed relative to thefluid conducting port 75 of thevalve body 49. Thevalve body 49 further includes aseal cavity 49e for retaining the sealingassembly 59, the latter of which is shown best inFIG. 2 . - When the lower
valve housing plate 47, theupper valve housing 45 and thevalve body 49 are assembled as shown inFIGS. 1A ,1B and1C , thefluid conducting port 75 of thevalve body 49, the firstfluid conducting passage 79 ofupper valve housing 45 and the secondfluid conducting passage 77 of the lowervalve housing plate 47 cooperate to open the slidingvalve assembly 30 when thefluid conducting port 75 of thevalve body 49 is aligned with thepassages port 75 withpassages valve assembly 30 is referred to as being the fluid conducting position or the opened position of the slidingvalve assembly 30. - Conversely, when the
fluid conducting port 75 of thevalve body 49 is not in alignment with the first conductingpassage 79 and thesecond conducting passage 77, respectively of theupper valve housing 45 and the lowervalve housing plate 47, the slidingvalve assembly 30 is in a blocked or closed position. This blocked or closed position of the slidingvalve assembly 30 is referred to herein as being the fluid blocking position or the closed position of the slidingvalve assembly 30. Additionally, when theupper valve housing 45, the lowervalve housing plate 47 and thevalve body 49 are assembled as shown inFIGS. 1A ,1B , and1C , the sealingassembly 51 is received in a recessed portion or sealcavity 45e of theupper valve housing 45 and the sealingassembly 59 is received in a recessed portion or sealcavity 49e in the lower fluidimpervious surface 49d of thevalve body 49, as discussed herein above. - For the standard internal combustion engine of
FIG. 1A , theintake valve 30 is illustrated as being in a fluid conducting position or in its intake stroke position wherein theintake valve 30 opens and a mixture of air and fuel is directed intocylinder 33 to force thepiston 37 downwardly as indicated by the arrow. For this intake stroke of slidingvalve assembly 30, theexhaust valve 130 is in its fluid blocking position or closed position wherein thevalve body 49 totally blocks thefluid conducting passage 79 of theupper valve housing 45 and thefluid conducting passage 77 of the lowervalve housing plate 47. In this instance and with respect to both theintake valve 30 and theexhaust valve 130, the sealingassembly 59 in theseal cavity 49e of thevalve body 49 becomes the primary seal and the sealingassembly 51 in theupper valve housing 45 becomes the secondary seal, which is commonly referred to as an "apron seal". Also in this instance as shown inFIG. 3 , as the pressure in thecombustion chamber 35 increases, the pressurized air or gas is caused to flow into theseal cavity 49e of thevalve body 49 as shown by the arrows and to act against sealingassembly 59, particularly against thesecond sealing ring 59b to force the sealingassembly 59 against a wall surface of theseal cavity 49e to increase the effectiveness of the sealingassembly 59 for bothvalve sliding assemblies combustion chamber 35 upon the intake stroke of the slidingvalve assembly 30 and is prevented from seeping out of theexhaust valve assembly 130 in view of itsrespective sealing assemblies assembly 59 withinvalve body 49 and the pressure acting upon the sealingassembly 59 as illustrated inFIG. 3 . - It is to be further appreciated that with reference to
FIG. 3 , the sealingassembly 59 is constructed similarly to that disclosed herein above with reference toFIGS. 1A through 2 . That is, the sealingassembly 59 ofFIG. 3 includes aprimary seal ring 59a, asecondary seal ring 59b positioned around the periphery of theprimary seal ring 59a, and aresilient member 59c. InFIG. 3 , theresilient member 59c is not shown for clarity purposes so as to more clearly indicate the path the pressure travels fromchamber 35. -
FIG. 1B shows a compression stroke or power stroke for a standardinternal combustion engine 31. As illustrated, theintake valve 30 and theexhaust valve 130 are both closed. In this compression stroke,piston 37 compresses the air and fuel to increase the pressure incylinder 33. A spark ignites the mixture beforepiston 37 reaches the top ofcylinder 33 causing thepiston 37 to be forced downwardly in thecylinder 33 in its power stroke as indicated by the arrow. Here again, sealingassembly 59 of each slidingvalve assembly assembly 51 in theupper valve housing 45 acts as a secondary seal or "apron seal". Here again, the pressure in thecylinder 33 travels into theseal cavity 49e as shown inFIG. 3 to force the sealingassembly 59 against a wall of theseal cavity 49e for enhancing the performance of the sealingassembly 59 for both slidingvalve assemblies -
