WO2013149315A1 - Moteur à piston servant à convertir un gaz sous pression en énergie mécanique - Google Patents

Moteur à piston servant à convertir un gaz sous pression en énergie mécanique Download PDF

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Publication number
WO2013149315A1
WO2013149315A1 PCT/CA2012/000376 CA2012000376W WO2013149315A1 WO 2013149315 A1 WO2013149315 A1 WO 2013149315A1 CA 2012000376 W CA2012000376 W CA 2012000376W WO 2013149315 A1 WO2013149315 A1 WO 2013149315A1
Authority
WO
WIPO (PCT)
Prior art keywords
crankshaft
housing
valve
inlet valve
piston engine
Prior art date
Application number
PCT/CA2012/000376
Other languages
English (en)
Inventor
Sheldon Robar
Original Assignee
Sheldon Robar
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 Sheldon Robar filed Critical Sheldon Robar
Priority to PCT/CA2012/000376 priority Critical patent/WO2013149315A1/fr
Priority to CA2868420A priority patent/CA2868420A1/fr
Publication of WO2013149315A1 publication Critical patent/WO2013149315A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L1/06—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like the cams, or the like, rotating at a higher speed than that corresponding to the valve cycle, e.g. operating fourstroke engine valves directly from crankshaft
    • 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
    • F01B17/00—Reciprocating-piston machines or engines characterised by use of uniflow principle
    • F01B17/02—Engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • 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
    • 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
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • 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
    • F01B7/04—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with oppositely reciprocating pistons acting on same main shaft
    • 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
    • F01L2003/25—Valve configurations in relation to engine
    • F01L2003/258—Valve configurations in relation to engine opening away from cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/06—Dip or splash lubrication
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to external heat engines, and more particularly to a piston engine for converting a pressurized gas into mechanical energy.
  • waste heat such as, for example, factory smokestacks, internal combustion engine cooling or exhaust heat, which provide large amounts of thermal energy at a relatively low temperature - typically in the 230°F to 280°F temperature range - and which are generally released as waste heat into the
  • External heat engines such as, for example, the Stirling engine, are well known in the art.
  • the first types of external heat engines have been developed in the early nineteenth century.
  • such engines are only efficient at large temperature differences requiring provision of the thermal energy at relatively high temperatures.
  • such engines are typically complex and costly to manufacture, thus impeding widespread employment in less efficient applications such as conversion of waste heat or solar heat into mechanical energy.
  • a piston engine for converting a pressurized gas into mechanical energy that is capable of converting waste heat or solar heat into mechanical energy. It is also desirable to provide a piston engine for converting a pressurized gas into mechanical energy that has substantially reduced maintenance requirements. It is also desirable to provide a piston engine for converting a pressurized gas into mechanical energy that is easily adapted for use with different working fluids.
  • one object of the present invention is to provide a piston engine for converting a pressurized gas into mechanical energy that is simple, compact, and cost-effective to
  • Another object of the present invention is to provide a piston engine for converting a pressurized gas into mechanical energy that is easily adapted for use with different working fluids.
  • a piston engine for converting a pressurized gas into mechanical energy.
  • a housing of the piston engine has disposed therein at least a cylinder. At least a piston is housed in a respective cylinder.
  • a crankshaft is rotatable mounted to the housing and connected to each of the at least a piston.
  • At least an inlet valve is disposed in the housing. The inlet valve is a disc valve movable mounted to the housing between a closed position and an open position such that the inlet valve is moved in an outward direction from a respective cylinder volume for enabling provision of a working fluid in the open position.
  • the working fluid has a first pressure and a first temperature.
  • At least an outlet valve is disposed in the housing. The outlet valve is movable between a closed position and an open position for exhausting the working fluid having a second lower pressure and a second lower temperature.
  • a valve control mechanism is disposed in the housing and connected to the crankshaft, the inlet valve and the outlet valve.
  • a piston engine for converting a pressurized gas into mechanical energy.
  • a housing of the piston engine has disposed therein a crankshaft with the crankshaft being rotatable mounted thereto.
  • Two cylinders are disposed in the housing on opposite sides of the crankshaft with the two cylinders being disposed along a same longitudinal axis.
  • Two pistons are connected to the crankshaft.
  • Each is piston housed in one of the two cylinders and linearly movable along the longitudinal axis.
  • At least an inlet valve is disposed in the housing and movable between a closed position and an open position for enabling provision of a working fluid in the open position.
