WO2017120141A1 - Moteur - Google Patents

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Publication number
WO2017120141A1
WO2017120141A1 PCT/US2017/012043 US2017012043W WO2017120141A1 WO 2017120141 A1 WO2017120141 A1 WO 2017120141A1 US 2017012043 W US2017012043 W US 2017012043W WO 2017120141 A1 WO2017120141 A1 WO 2017120141A1
Authority
WO
WIPO (PCT)
Prior art keywords
intake
exhaust
piston
assembly
internal combustion
Prior art date
Application number
PCT/US2017/012043
Other languages
English (en)
Inventor
Steven Charles Manthey
Micheal Steven MANTHEY
Original Assignee
Advanced Engine Dynamics Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Advanced Engine Dynamics Corporation filed Critical Advanced Engine Dynamics Corporation
Publication of WO2017120141A1 publication Critical patent/WO2017120141A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F01B3/0005—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B7/00—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F01B7/02—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with oppositely reciprocating pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • 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
    • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis
    • 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
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders

Definitions

  • This disclosure relates to a two-stroke opposed-piston internal combustion engines with ported cylinders.
  • An opposed-piston engine is a reciprocating internal combustion engine characterized by use of pairs of pistons operating with opposed motions in a common cylinder without need of a cylinder head.
  • An aspect of the present disclosure is the recognition that an opposed piston engine can have potential advantages including, high specific output, high specific torque, very high power density and increased thermal efficiency (arising in part from reduced heat soaking surface area as compared to conventional engines due to the elimination of the need for cylinder heads).
  • Potential advantages of certain embodiments of the disclosure described herein can include a low part-count given that the engine pistons can cyclically expose or occlude the exhaust and intake ports thereby eliminating the need for a valve train, camshaft pushrods, valve springs or valve keepers.
  • An aspect of the present disclosure can include a reciprocating internal combustion engine characterized by use of pairs of pistons operating with opposed motions in a common cylinder without need of a cylinder head.
  • the engine includes a plurality of cylinders that are positioned around an output shaft. The plurality of cylinders are stationary and the output shaft rotates.
  • the engine includes a pair of rotating cams.
  • An aspect of the present disclosure herein can include a reciprocating internal combustion engine of the type in which a plurality of cylinders are arranged in equally spaced relationship around a central axis, the pistons being parallel to one another and the said axis.
  • An aspect of the present disclosure can include a "Barrel Engine” configuration of the type in which the drive mechanism involves rotating cams to create rotation of a central power shaft from the reciprocating motion of the pistons.
  • An advantage of such an embodiment of type of engine is that a cam-actuated design can provide a programmable surface to tailor piston motion for each piston-stroke and realize a smoothness in piston motion in contrast to the extreme motion seen in conventional crank throw motion - thereby providing an opportunity for achieving improved thermal efficiency by increasing compression ratios beyond what the operational stresses associated with crankshaft-driven engines will generally permit.
  • Another aspect of the present disclosure is to provide such an engine which will be light in weight, small in size and consist of a minimum number of parts particularly in respect of the wearing parts.
  • Yet another object of certain embodiments of the disclosure is to provide such an engine capable of realizing high thermal efficiency by operating with very high compression ratios not generally considered viable with crankshaft - driven engines due to the prohibitively high operational and thermal stresses that such ratios would produce in conventional engines.
  • Yet another object of certain embodiments of the disclosure is to provide such an engine that can be easily coupled in a series of engines so as to aggregate the specific output of each engine and reduce the need in manufacture to produce engines of multiply sizes and displacements.
  • Other objects and advantages of the disclosure will be hereinafter apparent in light of the disclosure.
  • FIG. 1-13 are various views of an engine and its components according to an illustrated embodiment. In these Figures individual components are numbered in accordance with the number allocated to each component throughout this description.
  • Figure 1 is cross-sectional side view of the piston assemblies and cylinders of Figure 2 according to an illustrated embodiment of the present disclosure.
  • Figure 2 is a side perspective view of the engine of Figure 3 with an outer engine housing removed to illustrate the piston assemblies and cylinders according to an embodiment of the present disclosure.
  • Figure 3 is a side perspective view of the engine according to an illustrated embodiment.
  • Figure 4 is a front view of the inner and outer intake piston assemblies of the engine of Figure 3 according to an embodiment of the present disclosure.
  • Figure 5 is a side perspective view of the inner intake piston assembly and inner exhaust piston assembly of the engine of Figure 3 according to an embodiment of the present disclosure.
  • Figure 6 is a side perspective view of the outer intake piston assembly and outer exhaust piston assembly of the engine of Figure 3 according to an embodiment of the present disclosure.