FIG. 1C shows an exhaust stroke for a standardinternal combustion engine 31. As illustrated, theintake valve 30 is closed while theexhaust valve 130 is opened. In this exhaust stroke ofpiston 37, the burned gases are forced through theexhaust valve 130 and out ofcylinder 33. In this opened position forexhaust valve 130 thefluid conducting port 75 is aligned with the firstfluid conducting passage 79 of theupper valve housing 45 and with the secondfluid conducting passage 77 of lowervalve housing plate 47. Here again, the pressure incylinder 33 travels into theseal cavity 49e ofvalve body 49 as shown inFIG. 3 to enhance the performance of the sealingassembly 59 of both theintake valve 30 and theexhaust valve 130. For theexhaust valve 130, the enhanced performance of sealingassembly 59 aids in directing the burned gases out through the firstfluid conducting passage 79 ofupper valve housing 45. - Still referring to
FIGS. 1A ,1B and1C when the sealingassembly 51 is assembled, thesecondary seal ring 55 is positioned around the periphery of theprimary seal ring 53 which has an external groove (shown inFIG.2 at reference numeral 53a) for receiving thesecondary seal ring 55. As discussed herein above, the sealingassembly 51 is housed in the recessed groove orseal cavity 45e ofupper valve housing 45. There is preferably a sufficient clearance provided in theseal cavity 45e to allow at least thesecondary seal ring 55 to move freely within theseal cavity 45e. Theresilient member 57 in the form of a hoop spring is arranged in theseal cavity 45e to apply a resilient force between theprimary seal ring 53 and the wall of theseal cavity 45e to load theprimary seal ring 53 against the wall of theseal cavity 45e in theupper valve housing 45. Even though theresilient member 57 of thespring assembly 51 is shown as having a cylindrical shape it is to be appreciated that theresilient member 57 may have other shapes, for example, a non-cylindrical shape, for example, an obloid shape, a D-shape, or variations of a circle shape. It is also to be appreciated that theprimary seal ring 53 and thesecondary seal ring 55 preferably are split rings and that they may have a shape corresponding to theresilient member 57. It is also to be appreciated that theprimary seal ring 53, thesecondary seal ring 55 and theresilient member 57 of the sealingassembly 51 may have other shapes, for example, a non-cylindrical shape, for example, an obloid shape, a D-shape, or variations of a circle shape. - Still referring to
FIGS. 1A ,1B and1C in assembling the sealingassembly 59, thesecondary seal ring 59b is positioned around the periphery of theprimary seal ring 59a which has an external groove (shown inFIG.2 at reference numeral 59d) for receiving thesecondary seal ring 59b. The sealingassembly 59 is housed in the recessed groove orseal cavity 49e of thevalve body 49. There is preferably a sufficient clearance provided in theseal cavity 49e to allow at least thesecondary seal ring 49b to move freely within theseal cavity 49e. Theresilient member 59c in the form of a hoop spring is arranged in theseal cavity 49e to apply a resilient force between theprimary seal ring 59a and the wall of theseal cavity 49e to load theprimary seal ring 59a against the wall of theseal cavity 49e in thevalve body 49. Even though theresilient member 59c of thespring assembly 59 is shown as having a cylindrical shape it is to be appreciated that theresilient member 59c may have other shapes, for example, a non-cylindrical shape, for example, an obloid shape, a D-shape, or variations of a circle shape. It is also to be appreciated that theprimary seal ring 59a and thesecondary seal ring 59b preferably are split rings. It is also to be appreciated that theprimary seal ring 59a and thesecondary seal ring 59b may have other shapes corresponding to theresilient member 59c. It is also to be appreciated that theprimary seal ring 59a, thesecondary seal ring 59b, and theresilient member 59c of the sealingassembly 59 may have other shapes, for example, a non-cylindrical shape, for example, an obloid shape, a D-shape, or variations of a circle shape. -
FIG. 4 shows an example of theintake valve 30 and theexhaust valve 130 in aninternal combustion engine 78 wherein acylinder head 43 is integrated into an engine block containing apiston 37. This concept of a single-piece head block concept has several advantages such as a decrease in the number of engine parts, for example, head bolts and/or head gaskets, and therefore, a stronger engine block and reduced manufacturing costs. A further advantage would be easy access to the modular valve mechanisms for their service and/or replacement. -
