WO2006060859A1 - Moteur et pompe ameliores - Google Patents

Moteur et pompe ameliores Download PDF

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Publication number
WO2006060859A1
WO2006060859A1 PCT/AU2005/001847 AU2005001847W WO2006060859A1 WO 2006060859 A1 WO2006060859 A1 WO 2006060859A1 AU 2005001847 W AU2005001847 W AU 2005001847W WO 2006060859 A1 WO2006060859 A1 WO 2006060859A1
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WO
WIPO (PCT)
Prior art keywords
piston
cylinder
primary
chamber
valve
Prior art date
Application number
PCT/AU2005/001847
Other languages
English (en)
Inventor
Peter Robert Raffaele
Michael John Raffaele
Original Assignee
Peter Robert Raffaele
Michael John Raffaele
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
Priority claimed from AU2004906984A external-priority patent/AU2004906984A0/en
Application filed by Peter Robert Raffaele, Michael John Raffaele filed Critical Peter Robert Raffaele
Publication of WO2006060859A1 publication Critical patent/WO2006060859A1/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
    • F01L1/36—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle
    • F01L1/38—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle for engines with other than four-stroke cycle, e.g. with two-stroke cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • 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
    • F01B7/06—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 using only connecting-rods for conversion of reciprocatory into rotary motion or vice versa
    • F01B7/10—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 using only connecting-rods for conversion of reciprocatory into rotary motion or vice versa having piston-rod of one piston passed through other piston
    • 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
    • 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
    • F01B9/042—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 connections comprising gear transmissions
    • 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
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • 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
    • F01L11/00—Valve arrangements in working piston or piston-rod
    • F01L11/02—Valve arrangements in working piston or piston-rod in piston
    • 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
    • F01L11/00—Valve arrangements in working piston or piston-rod
    • F01L11/02—Valve arrangements in working piston or piston-rod in piston
    • F01L11/04—Valve arrangements in working piston or piston-rod in piston operated by movement of connecting-rod
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F01L7/021—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with one rotary valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F01L7/021—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with one rotary valve
    • F01L7/022—Cylindrical valves having one recess communicating successively with aligned inlet and exhaust ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/12—Rotary or oscillatory slide valve-gear or valve arrangements specially for 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
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • 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
    • 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
    • F01L1/026—Gear drive
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets
    • F01L1/25—Hydraulic tappets between cam and valve stem
    • F01L1/252—Hydraulic tappets between cam and valve stem for side-valve engines
    • 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
    • F01L2301/00—Using particular materials
    • 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
    • F01L2301/00—Using particular materials
    • F01L2301/02—Using ceramic materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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

Definitions

  • This invention relates to fluid machines, engines and pumps using a scotch yoke type connection to translate reciprocating linear piston motion into rotation of a operatively connected crankshaft.
  • scotch yoke is in relation to internal combustion engines which utilise scotch yoke type parallel slideways to connect a piston to a crankshaft big end.
  • scotch yoke is utilised to operatively connect at least one piston of the engine to a crankshaft big end journal of the engine. It is preferable that each piston in the engine be operatively connected to a respective big end journal of a crankshaft of the engine by scotch yoke type slideway means as disclosed herein..
  • a scotch yoke pump and engine device for rotating a crank about a main axis, said device including: a cylinder having a cylinder head; a primary piston reciprocatable within said cylinder; and a primary chamber defined at least partially by the primary piston and the cylinder head, said primary piston including a primary crown and a primary shank extending from said primary crown to a first scotch yoke device whereby to translate the linear reciprocal motion of said primary piston into the rotational motion of a first big end to rotate said crank operatively engaged thereto, wherein said device further includes: a secondary piston reciprocatable within said cylinder; and a secondary chamber defined at least partially by the primary and secondary pistons, the primary and secondary chambers being variable volume chambers.
  • the movement of the primary and secondary pistons is preferably coordinated relative to one another.
  • the primary and secondary pistons generally move in directions opposite to one another.
  • the primary and secondary pistons may move away from each other in a first phase whereby to fill the secondary or pumping chamber.
  • the secondary piston may be moved towards the primary piston to accentuate the squish or compression in the secondary chamber.
  • the fluid in the secondary chamber may thereby be pumped rapidly into the primary chamber as the primary and secondary pistons meet.
  • the device assists in pumping fluid such as air into the primary chamber preparatory, for example, to combustion in the primary chamber.
  • the device can therefore be adapted for use as a two stroke device.
  • the provision of a movable secondary piston to facilitate pumping of fluid into the primary chamber is permitted because the primary shank can be made to travel reciprocally along a linear path. This is achieved by the use of the scotch yoke connection of the primary shank to the big end. In conventional engines, the angular movement of the conrod makes such an arrangement problematic.
  • the secondary piston may be connected to a second big end by a second scotch yoke device or any number of conventional means provided the connecting means does not interfere with the primary shank.
  • the secondary piston need only have means to move towards and away from the primary piston in opposed synchronised movement therewith. However, preferably the secondary piston is also operatively connected to a second big end by a second scotch yoke.
  • the secondary piston may be moved by gearing mechanism operatively connected to a or the crank.
  • the secondary piston will preferably be operatively connected to a different big end compared to the primary piston.
  • the secondary piston may be operatively connected to a different crank as the primary piston.
  • the secondary piston is operatively connected by a secondary scotch yoke to a second big end mounted about said main crank.
  • the secondary piston's axial movement may be controlled by a gear mechanism operatively connected to main crank.
  • the second big end may be operatively connected to a second crank.
  • second big end is mounted about a common crank shaft axis shared by the first big end.
  • the primary shank may be aligned coaxial to the cylinder axis.
  • the secondary piston may be disc shaped with a central bore to slidingly and sealingly receive said primary shank.
  • the primary shank may alternatively be aligned parallel, but offset, relative to the cylinder axis.
  • the secondary piston may include a recess to slidingly and sealingly receive the primary shank.
  • the primary crown may include valve means to allow controlled communication with said secondary chamber.
  • the valve means may be a poppet valve coaxially mounted within said primary crown and/or said primary shank.
  • the piston valve means may be a ball valve, rotary valve or other valve means effective to permit fluid to be pumped selectively from the secondary chamber to the primary chamber.
  • the inner wall of said cylinder may include cylinder valve means to selectively and cyclically open and close inlet and/or exhaust ports.
  • the cylinder valve may be axially reciprocatable within a cylinder block whereby to control access to an inlet or outlet port communicating with the primary and/or secondary chamber.
  • the cylinder valve may comprise a shaft reciprocatable within a channel, track or bore in the cylinder wall.
  • the cylinder valve is preferably predominantly cylindrical in shape, at least in the region of its operative valve portion. Part of the internal surface of the cylinder head may form an annular valve seat for the valve cylinder.
  • the valve cylinder may have an upper skirt portion slidingly reciprocatable within said cylinder block. The valve cylinder may be moved up and down the cylinder by a range of means adapted to coordinate movement
  • a connecting element operably engaged to a drive means mounted on the crank.
  • the drive means may be any of a variety of means optionally, but not necessarily operatively connected to the crank or a big end.
  • the drive means may be a cam that cooperates with said connecting element to raise and lower said cylinder 30. valve.
