WO2015159083A1 - Machine à pistons opposés avec mécanismes d'entraînement rectiligne - Google Patents

Machine à pistons opposés avec mécanismes d'entraînement rectiligne Download PDF

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Publication number
WO2015159083A1
WO2015159083A1 PCT/GB2015/051149 GB2015051149W WO2015159083A1 WO 2015159083 A1 WO2015159083 A1 WO 2015159083A1 GB 2015051149 W GB2015051149 W GB 2015051149W WO 2015159083 A1 WO2015159083 A1 WO 2015159083A1
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WO
WIPO (PCT)
Prior art keywords
cylinder
piston
machine according
connecting rod
opposed
Prior art date
Application number
PCT/GB2015/051149
Other languages
English (en)
Inventor
Ali VESHAGH
Jean-Pierre Pirault
Original Assignee
Osp Engines Limited
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 Osp Engines Limited filed Critical Osp Engines Limited
Publication of WO2015159083A1 publication Critical patent/WO2015159083A1/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
    • 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
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft of Bourke-type or Scotch yoke
    • 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
    • F01B7/14—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with oppositely reciprocating pistons acting on different main shafts
    • 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
    • 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
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups

Definitions

  • This invention relates to opposed piston machines that use versions of a disc drive type mechanism, also sometimes known as an eccentric drive, for the operation of the crankshaft and piston rods and for driving a multiplicity of pistons connected to each crankpin of each crankshaft.
  • a disc drive type mechanism also sometimes known as an eccentric drive
  • At least one pair of these pistons are arranged to work in anti-phase with each other in a common cylinder and the other pistons may have individual cylinders.
  • the cylinders may be arranged in one embodiment to provide compressed air, or in another embodiment they may arranged to be a 2-stroke internal combustion engine.
  • Opposed piston machines operating as compressors or internal combustion engines are well known. In the case of opposed piston engines, these need a source of scavenging air for exhausting the cylinder and providing fresh air for combustion. Opposed piston engines are also usually operated with a phase angle difference between the pistons as this offers some performance advantages. The use of a phase angle introduces out of balance forces on the engine and this can be a nuisance for certain cylinder configurations, particularly a single cylinder engine.
  • the proposed invention also enables opposed piston machines and their various embodiments to be operated with in double acting mode with dry piston skirts which is an advantage for some compressor applications and will be a friction and emission reducing advantage for opposed piston machines when used for internal combustion applications.
  • a crankshaft is a shaft having a major axis of rotation, with some first journal elements of the shaft aligned along that axis of rotation, and having some second journal elements, sometimes known as crankpins, that are rigidly fixed by radial arms to said first elements, these second elements being offset from and parallel to the major axis of rotation of the shaft.
  • a main journal is a solid of revolution and usually an integral part of the crankshaft and is arranged concentrically on the main axis of a crankshaft and is supported by a bearing in a crankcase.
  • a crankpin is usually an integral part of a crankshaft which carries and is connected to the connecting rods that are in turn connected to the pistons via a slideable joint called the gudgeon pin.
  • Each engine cylinder usually has a piston, subjected to combustion gas pressure and connected via the gudgeon pin to the "small end" of the connecting rod.
  • the other end of the connecting rod called the “big-end”, connects rotatably with the crankpin.
  • a crankthrow of a crankshaft is usually an integral part of the crankshaft linking the main journal to the crankpin. There is usually at least one crankthrow connecting with each crankpin.
  • a crankshaft is usually a single part connecting all crankpins and main journals, the main journals.
  • a piston is the moving part of a positive displacement volumetric machine that acts on the fluid to displace, compress or expand the fluid.
  • the piston is usually of a male shape which engages in a cylinder of a female shape, the motion of the piston moving the fluid to and from the cylinder.
  • a yoke is a substantially rigid link that joins two other parts, usually having some clearance with each of these other two parts so that there is some degree of rotational freedom between the link and the two parts.
  • a rectilinear drive mechanism is an assembly comprising a crankshaft fitted with paired discs (usually cylindrically shaped) which can rotate with clearance about the crankpin of the crankshaft, each disc of the pair being guided and constrained with clearance by at least one linear rail and the rail(s) of each disc being orthogonal to each other.
  • paired discs usually cylindrically shaped
  • Paired discs are a component of a rectilinear drive mechanism which consist of two eccentric discs rigidly fixed together and which are able to rotate (as one body) about a point which is central between the two centres of the discs.