FIG. 5 shows the sliding valve assembly of the invention as used in an internal combustion engine which may be similar to that disclosed inU.S. Patent Application Publication No. 2007/0289562 A1 InFIG. 5 ,engine 81 has acompression cylinder 82 and anexpansion cylinder 83 which communicate with opposite ends of acombustion chamber 84, withreciprocating pistons pistons crankshaft 87 by connectingrods pistons crankshaft 87.Compression cylinder 82 receives fresh air through anintake conduit 90 andintake valve 91 and communicates with the inlet end ofcombustion chamber 84 through anoutlet valve 92. Fuel is injected into thecombustion chamber 84 through afuel injector 93 or other suitable fuel inlet, where it is mixed with the air from thecompression cylinder 82. The mixture burns and expands in thecombustion chamber 84, and the expanding gas flows into theexpansion cylinder 83 from the outlet end of thecombustion chamber 84 through aninlet valve 95. Exhaust gas is discharged from theexpansion cylinder 83 through an outlet valve orexhaust valve 96 and throughexhaust conduit 97. -
Intake valve 91,outlet valve 92,inlet valve 95, andexhaust valve 96 ofFIG. 5 , may be sliding valve assemblies of the invention similar to those discussed with reference toFIGS. 1A ,1B ,1C and2 . In this instance, theintake valve 91, theoutlet valve 92, and theexhaust valve 96 preferably will have anupper valve housing 45 similar to that disclosed hereinabove with reference toFIGS. 1A ,1B ,1C and2 , wherein thecap 45b is configured as shown in these figures and the pressure within thecompression cylinder 82 ofFIG. 5 acts primary on the sealingassembly 51 making this sealingassembly 51 the primary seal and the sealingassembly 59 the secondary or apron seal. Referring toFIGS. 5 ,6A and6B , since the expanding gas flows from thecombustion chamber 84 and into theinlet valve 95 ofexpansion cylinder 83, the upper valve housing 98 (FIGS. 6A and6B ) of the slidingvalve assembly 95 will have a configuration such as that illustrated inFIGS. 6A and6B wherein the expanding gas from thecombustion chamber 84 ofFIG. 5 acts upon the sealingassembly 51 contained within theupper valve housing 98 of the intake slidingvalve assembly 95. -
FIG. 6A illustrates, as indicated by the downward pointing arrow, an intake stroke for theexpansion cylinder 83 and thereciprocating piston 86 ofengine 81 ofFIG. 5 andFIG. 6B illustrates, as indicated by the upwardly pointing arrow, an exhaust stroke for thereciprocating piston 86 and theexpansion cylinder 83 ofFIG. 5 . InFIG. 6A the slidingvalve assembly 95 is opened wherein thefluid conducting passages fluid conducting port 75 ofvalve body 49 are in alignment. InFIG. 6A , the slidingvalve assembly 96 is closed wherein thefluid conducting passages fluid conducting port 75 ofvalve body 49 are not in alignment.FIG. 6B illustrates the exhaust stroke for thereciprocating piston 86 and theexpansion cylinder 83 ofFIG. 5 , wherein the slidingvalve assembly 95 is closed while the slidingvalve assembly 96 is opened. - Referring particularly to
FIGS. 6A and6B , the intake slidingvalve assembly 95 includes theupper valve housing 98 having anannular member 98a, acap 98b mounted in theannular member 98a and having a firstfluid conducting passage 98c and aseal cavity 98d for retaining a sealingassembly 51. It is to be appreciated that theupper valve housing 95 further includes cams similar tocams FIG. 2 andcam followers cam follower 67 is shown inFIG. 6A . Additionally, the slidingvalve assembly 95 further includes avalve body 49 having a sealingassembly 59 and alower valve housing 47. With regard to the slidingvalve assembly 95, theupper valve housing 98, the sealingassembly 51, thevalve body 49, the sealingassembly 59 in thevalve body 49, and thevalve housing 47 are constructed similarly to that shown inFIGS. 1A through 2 . However, the difference is thatcap 98b has at least six ports orchannels 98e, four of which are shown inFIGS. 6A and6B . Theseports 98e extend parallel to the firstfluid conducting passage 98c ofcap 98b. With particular reference toFIG. 6A , the expanding gas from thecombustion chamber 84 ofFIG. 5 will enterports 98e to act upon sealingassembly 51 to enhance the performance of the sealingassembly 51. In this instance, the sealingassembly 51 becomes the primary seal whereas the sealingassembly 59 in thevalve body 49 becomes the secondary seal or "apron seal" in the system. - Referring particularly to