  • the wall of said cylinder may include a slide valve axially reciprocatable within a cylinder block.
  • the slide valve may control access to an inlet or outlet port communicating with the primary chamber and or an inlet or outlet port communicating with the secondary chamber.
  • the drive means may include an additional yoke slideway operatively connected to the main crank, the first big end or another big end.
  • the drive means may control a rotary valve that governs an inlet to said secondary chamber.
  • the sealing surface of said valve cylinder that sealingly engages with said annular valve seat may be blinded or unblinded. Preferably it is blinded by a radially inwardly extending annular flange to take advantage of the pressure in the primary chamber to provide a better seal.
  • the axial movement of the primary piston shank may be guided by piston guides fixed relative to said cylinder or engine block.
  • the piston guides are mounted on an engine block.
  • the secondary chamber preferably operates as a pumping chamber to supply fluid to said primary chamber.
  • the primary chamber is preferably a combustion chamber.
  • the first scotch yoke device may include a first slideway along which a first drive block is retained to reciprocally slide as the first scotch yoke device moves about said first big end.
  • the cylinder in plan may define an axial projection having a cylinder perimeter and said first slideway and said first drive block preferably remain within said perimeter.
  • the ends of the slideways may extend marginally beyond the perimeter.
  • the first slideway preferably includes a pair of spaced parallel linear rails within which said first drive block is slidably retained.
  • the first drive block may have a central bore for receiving a rotating first big end.
  • the device may include a pair of opposed in-line cylinder groups each including a pair of said primary and secondary pistons. Each primary piston may be mounted to the first big end and each secondary piston may be mounted to a common second big end.
  • the device may include a pair of parallel cylinder groups each including a pair of said primary and secondary pistons, each primary piston mounted to the first big end and each secondary piston mounted to a common second big end.
  • the device may include a pair of V-form cylinder groups having cylinder axes normal to one another, each cylinder including a pair of said primary and secondary pistons, each said primary piston slidably mounted to said first big end by said first scotch yoke device and each said secondary piston mounted to a common second big end by a second scotch yoke device, each said scotch yoke device having a pair of slideways at right angles to one another fixed to each other for unitary movement.
  • the inner wall of said cylinder may include a false chamber wall coaxially aligned within a cylinder block, said false chamber wall including a lateral plate with a bore or recess through which extends said primary shank, said plate providing a false chamber head, said cylinder head and said primary piston defining a primary chamber, said primary and secondary pistons defining said secondary chamber, said false chamber head and an additional secondary piston defining an additional secondary chamber in limited communication with said secondary chamber by a valve means extending through said secondary piston and said false chamber head.
  • the present invention involves the placement of a second or secondary piston under a first or primary piston in a cylinder.
  • the primary piston operatively connected to a crank shaft bigend by scotch yoke slideways means.
  • the big ends being oppositely located across the crank main axis so that they are 180 degrees apart around said cranks main axis.
  • the secondary piston is preferably underneath the first piston relative the crank main axis, the two pistons, a primary piston and a secondary piston, cooperating to pump fluids in the engine.
  • the piston motions being generally or absolutely opposite each other within the cylinder so that whilst the primary piston is at its TDC (top dead centre) the secondary piston is at or near its BDC (bottom dead centre) position.
  • the pistons motion being such that as they reciprocate a volume is expanded and minimised once every 360 degree rotation of the crankshaft to which each piston is operatively connected.
  • the second piston is preferably driven mechanically and preferably by one or more scotch yokes, but other methods of reciprocating the second piston are also envisaged, for example, cams, levers, conventional conrods or desmodromic arrangements.
  • the primary piston is of one piece or rigidly connected to its yoke body and shank.
  • the secondary piston is of one piece or rigidly connected with its yoke body and shank.
  • the primary piston may have a shank which is separateable from the yoke and the shank may extend through the secondary piston to connect with its yoke body.
  • the or a piston of the device may be pivotably connected to its respective yoke.
  • the pistons and yokes are preferably guided by guide means common to the art or disclosed herein or described in our previous published patent applications dealing with scotch yoke engines, namely WO 00/60216, WO 02/27163 and WO 02/088530, the entire contents of each of which is incorporated herein by reference.
  • the invention provides an engine that employs primary and secondary pistons to enhance production of power and to more efficiently move fluids in and out of the device. This in part achieved by providing one primary piston and one secondary piston per cylinder.
  • the two pistons may define two variable volume chambers, a first chamber between the cylinder head and the primary piston crown, and a second chamber between the underside of the primary piston and the crown of the second piston.
  • the two pistons may sealingly engage a cylinder wall in which they axially reciprocate.
  • the second piston has additional sealing means to achieve sealing of the second chamber, accommodating an axial first piston shank depending from the first piston head and extending through the second piston.
  • the second piston preferably has two sets of rings, one set to seal against the cylinder and a second set to seal the first piston shank.
  • the second piston has only one set of rings which seal against both the cylinder and the primary piston shank.
  • the various components can be machined or manufactured to very high precision whereby sealing rings are not required due to the closeness of fit, the tolerances being such as any joint of concern is effectively gas-tight.
  • the invention provides a second piston sharing the same cylinder and cylinder axis as a primary piston and being on one side of the crank main axis, as indicated in the disclosure of the drawings herein, wherein the motions of the two pistons compensates for the volume lost due to the presence of the piston shank in the secondary chamber.
  • the secondary piston only displaces the volume needed to replace the shank volume present in a chamber when that chamber is a maximum volume.
  • the secondary piston may be used to pump in excess of this, it may for example be configured to displace significantly more volume than the primary piston can displace.
  • the secondary piston may be used to facilitate pumping of air in a four stroke cycle. This may for example be achieved by opening a valve in the piston crown or other transfer passage means at top dead centre (TDC).
  • TDC top dead centre
  • the cylinder head may be provided with valve means, such as a poppet valve, in line with four stroke design.
  • Another option is to draw air through the head region of the primary chamber and to compress the air in a secondary chamber, the air being subsequently released via porting or valving from the secondary chamber into the primary chamber. If the primary chambers valves are closed, the valves of the secondary chamber can continue to fill the secondary chamber to an extent in excess of the primary chambers actual physical dimensions and volume.
  • the first and second chambers simply need to be opened and closed according to combustion engine or pump principles.
  • the invention involves a piston pump or engine in which a scotch yoke is used to drive a primary piston and a second scotch yoke is used to drive a secondary piston. It is a preferment that the first and second scotch yokes are driven by the same crank shaft. It is further preferred that the first and second scotch yokes be mounted on different big ends. It is further preferred that the different big ends be oriented 180 degrees relative to each other for each primary and secondary piston pair.
  • crank or cranks may be altered on the fly.
  • the crank may be raised or lowered relative to the engine or pump block to facilitate variable compression as described in the applicant's earlier published patent specifications referenced above, namely WO00/60216, WO02/27163 and WO02/088530.
  • the first and or the second piston is guided by guide means, such as the cylinder walls, piston shanks, guide services and so on, as described in the aforementioned referenced published specifications of the applicants.
  • the primary piston head may be any one of a number of different shapes or configurations whilst still falling in the scope of the invention.
  • the secondary piston head provides a sealed barrier defining the lower moveable wall of the middle pumping chamber, whilst providing a passage for the primary piston shank to extend therethrough.