  • the working fluid has a first pressure and a first temperature.
  • At least an outlet valve is disposed in the housing and movable between a closed position and an open position for exhausting the working fluid.
  • the working fluid has a second lower pressure and a second lower temperature.
  • a valve control mechanism is disposed in the housing and connected to the crankshaft, the inlet valve and the outlet valve.
  • the advantage of the present invention is that it provides a piston engine for converting a pressurized gas into mechanical energy that is simple, compact, and cost-effective to
  • a further advantage of the present invention is that it provides a piston engine for converting a pressurized gas into mechanical energy that is capable of converting waste heat or solar heat into mechanical energy.
  • a further advantage of the present invention is that it provides a piston engine for converting a pressurized gas into mechanical energy that has substantially reduced maintenance requirements.
  • a further advantage of the present invention is that it provides a piston engine for converting a pressurized gas into mechanical energy that is easily adapted for use with different working fluids.
  • Figures la and lb are simplified block diagrams illustrating a cross sectional side view and a cross sectional top view, respectively, of a piston engine according to a preferred embodiment of the invention
  • Figure lc is a simplified block diagram illustrating a cross sectional top view of a cylinder head of the piston engine according to the preferred embodiment of the invention.
  • Figures Id and le are simplified block diagrams illustrating cross sectional side views of a cylinder head of the piston engine according to the preferred embodiment of the invention.
  • Figure 2 is a simplified block diagram illustrating a perspective view of a crankshaft of the piston engine according to the preferred embodiment of the invention
  • Figures 3a to 3c are simplified block diagrams illustrating perspective views of a cam wheel of the piston engine according to the preferred embodiment of the invention.
  • Figures 4a and 4b are simplified block diagrams illustrating a front view and a side view, respectively, of a piston rod of the piston engine according to the preferred embodiment of the invention
  • FIGS. 5a to 5d are simplified block diagrams illustrating a two cycle process performed by the piston engine according to the preferred embodiment of the invention.
  • Figure 6 is a simplified block diagram illustrating a system for converting thermal energy into mechanical energy employing the piston engine according to the preferred embodiment of the invention.
  • the piston engine 100 for converting a pressurized gas into mechanical energy according to a preferred embodiment of the invention.
  • the piston engine 100 preferably, comprises a single unit housing 102 having two substantially symmetrical housing portions 102A and 102B with each housing portion forming half of a crank case and one cylinder block housing a respective cylinder 104A, 104B therein.
  • the two cylinders 104A, 104B are disposed in the housing 102 on opposite sides of the crankshaft 1 18 with the two cylinders 104A, 104B being disposed along a same longitudinal axis 1 16 oriented substantially perpendicular to a rotational axis 120 of the crank shaft 1 18.
  • crankshaft 118 is rotatable mounted to the housing 102 in a conventional manner employing, for example, ball or roller type bearings 122 and 126 with the bearing 122 being disposed in the housing 102 and the bearing 126 being disposed in crankcase cover 1 10.
  • the crankcase cover 1 10 is of sufficient size for enabling insertion of: pistons 106A, 106B; piston rods 108A, 108B; and crankshaft 1 18, and for assembly of the same therein. Further access to the crankcase is enabled via crankcase access cover 1 13.
  • the crankcase cover 1 10 is designed to be of sufficient structural strength for supporting mounting of the crankshaft 1 18 via bearing 126 thereto.
  • the crankcase cover 1 10 comprises an extension 1 1 1 , for example, in the form of a collar fitting snugly into a respective opening of the housing 102 for centering the same with respect to the housing 102 to ensure proper alignment of the crankshaft 1 18.
  • the housing 102 is made of aluminum in a conventional manner with the cylinder bores being machined and, optionally, surface treated such as, for example, Nikasil coated for high load applications. Disposing the two cylinders 104A, 104B along the same longitudinal axis 1 16 substantially facilitates the machining process, for example, by enabling line boring of both cylinders in a single machining process.
  • the two housing portions 102A, B are provided as separate units - splitting, for example, the housing along a plane through an axis of rotation of the crankshaft 1 18 - and mounted together in a conventional manner.
  • Cylinder heads 1 12 A, B are mounted to the respective housing portions 102 A, B in a
  • the cylinder heads 1 12 A, B each comprise inlet channel 150A, B and outlet channel 152 A, B having inlet port 140A, B and outlet port 144 A, B mounted thereto, respectively.
