US3905340A - Engine valving and porting - Google Patents

Engine valving and porting Download PDF

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Publication number
US3905340A
US3905340A US375065A US37506573A US3905340A US 3905340 A US3905340 A US 3905340A US 375065 A US375065 A US 375065A US 37506573 A US37506573 A US 37506573A US 3905340 A US3905340 A US 3905340A
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Prior art keywords
reed
intake
valve
engine
port
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US375065A
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English (en)
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Eyvind Boyesen
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Performance Industries Inc
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Performance Industries Inc
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Priority to US375065A priority Critical patent/US3905340A/en
Priority to JP48092981A priority patent/JPS5759413B2/ja
Priority to US05/416,213 priority patent/US4000723A/en
Priority to US416215A priority patent/US3905341A/en
Priority to US05/586,138 priority patent/US4051820A/en
Application granted granted Critical
Publication of US3905340A publication Critical patent/US3905340A/en
Priority to US05/674,102 priority patent/US4062331A/en
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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
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group
    • F01L3/205—Reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/18—Other cylinders
    • F02F1/22—Other cylinders characterised by having ports in cylinder wall for scavenging or charging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/24—Pistons  having means for guiding gases in cylinders, e.g. for guiding scavenging charge in two-stroke engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2700/00—Measures relating to the combustion process without indication of the kind of fuel or with more than one fuel
    • F02B2700/03—Two stroke engines
    • F02B2700/037—Scavenging or charging channels or openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
    • F05C2201/0448—Steel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/08—Thermoplastics

Definitions

  • ABSTRACT The application discloses a two-cycle crankcase compression internal combustion engine having extended and specially positioned intake porting and reed-type intake valves, with the porting and valves arranged to improve various of the operating characteristics of the engine.
  • the present invention has the general objective of improving the performance, power output flexibility, response and fuel economy of internal combustion engines, especially two-cycle, variable speed, crankcase compression engines as used, for example, on motorcycles.
  • the, frequency of response of the reed petal (the time required by the reed petal to open and close) is exceeded and -;the reed petal therefore fails to provide positive control of the timing and strength of the incoming charge and allows the spit back of portions of the incoming charge into the carburetor.
  • the alternations in the crankcase from vacuum to positive pressure occur at intervals which are less in time than the response time of the reed petals, the reed petal, as it is in an open position, is subjected to the high positive pressure developed by the descending piston.
  • Such designs have contemplated positioning the piston ports so that communication be-- tween the inlet tract and the crankcase is cut off until almost 45 to 50 after bottom dead center position of the piston.
  • reed valves positioned in the intake tract snap open. This results in a discontinuous flow of combustible fluid to the engine and in the intake of lesser volumes of combustion fluid in comparison to engines utilizing aspects of the invention disclosed herein.
  • the invention has as a further object the employment of special intake ports, herein referred to as injector ports, interconnecting the intake passage at a point just downstream of the intake valve with the transfer ports, thereby providing still another channel through which intake of fuel may occur whenever the transfer ports are open.
  • injector ports interconnecting the intake passage at a point just downstream of the intake valve with the transfer ports, thereby providing still another channel through which intake of fuel may occur whenever the transfer ports are open.
  • FIG. 1 is a sectional view of a two-cycle internal combustion engine having intake valves and intake porting conforming with the present invention
  • FIG. 2 is a section of certain of the valve ports shown inFIG. 1;
  • FIG. 2G is a graph showing comparative curves representing the power output in relation to speed for conventional two-cycle engines and for engines utilizing certain features of the invention as disclosed in FIGS. 1 and 2;
  • FIG. 3 is a view similar to FIG. 1 but illustrating a modified valve arrangement
  • FIG. 4 is a view-of a cylinder showing certain improved inlet ports and showing also an arrangement of valves positioned as in FIG. 3;
  • FIG. 5 is an elevational view of a piston adapted for use in an arrangement according to the present invention and incorporating extended porting, as described hereinafter;
  • FIGS. 6A, 6B, 6C, 6D and 6E are schematic illustrations showing the operating sequence of an engine employing porting arrangements according to the present invention.
  • FIG. 7 is a graph showing the portion of the cycle during which the intake valves are open, in the arrangements illustrated in FIGS. 1 and 3 to 6E;
  • FIG. 8 is a graph showing comparative power curves of a prior art arrangement in comparison with an arrangement conforming with FIGS. 3 to 6E, and still further with curve number 30f graph 2G;
  • FIGS. 9 and 10 are views similar to FIGS. 3 and 4 but illustrating the provision of injector ports, as hereinafter explained.
  • FIG. 11 is a graph showing the power curves for two engines constructed according to the present invention, in one of which the injector ports are utilized and the other of which the injector ports are not utilized.
  • FIGS. 1, 2 and 2G Reference is first made to the embodimentillustrated in FIGS. 1, 2 and 2G.
  • FIG. 1 there is shown therein a schematic representation of a two-cycle piston engine having a cylinder ,12 and apiston 14.
  • the cylinder 12 includes main transfer ports 16 for delivering a combustible gas from the crankcase (not shown) to the combustion side of the piston 14.
  • main transfer ports 16 for delivering a combustible gas from the crankcase (not shown) to the combustion side of the piston 14.
  • combustible gases pressurized by the descending piston flow from the crankcase through suitable conduits (not shown) to the main transfer ports
  • the cylinder 12 also includes an inlet port '18 which communicates with a valve housing which may be mounted on or formed integrally with the barrel of cylinder 12, and which housing defines, at least in part, the above-mentioned intake passage or tract.
  • a valve assembly 27 is received in the housing 20 and may be secured therein by a readily removable cover plate 24 that extends over the flanges 22 of the valve assembly and which preferably includes an intake passage extension 26 for receiving a carburetor (not shown) thereon.
  • the valve assembly 27 can include a valve body 29 having two convergent surfaces 30 and 32 joined in an apex by a transverse member 35.
  • the surfaces 30 and 32 include at least one opening 34 and 36 extending through each of the surfaces 30 and 32. While the opening 34 and 36 could be made in the form of one continuous opening, it is preferred that at least two openings be formed in the surfaces 30 and 32 for reasons as will be hereinafter explained.