  • the secondary piston may comprise a plate, generally disc shaped with an axially extending through-void, passage, recess or bore for receive slidingly the primary piston shank.
  • the bore or recess may be co-axial with the second piston head or may be offset relative thereto.
  • the second piston head may be horse-shoe or kidney shaped whereby the primary piston shank is axially aligned adjacent the cylinder wall.
  • the secondary piston head is doughnut shaped with a central ball through which extends the primary piston shank.
  • the bore or recess may be defined by curved walls, such as circular or arc shaped walls when viewed in plan or may be polygonal.
  • the bore or recess may include sharp angles, such as a V- or triangular-shape or a hexagonal or octagonal shape.
  • the bore or recess is defined by smoothed or curved walls with no sharp angles whereby to optimise sealing.
  • more than one piston can be in operative connection with a yoke
  • the yoke and guide of a piston preferably fit within the projected axial footprint of the piston.
  • the side of the scotch yoke slideways path may lie within or without the projected footprint.
  • the distal ends of the path may extend beyond the footprint.
  • At least one piston and yoke set may be guided by the other piston and yoke set.
  • the shank of the secondary pistons may be guided by block mounted guides and the shank may then guide the primary elements.
  • the cylinders may guide at least one of the yokes of a set of pistons.
  • individual pistons may be guided by cylinder walls whilst other pistons of the same set are not.
  • the yokes and/or pistons may be guided in accordance with applicants' prior published specifications referenced above.
  • the pistons are driven by scotch yokes and even the cylinders may be driven in the same manner to improve valve performance using cylinder sleeve valves or cylinder poppet valves (see cylinder poppet valves in, for example, Figs. 10a - 1Og).
  • the scotch yoke may be used to drive other engine systems or components, for example, hydraulic pumps, magneto-electric devices, and so on.
  • the primary and secondary pistons, and in some instances detailed herein the cylinders of the device are guided by guide ways of a kind to those described in the applicants above referenced published specifications.
  • the guide means will generally include linear bearing surfaces extending parallel to the cylinder and piston axis and ultimately connected to the cylinder wall or crank web
  • the pistons and components may be made of any suitable material, combination of materials, or be formed of a composite of different materials.
  • the slideway surfaces may be treated or made to have suitable properties of hardness and wear resistance, lubrication adherence, chemical resistance, topographies, and strengths as required. Parts may be made from the non-exhaustive list of metals and alloys, or carbon based materials, organic/plastic materials and/or inorganic compounds, such as ceramics.
  • piston axis intersects the crank's main axis in the present invention. This is because such an arrangement produces the most balanced devices.
  • piston and ' main axes need not intersect as is also evident in this disclosure.
  • valve and gate the chambers defined by the cylinder and the pistons there are a number of ways to valve and gate the chambers defined by the cylinder and the pistons.
  • these valving means represent' a preferment of the present invention.
  • the big ends of each pair of big ends are 180° apart about the main axis. This is so that the pistons are closing on each other or retreating from each other simultaneously in pure sinusoidal motion.
  • non-sinusoidal motion is contemplated within the scope of the invention.
  • the second piston and its actuation can in some instances be a quasi-sinusoidal motion or some other motion to suit the need.
  • the top dead centre (TDC) of the secondary piston need not be aligned with the bottom dead centre (BDC) of the primary piston, it although it is preferable.
  • TDC top dead centre
  • BDC bottom dead centre
  • the angle of the path travelled by a drive block or working surface of a big end may be at 90° to the piston or the cylinder's path of travel as it reciprocates or at an angle to it.
  • the lever length may be variable or the lever and pivot point may have variable parameters.
  • Variable valve actuation has been described in the engine industry, although no admission of how wide spread such knowledge is made here. Variable valve actuation has been described, for example in relation to the device of a BMW company, Vanos, that alters the timing and event of valve reciprocation. Secondary piston reciprocation may be driven by such actuation systems and this may be used to achieve variable movement in the same manner that Vanos valves can.
  • the primary and secondary chambers may be used to provide pressurised air throughout the pump or engine device.
  • the chambers may be of equal volume, one chamber being used to perform a priming action for the other. However, other ratios are contemplated. It is possible to vary the displacement of each chamber by varying the stroke of the crankshaft.
  • the pistons and/or cylinders of the invention are guided in their reciprocations.
  • the guidance is provided by means other than or additional to the cylinder/piston wall interface; although in some circumstances cylinder wall guidance of a piston will be sufficient.
  • the reciprocating pistons may be guided by means other than the cylinder wall interface.
  • the piston shape and actual dimensions thereof become less critical than those of prior art devices which may rely on a cylinder wall for piston guidance. This opens up the options of having non-circular pistons in cross-section, so that the pistons may be of irregular shape.
  • the piston cross-sectional shape may be generally triangular, cruciform, amoeba, c-shaped, t-shaped, kidney-shaped, square etc.
  • the piston may be extruded to achieve such cross-sectional profiles.
  • the cylinders and their walls may also be extruded to achieve corresponding profiles to the pistons.
  • Piston shank and slideway components as well as other components of the engine may be made by conventional manufacturing techniques including but not limited to sintering, casting, or forging, or by gluing of composite materials.
  • Pair piston devices according to the invention may have multiple crank shafts sharing a common main axis. In such cases, each crank may include multiple big ends, including a first big end and/or a second big end. More than two big ends may be included on a single crank. Each crank may be operatively connected to one or more pistons in the engine.
  • the transfer shaft can be the power take off shaft. It is preferable that one or more transfer shafts are used to link multi crank arrangements and it is preferable that they are parallel to the crank axis.
  • the intermediate, transfer or connecting shaft has gears attached to each crank. The shaft and its gears may keep the split crank paired piston cranks in registration with one another. An example of a device having separate cranks is shown in Fig. 58a below. In the dual crank arrangement, the crank shafts may be parallel but not coaxial.
  • Figure Ia is a end view
  • Figure Ib is an top view
  • Figure 2a is a end view
  • Figure 2b is top view
  • Figure 2c is a plan view
  • Figure 2d is a schematic representation
  • Figure 3b is a top view
  • Figure 4 is a side sectional view
  • Figure 5 is a sectional side view
  • Figures 6a and 6b are sectional end views
  • Figures 7a and 7b are sectional end views;
  • Figure 8 is a sectional end view;
  • Figures 10a, 10c and 1Oe are sectional views; Figures 10b, 1Od and 1Of are sectional views; :
  • Figure 1Og is a sectional end view
  • Figure 12a is a top view of a secondary piston
  • Figure 12b is an isometric view of the secondary piston of figure 12a;
  • Figure 12c is a top view of a secondary piston;
  • Figure 12d is an isometric view of a primary piston and shank
  • Figure 13a is a top view
  • Figure 13b is an isometric view
  • Figure 13c is a isometric view
  • Figure 14a is a schematic side view
  • Figure 14b is a schematic side view
  • Figure 14c is a sectional top view of a square shaped piston used in the invention.