  • the cylinder heads 112A, B each house inlet valves, outlet valves, and associated valve mechanisms.
  • Two pistons 106A, 106B are connected to the crankshaft 1 18 with each piston 106 A, 106B being housed in one of the two cylinders 104A, 104B, respectively, and linearly movable along the longitudinal axis 116.
  • the two pistons 106A, 106B are connected to a single crankshaft journal 180, illustrated in Figures la and 2, via piston rods 108A, 108B, respectively, with the piston rods 108A, 108B being pivotally movable mounted to the crankshaft journal 180 in a conventional manner.
  • the pistons 106A, 106B are, preferably, made of cast aluminum in a conventional manner.
  • the piston rods 108 A, 108B are pivotally movable mounted to the pistons 106A, 106B in a conventional manner via, for example, piston pins and needle bearings. Sealing between the pistons 106A, 106B and the respective walls of the cylinders 104A, 104B is provided in a conventional manner using, for example, one oil control ring and two sealing rings.
  • the top sealing ring comprises a slight upward facing bevel in order for the cylinder pressure to provide a stronger seal for substantially preventing the pressurized gas from leaking into the crankcase.
  • the piston rods 108 A, 108B preferably, comprise a predetermined offset-distance D between a first end portion 108.1 A, 108. IB - mounted to the crankshaft journal 180 - and a second end portion 108.2A, 108.2B - mounted to the respective piston 106 A, 106B.
  • the offset-distance D provides alignment between the first end portion
  • piston rods 108A, 108B are made of aluminum or steel in a conventional manner.
  • the piston rods 108 A, 108B are straight and mounted to the respective piston 106A, 106B at an offset-distance.
  • the crankshaft 1 18 further comprises counterweights 130 to reduce vibrations caused by the piston movement.
  • the crankshaft 1 18 is made, for example, as a one- piece cast-steel design or forged-steel design.
  • the crankshaft 118 is made of a plurality of pieces using, for example, conventional press-fitting technology, to enable provision of needle bearings on the crankshaft journal 180 for higher load applications.
  • crankshaft 1 18 has mounted thereon - using, for example, conventional form fitting technology - cam wheel 132 for controlling the movement of inlet valves 142A, 142B and outlet valves 146A, 146B in dependence upon the rotational movement of the crankshaft 1 18 and wheels 124 and 128 such as, for example, sprocket wheels, for providing the mechanical energy generated by the piston engine 100.
  • cam wheel 132 for controlling the movement of inlet valves 142A, 142B and outlet valves 146A, 146B in dependence upon the rotational movement of the crankshaft 1 18 and wheels 124 and 128 such as, for example, sprocket wheels, for providing the mechanical energy generated by the piston engine 100.
  • the cam wheel 132 preferably, comprises a cam wheel center element 132.1 having removable mounted thereto, on a first side, inlet cam ring segment 132.2 with inlet cam 182 and, on a second opposite side, outlet cam ring segment 132.3 with outlet cam 184.
  • the cam ring segments 132.2 and 132.3 are removable mounted to the cam wheel center element 132.1 in a conventional manner using, for example, screw bolts. Removable mounting of the inlet cam ring segment 132.2 substantially facilitates adjustment of the time interval the inlet valves 142 A, B are kept in the open position by simply exchanging a first inlet cam ring segment
  • crankcase access cover 113 is placed and of sufficient size to enable insertion and assembly of at least the inlet cam ring segment 132.2 therethrough.
  • the cam wheel center element 132.1 is designed to have sufficient mass, thus enabling the cam wheel 132 to act as a flywheel. Further preferably, fins are disposed on a side surface of the cam wheel center element 132.1 for providing splash lubrication by picking up lubricant disposed in the bottom of the crankcase and splashing the same.
  • roller style cam followers are mounted to a first end of inlet pushrods 134A, B and outlet pushrods 136A, B to follow the inlet portion and the outlet portion of the cam wheel 132, respectively.
  • the pushrods 134A, B and 136A, B are accommodated in respective bores disposed in the housing 102 A, 102B and in the cylinder heads 1 12 A, 1 12B.
  • the cylinder heads 1 12 A, B are mounted to the respective housing portions 102 A, B with each comprising inlet channel 150A, B and outlet channel 152 A, B having inlet port 140 A, B and outlet port 144 A, B mounted thereto, respectively.