  • the reed petals 38 and 42 at the top are shown closed, but those at the bottom are shown open. It will be un' derstood that is actual use the flexing of both sets of reed petals on both sides of the valve will always be substantially the same, depending upon the operation condition.
  • reed petal assemblies to be hereinafter described are the same on surface 30 as on surface 32, hereinafter reference will be made only to the reeds disposed on surface 30, it being understood that the comments so made are equally applicable to the assemblies on surface 32.
  • Disposed over the opening 34 is a primary reed 38.
  • the size and shape of the primary reed is such that peripheral surfaces thereof extend beyond side edges of the openings 34 so that the flow of fluid through opening 34 is substantially precluded when the reed 38 is urged by its own resilience against the surface 30.
  • the primary reed 38 has a vent or opening 40 formed therethrough.
  • a secondary reed 42 of a size and shape sufficient to overlay vent 40 is mounted over the vent 40 by, for instance, a machine screw 44 that secures both the secondary reed 42 and the primary reed 38 to the valve body 29.
  • the primary and secondary reeds 38 and 42 respectively are both formed of a yieldable, resilient material. However, it is important that the secondary reed 42 be more yieldable than the primary reed 38 because secondary reed 42 must open at lower intake port pressures than primary reed 38, as will hereinafter be described. It should be understood that any thin, resilient material can be used to form the primary and secondary reeds.
  • a preferred material that has been used with good result is a woven glass fiber and epoxy laminate commonly identified as G-10, for example as marketed by the Formica Company. Reed assemblies of this material wherein the thickness of the primary reed is about 0.022 to about 0.026 and wherein the thickness of the secondary reed is about 0.014 to about 0.016
  • FIG. 3 An arrangement similar to that described above is illustrated in FIG. 3, which latter Figure is more fully described hereinafter, but with reference to which it should be noted that it is preferred in all of the arrangements according to the invention that it is preferred in all of the arrangements according to the invention that the primary reeds 38 should overlie the entire opening 34, (shown in broken lines in FIG. 3), and further that the primary reeds 38 are wider and longer than the secondary reeds 42. This has the advantage of greatly reducing the mass of each secondary reed 42 making it more responsive to lower pressure differentials across the valve assembly and more able to work independently of the operation of primary reed 38.
  • vent 40 is positioned closer to the end of reed 38 which is secured to the valve body 29. This allows the length of the secondary reed 42 to be kept to a minimum, thereby resulting in a decrease in the mass of the secondary reed as heretofore noted.
  • vent 40 reduces the mass of the primary reed 38 thereby further decreasing inertial effects on that reed.
  • the decrease in mass of the primary and secondary reeds results in increased reed life as it reduces overflexing and eliminates the need for reed stops.
  • both primary and secondary reeds are open, a larger volume of charge passes through the valve, in comparison to single reed valves, because the impedance of the primary reed to flow is reduced as portions of the charge can flow through the vent which is opened by the more yieldable secondary reed.
  • the mass of each of the reeds is maintained at a minimum. This in turn reduces inertial effects on the primary and secondary reeds and increases the frequency of response of the reeds thereby making the engine more responsive to changes in throttle settings.
  • the valve body 29 includes a transverse apex forming member 35 formed at the point of convergence of surfaces 30 and 32.
  • the member 35 has formed thereon an aerodynamic surface 37 which gives the member 35 an air foil or tear drop cross section.
  • the member 35 offers minimum resistance to passage of incoming gas.
  • the corresponding surface 37 of the apex member 35 is flat or pointed and presents a non-aerodynamic sub-sonic barrier to the passage of gases thereover.
  • the flat or pointed surface is required in certain single reed designs to lift the reeds from the surfaces of the valve body to which they were mounted, by means of the shock and turbulence created at the apex member, which, it is felt, interferes with the timed, uniform delivery of the charge into the intake port.
  • the valve assembly as heretofore disclosed operates in the following manner.
  • the secondary reed 42 opens each time the piston 14 moves upwardly in the cylinder 12 to uncover the inlet port 18, as the force generated by the pressure of the combustible gas, for instance, air-fuel mixture from a carburetor (not shown) on the -upstream side of the secondary reed. 42 is sufficient to overcome the resistive force generated by the relatively yieldable secondary reed. This allows the passage'of a'quantity of air-fuel mixture into the inlet port at each stroke of the piston and provides a timed supply of the air-fuel mixture to the cylinder 12 at very low engine speed.
  • the pressure differential across the valve assembly becomes great enough to cause the primary reed 38 to begin to operate, alternately opening and closing with the stroke of piston 14 to deliver a timed charge of the air-fuel mixture through the opening 30 to the inlet port 18.
  • secondary reed 42 remains open, varying in position in accordance with the crankshaft rotation, while the less yieldable primary reed 38 continues to provide a timed charge in the manner heretofore described.
  • the system described provides valve timing throughout the entire speed range of the engine. The blow back of the air-fuel mixture through the opened vents 40 at high RPM is prevented by the restricted area of these vents and by the momentum of the entering high velocity intake charge.
  • the more efficient porting involves an increase in the charge delivered to the combustion side of the piston 14, by reason of a supercharging effect at low RPM occuring through main transfer ports 16 and auxiliary transfer port 46.
  • This supercharging effect at low RPM ranges results from the low pressure wake occurring in the crankcase as the compressed charge suddenly exits from the crankcase through the main transfer ports 16 and auxiliary transfer port 46.
  • the low pressure in the crankcase is communicated via a port 58 in the piston (more fully described hereinafter) to the intake port 18.
  • An advantage of the system herein described is that at high RPM, the flow of the air-fuel mixture into the intake port 18 is significantly more constant because the secondary reeds 42 remain open. In systems using single reeds, the flow of the air-fuel mixture is stopped and started by the opening and closing of the single reed thereby reducing the speed and uniformity of the flow of the air-fuel mixture into the intake port 18.
  • valve assembly herein disclosed Another advantage of the valve assembly herein disclosed is that the secondary reeds, which operate at low engine pressure differentials and which have faster response times allow a more efficient porting of the cylinder and piston.