  • Figure 15 is a side sectional view of a potential boxer layout scotch yoke engine of the invention
  • Figure 16a is a schematic representation of the relative location of the pistons compared to the crank shaft
  • Figure 16b is a schematic representation of the relative locations of the pistons relative the crank main or big end axis
  • Fig. 17 is a schematic sectional end
  • Fig. 18 is a schematic sectional end
  • Fig. 20 is a sectional side view
  • Fig. 21a is a sectional side view of a twenty-first embodiment of the invention.
  • Fig 21b is a sectional end view of the twenty-first embodiment shown in Fig. 21a rotated 90°;
  • Fig 22 is a sectional end view of the invention.
  • Fig 23 is a sectional side view of a twenty-third embodiment of the invention.
  • Fig. . 24 is a graphical representation of piston movements according to a preferred embodiment of the invention
  • Fig. 25 is a sectional end view of the invention
  • Fig. 26 is a sectional end view of the invention
  • Fig. 27 is a graphical representation of piston movements according to an embodiment of the invention
  • Fig. 28 is a graphical representation of piston movements according to an embodiment of the invention
  • Fig. 29 is a graphical representation of piston movements according to an embodiment of the invention
  • Fig. 30 is a sectional end view
  • Figs. 31a and 31b are sectional end views
  • Figs 32a is a side sectional view of a twenty-eighth embodiment of the invention from an end view of the crank axis;
  • Figs 32b is a side sectional view of the twenty-eighth embodiment shown in Fig. 32a rotated 90°;
  • Fig. 32c is a top sectional view of the twenty-eighth embodiment shown in Fig. 32b rotated 90°;
  • Figs.34a is a side sectional view of a device showing actuation means that may or may not be used in embodiments made according to the invention;
  • Fig. 34b is a side sectional view of the device shown in Fig. 34a rotated 90°;
  • Fig. 35a is a side sectional view of a device showing actuation means that may be used in embodiments made according to the invention
  • Fig. 35b is a side sectional view of the device shown in Fig. 35a rotated 90°;
  • Fig. 36 is a schematic sectional end view
  • Fig. 37a is a schematic sectional end view
  • Fig. 37b is a schematic sectional end view
  • Fig. 38 is a schematic sectional end view
  • Fig. 39 is a schematic sectional end view
  • Fig. 40 is a schematic sectional end view
  • Fig. 41 is a schematic sectional end view
  • Fig. 42 is a schematic sectional end view
  • Figs. 44a and 44b are schematic sectional end views;
  • Fig. 45a is a side sectional view of a ported and valved piston;
  • Fig. 45b is a top sectional view of the device shown in Fig. 45a looking down the cylinder axis;
  • Figs 46 is a schematic sectional end view; Figs. 47a - 47f are views of various aspects of a thirty-ninth . embodiment according to the invention;
  • Fig. 48a is an isometric view
  • Fig. 48b is a side sectional view
  • Fig. 49 is a schematic sectional end view
  • Figs. 50a - 5Of are top plan views of various piston profiles
  • Fig. 51a is an isometric view of a piston blank, piston shank or cylinder extrusion according to various aspects of one embodiment of the invention.
  • Fig. 51b is an end view of the piston or cylinder shown in Fig. 51a;
  • Fig. 51c is an isometric view of a piston blank, piston shank or cylinder extrusion according to various aspects of one embodiment of the invention;
  • Fig. 52a is sectional view
  • Fig. 52b is an top sectional view
  • Fig. 52c is a sectional view;
  • Figs. 53a - 53c are isometric views showing a slide valve arrangement being a variation of Fig. 52a;
  • Fig. 54 shows a slide valve arrangement in end view
  • Fig.55 is a schematic sectional end view
  • Fig. 56a is a schematic sectional view of a crank according to one aspect of various embodiments of the invention.
  • Fig. 56b is a sectional top view
  • Fig. 56c is a sectional top view
  • Fig.56d is a top sectional view
  • Fig. 57a is an end sectional view
  • Fig. 57b is an end sectional view
  • Fig. 57c is a sectional top view
  • Fig. 57d is a top sectional view of the crank shown in Fig. 57c rotated 90° about a main axis;
  • Fig. 58a is a side sectional view
  • Fig. 58b is a schematic end view
  • Fig. 65a is a schematic
  • Fig 65b is a schematic top view of the forty-fourth embodiment shown in Fig. 65a;
  • Fig. 66 is a schematic sectional end view
  • Fig. 67 is a schematic sectional end view
  • Fig. 68 is a sectional end view
  • Fig. 69 is a sectional end view
  • Fig. 70 is a sectional end view
  • Fig. 71 is a sectional end view
  • Fig. 72 is a end view
  • Fig. 73 is a schematic sectional end view
  • Figs. 74a and 74b are schematic top views
  • Fig. 75 a is a schematic top view
  • Fig. 76b are a schematic top views of a number of crank arrangements; Fig. 77 is a schematic top view;
  • Fig. 79a is a schematic sectional end
  • Figs. 79b - 79m are top views
  • Fig. 80a is a sectional schematic end view
  • Figs. 80b - 80e are schematic plan views of various components according to various aspects of various embodiments of the invention.
  • Figs. 81a - 81 d are schematic plan views of various components according to various aspects of various embodiments of the invention.
  • Figs. 82a- 82c are top plan views of crescent shank arrangements; Figs. 83a - 83c are top plan views of piston axis and perimeter positions; Fig. 84a is a schematic side view of a fifty-sixth embodiment of the invention
  • Fig. 84b is a perspective view of the device shown in Fig. 84a;
  • Figs. 84c - 84e are schematic plan views of various elements of the device shown in Fig. 84a.
  • FIG. 1a there is shown a internal combustion scotch yoke engine 10 having a scotch yoke 60 rigidly connected to the shank 71 of a primary piston 70.
  • the primary piston 70 reciprocates along cylinder axis 21 within a cylinder 20.
  • the scotch yoke 60 having slideways X60 which slidingly engage a scotch yoke drive block 525 mounted for rotation on a first big end 80 of a crankshaft 90 to translate the reciprocating linear motion
  • the secondary piston 100 is in the form of a disc with an axial bore 101 through which can extend a length of the shank 71.
  • the secondary piston 100 defines a lower movable internal wall of a pumping chamber 22 the secondary piston 100 has chamber seal means 15 in the form of an outer ring 102 and an inner ring 103 as seen in Figure Ib the outer ring sealing between the cylinder 20 the piston 100 and the inner ring sealing between the shank 71 and the axial bore 101.
  • Figure Ib also shows the yoke path 61 defined in plan view.
  • FIG. 2a there is shown a scotch yoke engine 10a having a cylinder 20a with a cylinder 20 axis 21 within which reciprocates a primary piston 70a. which is rigidly attached via an piston shank 71a to a primary scotch yoke 60a.
  • the scotch yoke slideways X60 slidingly engages with a big end 80 (not shown).
  • the piston shank 71a is offset relative to the cylinder axis 21a and slidingly engages with a secondary piston 100a which also reciprocates within the cylinder 20a along the cylinder axis 21a.
  • the secondary piston 25 100a includes, when viewed in plan, a recess 101a defined by the horse-shoe or U-shaped shaped secondary piston 100a.
  • the secondary piston 100a together with the primary piston 70a and the internal wall of the cylinder 20a defines a lower pumping chamber 22a.
  • the lower chamber 22a is sealed against communication to the outside area 23a by a peripheral seal 104a.