  • the discs are of a small diameter and are in the form of pins which are joined by a rigid bar. The assembly of the bar and the two pins thus forms paired discs.
  • a reciprocating machine is a mechanism in which at least one component oscillates (travels along a single line with periodically reversing direction of motion) and which has a link between that reciprocating motion and the rotational motion of at least one shaft.
  • IDC Inner dead centre
  • ODC Outer dead centre
  • “Scavenging" air flow of a 2-stroke engine is the frequently used jargon to describe the air flow that passes into a 2-stroke engine, some of which is retained for combustion. The remainder of the air passes through to the exhaust system, removing or scavenging the burned products of combustion, also known as the exhaust products of combustion, from the cylinder.
  • Ports of 2-stroke engines are the apertures in the cylinder walls that enable the flow of gases from or into the cylinder. Ports are opened and closed by the motion of the power pistons .
  • An air duct or conduit also known as a pipe, is a passageway or connecting route which allows air to be transferred from one point to another. Pipe and conduit are taken to have the same meaning in the following text.
  • a double diameter, also known as stepped, piston is a piston with two diameters each of which separately engages one of two female cylinders, the diameters of said cylinders lying on a common axis.
  • the two piston diameters are usually rigidly connected, with the smaller diameter piston being the power piston and the larger diameter being the air transfer piston.
  • a stepped cylinder comprises a first cylinder, which has a first diameter for a first length and which is joined to a second cylinder which has a second diameter for a second length, the axes of first and second cylinders lying on the same axis.
  • the stepped piston and the stepped cylinder may be part of either a compressor or an engine.
  • a double acting piston is one which acts on a first volume of the working fluid with a first area on one side of the piston and which acts on a second volume of the working fluid with a second area on the other side of the piston.
  • a check valve is a flow control mechanism that allows flow in one direction and prevents flow in the reverse direction.
  • the mechanism is usually a simple leaf-spring flap, located in a conduit, that opens in one direction and closes against an abutment in the reverse direction.
  • the opening pressure of a check valve is the flow pressure required to enable flow in one direction.
  • the compression ratio of a cylinder volume with a piston that moves from an innermost to outer most position within the cylinder volume is the ratio of total cylinder volume with the piston at its outermost position divided by the cylinder volume with the piston at its innermost position.
  • the broadest aspect of this invention is a machine comprising at least a first and second opposed piston in a common cylinder, a first rectilinear drive mechanism with a first connecting rod yoke joined to said first opposed piston moving along a first axis, and with a third connecting rod yoke joined with a third piston element moving along a second axis which is orthogonal to the first axis, a second rectilinear drive mechanism with a second connecting rod yoke joined to said second opposed piston, moving substantially in-phase with the first opposed piston, but in an opposite direction, and along the same first axis and in said common cylinder with the first opposed piston, and said second rectilinear drive mechanism with a fourth connecting rod yoke joined to a fourth piston element moving along a third axis which is also orthogonal to the first axis and parallel to the second axis, and means for synchronously phasing the first and second rectilinear drive mechanisms.
  • the invention with only one pair of single throw crankshafts rotatably linked to each other, is applied with appropriate airway connections and check valves to provide up to seven compressor displacement volumes or a compressor with up to seven stages of compression.
  • the invention with only one pair of single throw crankshafts rotatably linked to each other, is used with appropriate airway connections, fuelling systems, ignition and exhaust systems to provide an opposed piston internal combustion engine with its own scavenge pump which can be arrange to be either 90° or 180° phasing, or both, to the power cylinders.
  • the frame 80 is shown as a unique part with the guides 36 and 37, parallel to each other and the axis 35, and parallel to the pads 3a and 3b of the connecting rod yoke 3, and with the guides 26 and 27 parallel to each other and the axis 34, and parallel to the pads 4a and 4b of the connecting rod yoke 4.
  • the guides 26 and 27 are therefore orthogonal to the guides 36 and 37.
  • this shows an assembly of the items shown in Figure 1 and also a second crank throw with balance crankshaft balance weights and webs 41 a and 41 b, said second crankthrow in this example being arranged at 180° crankangle to the first crankpin 22, which is masked in this figure by the crankweb 20e.
  • the connecting rod yoke 4 which engages with the disc 32, has rigidly connected piston rods 444a and 444b which are arranged along a common axis 34 but in opposite senses, said piston rods being connected respectively to pistons 442 and 2.
  • the connecting rod yoke 3 which engages with the disc 31 , has rigidly connected piston rods 333a and 333b which are arranged along a common axis 35 but in opposite senses, said piston rods being connected respectively to pistons 331 and 1 .