  • Single reed petal designs require greater vacuum in the inlet port to open the reed petals and require the piston to close off the intake system from the crankcase so that the necessary vacuum can be achieved.
  • the foregoing is a problem occuring most frequently in larger displacement engines, for instance engines having a displacement exceeding 100 cc.
  • the intake system of the engine may be ported directly to the crankcase at all times to yield better flow of the air-fuel mixture at low engine speeds for larger displacement engines.
  • vented reed system herein disclosed is increased responsiveness of the engine. This arises from the situation that when the throttle plate of the carburetor (not shown) is closed, the vacuum upstream from the valve assembly 27 is the same as the crankcase vacuum and both reeds remain closed. But immediately upon the opening of the throttle plate in the carburetor (not shown), the vacuum upstream of the valve assembly 27 drops while the vacuum in the crankcase remains.
  • the vented reeds snap open earlier and more quickly, in comparison to single reed designs, because the vented valves are responsive to lower pressure differentials occurring across the valve assembly and provide more area for the flow of gases with less flexing, as earlier described.
  • FIG. 2G there is shown therein a graph indicating the power output in relation to engine speed for an engine modified as heretofore described.
  • the graph shows the result of tests performed on a 250 cc. two-cycle engine utilizing, in stock form, piston controlled inlet ports and exhaust expansion chambers for exhaust extraction.
  • the line identified by the numeral 1 represents the I results of dynamometer testing for the above engine not utilizing reed valves of the type herein disclosed and employing carburetor jetting suitable for normal use at varying speeds and loads.
  • peak power of about 22 horsepower is developed at a speed of about 6600 RPM and power output falls off rapidly beyond the peak power speed.
  • Line 2 shows the result of testing the engine as equipped in test 1 with the exception that the carburetor jetting was chosen to obtain maximum dynamometer power. A maximum power of about 28 horsepower was achieved at a speed of approximately 6600 RPM. Again, as with test 1, there was experienced a rapid fall off in power after the peak power point, and maximum RPM safely achievable was indicated to be about 8500 RPM. It should be pointed out that the engine as set up in test 2 was not suitable for use in applications requiring varying speeds as the mixture became unduly rich each time the throttle plate was closed thereby loading the cylinder with unburned fuel.
  • test 3 an engine of the type used in tests 1 and 2- but further including reed valves of the type herein disclosed was tested.
  • power output below 5000 RPM is significantly increased, somewhere in the order of 50% and peak power of about 29 horsepower was achieved at a speed of about 7300 RPM.
  • power output beyond peak power speed falls off more gradually than that for the number 1 and number 2 tests.
  • maximum engine speeds of almost 11,000 RPM were achieved.
  • test 4 an engine with the same modifications as that in number 3 and further including a carburetor with a larger venturi diameter, auxiliary transfer porting, modified exhaust porting, and a modified exhaust expansion chamber was used. Peak power on this engine rose to 34 horsepower at a speed of about 9200 RPM. Maximum engine speed was found to be in excess of 12,500 RPM.
  • valve assemblies having more than two reeds are contemplated according to the invention.
  • triple reed valve arrangements may be employed, in which event the secondary reeds will be apertured or vented, so that the third or tertiary reeds serve to open and close the vent in the secondary reeds.
  • the tertiary reeds are desirably smaller and more flexible than the secondary reeds.
  • FIG. 3 it is pointed out that the arrangement of FIG. 3 is similar to that described above and that all of the parts described above are also employed, but the reed valve assembly is differently positioned in the valve housing 20.
  • the reed valve assembly in FIG. 3 is merely rotated 90 in the valve housing, as compared with its position in FIGS. 1 and 2.
  • the reed valves themselves occupy a different position in relation to the porting and to the axis of the cylinder. This is of advantage because it allows a more predictable flow pattern of combustion fluid through the system, especially during high speed engine operation.
  • the flow is more evenly divided between the sets of reeds disposed on each side of the valve body 29 and is directed in a manner which conforms to the natural directions of the fluid flow through the engine, i.e., curved toward the sides of the crankcase where the transfer passages are open to the crankcase, by reason of the fluid flowing through the valve port which acts as an orifice having a fixed side and a yieldable side defined by the reeds which cause the flow to curve.
  • the reeds are placed closer to the port 46 and the flow into port 46 is smoother because the fluid does not have to flow upwardly from the reeds as in the FIG. 1 embodiment.
  • This orientation of the reed valves is also desirable because it improves cold starting of the engine, which is particularly advantageous with engines requiring manual starting.
  • the reason for this is that when the engine is at rest, there is no vacuum in the crankcase to operate the reeds. Thus, at start-up, the engine must be cranked to develop sufficient vacuum in the crankcase to cause the reeds to open and allow the passage of the combustion fluid into the engine.
  • the valves When the valves are positioned as shown in FIG. 1, the combustion fluid passing through the bottom set of reeds must flow upwardly as it enters the valve assembly 27 so that it can exit through the vent in the primary reed 38.
  • FIGS. 4, 5, and 6A to 6E attention is directed to the porting employed in accordance with the present invention.
  • FIG. 4 shows a cross-section, taken along line 4-4 of FIG. 3, of a typical cylinder showing the preferred manner of mounting the valve assemblies 27 in relation to the cylinder.
  • two valve assemblies 27, are positioned vertically as discussed above with respect to FIG. 3 in a housing 20 which is attached to the cylinder C.
  • the valve assemblies 27 are positioned so that each valve assembly is aligned with one of the intake ports 18.
  • the use of the two valve assemblies 27 is advantageousbecause it causes the flow of combustion fluid to agree with the natural flow pattern of the engine, and this results in a smoother, more directional flow of combustion fluid through the engine.
  • the combustion fluid flows through each of the valves 27 into an aligned inlet port 18 and into the crankcase of the engine and from there into the transfer passages 53 and is introduced to the combustion side of the piston through the transfer ports 16.
  • this is particularly important in the preferred embodiment of cylinder arrangements as shown in FIGS. 3 and 4 because in such designs, the axes of the transfer ports 16 are angularly displaced from the axis of the intake tract by about as is shown in FIG. 4.