  • Figure 7 is a side view of the output shaft, intake cam and exhaust cam of the engine of Figure 3 according to an embodiment of the present disclosure.
  • Figure 8 is a side perspective view of the output shaft of Figure 7.
  • Figure 9 is a rear perspective view of the engine of Figure 3.
  • Figure 10 is a front perspective view of the engine housing with the pistons removed.
  • Figure 1 1 is a top perspective view of the inner and outer intake assemblies and their associated pistons according to an embodiment of the present disclosure.
  • Figure 12 illustrates the rockers and rocker posts shown in Figure 1 1 with the inner and outer intake assemblies and their associated pistons removed.
  • Figure 13 is a front view of an intake manifold of the engine of Figure 3 according to an embodiment of the present disclosure. DETAILED DESCRIPTION OF THE CERTAIN EMBODIMENTS
  • Figures 1 -13 illustrate one example embodiment of an internal combustion engine which includes a plurality of cylinders (1) around a central axis and fixed as part of the engine housing (25).
  • Figure 3 is a perspective view of the engine according to one embodiment.
  • a pair of opposed pistons (2) that reciprocate to and from each partner piston where each plurality of pistons (2) are part of a single assembly.
  • the entire engine contains four such assemblies comprising of two broadly concentric “intake” piston assemblies (3,5) ), which include inner intake piston assembly 3 (see Figure 5) and outer intake piston assembly 5 (see Figure 6) and two broadly concentric “exhaust” piston assemblies (4,6), which includes inner exhaust piston assembly 4 (see Figure 5) and outer exhaust piston assembly 6 (see Figure 6).
  • intake piston assemblies 3,5)
  • outer intake piston assembly 5 see Figure 6
  • exhaust piston assembly 4 see Figure 6
  • Figure 6 is a front view of the inner and outer intake assemblies (3,5).
  • Each pair of opposing pistons reciprocate within a single cylinder (1 ).
  • an inlet port (7) is positioned at one end of the cylinder and an exhaust port (8) is positioned at the opposite end of the cylinder.
  • An aperture (9) is provided in the side wall and at the approximate center of the cylinder's length allowing for a spark-plug (1 1) to be exposed to an interior of the cylinder (1).
  • the operation of the system involves the reciprocating motion of the pistons (2) within each cylinder (1 ) causing the piston assemblies (3,4,5,6) to move parallel to the axis of the center output shaft (17) and whereby each of these four assemblies have regularly spaced cam rollers (20) that keep contact with the face of the cams (13, 14) at all times thereby causing the cams (13, 14) to rotate which in turn rotates the center output shaft (17).
  • Each individual piston assembly has four regularly spaced cam rollers (20) and four pistons (2).
  • each linear bearing ring (23,24) embodies one half of a linear bearing assembly (26), the other half of the linear bearing assembly (27) is part of the inner piston assemblies (3,4) .
  • a total of eight of these linear ball race assemblies are utilized in this manner between the linear bearing rings (23,24) and inner piston assemblies (3,4).
  • the housing (25) incorporates one half of a linear ball race assembly (41), the other half of the linear bearing assembly (42) is part of the outer piston assemblies (5,6). A total of eight of these linear ball race assemblies are utilized in this manner between the housing (25) and outer piston assemblies (5,6).
  • Each linear bearing includes balls (43) as part of their respective assembly (26,27,41 ,42).
  • the said rotating output shaft (17) passes through the center of the engine supported by the radial bearings (21,22) allowing a flywheel (29) (or alternatively an armature or similar assembly depending on application) to be connected at one end (30) and allowing location (32)for a harmonic balancer (31 ) and location (34) for supercharger and auxiliary drive pulleys (33).
  • a flywheel (29) or alternatively an armature or similar assembly depending on application
  • the intake manifold (35) is formed as part of the engine housing (25) and runs around the inner circumference of said housing (25) to enable aspiration to the plurality of cylinders (1 ), the airflow of which is effected via a supercharger (36).
  • An idle speed controller (63) (see Figure 9) can be used to assist with smooth idle.
  • a charge of fuel is injected into the pressurized airflow and this mix enters the cylinders (1 ) at one end through intake ports (7) when exposed by the pistons (2) at that end of their stroke, and as these intake pistons and the exhaust pistons converge within each cylinder (1 ) creating compression and at the optimal point are ignited by a spark-plug (1 1 ) situated at the aperture (9) in the side of each cylinder between the compressing pistons (2), a separating force is applied to each pair of pistons within each cylinder.
  • the said cams (13, 14) are positioned relative to each other so as to alter port timing so that the exhaust port (8) is closed before the intake port (7).
  • the inner and outer piston assemblies (3,4,5,6) are positioned relative to each other so that they are always operating at opposite stages of the engine cycle.
  • rockers (37) are situated between the said assemblies (3,5) whereby the motion of one assembly forces the rocker to push the other assembly in the opposing direction.
  • Skid plates (38) are positioned on each assembly to coact with each rocker (37).
  • the curvature of the rockers can be tailored to complement the curvature of the "intake” cam (13) thereby ensuring the cam rollers (20) always remain in contact with the face of the cam (13).