  • piston rods 444a and 444b of the connecting rod yoke 4 may be arranged to be cylindrical, as shown, and either pistons 2 and 442 may be detachable from their respective piston rods, or the pistons detachable from the main body of the connecting rod yoke 4. It is therefore possible to arrange for each piston rod, such as 444a, to pass through a seal in a static plate (not shown) in the crankcase 80 so that the volume contained between the underside 442a of the piston 442 and the static plate is alternately increased and reduced.
  • piston 442 and its cylinder may act as a double acting compressor.
  • pistons 1 , 2, and 331 and their respective piston rods may each be arranged to pass through a seal in a static plate (not shown) in the crankcase 80 so that the volumes contained between the undersides of said pistons and their corresponding static plates are alternately increased and reduced, these systems therefore being double acting compressors.
  • the presence of the seal in each static plate also excludes any crankcase liquid lubricant, such as oil from entering the fluid volumes above and below the pistons so that the fluid being pumped or compressed is not contaminated with lubricant.
  • crankcase halves 280 and 281 encompass the two rectilinear drive mechanisms 500 and 600 which are largely masked by the crankcase halves.
  • the assembly 700 is a complete rectilinear drive unit which may be connected to at least one or several cylinders, and associated fluid conduits which can function as at least one or several compressors or as at least one or several internal combustion engines.
  • the guide frames are located relative to the crankshaft, disks and connecting rod yokes by dowels between the frame and the crankcase halves, and retained rigidly to the crankcase halves via fixings such as bolts that arranged peripherally around the crankcase halves at location such as 280a, 280b, 280c, 281 a and 281 c, the other fixing location being hidden in this view.
  • the pistons or piston elements emerge from the crankcase halves via apertures that allow the piston skirts or peripheries to be assembled and pass into the crankcase halves if required. In the case of machines used as compressors or engines, cylinders would be fitted to or would be part of the shown surfaces of the crankcase halves.
  • a first rectilinear drive unit 700a is connected to a first piston 1 and a third piston 2, which engage respectively with cylinders 199 and 299 arranged respectively along axes 35 and 34, the cylinders being assembled on the crankcase 80.
  • a piston rod 318 passes through seal 316 which is attached to the crankcase 80.
  • This arrangement in combination with inlet air check valve 191 and air delivery check valve 1 92, comprises a first air pump or compressor which delivers air 193 to a receiver 302.
  • piston rod 3 also connected to the rectilinear drive mechanism 700a, is linked to piston 1 which moves along axis 35 in an opposed cylinder 199, which also engages with piston 1 1 1 .
  • the motion of piston 1 in combination with an appropriately phased motion of piston 1 1 1 , operating in the cylinder 199 fitted with inlet airway check valve 303a, and a delivery airway check valve 198a, allows air 303 to be induced via the inlet ports 304 into the volume between the first and second pistons 1 and 1 1 1 in the cylinder 199, and to be subsequently displaced via the delivery ports 198 and delivery air check valve 198a to the receiver 302, supplementing the air delivered from the third piston 2 and also from any counterpart piston attached to the connecting rod yoke that drives the third piston 2, as described earlier in this paragraph, and from any double acting arrangements of the third piston 2 and its counterpart.
  • piston rod 1 13, connected to the rectilinear drive mechanism 700b, is linked to piston 1 1 1 which moves along axis 35 in an opposed cylinder 199, which also engages with piston 1 , as previously mentioned.
  • the motion of the second piston 1 1 1 in combination with an appropriately phased motion of the first piston 1 , operating in the cylinder 199 fitted with inlet airway check valve 303a, and a delivery airway check valve 198a, allows air 303 to be induced via the inlet ports 304 into the volume between the first and second pistons 1 and 1 1 1 in the cylinder 199, and to be subsequently displaced via the delivery ports 198 and delivery air check valve 198a to the receiver 302, supplementing the air delivered from the third piston 2 and also from any counterpart piston attached to the connecting rod yoke that drives the third piston 2, as described earlier in this paragraph, and from any double acting arrangements of the third piston 2, cylinder and its counterpart piston and cylinder.
  • a second rectilinear drive unit 700b is connected to the second piston 1 1 1 and a fourth piston 1 13 which engage respectively with cylinders 399 and 199 arranged respectively along axes 134 and 35, the cylinders being assembled on the crankcase 180.
  • a piston rod 319 passes through a seal 317 which is attached to the crankcase 180, and this arrangement in combination with inlet air check valve 195 and air delivery check valve 196 comprises a first air pump or compressor which delivers air 197 to a receiver 302.
  • the connecting rod yoke which is rigidly fitted to the piston rod 319 can be fitted with a similar piston rod and piston, also known as a counterpart piston, operating in the diametrically opposite direction and said piston rod and piston engaging with a seal (not shown) which is attached to the crankcase 180, and this arrangement in combination with inlet an air check valve (not shown) and a delivery air check valve (not shown) comprises another second air pump or compressor which delivers air via conduits (not shown) to a receiver 302.