  • the cylinder heads 1 12A, B each house the inlet valves 142A, 142B, the outlet valves 146A, 146B, and associated valve mechanisms, which are covered by cylinder head covers 1 14 A, B.
  • the inlet valves 142 A, 142B and the outlet valves 146 A, 146B are provided as disc valves disposed in the respective cylinder heads 1 12A, 1 12B and kept in a closed position in a conventional manner using, for example, coil return springs (not shown).
  • the cylinder heads 1 12A, 1 12B are made of aluminum in a conventional manner with the valve seats 156A, B and 160 A, B being directly machined into the cylinder heads 1 12 A, B or with steel valve seats being mounted thereto depending on the grade of the aluminum employed.
  • the mechanism for opening the outlet valve 146 A, B is of conventional design with a second opposite end of outlet pushrod 136A, B pushing a first end of pivotally movable mounted - at pivot 170A, B - rocker arm 164A,B which in turn pushes outlet valve disc 158A, B into the cylinder volume - indicated by block arrows.
  • the cylinder head 1 12 A, 1 12B is designed to be of sufficient thickness for providing proper guidance (by way of, for example, a Teflon coated valve guide securely positioned within a bore disposed in the cylinder head 112 A, 1 12B) to a stem of the outlet valve 146 A, B disposed in a bore through the Teflon coated valve guide.
  • inlet valve 142 A, B is moved in an outward direction from a respective cylinder volume for opening, as indicated by the block arrow.
  • High pressure of the pressurized gas in the inlet channel 150A, B acting on the inlet valve disc 154A, B pushes the same into the valve seat 156A, B, thus preventing the pressurized gas from entering the cylinder volume when the inlet valve 142 A, B is in the closed position.
  • the inlet valve mechanism comprises a linear movable bridge 162 A, B guided along linear bearings 168 A, B having the inlet valve 142A, B mounted thereto at a first end.
  • Inlet pushrod 134A, B pushes a second opposite end of the bridge 162 A, B which in turn pulls the inlet valve 142A, B with the inlet valve disc 154A, B outward from the cylinder volume - as indicated by the block arrows.
  • the inlet valve 142 A, B is inserted through opening 165 A, B disposed in the cylinder head 112A, B and liner movable mounted thereto via inlet valve nut 166 A, B having a threaded collar, as illustrated in Figure lc.
  • the inlet valve nut 166A, B is designed to be of sufficient thickness for providing proper guidance (by way of, for example, a Teflon coated valve guide 163A,B securely positioned within the inlet valve nut 166A) to a stem of the inlet valve 142 A, B disposed in a bore through the Teflon coated valve guide 163 A, B , providing a proper seal for preventing leakage of the working fluid disposed in the inlet channel 150A, B.
  • Inlet valve return spring 167A, B is, for example, disposed in the inlet channel 150A, B between a shoulder disposed on the inlet valve disc 154A, B and a bottom surface of the inlet valve nut 166A, B and abutted thereto.
  • the inlet valve return spring 167A, B pushes the valve disc 154A, B into the inlet valve seat 156A, B when the inlet valve 142A, B is in the closed position.
  • a rocker arm is pivotally movable mounted at a first end and pushed by the inlet pushrod 134A, B at a second opposite end, thus pulling the inlet valve 142A, B which is pivotally movable mounted to the rocker arm between the first end and the second end.
  • a small linkage is employed to reduce side loading acting on the inlet valve 142 A, B.
  • the inlet valve 142 A, B and the corresponding valve mechanism is not limited for use with the two cylinder piston engine described hereinabove, but is also applicable for use with various other types of pressurized gas driven piston engines.
  • the piston engine 100 performs a two cycle process with the down-stroke being the power cycle and the up-stroke being the exhaust cycle with each cycle corresponding to a half revolution of the crankshaft, as illustrated in Figures 5a to 5d.
  • Pressurized gas is received having a first pressure and a first temperature.
  • the pressurized gas is provided to the cylinder volume and expanded therein, thus pushing the piston down.
  • the expanded gas is exhausted with the gas then having a second lower pressure and a second lower temperature.
  • the thermal energy corresponding to the difference between the first and the second pressure and the first and the second temperature of the gas is substantially converted into mechanical energy acting on the crankshaft.