  • These designs require that the combustion fluid make an abrupt change in direction once inside the engine, i.e., a direction change of 90 to either side of the engine to enter the transfer passages 53, and without the arrangements as shown in FIGS.
  • the charge has little inherent directional tendency to flow toward either side of the crankcase, and in fact does not do so until after the charge has been compressed and flow starts through the transfer passages.
  • the time during which the change in direction can occur is short and therefore the change must occur quite rapidly.
  • the valve assemblies give direction to the combustion fluid streams before the streams enter the engine. This predetermining results in the combustion fluid stream undergoing the direction change more efficiently, rapidly, and smoothly, thereby ultimately resulting in the delivery of a larger volume charge to the combustion side of the piston.
  • the axis of the entire inlet tract of the engine shown in FIG. 4, including the valve assemblies 27 and the intake ports 18, is positioned so that it is aligned along a radius emanating from the center of the cylinder bore and is angularly offset from the axes of the transfer ports.
  • FIG. There is shown in FIG. is a piston 56 which is usable in conjunction with a cylinder such as shown in FIG. 4.
  • the piston 56 includes two spaced piston ports 58, each of which is positioned to be aligned with one of the intake ports 18 of cylinder C.
  • An important aspect of the piston shown in FIG. 5 is that the height of the ports 58 is greatly increased over that of prior designs. As will be hereinafter more fully explained, this results in allowing the inlet ports 18 (and thus the inlet tract including the reed valves) to communicate with the crankcase at all times during the engine cycle.
  • the height of the ports 58 can be increased in designs as shown in FIGS. 3 and 4 both with single reed valves and with vented valves as heretofore disclosed.
  • FIGS. 6A-E a schematic representation of the operating cycle of an engine employing vented reed valves of the type heretofore described and employing a ported piston as shown in FIG. 5.
  • FIG. 6A shows the position of the piston 56 just slightly before it reaches bottom dead center.
  • the combustion fluid charge compressed by the descending piston 56 has exited from the crankcase 60 and is intro symbolized via the transfer ports 16 and somewhat through auxiliary port 46 to the combustion side of the piston.
  • the rapid exiting of the compressed combustion fluid from the crankcase 60 causes a vacuum to be created in its wake in the crankcase 60.
  • This vacuum is transmitted via the piston port 58 to the reed valves which open allowing the introduction of additional charge of combustion fluid through the auxiliary transfer port 46 to the combustion side of the piston and also into the crankcase 60 through the piston port 58, resulting in extended delivery of charge through ports 16 (as shown by the arrows).
  • this portion of the charge bypasses the crankcase at high RPM to fill the cylinder thoroughly. Any of the charge tending to escape through the exhaust port as the piston moves upwardly is now held in the cylinder by a positive reflective wave generated by a typical exhaust expansion chamber. Also, because the secondary reeds remain open at high RPM ranges, there is an increase in the amount of charge drawn into the crankcase through the skirt port 58 and a correspondingly increased flow of gases through the crankcase and to the transfer ports.
  • FIG. 6B shows the piston as it has just closed off the transfer port 16 and auxilary port 46.
  • the piston is ascending, thereby creating a vacuum in the crankcase which is communicated to the reed valves via the piston port 58, thereby causing the reed valves to open further.
  • Combustion fluid flows from the inlet port 18, and also from the auxiliary transfer port 46 when the piston 56 has moved high enough, through the piston post 58 to the crankcase. At this point, the skirt of the piston has not yet begun opening the intake port 18.
  • the piston 56 is approaching the top of its stroke, the bottom edge of the skirt has completely opened the intake port 18, thereby allowing a great volume of combustion fluid to be drawn into the crankcase through the open reed valves.
  • FIG. 6E shows the piston 56 descending and closing off the intake port 18.
  • the piston is of course compressing the volume of combustion fluid drawn into the crankcase during the previous up stroke of the piston.
  • the pressure of the fluid in the crankcase is greater than the pressure on the upstream side of the valve assembly and blowback of the pressurized charge is prevented by the closed reeds in the lower RPM ranges and by the restricted area of the vents and the momentum of the incoming charge entering through the vents at high RPM ranges.
  • the crankcase is in communication with the intake tract, either via the piston port 58, the inlet port 18, or a combination of both. This provides for the induction of larger quantities of combustion fluid into the engine and results in higher power and higher torque outputs.
  • FIG. 7 is a graph based upon the type of valve and port arrangements shown in FIGS. 1, 3, 4, 5, and 6A to 6E, including the vertically extended porting 58 provided in the piston skirt as shown in FIG. 5.
  • the graph there shown plots two curves, curve 1 representing typical operating behavior of the reed petals at low intake velocities, i.e., engine speeds below the power peak, and curve 2 representing typical operating behavior of the reed petals at high intake velocities, i.e., engine speeds above the power peak.
  • the intake is open to at least some extent throughout the entire cycle of operation of the engine.
  • 180 represents the bottom dead center position of the engine crank
  • 360 represents the top dead center position of the engine crank.
  • the vertical scale of the graph of FIG. 7 represents the degree of reed valve opening, graduated at quarterly intervals from zero opening to full opening, and the lowermost quarter of this scale comprehends the extent of opening provided by the secondary reeds, it being assumed that at the onequarter position on the graph the secondary reeds are fully open.
  • the graph of FIG. 7 also shows that even at low intake air velocity, the duration of reed or valve opening is extended throughout approximately 240 of the cycle of operation. This aids in maintaining relatively high output and performance at low engine RPM, under which condition both the primary and secondary reeds cycle, as has been described.
  • the duration of reed opening as described above in relation to FIG. 7 is greater than prior arrangements both at low as well as at high intake air velocity, and these conditions can only be achieved when the skirt porting 58 is high enough to be open whenever the piston skirt would block communication from the intake passage to the crankcase.
  • the commencement of opening of the valve is delayed to or beyond the 180 position, i.e., bottom dead center. Such prior arrangements adversely affect the torque at both high and low engine RPM.