FIGS. 6A and6B , the exhaust slidingvalve assembly 96 ofFIG. 5 includes anupper valve housing 99 having anannular member 99a and acap 99b mounted in theannular member 99a, a firstfluid conducting passage 99c incap 99b, aseal cavity 99d formed within theannular member 99a, and a sealingassembly 51 retained in theannular member 99a of theupper valve housing 99. Again, the exhaust slidingvalve assembly 99 with itsvalve body 49, the sealingassembly 51, and sealingassembly 59 within thevalve body 49 are constructed similarly to the slidingvalve assemblies FIG. 5 , which in turn, are constructed similarly to the slidingvalve assemblies FIGS. 1A through 2 . That is, the pressure in theexpansion cylinder 83 ofFIGS. 6A and6B will act primarily on the sealingassembly 59 of the exhaust slidingvalve assembly 96, thereby making the sealingassembly 59 of the exhaust slidingvalve assembly 96 the primary seal and the sealingassembly 51 of the exhaust slidingvalve assembly 96 the second seal or "apron seal". - Referring again to
FIG. 2 ,valve assemblies cams cam followers actuating rod 61 which arrangement, in effect, is designed to perform one or more functions. For example,cams cam followers valve body 49 within the valve housing by actuatingrod 61 act to: 1) constrain thevalve body 49 during its translating movements within the valve housing for opening and closing thevalve assembly assembly 59 against the top sealing surface of the lower valve housing orplate 47 when in a closed or blocking position ofvalve assembly cams sides valve body 49 with thefollowers lateral sides cam followers valve body 49 away from the valve housing during the translational movement of thevalve body 49 thereby effectively separating thevalve body 49 from the valve housing and thus spacing at least the sealingassembly 59 from thelower valve housing 47. The movement of thevalve body 49 and the sealingassembly 59 away from thelower valve housing 47 reduces the friction which otherwise may exist between the two sealing surfaces if the sealingassembly 59 still engages the fluidimpervious surface 49a of thevalve body 49. Thelinear cams cam followers valve body 49 with its sealingassembly 59 from the sealing surfaces and to break contact between the sealingring assembly 59 and the sealing surfaces thereby reducing friction between the two surfaces, and to break free of the frictional contact between thevalve body 49 and the sealingassembly 51 and thereby allowing a more effective opening and/or closing of the sliding valve assembly of the present invention. - Referring particularly to
FIGS. 1A through 1C , the sealingassemblies valve assembly assemblies sealing assemblies valve assembly - As will be apparent to one skilled in the art, various means for actuating the
actuating rod 61 to control actuation ofintake valve 30 andexhaust valve 130 during operation of the engine illustrated inFIGS. 1A -1C may be employed. For example, camshafts, solenoids, rocker arms, chains, gears, belts, and hydraulic, pneumatic, electric actuators, and/or other means may be employed to cause translational movement of thevalve body 49 byactuator 61. - Referring again to
FIGS. 1A-1C , operation ofengine 31, when used in conjunction with the sliding intake andexhaust valves U.S. Patent No. 6,976,464 B2 issued on December 20, 2005 , the teachings of which are incorporated by reference herein in their entirety. In this patent, the intake and exhaust valves 20 and 120 are semi-rotating valve assemblies instead of sliding valve assemblies. Whileengine 31 and slidingvalve assemblies FIGS. 1A-1C appear in the environment of a four stroke Otto cycle, it will be apparent to one skilled in the art that slidingvalve assemblies -
FIGS. 7, 8 and 9 show a further embodiment for a valve body of a sliding valve assembly of the present invention. In this embodiment, thevalve body 100 includes afront cam follower 101 and arear cam follower 103 both of which extend substantially across the width of thevalve body 100. Additionally,valve body 100 includes afluid conducting port 105 and anactuator rod 107 for translating movement ofvalve body 100 within a valve housing similar to that discussed hereinabove with reference toFIGS. 1A through 2 .Valve body 100 further includes a sealingassembly 109 on itslower surface 111 wherein sealingassembly 109 is constructed and functions similarly to that of sealingassembly 59 ofFIGS. 1A through 2 .Valve body 100 operates within the valve housing similar to that discussed herein above wherein thefluid conducting port 105 comes into and out of alignment with first fluid conducting passage and the second fluid conducting passage of the valve housing. As particularly shown inFIG. 9 , thefront cam follower 101 and therear cam follower 103 cooperate withcam surfaces valve body 100 within the valve housing and to reduce the frictional forces between the contact surfaces to enhance the life of the sealingassembly 109 and to allow the valve to effectively open and close. Cam surfaces 112, 114 may also have straight profiles. - The sealing