  • Each of the two pistons performs the same two cycle process a half revolution apart, for example, while piston 106A is at Top Dead Center (TDC) piston 106B is at Bottom Dead Center (BDC) or, while piston 106A moves towards Top Dead Center (TDC) piston 106B moves towards Bottom Dead Center (BDC) and vice versa.
  • Vaporized and pressurized Freon is supplied to each cylinder 104A, B entering the inlet channels 150A, B via inlet ports 140A, B.
  • the inlet cam 182 on the cam wheel 132 actuates the inlet push rod 134A which then actuates the bridge 162A, thus lifting the inlet valve 142 A off its seat - Figure 5 a.
  • the Freon then passes into the cylinder 104 A pushing the piston 106A down.
  • the inlet push rod 134A comes off the cam 182 - typically after one quarter to one half of the down-stroke - the spring in concert with the pressurized Freon closes the inlet valve 142A - Figure 5b.
  • the outlet cam 184 on the cam wheel 132 actuates the outlet push rod 136A which then actuates the rocker arm 164 A, thus pushing the outlet valve 146A off its seat - Figure 5c.
  • the expanded Freon is exhausted through the outlet channel 152A - Figure 5d.
  • vaporized and pressurized Freon is supplied to each cylinder 104A, B of the piston engine 100 having a pressure in the range of, for example, preferably 240-250 psi - and further preferably 250 psi - and a temperature in the range of for example, preferably 240-300°F - further preferably 250°F.
  • the Freon is passed through a 1.5 inch throttle valve and the supply is then split into two .75 inch lines connected to each cylinder.
  • the Freon is then exhausted having a pressure in the range of for example, preferably 4-15 psi - further preferably 5 psi - and a temperature in the range of for example, preferably 78-1 10°F - further preferably 90°F.
  • the piston engine 100 preferably provides, for example, a substantially constant torque of approximately 122 ft-lbf and a horsepower in the range of 80- 160 net horse power at a rotational speed in the range of 25-4000 rpm - preferably 1800 rpm.
  • the aligned twin cylinder design of the piston engine 100 substantially reduces the number of moving parts and provides a piston engine that is simple, compact, cost effective to manufacture and has substantially reduced maintenance requirements. The maintenance is further reduced when the piston engine 100 is operated at lower temperatures, i.e. when operated with refrigerants such as Freon.
  • the piston engine 100 is implemented in a system 200 for converting heat into mechanical energy according to a preferred embodiment of the invention.
  • the piston engine 100 is disposed on table 201 together with a heat exchanger 208 of conventional design and a condenser 202 of conventional design.
  • Heat such as, for example, waste heat from an engine cooling system or smokestack is received at inlet 210 of the heat exchanger 208, indicated by the block arrow.
  • the heat exchanger 208 vaporizes the Freon received at inlet 214 from the condenser 202 via pump 218 - indicated by a dashed line - and provides the vaporized and pressurized Freon via outlet 216.
  • the outlet 216 is connected via throttle valve 220 to the inlet ports 140A, B of the piston engine 100 - indicated by a solid line. Furthermore, a bypass directly connects the outlet 216 to the inlet 204 of the condenser 202 controlled by safety valve 222 - indicated by a solid line.
  • the outlet ports 144 A, B of the piston engine 100 are connected to the inlet 204 of the condenser 202 - indicated by a dotted line. Furthermore, the crankcase of the piston engine 100 is connected to the inlet 204 of the condenser 202 for venting Freon leaked therein - indicated by a dotted line. Optionally the venting line is omitted in case other working fluids are employed such as air or steam which are vented into the environment. The condensed Freon is then provided via outlet 206 to the pump 218 - indicated by a dashed line. Operation of the system 200 is controlled, for example, by processor 228 of control unit 226 executing executable commands stored in memory 230 and in dependence upon operator instructions received via user interface 232.
  • the processor 228 is connected to - indicated by a dash-dot line: governor 224 sensing the rotational speed of the crankshaft 1 18; the throttle valve 220; the safety valve 222; the pump 218; control valve 224; as well as pressure and temperature sensors (not shown) disposed, for example, in the piston engine 100, the condenser 202, and the heat exchanger 208.
  • governor 224 sensing the rotational speed of the crankshaft 1 18
  • the throttle valve 220 the safety valve 222
  • the pump 218 control valve 224
  • pressure and temperature sensors not shown
  • the rotational speed of the crankshaft is adjusted via the throttle valve 220 while provision of the Freon to the heat exchanger is adjusted accordingly via the pump 218 and the control valve 224.