  • the graphs shown in FIG. 7 are representative of engines employing standard transfer port timing, i.e., usually not in excess of 120 duration. It has been-found that when using vented reed valves as herein disclosed, especially in conjunction with piston porting as heretofore described, that the height of the transfer ports 16, as shown in FIGS. 1, 3, and 6A-E, 9, and 10, can be raised to give greater transfer duration. Engines having transfer port durations of about 148 have been found to have power curves as depicted by line 4 of FIG. 2G. It will be noted that greatly increased power results at high RPM. In addition, the height of the exhaust port can be raised, resulting in increased scavenging time and concomitant higher engine outputs.
  • the graph indi- ;cated by the numeral 1 represents a prior known single reed valve engine and is characterized by rapid dropoff of horsepower after the power peak is passed.
  • curve identified by the numeral 2 is similar to curve 3 of FIG. 26, and illustrates one arrangement or embodiment of the present invention incorporating a vented reed valve assembly. This curve shows much less tendency for the horsepower to drop off after the peak is reached.
  • FIGS. 3 and 4 In another embodiment conforming with the present invention of the kind shown in FIGS. 3 and 4,
  • FIGS. 9 and 10 there is here shown still another feature as applied to arrangements similar to those illustrated in FIGS. 3 and 4. Similar parts are again identified by the same reference numerals.
  • additional ports herein referred to as injector ports.
  • injector ports Two injector ports are illustrated at 62, 62. Each of these ports interconnects one of the intake passages 18 with one of the transfer passages 53, as is shown in FIGS. 9 and 10.
  • injector ports are open at all times, and serve to increase intake of fuel at the higher RPMs, especially above 6000 or 7000 RPM.
  • the longitudinal axis of the injector ports 62 is arranged at substantially a angle to the axis of the transfer passage 53.
  • the charge contained in the crankcase is pressurized by the descending piston, the charge is caused to flow upwardly through the transfer passages 53 to the transfer ports 16 at high velocity.
  • the rapidly moving charge in the passage 53 moving past the opening of injector port 62 causes an eductor efi'ect in the injector port 62 which causes a low pressure to exist in the port 62, which low pressure is communicated to the intake tract just downstream of the reed assemblies.
  • injector ports can be used with beneficial results in two-cycle engine designs having valving in the inlet tract, for example, rotary intake valves. As will be noted below, in connection with the discussion of FIG. 11, especially good results are achieved when injector ports are used in engines having reed valves, especially vented reed valves of the type disclosed herein.
  • reed valves also makes possible extensive increase in the total cross-sectional area of the intake porting, as is disclosed herein, and still further makes possible considerable increase in the total time in the cycle during which the valves are open, both at low speed and at high speed.
  • the employment of reed valves further makes possible extending the porting 58 in the piston skirt to the point where the intake tract is open to the crankcase when the transfer ports are open.
  • the use of reed valves also enables the vertical extension of the piston skirt porting to a point such that the intake tract is constantly open to the crankcase throughout the entire cycle of operation of the engine.
  • a fuel intake system for a variable speed two-cycle crankcase compression internal combustion engine having a piston working in a cylinder with transfer porting extended between the compression and the intake sides of the piston and with an intake port adapted to communicate with the cylinder at the intake side of the piston when the piston is positioned to block the transfer porting, a fuel intake chamber for receiving fuel from a supply source and for delivering the fuel to the intake port, a ported valve seat presented downstream of the fuel flow through the intake chamber, a primary reed valve covering the valve port and being sufficiently flexible to open the port under the influence of decrease in pressure in the intake chamber incident to high speed engine operation but being sufficiently rigid to remain closed under the influence of decrease in pressure in the intake chamber incident to low speed engine operation, said primary reed having a secondary valve port therethrough of smaller size than the port through the valve seat, and a secondary reed valve covering the secondary port and being sufficiently flexible to open the secondary port under the influence of decrease in pressure in the intake chamber incident to engine operation either at said high speed or at said low speed, the primary
  • a reed valve assembly for controlling the flow of fuel to the intake port of a variable speed, crankcase compression engine comprising a valve body having two converging surfaces, the surfaces being joined by a transverse apex member, an opening in each of the surfaces, a primary reed overlying the opening on each of the surfaces, a vent formed in each of the primary reeds, each vent being positioned in a portion of the primary reed which overlays the opening over which the reed is positioned, the area of each of the vents being less than the area of each of the openings, sec ondary reeds overlying each of the vents, the secondary reeds having smaller area and being more yieldable than the primary reeds.
  • a fuel intake system for a variable speed two-cycle crankcase compression internal combustion engine having a piston working in a cylinder, a crankcase, transfer passages extending between the crankcase and the combustion side of the piston terminating in transfer ports in the cylinder spaced from each other circumferentially of the cylinder, a pair of intake channels in fluid communication with two intake ports in the cylinder, the intake ports arranged intermediate the transfer ports, a valve assembly positioned in each of the channels, a first one of the channels aligned with one of the intake ports, and a second one of the channels aligned with the other of the intake ports each valve assembly comprising a hollow wedge-shaped body hav ing an inlet in its base end, a pair of imperforate opposed parallel end walls and a pair of inclined walls meeting along an apex line presented downstream of the fuel flow, the valve bodies being oriented so that the opposed end walls of each valve body are transverse to the axis of the cylinder and so that the apex line of each valve assembly generally parallels the direction of movement
  • reed valves include a primary reed, a vent in the primary reed, and a secondary reed more yieldable than the primary reed positioned to control the flow of fluid through the vent in the primary reed.