assemblies assemblies assemblies - From the above it can further be appreciated that the sealing
assembly 59 is generally in communication with a combustion chamber wherein pressure is increased in the system and this increased pressure acts on the sealingassembly 59 to increase its sealing effectiveness. However, inFIGS. 6A and6B pressure is directed from thecombustion chamber 84 and into the ports orchannels 98e of thecap 98b and against the sealingassembly 51. It is apparent that the cap mounted in the upper valve housing may be removable and interchangeable depending on whether pressure is received relative to the upper valve housing or relative to the lower valve housing. That is, if the pressure in the system is available from thecombustion chamber 84 ofFIGS. 6A and6B , then cap 98b withchannels 98e for delivering the pressure directly against the sealingassembly 51 may be provided in theupper valve housing 98; however if the pressure in the system is available from thecompression cylinder 82 ofFIG. 5 , then a cap without channels may be provided in the upper valve housing such ascap 45b of theupper valve housing 45 ofFIGS. 1A through 1C . - As discussed herein above, it is also to be appreciated that even though the valve assembly of the invention has been disclosed relative to its being a sliding valve assembly for use in an energy conversion engine, the valve assembly of the invention may be a rotary valve assembly, a semi-rotating valve assembly, an oscillating valve assembly or any other type of valve assembly used in various applications especially pressure systems for effectively operating the sealing assembly of the present invention.
- While the present invention has been described in connection with the embodiments of the various figures, it is to be understood that other similar embodiments may be used or modifications and additions may be made to the described embodiments for performing the same function of the present invention without deviating there from. Therefore, the present invention should not be limited to any single embodiment, but rather construed in breadth and scope in accordance with the recitation of the appended claims.
Claims (14)
- A sliding valve assembly (30, 130) for introducing and/or exhausting a fluid medium relative to a cylinder (33) containing a reciprocating piston (37) for an energy conversion engine which includes pressure within the system, said sliding valve assembly (30, 130) comprising:a valve housing (45, 47) having first fluid conducting passage (79) and second fluid conducting passage (77) separated by a valve cavity (45d);a valve body (49) housed in the valve cavity (45d) of the valve housing (45, 47) and having a fluid conducting port (75) adjacent to a fluid impervious surface (49d);an actuator (61) for translating movements of the valve body (49) within the valve cavity (45d) of the valve housing (45, 47) into a fluid conducting position wherein the fluid conducting port (75) of the valve body (49) allows a fluid conducting relation between the first fluid conducting passage (79) and the second fluid conducting passage (75) of the valve housing (45, 47) and into a fluid blocking position where the fluid impervious surface (49d) of the valve body (49) obstructs a fluid conducting relation between the first fluid conducting passage (79) and the second fluid conducting passage (77) of the valve housing (45, 47);wherein the valve housing (45, 47) of the valve body (49) have cooperating surfaces for constraining the valve body (49) during the translating movements of the valve body (49) within the valve cavity (49d) of the valve housing (45, 47) between the fluid conducting position and the fluid blocking position of the valve body (49); andat least a first sealing assembly (59) located within the fluid impervious surface (49d) of the valve body (49) for forming a first sealing relationship between the valve body (49) and the valve housing (45, 47)characterized in that the cooperating surfaces (63a, 63b, 65a, 65b) includes cams (112, 114) and cam followers (67, 69, 71, 73, 101, 103) responsive to the actuator (61) for releasing the sealing pressure of at least the first sealing assembly (59) from the valve housing (45, 47) when the sliding valve assembly (30, 130) is in its blocking position.