  • the pump 218 is driven, for example, by the piston engine 100 using a belt drive.
  • a starter motor is connected to the crankshaft 1 18 for starting the piston engine 100.
  • electric heaters are disposed in the cylinder head and the cylinder

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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)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

L'invention concerne un moteur à piston servant à convertir un gaz sous pression en énergie mécanique. Un carter du moteur à piston loge au moins un cylindre. Au moins un piston est logé dans un cylindre respectif. Un vilebrequin est monté de manière rotative sur le carter et est raccordé à chacun dudit au moins un piston. Au moins une soupape d'admission est disposée dans le carter. La soupape d'admission est une soupape à disque mobile, montée sur le carter entre une position fermée et une position ouverte de sorte que la soupape d'admission se déplace dans une direction allant vers l'extérieur depuis un volume de cylindre respectif pour permettre l'apport d'un fluide de travail dans la position ouverte. Le fluide de travail a une première pression et une première température. Au moins une soupape de refoulement est disposée dans le carter. La soupape de refoulement peut se déplacer entre une position fermée et une position ouverte à des fins d'évacuation du fluide de travail ayant une seconde pression inférieure et une seconde température inférieure. Un mécanisme de commande de soupape est disposé dans le carter et est raccordé au vilebrequin, à la soupape d'admission et à la soupape de refoulement.
PCT/CA2012/000376 2012-04-03 2012-04-03 Moteur à piston servant à convertir un gaz sous pression en énergie mécanique WO2013149315A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/CA2012/000376 WO2013149315A1 (fr) 2012-04-03 2012-04-03 Moteur à piston servant à convertir un gaz sous pression en énergie mécanique
CA2868420A CA2868420A1 (fr) 2012-04-03 2012-04-03 Moteur a piston servant a convertir un gaz sous pression en energie mecanique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CA2012/000376 WO2013149315A1 (fr) 2012-04-03 2012-04-03 Moteur à piston servant à convertir un gaz sous pression en énergie mécanique

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WO2013149315A1 true WO2013149315A1 (fr) 2013-10-10

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2937508A1 (fr) * 2014-04-23 2015-10-28 Walter Stöckli Moteur de dispositif de ping-pong
GB2535005A (en) * 2015-02-03 2016-08-10 Fluid Energy Solutions Int Ltd Energy generation systems

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US410432A (en) * 1889-09-03 Steam-engine
FR1299394A (fr) * 1961-09-05 1962-07-20 Soupape d'échappement pour moteur à combustion
GB1066900A (en) * 1965-05-20 1967-04-26 Schmidt Gmbh Karl A connecting rod
US5182913A (en) * 1990-12-31 1993-02-02 Robar Sheldon C Engine system using refrigerant fluid
US20090044778A1 (en) * 2007-08-13 2009-02-19 Scuderi Group. Llc. Pressure balanced engine valves
WO2012022954A1 (fr) * 2010-08-17 2012-02-23 Artemis Intelligent Power Limited Came annulaire et machine à fluide de travail comprenant la came annulaire
US8122715B2 (en) * 2006-05-18 2012-02-28 Rapitis Marios K Self-contained refrigerant powered system

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US410432A (en) * 1889-09-03 Steam-engine
FR1299394A (fr) * 1961-09-05 1962-07-20 Soupape d'échappement pour moteur à combustion
GB1066900A (en) * 1965-05-20 1967-04-26 Schmidt Gmbh Karl A connecting rod
US5182913A (en) * 1990-12-31 1993-02-02 Robar Sheldon C Engine system using refrigerant fluid
US8122715B2 (en) * 2006-05-18 2012-02-28 Rapitis Marios K Self-contained refrigerant powered system
US20090044778A1 (en) * 2007-08-13 2009-02-19 Scuderi Group. Llc. Pressure balanced engine valves
WO2012022954A1 (fr) * 2010-08-17 2012-02-23 Artemis Intelligent Power Limited Came annulaire et machine à fluide de travail comprenant la came annulaire

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2937508A1 (fr) * 2014-04-23 2015-10-28 Walter Stöckli Moteur de dispositif de ping-pong
GB2535005A (en) * 2015-02-03 2016-08-10 Fluid Energy Solutions Int Ltd Energy generation systems
GB2546423A (en) * 2015-02-03 2017-07-19 Fluid Energy Solutions Int Ltd Energy generation systems

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