  • a fuel intake system for a variable speed, twocycle crankcase compression internal combustion engine having a skirted piston working in a cylinder with transfer porting extending between the crankcase and the combustion side of the piston, an intake port positioned in the cylinder to provide for direct communication with the crankcase when the piston is positioned to block the transfer porting, a fuel intake passage for receiving fuel from a supply source and delivering the fuel to the intake port, and a reed valve assembly for controlling the flow of fuel through the intake passage, the reed valve assembly including a hollow wedgeshaped valve body in the fuel intake passage and having an inlet in its base end, a pair of opposed imperforate end walls and a pair of inclined walls arranged in inclined planes meeting along an apex line, the valve body being oriented so that the apex line generally parallels the axis of the cylinder, the axis of the fuel intake passage from the intake port to the region of the valve body being extended generally radially of the cylinder and providing delivery of the fuel from the valve body through the
  • a fuel supply system for a variable speed internal combustion engine having fuel intake porting subject to pressure fluctuations with variation in engine speed comprising a hollow wedge shaped valve body having an inlet in its base end, having a pair of spaced and opposed end walls and a pair of inclined walls meeting along the apex line of the body and having valve ports therein, and assemblies of reed valve petals for the valve ports at the downstream sides of the inclined walls, each assembly comprising a primary petal and a superimposed secondary petal connected at adjacent ends thereof with the valve body between a valve port and the base end of the body and having their other ends free to flex away from the valve body, the primary reed petal being extended over said valve port and having a vent in registry with the underlying valve port, the secondary reed petal extending over said vent but being shorter and more yieldable than the primary reed petal, the secondary reed petal being sufficiently flexible to open under pressure conditions incident to operation of the engine at any speed and the primary reed petal being sufficiently flexible to open
  • a fuel supply system for a variable speed internal combustion engine having fuel intake porting subject to pressure fluctuations with variation in engine speed comprising a valve housing defining an intake passage adapted to deliver fuel to the intake porting of such an engine, an inclined wall in said passage extended in a plane obliquely angled to the axis of the passage and having a valve port therein, and an assembly of reed valve petals for said valve port positioned at the downstream side of said inclined wall and comprising a primary petal and a superimposed secondary petal connected at adjacent ends thereof with the inclined wall toward the upstream end thereof and having their other ends free to flex away from the inclined wall, the primary reed petal being extended over said valve port and having a vent in registry with the underlying port and spaced from the free end of the primary reed petal, the secondary reed petal extending over said vent but being shorter and more yieldable than the primary reed petal, the secondary reed petal being sufficiently flexible to open under pressure conditions incident to operation of the engine at
  • Col. line 30 change "is” to read -in li 65, nge "about 0.022 to about 0.026” to read -about 0.022" to about 0.026"-;
  • line 66 change about 0.014 to about 0.016" to read --about 0.014" to about 0.0l6"--.
  • Col. 8 1 ine 6l after "closed" insert -pl us auxiliary transfer porting of the type herein disclosed--.
  • Col l2, l i ne 26, change "post” to read --port- C01. 1 f1 l i ne 52, after “10” insert -except-- line 59, after "in delete "the”.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Supercharger (AREA)
  • Check Valves (AREA)
US375065A 1972-08-22 1973-06-29 Engine valving and porting Expired - Lifetime US3905340A (en)

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US375065A US3905340A (en) 1972-08-22 1973-06-29 Engine valving and porting
JP48092981A JPS5759413B2 (de) 1972-08-22 1973-08-21
US05/416,213 US4000723A (en) 1972-08-22 1973-11-15 Engine valve means and porting
US416215A US3905341A (en) 1972-08-22 1973-11-15 Engine valve means and porting
US05/586,138 US4051820A (en) 1973-06-29 1975-06-11 Engine valving and porting
US05/674,102 US4062331A (en) 1972-08-22 1976-04-06 Two cycle internal combustion engine

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US28273472A 1972-08-22 1972-08-22
US36140773A 1973-05-18 1973-05-18
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US416215A Division US3905341A (en) 1972-08-22 1973-11-15 Engine valve means and porting
US05/416,213 Continuation-In-Part US4000723A (en) 1972-08-22 1973-11-15 Engine valve means and porting
US05/416,213 Division US4000723A (en) 1972-08-22 1973-11-15 Engine valve means and porting

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US05/586,138 Continuation-In-Part US4051820A (en) 1972-08-22 1975-06-11 Engine valving and porting
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Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52120219U (de) * 1976-03-10 1977-09-12
US4051820A (en) * 1973-06-29 1977-10-04 Performance Industries, Inc. Engine valving and porting
US4062331A (en) * 1972-08-22 1977-12-13 Performance Industries, Inc. Two cycle internal combustion engine
JPS535615U (de) * 1976-06-30 1978-01-19