  • the air delivery volume will depend on the stroke of the mechanism 700b, which is four times the crankthrow of said mechanism, and the diameter of the piston 1 12 and the diameter of its counterpart piston connected to the connecting rod yoke which may be smaller or larger than the piston 1 12. It is also possible to achieve another four stages of compression by appropriate sizing of the diameters of piston, cylinder and its counterpart piston and cylinder.
  • the third piston 2 and/or the fourth piston 1 12 may instead be a mass, equivalent to the mass of the other piston (i.e. the first 1 and second 1 1 1 pistons, respectively) and the other connecting rod yoke, said piston balance mass being reciprocated by its connecting rod yoke without having to be in a cylinder bore. So in this way, the third piston 2 and fourth piston 1 12 may be balancing piston masses, for the purpose of balancing the first 1 and second 1 1 1 piston elements, rather than specifically working volumes within respective cylinders as working piston heads.
  • connecting rod yokes 3 and 1 13 moving on axis 35 may also each be fitted with counterpart pistons driven respectively by rectilinear drive mechanisms 700a and 700b, and said counterpart pistons may be double acting, as previously described with reference to the pistons moving along axes 34 and 134.
  • the pistons moving along axis 35 can therefore deliver another eight volumes of air per rotation of the mechanisms 700a and 700b.
  • the phasing of the air delivery from the pistons operating along axis 35 and driven by rectilinear drive mechanisms 700a and 700b depend on the phasing between the crankshaft in mechanism 700a and the crankshaft in mechanism 700b.
  • crankshafts of mechanisms 700a and 700b may be phased so that pistons 1 and 1 1 1 moving on axis 35 arrive simultaneously at the inner dead centre of cylinder 199 in which case the receiver 302 will have compressed air delivery from mechanisms 700a and 700b at each 90° of rotatbn of the combined crankshafts.
  • Such embodiments of the invention are, with the appropriate balance masses on each crankshaft, in complete rotary and reciprocating balance.
  • the "third piston” and "fourth piston” are balancing piston masses 2, 1 12.
  • crankshafts of mechanisms 700a and 700b may be phased so that pistons 1 and 1 1 1 moving on axis 35 are arranged to arrive 45° before or after each other at the innerdead centre of cylinder 199 in which case the receiver 302 will have compressed air delivery from mechanisms 700a and 700b at each 45° of rotation of the combined crankshafts.
  • This compressor embodiment of the invention is, with the appropriate balancing piston masses on each crankshaft, in complete rotary and reciprocating balance.
  • the various pistons and their cylinders in combination with double acting operation and use of counterpart pistons and cylinders, and appropriate check valves and airway conduit connections between cylinders, and appropriate sizing of pistons and cylinders, and intercooling between stages, can be configured to provide 15 stages of compression with a fully balanced machine.
  • the inventive step with respect to the system described in Figures 7 is the use of two rectilinear drives, with appropriate balance masses on their crankshafts, having at least one opposed piston from each rectilinear drive engaged in a common opposed cylinder and with a synchronous connection between the crankshafts of the rectilinear drives so that the machine can operate with any phasing between the rectilinear drives without any out-of-balance forces acting on the machine as a whole.
  • this machine which is configured as a 2-stroke internal combustion engine, has many similarities to the compressor machine explained with reference to Figure 7.
  • the arrangement of the rectilinear drives 700a and 700b and their interconnection through a synchronous drive by toothed belt and sprockets, gears, chains and sprockets, eccentric rods and shafts with bevel gears is the same for the compressor machine of Figure 7 and for the 2-stroke internal combustion engine of Figure 8.
  • any pistons which are not engaged in the common opposed cylinder 199 such as piston 2 and its counterpart (not shown), and piston 1 12 and its counterpart (not shown), and of any counterpart pistons (not shown) to pistons 1 and 1 1 1 , and of any double acting versions (not shown) of any of these pistons, is to provide scavenge air for the combustion volume controlled by the opposed pistons 1 and 1 1 1 in the opposed cylinder 199.
  • the scavenge air for the combustion volume controlled by the opposed pistons 1 and 1 1 1 in the opposed cylinder 199 is supplied from a counter piston (not shown), attached on the other side of the connecting rod yoke 3 to piston 1 , said counter piston operating in a cylinder fitted with check valves (not shown) to control the inflow and delivery of air which is routed into conduit 193 to the air ports 198.
  • the counter piston is phased at 180° to the piston 1 so that the counter piston reaches its top dead centre (TDC) position and completes its air delivery to the volume between pistons 1 and 1 1 1 when said volume is a maximum, i.e.
  • pistons 1 and 1 1 1 are at their outer dead centre (ODC) positions.
  • the displaced volume from said counter piston may be less than, equal to, or more than the combined volumetric displacements of pistons 1 and 1 1 1 in cylinder 199 depending on the desired performance of the engine.