  • FIG. 3a and 3b there is shown scotch yoke engine 10, it is depicted at half stroke, that is at 90 degrees to TDC.
  • the engine 10 includes a cylinder 20 in which two separate pistons, a first piston 70 which is the primary piston and, a second piston 100, which is the secondary piston, are caused to reciprocate within, by a novel scotch yoke slideway and cranking arrangement.
  • the crankshaft has two types of bigends, a primary bigend,
  • the cylinder is closed at one end by a cylinder head 29b, and together with primary piston 70, a combustion chamber 28 is there-between defined, the primary piston has sealing means X205 in the form of piston rings to seal against the wall of cylinder 20.
  • a second chamber 22 Between chamber 28 and the crank main axis 91 is a second chamber 22, this chamber is the secondary chamber.
  • the secondary chamber is defined by the underside of the primary piston 70, the cylinder wall 20, the crown of a second piston and that portion of the shank exposed to the secondary chamber.
  • the cylinder 20 is. formed in or mounted to a cylinder block 32b the cylinder having a transfer port located in a first location around the cylinder axis 21b and extending through the wall of cylinder 20, an exhaust port 34b located in a second location around cylinder axis 21b and extending through the wall of cylinder 20, an inlet port 35b located in a third location and extending through the wall of cylinder 20 into the volume 22 between the locations of the transfer port 33b and the exhaust port 34b around the cylinder 20 axis.
  • crank shaft 90b has a primary big end journal 80b and a secondary big end journal 81b.
  • Rotatably mounted on primary big end 80b is a primary scotch yoke drive block 92b which is in sliding engagement with primary yoke slideways X60, the crank includes a secondary big end drive surface W60 in the form of the secondary big end journal 81b in sliding engagement with secondary yoke slideways X80.
  • crankshaft Rotation of the crankshaft around its main axis will result in the pistons moving towards each other for 180 degrees and moving away from each other for 180 degrees of the crankshaft rotation.
  • the pistons are operatively connected to respective big ends of the same common crankshaft by scotch yoke means.
  • the primary piston is at TDC when the secondary piston is at BDC and vice versa.
  • figures 3ab and 3ac can be seen the alignment and positioning of the yoke slideways and the fitting arrangement between the shank of the primary piston and the recess in the secondary piston relative to the crankshaft axis and the cylinder and piston axes.
  • the shank 71 is shown extending like a thumb from an outer circumference V70 of the primary piston 70 towards piston and cylinder axis 21.
  • the somewhat horse-shoed perimeter of the secondary piston is displayed along with its relative position to the secondary yoke path to a centerline, shared across both drawings as a datum and reference position for the two images.
  • the images 3b and 3ba can be overlaid by the reader and aligned using the datum's and axis common to both images to come up with the composite view of the two piston arrangement of figure 3a seen looking down the cylinder and pistons axis.
  • the slideways paths are parallel to each and are in spaced relation to each other, there being a gap between their near flanks.
  • the sides of paths lay in a projection of the piston perimeter along its axis.
  • FIG 3b it can be seen in plan view that the primary yoke path 62b is offset relative to secondary yoke path 63b.
  • the device 10b further includes a secondary piston 100b reciprocatable within the cylinder 20b along a longitudinal axis parallel to the cylinder and primary piston axis 21b.
  • the engagement of the primary piston shank 21b to the secondary piston 100b is similar to that described with reference to the primary piston shank 21a to the secondary piston 100a of the second embodiment shown in Figures 2a and 2b.
  • figure 4 can be seen another schematic of scotch yoke engine 10 which includes a cylinder 20 forming part of a cylinder block 32.
  • an upper combustion chamber 28 which is headed by cylinder head 29 which includes .valving means in the form of poppet valves 38c controlled by a valve actuation means in the form of a cam shaft 39.
  • the valving means is installed in the cylinder head 29.
  • Formed in the cylinder head 29 are an inlet port 35 and exhaust port 34.
  • the ports open into the primary chamber and, seated in each of these openings is a poppet valve which is actuated by cam lobe of a cam shaft.
  • the primary piston 70 forming a moveable lower wall of chamber 28 of cylinder 20 and a moveable upper wall of chamber 22.
  • the engine 10 includes an engine block 32, main bearings 36 into which is rotatably mounted the crank 90 for rotation around said cranks main axis 91.
  • crank axes 91 and are aligned 90 degrees to the piston axis and to the cylinder axis, preferably the cam shaft 39 rotates on an axis said axis preferably parallel to the crank axes.
  • engine 10 is shown that is similar in design to the engine 10 shown in Figure 4, except that a selectively openable port, and connecting passage way which extends through the primary piston 70 to open again into the lower chamber, that is the secondary chamber.
  • the selectively openable port is equipped with a poppet valve 73 and seat means, the valves head facing away from the crankshaft main axis. Poppet valve 73 seats in the crown of piston 70.
  • the selectively openable port is opened or closed to allow air to be transported from secondary chamber 22 to the primary chamber 28.
  • the primary chamber is the combustion chamber.
  • the poppet valve 73 may be lifted from its seat in the piston crown by cam means in the form of a cam profile rigidly connected to the primary big end of crank.
  • cam means in the form of a cam profile rigidly connected to the primary big end of crank.
  • the cam design must take into consideration that the primary bigend is reciprocating back and forth under the stationary poppet valve 73.
  • the poppet valve 73 may be actuated by cam means which are stationary in terms of axis. The main axis of the crankshaft being the centre for the base circle of a cam lobe which is.
  • a scotch yoke pump or engine 10 which includes and employs more than one crankshaft to raise and lower a piston in a chamber of the device 10.
  • This particular embodiment features three crankshafts.
  • a scotch yoke drive block is mounted for rotation on the first crank big end and said drive block is in sliding engagement with primary yoke slideways, the primary slideways defining a path along which the primary drive block must reciprocate as the bigend on 5 which it is rotatably mounted makes its orbit of the main axis of the first crankshaft.
  • the first crank and its big end reciprocate, by means of a scotch yoke connection, the primary piston 70 within cylinder 20 along axis 21.
  • the primary piston defining a moving wall of primary chamber 28 and a moving wall of secondary chamber 22.
  • a second and a third crank are aligned axially parallel to said first crank and mounted for
  • crankshafts counter rotate and each has a big end which has mounted for rotation around its axis big end axis a scotch yoke drive block, each drive block being slidingly engaged by a respective scotch yoke slideways in a double headed yoke and piston arrangement, the two crank shafts being in mechanical link with each other by way
  • crankshafts may be rotationally connected by means of gears or. belts or chains or bar linkages or other registration or indexing system so that the primary piston, and the crankshafts
  • 20 secondary piston may be reciprocated in the cylinder .20 in a synchronised fashion.
  • the engine 10 includes a inlet port 35 opening into a secondary chamber 22 thru the wall of cylinder 20, an exhaust valve 38 and respective exhaust port 34 in the cylinder head 29 of the primary chamber 28, and a transfer port and passage means which extends through the primary piston crown to fluidly join the primary chamber to the secondary chamber, 25 the passage being gated by poppet valve means 73 the poppet valve head facing away from the crank main axis and seated in the mouth or lips of port which opens into the primary chamber via the primary piston passage, the valve able to seal the passage and prevent or modify flow through said passage between the chambers 22,28.