US4178886A (en) * 1976-02-18 1979-12-18 Kawasaki Jukogyo Kabushiki Kaisha Two stroke engines
JPS5510075A (en) * 1978-07-10 1980-01-24 Suzuki Motor Co Ltd Intake and scavengineg apparatus of 2-cycle engine
US4202299A (en) * 1972-08-22 1980-05-13 Performance Industries, Inc. Two cycle internal combustion engine
US4202298A (en) * 1972-08-22 1980-05-13 Performance Industries, Inc. Fuel porting for two cycle internal combustion engine
US4228770A (en) * 1979-05-29 1980-10-21 Performance Industries, Inc. Internal combustion engine fuel supply system
US4235206A (en) * 1978-12-14 1980-11-25 Performance Industries, Inc. Two cycle internal combustion engine
US4331118A (en) * 1978-07-17 1982-05-25 Cullinan John R Primary-secondary induction internal combustion engine
US4389982A (en) * 1981-10-20 1983-06-28 Performance Industries, Inc. Internal combustion engine fuel supply system
US4449242A (en) * 1982-08-31 1984-05-15 The United States Of America As Represented By The Secretary Of The Air Force Flexible, resilient anti-contamination baffle
US4643139A (en) * 1983-07-20 1987-02-17 Hargreaves Bernard J Reed valves for internal combustion engines
US4917058A (en) * 1986-02-19 1990-04-17 Clemson University Method of reducing pumping losses and improving brake specific fuel consumption for an internal combustion engine
US5036806A (en) * 1990-01-16 1991-08-06 Performance Industries, Inc. Reed valves for internal combustion engines
US5143027A (en) * 1991-05-01 1992-09-01 Land & Sea, Inc. Reed valves for two stroke engines
US5176170A (en) * 1991-08-05 1993-01-05 Performance Industries, Inc. Multiple stage reed valves for use in internal combustion engines
US5243934A (en) * 1993-01-04 1993-09-14 Eyvind Boyesen Multiple stage reed valves for use in internal combustion engines
US5247912A (en) * 1991-12-24 1993-09-28 Performance Industries, Inc. Reed valve mechanism and method for constructing same
US5417186A (en) * 1993-06-28 1995-05-23 Clemson University Dual-acting apparatus for variable valve timing and the like
US5636658A (en) * 1995-01-24 1997-06-10 Powell; William F. High flow reed valve
US6135072A (en) * 1997-11-18 2000-10-24 Kishita; Toshiji Air regulated two cycle engine
US6609535B2 (en) * 2001-07-24 2003-08-26 Henry A. Opperman Reed valve and method of making same
US6691649B2 (en) 2000-07-19 2004-02-17 Bombardier-Rotax Gmbh Fuel injection system for a two-stroke engine
US20060102114A1 (en) * 2004-11-01 2006-05-18 Brad Holtorf Motorcycle engine method & apparatus
US7051824B1 (en) 2003-11-03 2006-05-30 Accessible Technologies, Inc. Supercharged motorcycle
US20070193548A1 (en) * 2006-02-21 2007-08-23 Bauman Daniel F Sr Multi-port piston and internal combustion engine
US20090100811A1 (en) * 2007-10-17 2009-04-23 Scheckel Benjamin L Inertial Gas-Liquid Separator with Constrictable and Expansible Nozzle Valve Sidewall
US7549493B1 (en) 2006-02-28 2009-06-23 Jones Daniel W Wet belt supercharger drive for a motorcycle
US20100288253A1 (en) * 2006-03-03 2010-11-18 Cameron International Corporation Air intake porting for a two stroke engine
US20150337774A1 (en) * 2012-12-21 2015-11-26 Caterpillar Energy Solutions Gmbh Unburned fuel venting in internal combustion engines
US20170021485A1 (en) * 2014-08-28 2017-01-26 Power Tech Staple and Nail, Inc. Elastomeric exhaust reed valve for combustion driven fastener hand tool
US9989161B2 (en) 2009-11-18 2018-06-05 Zahroof Valves, Inc. Systems and methods for a reed valve module and valve assembly
US10371042B2 (en) * 2014-10-30 2019-08-06 Ihi Corporation Uniflow scavenging two-cycle engine
US10995866B2 (en) 2017-06-30 2021-05-04 Zahroof Valves Inc. Stacked valve assembly

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5311694Y2 (de) * 1975-10-28 1978-03-30
JPS5410824A (en) * 1977-06-24 1979-01-26 Kawasaki Heavy Ind Ltd Air supply device for two cycle internal combustion engine
JP2694281B2 (ja) * 1988-08-26 1997-12-24 スズキ株式会社 リードバルブ

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US157791A (en) * 1874-12-15 Improvement in compound valves
US861566A (en) * 1907-03-07 1907-07-30 Eduard Wiki Flap-valve.
US893852A (en) * 1906-05-28 1908-07-21 John George Leyner Air-valve for air-compressors.
US919036A (en) * 1905-03-22 1909-04-20 Paul Langer Valve.
US939549A (en) * 1909-06-03 1909-11-09 Frederick C Reineking Reed air-intake regulator for carbureters.
US961315A (en) * 1908-02-10 1910-06-14 Armand Peugeot Two-stroke cycle-motor.
US1614124A (en) * 1926-08-07 1927-01-11 Ingersoll Rand Co Gas-compressor valve
US2621889A (en) * 1947-05-23 1952-12-16 Grove Regulator Company Expansible sleeve type valve
US2689552A (en) * 1950-09-11 1954-09-21 Elmer C Kiekhaefer Reed valve for internal-combustion engines
US2801621A (en) * 1954-11-24 1957-08-06 Mall Tool Company Fuel-pump carburetor
US3107659A (en) * 1960-01-09 1963-10-22 Fichtel & Sachs Ag Two-cycle internal combustion engine
US3453994A (en) * 1966-07-11 1969-07-08 Tillotson Mfg Co Fuel feed system and charge forming apparatus
US3687118A (en) * 1969-07-14 1972-08-29 Yamaha Hatsudaki Kk Crank chamber compression-type two-cycle engine
US3690304A (en) * 1970-01-16 1972-09-12 Walbro Corp Carburetor construction to eliminate fuel accumulation at the reed valve

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US157791A (en) * 1874-12-15 Improvement in compound valves
US919036A (en) * 1905-03-22 1909-04-20 Paul Langer Valve.
US893852A (en) * 1906-05-28 1908-07-21 John George Leyner Air-valve for air-compressors.
US861566A (en) * 1907-03-07 1907-07-30 Eduard Wiki Flap-valve.
US961315A (en) * 1908-02-10 1910-06-14 Armand Peugeot Two-stroke cycle-motor.
US939549A (en) * 1909-06-03 1909-11-09 Frederick C Reineking Reed air-intake regulator for carbureters.