  • the scavenge air for the combustion volume controlled by the opposed pistons 1 and 1 1 1 in the opposed cylinder 199 is supplied from a counter piston (not shown), attached on the other side of the connecting rod yoke 1 13 to piston 1 1 1 , said counter piston operating in a cylinder fitted with check valves (not shown) to control the inflow and delivery of air which is routed into conduit 197 to the air ports 198.
  • the counter piston is phased at 180° to the piston 1 1 1 so that the counter piston reaches its top dead centre (TDC) position and completes its air delivery to the volume between pistons 1 and 1 1 1 when said volume is a maximum, i.e. pistons 1 and 1 1 1 are at their outer dead centre (ODC) positions.
  • the displaced volume from said counter piston may be less than, equal to, or more than the combined volumetric displacements of pistons 1 and 1 1 1 in cylinder 199 depending on the desired performance of the engine.
  • the piston(s), counter-piston(s) and double acting piston(s) operating along either axis 34 or 134 may be used singularly or in combination to provide the scavenge air for the displaced volume controlled by pistons 1 and 1 1 1 .
  • the displaced volume above piston 2 and contained by the cylinder 299 fitted with a closing plate (not shown) and check valves (not shown) to control the inflow and delivery of air is routed into conduit 193 to the air ports 198.
  • This air delivery is 90° retarded from the motions of the pistons 1 and 1 1 1 and this is advantageous for improved scavenging and air supply for the pistons 1 and 1 1 1 .
  • the displaced volume above piston 1 12 and contained by the cylinder 399 fitted with a closing plate (not shown) and check valves (not shown) to control the inflow and delivery of air is routed into conduit 197 to the air ports 198.
  • This air delivery is 90° retarded from the motions of the pistons 1 and 1 1 1 and this is advantageous for improved scavenging and air supply for the pistons 1 and 1 1 1 .
  • the scavenge air for the displaced volume controlled by pistons 1 and 1 1 1 may be provided by the air delivery from the double acting portion of the counter piston associated with the connecting rod yoke 318.
  • the volume swept by the underside of the counter piston on connecting rod yoke 318 moves in phase with the volume above the piston 2 and therefore this volume on the underside of the counter piston of connecting rod yoke 318, when fitted with check valves to control the inflow and delivery of air from the volume, may be used to supply air to the conduit 193 and then to the air ports 198.
  • Further scavenge air delivery arrangements are possible using combinations of the pistons, counter pistons and double acting pistons.
  • the double acting and counter pistons associated with connecting rod yoke 3 and piston 1 would provide the air required for combustion between pistons 1 and 1 1 1 . This would obviate the need to have any scavenge air supply from scavenge pumps associated with piston 1 1 1 .
  • the double acting and counter pistons associated with connecting rod yoke 1 13 and piston 1 1 1 would provide the air required for combustion between pistons 1 and 1 1 1 . This would obviate the need to have any scavenge air supply from scavenge pumps associated with piston 1 .
  • the third piston element may be a compression and expansion piston and moving in a second cylinder whose major axis is coaxial with the second axis and the fourth piston element is a compression and expansion piston and moves in a third cylinder whose major axis is coaxial with the third axis.
  • rod yoke used in the context of a connecting rod yoke linked to a balancing piston mass simply means that the yoke provides a rigid link that connects the balancing piston mass to the driving mechanism.
  • the invention as described may be used with appropriate valves, connecting conduits and intercoolers for single and multi-stage compressors and may be used other appropriate valves, connecting conduits, fuelling and ignition systems for internal combustion engines which may be either of compression ignition or spark ignition combustion types.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne une machine, qui comprend au moins un premier et un second piston opposés dans un cylindre commun, un premier mécanisme d'entraînement rectiligne doté d'une première culasse de bielle reliée audit premier piston opposé se déplaçant le long d'un premier axe et d'une troisième culasse de bielle reliée à un troisième élément de piston se déplaçant le long d'un deuxième axe, orthogonal au premier axe, un second mécanisme d'entraînement rectiligne doté d'une deuxième culasse de bielle reliée audit second piston opposé, se déplaçant sensiblement en phase avec le premier piston opposé, mais dans une direction opposée et le long du même premier axe et dans ledit cylindre commun avec le premier piston opposé et ledit second mécanisme d'entraînement rectiligne avec une quatrième culasse de bielle reliée à un quatrième élément de piston se déplaçant le long d'un troisième axe également orthogonal au premier axe et parallèle au deuxième axe, ainsi que des moyens destinés à mettre en phase synchrone les premier et second mécanismes d'entraînement rectiligne. L'invention peut être utilisée pour des compresseurs et des moteurs.
PCT/GB2015/051149 2014-04-16 2015-04-16 Machine à pistons opposés avec mécanismes d'entraînement rectiligne WO2015159083A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1406827.4 2014-04-16
GB1406827.4A GB2525213B (en) 2014-04-16 2014-04-16 Opposed piston machine with rectilinear drive mechanisms