  • valve stem 74 having an elongate valve stem 74 aligned coaxially with a shank 71 e of the primary piston 70. Both the valve stem 74 and the walls of the piston shank 71 are coaxially aligned with the cylinder 20. To ensure coaxial alignment of the valve 73 a valve guide
  • the guide means 75 is provided in the shank of the primary piston, the valve guide slidingly engaging the stem 74 of the valve.
  • the guide means 75 includes complementary cooperating surfaces
  • the guide means 75 may include parallel on the valve stem 74 that slidingly cooperate with complementary surfaces on an internal surface of the piston shank 71.
  • the distal end 16 of the valve stem 74 or extension of same is operatively engaged with a cam surface which is fixed to and extends from the primary big end 80.
  • the big end 80 orbits
  • crank shaft 90 40 main axis 91 of crank shaft 90.
  • the primary big end 80 is slidingly engaged by the slideways of a primary scotch yoke 60 via a primary scotch yoke drive block 61.
  • the primary piston 70 and and or yoke may include an axially parallel extension in the form of a tail guide 94 which extends in an opposite direction to chambers of the device relative the crank axis the guide surfaces being parallel to the piston axis 21.
  • the tail guide it is preferable, as disclosed, for the tail guide to be axially parallel or indeed coaxial to the respective piston and cylinder axes of device 10.
  • the tail guide 94 slidingly engages aligned complementary surfaces of a block mounted guide 95 to ensure that the yoke and guide are not axially deflected off their respective axis.
  • the second and third crankshafts big ends being secondary bigends of the multi crank cranking arrangement on display in fig 6a and 6b and being indexed to the first crank by rotational indexing means in the form of gears or toothed belts or chains, wherein their respective yokes and pistons are driven to TDC at or around the same time as the first crankshaft big end and respective yoke and piston is at BDC.
  • the arrangement being such that the reciprocal movements of the primary and . secondary pistons within cylinder 20 are substantially opposite in direction.
  • the aim of this invention is to combine in one cylinder of a scotch yoke engine a scotch yoke driven primary piston and a secondary driven piston which is preferably driven by a crankshaft common to the two pistons.
  • the common crankshaft have oppositely spaced bigends about its main axis, although in some potential layups of the invention the bigends may not be displaced evenly about the common crank main axis the big ends being situated around the main axis of the crank less than 180 degrees apart, from a starting point and measured in one direction around the crank main axis.
  • the secondary chamber working as a supply pump for the primary chamber.
  • crankshaft common to both piston and yoke sets.
  • the disclosures of figure 6a and 6b sets out some nonlimiting examples of how multiple crankshafts can be harnessed to actuated and translate in an oppositely synchronised manner the reciprocating motion of the pistons and in doing so create the piston movement cycle of the invention.
  • a scotch yoke engine 10 that utilises two scotch yokes, this being a feature which is preferably common to all embodiments where possible, a first or primary scotch yoke 60, and, a second or secondary scotch yoke 66, to each drive a respective piston, a first piston the primary piston 70 is operatively and preferably rigidly connected to the primary scotch yoke 60 and the second or secondary piston 100 is operatively and preferably rigidly connected to the secondary scotch yoke 80, the piston reciprocate within a cylinder 20.
  • the primary scotch yoke 60 and the primary piston 70 reciprocate in unison along an axis substantially coaxial with the cylinder axis 21 between chambers 28 and 22 the primary piston 70 forming the lower moveable wall of the primary chamber 28 and the upper moveable wall of the secondary chamber 22, between the moveable upper wall of the secondary chamber and the crank axes is located a second or secondary piston 100 which is- a lower moveable wall of the second or secondary chamber, it closes the bottom end of the cylinder 20 to complete the outer bounds of chamber 22.
  • Passing thru chamber 22 is a primary piston shank 71, said shank including surfaces substantially parallel to the cylinder and piston axes.
  • the surfaces being sealing surfaces and or bearing surfaces enabling said shank surfaces to be sealed against and or enabling said shank surface to be used as a linear guide bearing for the primary piston reciprocation or secondary piston reciprocation within cylinder 20
  • Underneath, coaxially aligned and movably spaceable from the first piston 70 is the second piston 100, together the pistons 70,100 and the cylinder 20 defining a lower pumping chamber 22.
  • the movement of the second piston 100 is governed by the secondary scotch yoke 66 and the associated second big end 81.
  • the secondary piston 100 is displaceable within the variable volume chamber 22 and may assist in pumping a fresh charge into the primary chamber 28 from the secondary chamber 22.
  • the common crankshaft primary big end 80 and secondary big end 81 are 180° relative to each other around the main axis of the crank 91.
  • device 10 includes a side valve which is a poppet valve, as an exhaust valve for the primary chamber 28, a rotary valve as a inlet valve for the secondary chamber 22 and, a transfer port and passage means which extends and connects fluidly between the primary chamber 28 and the secondary chamber 22 at or around BDC of the primary piston 70 in its chamber 28.
  • the embodiment also features the use of two different types of scotch yoke, a minimum parts type scotch yoke big end bearing drive surface to engage the slideways of the secondary scotch yoke and, a donkey crosshead style, primary scotch yoke whose slideways slidingly engage a primary scotch yoke drive block which is mounted for rotation on the primary big end of the shared crankshaft
  • the primary piston and the wall of cylinder 20 and the cylinder head 29 may define the bounds of the primary chamber 28 of the invention.
  • the main or primary scotch yoke 60 and the primary piston 70 may be separately formed and joined together.
  • the primary shank 71 of the first piston 70 extends through a central bore or void 101 in the second piston 100 and is attached at its distal end 76 to the primary scotch yoke 60.
  • the two pistons 70, 100 are preferably coaxial, but at least have parallel axes.
  • the piston axes of the pistons 70, 100 are at least parallel to a plane which is perpendicular to the main axis 91 or substantially perpendicular to the crank main axis 91.
  • the axes of big ends 80, 81 are each preferably substantially parallel to the main crank axis 91.
  • the cylinder 20 includes a inlet 35 controlled by a rotary valve 40.
  • the rotary valve 40 opens and closes as it rotates allowing the secondary chamber to be filled with a fresh charge and closed to prevent gases meant to be trapped in chamber 22 from escaping out of the device through the inlet of the secondary chamber 22.
  • Other valve mechanisms able to be. used instead of rotary valve and are, of course, contemplated and proposed as a substitute for rotary valve 40 including slide valves, poppet valves, barrel valves, cylinder sleeve valves, reed valves, butterfly valves and all manner of useful gating means suitable for the purpose.
  • a cam 41 which is used to displace a poppet valve 38 which is oriented in a side valve orientation with its head facing generally away from the main axis of the common crankshaft and the crown of the primary and secondary pistons.
  • the cam 41 actuates a cam follower 42 of the side valve to open and close once every 360 degrees of crankshaft rotation.
  • the poppet valve 38 controls the opening and closing of an exhaust port 34 positioned under the cylinder head 29 and fed off to the same side of the cylinder block 2Of as the inlet 35.
  • the axis of the rotary valve 40 and the cam 41 may be shared as shown elsewhere in this disclosure.
  • the circular cams face, of the secondary big end 81 oscillates in the secondary yoke 66 along a path defined by the slideways of the secondary yoke as the crankshaft rotates.