US1614124A (en) * 1926-08-07 1927-01-11 Ingersoll Rand Co Gas-compressor valve
US2621889A (en) * 1947-05-23 1952-12-16 Grove Regulator Company Expansible sleeve type valve
US2689552A (en) * 1950-09-11 1954-09-21 Elmer C Kiekhaefer Reed valve for internal-combustion engines
US2801621A (en) * 1954-11-24 1957-08-06 Mall Tool Company Fuel-pump carburetor
US3107659A (en) * 1960-01-09 1963-10-22 Fichtel & Sachs Ag Two-cycle internal combustion engine
US3453994A (en) * 1966-07-11 1969-07-08 Tillotson Mfg Co Fuel feed system and charge forming apparatus
US3687118A (en) * 1969-07-14 1972-08-29 Yamaha Hatsudaki Kk Crank chamber compression-type two-cycle engine
US3690304A (en) * 1970-01-16 1972-09-12 Walbro Corp Carburetor construction to eliminate fuel accumulation at the reed valve

Cited By (50)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4202299A (en) * 1972-08-22 1980-05-13 Performance Industries, Inc. Two cycle internal combustion engine
US4202298A (en) * 1972-08-22 1980-05-13 Performance Industries, Inc. Fuel porting for two cycle internal combustion engine
US4062331A (en) * 1972-08-22 1977-12-13 Performance Industries, Inc. Two cycle internal combustion engine
US4051820A (en) * 1973-06-29 1977-10-04 Performance Industries, Inc. Engine valving and porting
US4178886A (en) * 1976-02-18 1979-12-18 Kawasaki Jukogyo Kabushiki Kaisha Two stroke engines
JPS587056Y2 (ja) * 1976-03-10 1983-02-07 川崎重工業株式会社 ２サイクルエンジンにおける吸気装置
JPS52120219U (de) * 1976-03-10 1977-09-12
JPS535615U (de) * 1976-06-30 1978-01-19
JPS587809B2 (ja) * 1978-07-10 1983-02-12 スズキ株式会社 ２サイクルエンジンの吸気及び掃気装置
JPS5510075A (en) * 1978-07-10 1980-01-24 Suzuki Motor Co Ltd Intake and scavengineg apparatus of 2-cycle engine
US4331118A (en) * 1978-07-17 1982-05-25 Cullinan John R Primary-secondary induction internal combustion engine
US4235206A (en) * 1978-12-14 1980-11-25 Performance Industries, Inc. Two cycle internal combustion engine
US4228770A (en) * 1979-05-29 1980-10-21 Performance Industries, Inc. Internal combustion engine fuel supply system
US4389982A (en) * 1981-10-20 1983-06-28 Performance Industries, Inc. Internal combustion engine fuel supply system
US4449242A (en) * 1982-08-31 1984-05-15 The United States Of America As Represented By The Secretary Of The Air Force Flexible, resilient anti-contamination baffle
US4643139A (en) * 1983-07-20 1987-02-17 Hargreaves Bernard J Reed valves for internal combustion engines
US4917058A (en) * 1986-02-19 1990-04-17 Clemson University Method of reducing pumping losses and improving brake specific fuel consumption for an internal combustion engine
US5036806A (en) * 1990-01-16 1991-08-06 Performance Industries, Inc. Reed valves for internal combustion engines
US5143027A (en) * 1991-05-01 1992-09-01 Land & Sea, Inc. Reed valves for two stroke engines
US5176170A (en) * 1991-08-05 1993-01-05 Performance Industries, Inc. Multiple stage reed valves for use in internal combustion engines
US5247912A (en) * 1991-12-24 1993-09-28 Performance Industries, Inc. Reed valve mechanism and method for constructing same
US5243934A (en) * 1993-01-04 1993-09-14 Eyvind Boyesen Multiple stage reed valves for use in internal combustion engines
US5417186A (en) * 1993-06-28 1995-05-23 Clemson University Dual-acting apparatus for variable valve timing and the like
US5636658A (en) * 1995-01-24 1997-06-10 Powell; William F. High flow reed valve
US6135072A (en) * 1997-11-18 2000-10-24 Kishita; Toshiji Air regulated two cycle engine
US6691649B2 (en) 2000-07-19 2004-02-17 Bombardier-Rotax Gmbh Fuel injection system for a two-stroke engine
US6609535B2 (en) * 2001-07-24 2003-08-26 Henry A. Opperman Reed valve and method of making same
US7051824B1 (en) 2003-11-03 2006-05-30 Accessible Technologies, Inc. Supercharged motorcycle
US20060102114A1 (en) * 2004-11-01 2006-05-18 Brad Holtorf Motorcycle engine method & apparatus
US7458344B2 (en) 2004-11-01 2008-12-02 Brad Holtorf Motorcycle engine method and apparatus
US20070193548A1 (en) * 2006-02-21 2007-08-23 Bauman Daniel F Sr Multi-port piston and internal combustion engine
US7549493B1 (en) 2006-02-28 2009-06-23 Jones Daniel W Wet belt supercharger drive for a motorcycle
US9291090B2 (en) 2006-03-03 2016-03-22 Ge Oil & Gas Compression Systems, Llc Air intake porting for a two stroke engine
US8757113B2 (en) 2006-03-03 2014-06-24 Cameron International Corporation Air intake porting for a two stroke engine
US20100288253A1 (en) * 2006-03-03 2010-11-18 Cameron International Corporation Air intake porting for a two stroke engine
US20110138998A1 (en) * 2006-03-03 2011-06-16 Cameron International Corporation Air intake porting for a two stroke engine
US7963258B2 (en) * 2006-03-03 2011-06-21 Cameron International Corporation Air intake porting for a two stroke engine
US20110232599A1 (en) * 2006-03-03 2011-09-29 Cameron International Corporation Air intake porting for a two stroke engine
US8104438B2 (en) 2006-03-03 2012-01-31 Cameron International Corporation Air intake porting for a two stroke engine
US8235010B2 (en) 2006-03-03 2012-08-07 Cameron International Corporation Air intake porting for a two stroke engine
US8495975B2 (en) 2006-03-03 2013-07-30 Cameron International Corporation Air intake porting for a two stroke engine
US7857883B2 (en) * 2007-10-17 2010-12-28 Cummins Filtration Ip, Inc. Inertial gas-liquid separator with constrictable and expansible nozzle valve sidewall
US20090100811A1 (en) * 2007-10-17 2009-04-23 Scheckel Benjamin L Inertial Gas-Liquid Separator with Constrictable and Expansible Nozzle Valve Sidewall
US9989161B2 (en) 2009-11-18 2018-06-05 Zahroof Valves, Inc. Systems and methods for a reed valve module and valve assembly
US11002377B2 (en) 2009-11-18 2021-05-11 Zahroof Valves Inc. Systems and methods for a reed valve module and a modular reed valve assembly
US20150337774A1 (en) * 2012-12-21 2015-11-26 Caterpillar Energy Solutions Gmbh Unburned fuel venting in internal combustion engines
US20170021485A1 (en) * 2014-08-28 2017-01-26 Power Tech Staple and Nail, Inc. Elastomeric exhaust reed valve for combustion driven fastener hand tool
US11554471B2 (en) * 2014-08-28 2023-01-17 Power Tech Staple and Nail, Inc. Elastomeric exhaust reed valve for combustion driven fastener hand tool
US10371042B2 (en) * 2014-10-30 2019-08-06 Ihi Corporation Uniflow scavenging two-cycle engine
US10995866B2 (en) 2017-06-30 2021-05-04 Zahroof Valves Inc. Stacked valve assembly

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JPS5759413B2 (de) 1982-12-14

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