  • rockers (37) are similarly placed between the "exhaust” inner piston assembly (4) and “exhaust” outer piston assembly (6) thereby ensuring the cam rollers (20) always remain in contact with the face of the "exhaust” cam (14).
  • the rockers (37) are affixed to the engine housing (25) through the use of rocker posts (39) at sixteen recessed locations (40) situated on the housing (25) between the cylinders (1 ).
  • cams (13, 14) can provide a programmable surface to tailor piston motion for each stroke so as to improve engine performance.
  • the cam rollers (20) are in continuous rolling contact with their corresponding cam (13, 14) whereby reciprocation of the pistons (2) results from cyclical combustion of the fuel in the cylinders (1) or the coacting of the cam rollers (20) with the cams (13, 14).
  • Scavenging is achieved by phasing the two cams (13, 14) in relation to one another thus enabling the pistons (2) part of the "exhaust” assemblies (4,6) to expose the exhaust port (8) prior to the pistons (2) part of the “intake” assemblies (3,5) exposing the inlet port (7) in a sequence so that combustion gases start to flow out of the exhaust whilst the inlet port (7) is still closed.
  • the intake port (7) opens whilst the exhaust port (8) is still open and pressurized air is forced into each cylinder (1) driving exhaust gases out of the exhaust port (8) thus displacing exhaust gas from each cylinder (1 ) through the exhaust port (8) whilst pressurized air is admitted through the intake port (7).
  • each piston (2) has a cylindrical operative end to be fitted with piston rings (not shown) while its inoperative end is attached to an assembly (3,4,5,6) that incorporates a suitable number of rollers (20).
  • the piston rings engage in the bores of their respective cylinders (1).
  • Each cam roller (20) is part of a piston assembly (3,4,5,6) as previously described and mounted rotatably on a cam pin (47) having its axis at right angles to the axis of the center output shaft (17).
  • the piston dwell can be set at any duration through the profiling of each cam' s sinusoidal undulations or alternatively, by rotating the cams relative to each other about the axis of the center output shaft (17).
  • each cam (13, 14) undulates between high and low sections with the profiling of this undulation used to effect the most optimum or desired reciprocation of the pistons (2) within their respective cylinder (1 ) thereby enabling the engine to follow its two-stroke cycle and optimise scavenging as the engine's pistons (2) cyclically expose or occlude the intake and exhaust ports (7,8).
  • the cams are characterized by four high and four low sections that result in each cylinder firing four times per cam revolution.
  • the curvature of these undulations will also result in the pistons momentarily moving in the same direction thereby delaying further compression of the charge before ignition occurs at the optimum moment.
  • temperature control is achieved through circulation of coolant throughout the housing (25) using chambers that encircle all cylinders (1) with the said chamber being separated into a combustion segment and exhaust segment of the housing (25) with separate thermostats and exiting through a coolant outlet (61) and reenters the engine through inlet (60). Coolant can be re- circulated throughout the engine once it has passed through a suitable heat exchanger.
  • a hall effect sensor (55) and trigger wheel (50) is used to determain the position of the engine within a cycle in order to electronically control the timing of the spark and fuel delivery to the engine.
  • Conditional language such as “can,” “could,” “might,” or “may,” unless specifically stated otherwise, or otherwise understood within the context as used, is generally intended to convey that certain embodiments include, while other embodiments do not include, certain features, elements, and/or steps. Thus, such conditional language is not generally intended to imply that features, elements, and/or steps are in any way required for one or more embodiments or that one or more embodiments necessarily include logic for deciding, with or without user input or prompting, whether these features, elements, and/or steps are included or are to be performed in any particular embodiment.
  • a device configured to are intended to include one or more recited devices. Such one or more recited devices can also be collectively configured to carry out the stated recitations.
  • a processor configured to carry out recitations A, B, and C can include a first processor configured to carry out recitation A working in conjunction with a second processor configured to carry out recitations B and C.
  • the terms “approximately,” “about,” and “substantially” as used herein represent an amount close to the stated amount that still performs a desired function or achieves a desired result. For example, in some embodiments, as the context may dictate, the terms “approximately”, “about”, and “substantially” may refer to an amount that is within less than or equal to 10% of the stated amount.
  • the term “generally” as used herein represents a value, amount, or characteristic that predominantly includes, or tends toward, a particular value, amount, or characteristic.
  • the term "generally parallel” can refer to something that departs from exactly parallel by less than or equal to 20 degrees and/or the term “generally perpendicular” can refer to something that departs from exactly perpendicular by less than or equal to 20 degrees.
  • any of the various disclosed systems include the container and/or include pluralities of the container; some embodiments do not include the container.
  • Those skilled in the art will recognize that the disclosure may be embodied or carried out in a manner that achieves one advantage or a group of advantages as taught herein without necessarily achieving other advantages as may be taught or suggested herein.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