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Publication Number Publication Date
WO2015159083A1 true WO2015159083A1 (fr) 2015-10-22

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CN113374587A (zh) * 2020-03-10 2021-09-10 隆鑫通用动力股份有限公司 一种发动机驱动型发电机及其控制方法、控制系统

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GB2615808A (en) * 2022-02-21 2023-08-23 Jean Pierre Pirault Outboard motor with engine in vertically split casing

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FR1024233A (fr) * 1949-10-01 1953-03-30 Sulzer Ag Moteur à combustion interne à pistons opposés à deux temps
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US5503038A (en) * 1994-04-01 1996-04-02 Aquino; Giovanni Free floating multiple eccentric device
WO2013032431A1 (fr) * 2011-08-29 2013-03-07 Diggs Matthew B Ensemble moteur en x équilibré
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EP2650502A1 (fr) * 2010-12-06 2013-10-16 Beijing Sinocep Engine Technology Co., Ltd Mécanisme à blocs coulissants circulaires de vilebrequin et élément alternatif, bloc-cylindres, moteur à combustion interne et compresseur

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Publication number Priority date Publication date Assignee Title
US2359564A (en) * 1941-11-08 1944-10-03 Sulzer Ag Two-shaft opposed-piston internal-combustion engine
GB580704A (en) * 1944-07-18 1946-09-17 Doxford William & Sons Ltd Improvements in or relating to scavenging pumps for internal-combustion engines
FR1024233A (fr) * 1949-10-01 1953-03-30 Sulzer Ag Moteur à combustion interne à pistons opposés à deux temps
DE4035322A1 (de) * 1990-11-07 1992-05-14 Martin Dietrich Axialkolbenmotor
US5503038A (en) * 1994-04-01 1996-04-02 Aquino; Giovanni Free floating multiple eccentric device
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WO2013032431A1 (fr) * 2011-08-29 2013-03-07 Diggs Matthew B Ensemble moteur en x équilibré
US20130220267A1 (en) * 2011-09-06 2013-08-29 Mahle Koenig Kommanditgesellschaft Gmbh & Co Kg Bearing connection, engine cylinder, and engine with the bearing connection

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113374587A (zh) * 2020-03-10 2021-09-10 隆鑫通用动力股份有限公司 一种发动机驱动型发电机及其控制方法、控制系统
CN113374587B (zh) * 2020-03-10 2022-10-18 隆鑫通用动力股份有限公司 一种发动机驱动型发电机及其控制方法、控制系统

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GB2525213A (en) 2015-10-21

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