- The sliding valve assembly (30, 130) according to claim 1 wherein the first sealing assembly (59) is in communication with the pressure in the system and adapted to receive the pressure in the system for increasing the effectiveness of the first sealing assembly (59).
- The sliding valve assembly (30, 130) according to claim 1, wherein the first sealing assembly (59) is located within a seal cavity (49e) of the valve body (49) and forms said first sealing relationship between the valve body (49) and the valve housing (45, 47) at lease when the valve body (49) is in the fluid blocking position within the valve cavity (45d) of the valve housing (45, 47) and when the pressure in the system is applied to the first sealing assembly (59).
- The sliding valve assembly (30, 130) to claim 1 wherein the first sealing assembly (59) includes a primary seal ring (59a), a secondary seal ring (59b) surrounding the periphery of the primary seal ring (59a) and a wall of the seal cavity (49e) of the valve body (49) for loading the primary seal ring (59a) against the wall of the seal cavity (59e) of the valve body (49) of the sliding valve assembly (30, 130).
- The sliding valve assembly (30, 130) according to claim 4 wherein the secondary seal ring (59b) of the first sealing assembly (59) is freely moveable relative to the seal cavity (59e) of the valve body (49).
- The sliding valve assembly (30, 130) according to claim 1 further including a second sealing assembly (59b) located within the valve housing (45, 47) for forming a second sealing relationship between the valve housing (45, 47) and the valve body (49).
- The sliding valve assembly (30, 130) according to claim 6 wherein said second sealing assembly (59b) is in communication with the pressure in the system and adapted to receive the pressure in the system for increasing the effectiveness of the second sealing assembly (59a).
- The sliding valve assembly (30,130) according to claim 6 wherein the second sealing assembly (59b) is located within the seal cavity (49e) of the valve housing (45, 47) and forms said second sealing relationship between the valve body (49) and the valve housing (45, 47) at least when the valve body (49) is in the fluid blocking position within the valve cavity (45d) of the valve housing (45, 47) and when the pressure in the system is applied to the second sealing assembly (59b).
- The sliding valve assembly (30, 130) according to claim 6 wherein the second sealing assembly (59b) includes a primary seal ring (59a), a secondary seal ring (59b) surrounding the periphery of the primary seal ring (59a), and a resilient member (59c) arranged to apply a resilient force between the primary seal ring (59a) and a wall of the seal cavity (49e) of the valve housing (45, 47) for loading the primary seal ring (59a) against the wall of the valve housing (45, 47).
- The sliding valve assembly (30, 130) according to claim 9 wherein the secondary seal ring (59b) of the second sealing assembly (59b) is freely moveable relative to the seal cavity (49e) of the valve housing (45, 47).
- The sliding valve assembly (30, 130) according to claim 7 wherein the valve housing (45, 47) further includes at least once channel (FIG 3) forming a passage for passage of the system pressure against the second sealing assembly (59b) to further force the second sealing assembly (59b) within the seal cavity (49e) of the valve housing (45, 47).
- The sliding valve assembly (30, 130) according to claim 7 wherein the valve housing (45, 47) further includes a cap (45b) defining the first fluid conducting passage (79) and including a plurality of channels (FIG 3) extending parallel to the first fluid conducting passage (79) for passage of the system pressure against the second sealing assembly (59b) to further force the second sealing assembly (59b) within the seal cavity (49e) of the valve housing (45, 47).
- The sliding valve assembly (30, 130) according to claim 1 wherein the cam followers (67, 69, 71, 73, 101, 103) are mounted to the lateral sides of the valve body (49) and the cams (112, 144) are located along the lateral sides of the valve body (49) and include cam surfaces (63a, 73b, 65a, 65b) engaged by the cams followers (67, 69 71, 73, 101, 103).