  • the distance between the main axis 91 of crank and the axis of the secondary big end 81 can be seen in the image of 7a and 7b to be a fraction of the distance between the main axis 91 and the primary big end.
  • the embodiment is drawn at mid stroke.
  • the primary and the secondary piston motions are 180 degrees opposite so that they meet and retreat from each other in cylinder 20 once every crankshaft revolution as in most preferred embodiments disclosed herein.
  • scotch yoke connections between the crankshaft or crank shafts of the engine or pump of the invention and its pistons can allow for both pistons to reciprocate in a pattern which can be described as simple harmonic motion, it is preferable that both the primary piston and the secondary piston reciprocating motions be simple harmonic motion.
  • Pure sinusoidal motion is another term to describe the motion of the scotch yoke 60, 66 along the piston and cylinder axis if its slideways are set at 90 degrees to the piston and cylinder axis and the crank axis 91 or at.
  • Other piston motions can be developed with scotch yoke connections including motions developed from a scotch yoke slideway 60 or 66 or other like slideway.
  • the relevant slideway need not be aligned 90 degrees to the crank axis 91 of crank 90.
  • the slideway may be aligned for example at an angle to the piston and cylinder axis.
  • the secondary piston and the primary piston preferably share a common crankshaft 90 on which with their respective bigends are displaced preferably 180 degrees apart.
  • the reciprocating motion of the primary piston 70 and of the secondary piston of the pair of pistons may be equal or unequal in terms of motion pattern or distance travelled per crank 90 revolution.
  • the motion of the pistons in a pair may balance out over the crank 90 main axis 91.
  • each piston and yoke set of the pair of pistons in cylinder 20 may be equal or unequal to balance the inertia forces of the other over the crank 90 main axis 91. If the secondary piston travels less distance than the primary piston and both pistons have a matching motion, eg simple harmonic motion then it is still possible to balance the engine invention of this disclosure. This can be done by adding mass to the lighter piston and yoke set in order to increase the inertia value of the set in comparison to the other in the set inertia value or alternatively it is possible to balance the device 10 by auxiliary balance shaft means.
  • a feature of this invention being the ability to balance the motion of the primary piston against the motion of the secondary piston in order that the inertia values of each in the pair are equal over the crankshaft axis 9 L It, is possible for the device to include other drive means other than scotch yoke type sliding connections to crankshaft bigend to raise and lower the secondary piston of the invention, including the conventional connecting rod.
  • a parting line 54 is shown in Figure 7a and bolt or other fastener means 55 is provided to clamp the cylinder head 29 to the cylinder block 32.
  • a scotch yoke engine 10 having an arrangement similar to that shown in Figures 6a and 6b, except with respect to a secondary piston lOOg connected by arms 105g to an additional scotch yoke body 66g.
  • the arms l05g are fixed to the second yoke body 66g and hinged to the second piston lOOg by a gudgeon pin 106g or the like.
  • the arms 105g may be connected to the second yoke body 66g by various fixing means, for example gudgeon pins or pins, bolts, adhesive and the like.
  • An inlet port and passage means 35 of the secondary chamber 22 includes a butterfly valve 44 in the inlet 35 tract and a rotary valve 4Og to control the inlet 35.
  • the rotary valve 4 coacts with the small second scotch yoke 66, the rotary valve 4Og and scotch yoke crank axis 67 being shared.
  • the second scotch yoke 66 includes opposed slideways 68, their movement governed by an additional yoke drive block 65 rotatably mounted on a an additional big end 69 rotatable about a crank 69 having a main axis 69.
  • the additional drive block 65 is controlled by a gearing mechanism (not shown) operative connected to the primary crank 90.
  • the second piston 100 typically has sealing means in and along its axial bore 101 and its outer periphery to the wall of cylinder 20 by ring seals or the like 103,104 whereby a first piston 70 its shank and the second piston 100 with the cylinder wall 20 define a sealed pumping chamber 22.
  • Figures 9a- 9d show some relational distances between the various components of ninth to twelfth embodiments of the invention.
  • the volume AB shown in Figure 9c compared to the volume CD may have the following relationships:
  • Ratio X may equal 1 or may be in a range to provide appropriate volumetric flow for the engine shown in Figure 9C.
  • FIG. 10a, 10c, 1Oe and 1Og there is shown slightly different versions of engine 10 with a primary piston 70 and a secondary piston 100 and a combination cylinder poppet valve 47, all reciprocatable and all driven by surfaces on the one crank shaft 90.
  • the cylinder poppet valve 47 includes a cylinder wall section that is attached to, or formed integrally with a downwardly extending web M45 extending down to a tail guide 46. The cylinder poppet valve 47 is lifted off its seat parallel to the piston and cylinder axis.
  • the cylinder poppet valve 47 is lifted of its seat intermittently by valve actuation means in the form of a cam, the cam having a base circle whose center is the main axis of the crank, of course other axis of the crank parallel to the main axis of the may also be adapted for the purpose, the cam being driven by way of it being a fixed member of the rotating crank, it travels with the crank at crank speed because it is one with the crank, it is fixedly mounted to the crank.
  • the cylinder poppet valve 47h is lifted along the cylinder axis 21.
  • the cylinder poppet valve 47h is guided by guide bearing surfaces of a kind common to poppet valves, namely valve guides or "valve stem guides".
  • the cylinder poppet valve is a variety of poppet valve and just like other poppet valves it has a valve stem or the equivalent thereof in view of format of its outer and inner surfaces.
  • the cylinder poppet valve is received in a cylinder well X400, along the length of well X400 are valve stem bearings which slidingly guide the poppet valve as is the practice in the art of poppet valve guidance.
  • the cylinder poppet valve stem guide system of the device may include oil and pressure seal means to further enhance its performance.
  • the valve stem may be cooled by cooling oil or fluid means flowed through galleries included in the valves body and where it contacts its guide surfaces.
  • the cylinder poppet valve 47h is biased to a closed position against its valve seat by a spring, the spring being in this example a compression spring 49h interposed between a lower base spring stop-plate 58h formed integrally with or attached to a lower distal end portion of the valve web extension 45h and an opposed plate 49X of the engine block 32.
  • the poppet cylinder valve 57h is driven downwardly relative the crank shaft and hence off its seat in the head of the primary chamber or variable volume chamber by cam lobe of cam 59h against the force of the return spring 49h.
  • the web extension 56h includes a cam follower surface portion 56h cam follower surface portion of 56h engages the cam lobe of the cam so that the valve is able to be lifted off its seat in the variable volume, which in this case is a variable volume chamber of a reciprocating piston engine or fluid pump.
  • the cam follower portion of web extension 56h including a surface opposed to the direction of valve lift and in position to be lifted by the actuation means, that being in this instance a cam. It can be seen therefore that the fluid device of the invention may have a liftable or reciprocatable poppet style cylinder valve which may be lifted off its seat by actuation means to open a port in a chamber, that chamber in this case being a primary chamber 28 of the fluid device 10.