L'invention concerne un moteur et, dans un mode de réalisation donné à titre d'exemple, un moteur à combustion interne deux temps à pistons opposés et à cylindres à orifices. Dans certains modes de réalisation, le moteur est un moteur de type en barillet à pistons opposés.
PCT/US2017/012043 2016-01-04 2017-01-03 Moteur WO2017120141A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US201662274633P 2016-01-04 2016-01-04
US62/274,633 2016-01-04
US201662321048P 2016-04-11 2016-04-11
US62/321,048 2016-04-11

Publications (1)

Publication Number Publication Date
WO2017120141A1 true WO2017120141A1 (fr) 2017-07-13

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ID=59274043

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2017/012043 WO2017120141A1 (fr) 2016-01-04 2017-01-03 Moteur

Country Status (1)

Country Link
WO (1) WO2017120141A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11428150B2 (en) * 2019-03-01 2022-08-30 Matthew Jackson System and method for rotational combustion engine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4215660A (en) * 1978-04-28 1980-08-05 Finley Donald G Internal combustion engine
US5375567A (en) * 1993-08-27 1994-12-27 Lowi, Jr.; Alvin Adiabatic, two-stroke cycle engine
US6155214A (en) * 1996-08-09 2000-12-05 Advanced Engine Technology Pty Ltd Axial piston rotary engines
US20030150410A1 (en) * 2002-02-14 2003-08-14 Leonhard Schuko Balanced five cycle engine with shortened axial extent
US20080302343A1 (en) * 2007-05-30 2008-12-11 High Density Powertrain, Inc. Super Charged Engine
US20100024764A1 (en) * 2008-08-01 2010-02-04 Gaby Traute Reinhardt Thermal engine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4215660A (en) * 1978-04-28 1980-08-05 Finley Donald G Internal combustion engine
US5375567A (en) * 1993-08-27 1994-12-27 Lowi, Jr.; Alvin Adiabatic, two-stroke cycle engine
US6155214A (en) * 1996-08-09 2000-12-05 Advanced Engine Technology Pty Ltd Axial piston rotary engines
US20030150410A1 (en) * 2002-02-14 2003-08-14 Leonhard Schuko Balanced five cycle engine with shortened axial extent
US20080302343A1 (en) * 2007-05-30 2008-12-11 High Density Powertrain, Inc. Super Charged Engine
US20100024764A1 (en) * 2008-08-01 2010-02-04 Gaby Traute Reinhardt Thermal engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11428150B2 (en) * 2019-03-01 2022-08-30 Matthew Jackson System and method for rotational combustion engine

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