- The sliding valve assembly (30, 130) according to claim 1 wherein the cam followers (67, 69 71, 73, 101, 103) include a front cam follower (101) across the width of the valve body (49) and a rear cam follower (103) extending across the width of the valve body (49) and wherein the cams (112, 114) include cam surfaces (63a, 63b, 65a, 65b) on the valve housing (45, 47) and which cam surfaces (63a, 63b, 65a, 65b) are engaged by the cam followers (101, 103).
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PCT/US2010/001116 WO2011129799A2 (en) | 2010-04-15 | 2010-04-15 | A sliding valve assembly |
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EP2558705A2 EP2558705A2 (en) | 2013-02-20 |
EP2558705A4 EP2558705A4 (en) | 2015-02-25 |
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JP (1) | JP5748241B2 (en) |
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CN102913298B (en) * | 2012-10-09 | 2015-09-23 | 陕西理工学院 | Slider type engine air valve |
MX2019002668A (en) | 2016-09-09 | 2020-08-13 | Charles Price | Variable travel valve apparatus for an internal combustion engine. |
CN115306916B (en) * | 2022-07-29 | 2024-09-17 | 成都中科唯实仪器有限责任公司 | Vacuum pendulum valve |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
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FR431248A (en) * | 1911-06-17 | 1911-11-06 | Alfred Edouard Henry D Alton | Spool distribution system for internal combustion engines |
GB246287A (en) * | 1924-12-29 | 1926-01-28 | Percy Riley | Improvements in and relating to slide-valve internal combustion engines |
US1722873A (en) | 1928-06-25 | 1929-07-30 | George Kretzler | Sliding valve for gasoline engines |
US1922678A (en) | 1928-10-22 | 1933-08-15 | Gen Motors Res Corp | Slide valve engine |
US2074487A (en) * | 1934-05-25 | 1937-03-23 | Winfield P Porter | Valve and valve gear for internal combustion engines |
US2782801A (en) * | 1953-01-16 | 1957-02-26 | Walter D Ludwig | Sliding valve spool seal |
US3457957A (en) * | 1966-06-08 | 1969-07-29 | Teledyne Inc | Multiple-ported balanced slide valves |
US4201174A (en) * | 1976-01-28 | 1980-05-06 | Alto Automotive, Inc. | Rotary valve system for motors and the like having improved sealing means |
US4281819A (en) * | 1978-03-23 | 1981-08-04 | Linder Morris B | Balanced stem gate valve |
US4643395A (en) * | 1985-11-21 | 1987-02-17 | Joy Manufacturing Company | Valve with protected seats |
US4765287A (en) * | 1987-11-02 | 1988-08-23 | Taylor Bill A | Slide valve apparatus for internal combustion engine |
US4878651A (en) * | 1988-03-24 | 1989-11-07 | Worldwide Oilfield Machine, Inc. | Valve seat assembly |
DE3902920C1 (en) * | 1989-02-01 | 1990-06-13 | Peter 8104 Grainau De Scherer | |
RU2073097C1 (en) * | 1992-03-02 | 1997-02-10 | Александр Владимирович Романов | Valve timing gear for internal combustion engine |
US5694890A (en) | 1996-10-07 | 1997-12-09 | Yazdi; Kamran | Internal combustion engine with sliding valves |
JP4230529B1 (en) * | 2008-05-04 | 2009-02-25 | 康仁 矢尾板 | Engine with sliding valve |
-
2010
- 2010-04-15 CN CN201080067381.5A patent/CN103237980B/en active Active
- 2010-04-15 JP JP2013504869A patent/JP5748241B2/en active Active
- 2010-04-15 WO PCT/US2010/001116 patent/WO2011129799A2/en active Application Filing
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CN103237980B (en) | 2016-03-09 |
CN103237980A (en) | 2013-08-07 |
EP2558705A2 (en) | 2013-02-20 |
JP2013533410A (en) | 2013-08-22 |
WO2011129799A2 (en) | 2011-10-20 |
EP2558705A4 (en) | 2015-02-25 |
JP5748241B2 (en) | 2015-07-15 |
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