  • the inner wall or walls of the cylinder valves of this invention may be used, as the cylinder of a, or the, chambers of the device 10. Accordingly the invention includes the use of at least two pistons laid up and driven in accordance with the embodiments of, and disclosure of, the invention herein, and wherein a cylinder sleeve valve is included in the arrangement which has a basically central bore which is adapted to be, and function as, the cylinder wall of the primary and or secondary chamber of the engine 10.
  • the sleeve valve axis being in a plane which is perpendicular to the crank 90 main axis 91.
  • a slide valve may form a part of a cylinder wall or a sector of a cylinder wall in the device.
  • the reader is directed to consider the inclusion in a particular design variant of the invention the use of a cylinder sleeve valve, whether it be a poppet variety or some other, in the design.
  • the head 29 of primary chamber 28 is equipped with an inwardly inclining poppet cylinder sleeve valve seat.
  • This seat is a cone-like or slanting inwards surface, it is in section a truncated cone, the truncated but narrow end of the cone type poppet valve seat facing generally if not -directly toward the crankshaft main axis 91.
  • Behind the seat is a passage which is able to receive and convey fluid passing thru the open valve way or port of the passage when the valve is open.
  • the valve seat may be cut at angles similar to those cut in seats of conventional poppet valves.
  • the cylinder sleeve poppet valve may include one or more angles in its seat, as a non limiting eg the seat may includes one, two, or,
  • poppet valves typically have a two or three angle seat.
  • the head valve seat engages a valve face angle on the seating face of the poppet valve just as it does similarly in conventional poppet valve practice.
  • the cylinder poppet valve will have valve seating arrangements similar to those of conventional poppet valves. It is possible to seat the cylinder poppet valve with a single face angle shared between both the head situated poppet valve seat and the seating face of the cylinder poppet valve. In any event it is preferable that the cylinder poppet sleeve valve seat by way of an angled seat and face arrangement as is common in the art.
  • the cam follower portion of the cylinder poppet valve may include a reaction surface or a roller follower or a hydraulic lifter arrangement which can help quieten the actuation noise emanating from device 10.
  • the actuation of the cylinder sleeve valve is performed by actuation means.
  • the actuation means may be a spring means or a return means independent of the lift means or the cam and cam follower means.
  • the poppet sleeve cylinder valve may be actuated by a cam system which controls valve lift in either directions, both off and onto the seat. There are obviously a great many desmodromic type arrangement which may be adapted to the purpose.
  • the primary piston of the device 10 is in operative connection to a primary bigend of a crank shaft and the secondary piston of the device 10 is operatively connected to a secondary big end of a crank shaft, the primary and secondary big ends being 180 degrees apart in relation to crank angle or generally opposite each other relative the crank 90 main axis 91. It is preferable as depicted in figure 10a, 10b,10c,l Od 5 IOg 5 IOeCt that a single crankshaft 90 carry both oppositely located big ends, they being, the primary big end, and, the secondary big end of device 10.
  • the operative connection between the pistons and the crankshaft big end being a scotch yoke form of connection which relies on scotch yoke style slideways to slidingly engage the relevant big end of the crank shaft 90 and thereby provide a operative connection there between, device capable of converting rotational motion of the crankshaft into the reciprocating motion of a operatively connected piston, and vice versa.
  • the embodiment in figure 10 is equipped with a cylinder poppet valve 47h which is lifted by a cam 59h centred on a common crank main axis 9 Ih.
  • the lower portion of the primary piston head 70 includes recesses for receiving complementary protrusions on the upper surface of the secondary piston 100 to ensure that the volume left between the primary and secondary pistons 70,100 is minimised at the smallest volume achieved by the two pistons when forced close together complete exhaustion of the pumping chamber 22.
  • the primary piston 70 being at BDC and the secondary piston being at or around TDC.
  • the primary piston 7Oh further includes passages for communicating lubrication.
  • the poppet cylinder valve 47h may have an internal cavity for passage of coolant within or thru certain sections of the cylinder wall.
  • the cavity may extend generally parallel with the cylinder axis or be arrayed around the cylinder axis and within the wall body of the poppet valve cylinder, which if you need reminding is to be treated as and regarded as a poppet valve stem.
  • the cylinder poppet valve 47h may include cooling galleries or chambers which may be used to convey cooling medium to places within the valve or without the valve which can assist in cooling or otherwise servicing the valve or its functions.
  • the cooling galleries of lubricant galleries may be in fluid connection to the or a pressure fluid circuit of the engine, one such would be the oil pump and pressure circuit of the engine.
  • valve actuated and valve types to effect correct valve timing and flow sequencing for the device 10 to function in its particular incarnation as a pump or engine of the device with a certain pumping and fluid or gas flow cycle, it is therefore envisaged that the various valves and motion are cooperatively managed or indexed to effect flow of fluids or gases throughout the device 10.
  • FIGS 10a - lOe there is shown the engine 10 also shown in Figures 10a and 10c.
  • Figure 1Oe is a view of engine or pump 10 aligned with the crank shaft axis 9 Ih.
  • the engine 1Oh is a dual piston device also including a new type of valve, namely a cylindrical poppet valve 47h having a sealing surface 5 Ih declined from the outer wall of the cylinder 47h to the inner wall thereof so that the sealing surface 5 Ih has a truncated conical shape with the narrow end of the truncated cone facing towards the crank shaft main axis or, at least generally so, and, the truncated cone wider end being arranged further away from the crank shaft main axis 91 than the narrow end of the truncated cone.
  • the truncated coned face being the valve seat cut or otherwise formed in the cylinder head of the chamber said chamber being the primary chamber 28.
  • the cylinder valve is preferably therefore, blinded at its working end as shown in the alternative embodiment in Figures 14b and 14c.
  • the blinded valve end of the cylinder poppet valve of the figure 14b can be readily substituted into this and other embodiments of the device 10.
  • 14c and 14d attempt to show the reader some of the variation available in poppet valve head design, it it is included within the scope of the invention that the head of the poppet valve, its sealing surface and, the complementary valve seat surface of the seat and passage in head 29 can be shapes other than circular, in these two examples the valve, its seat and sealing surfaces are non round, rather being somewhat square-ish in the one and composed of curved surfaces in the other, said surfaces being recesses and protrusions, when seen in section looking down the poppet valve axis.
  • FIG 14a there is shown an unblinded cylinder valve 47h.
  • a blinded cylinder valve 47j seating on a seat in the surface of the cylinder head 29, the valve 47j having a sealing face 5 Ij around the inner face or lip of an inwardly extending annular flange 53j.
  • the valve sealing surface 5 Ij cooperates sealingly with a valve seat 52j in the cylinder head 29j.
  • the valve cylinder 47j can be centred on the axis of the primary piston 7Oj or the cylinder axis 21j using valve guide means Hj associated with or incorporated into the receiving well of the cylinder block, said sealing means and elements being laid out parallel to the cylinder axis 21.
  • the cylinder poppet sleeve valve be guided by guide ways with surfaces parallel to axis 21.
  • the valve guide means 1 Ij is shown forming part of the internal wall or surface 27j of receiving well X400.
  • the blinded cylinder valve 47j is preferable because the pressure in the combustion chamber 28j assists in holding the cylinder valve sealing surface 5 Ij against its seat 52j.
  • the return spring 49j or other return system such as magnetic, mechanical, fluid, etc. uses a mechanism effective to ensure good sealing abutment of the valve sealing surface 5 Ij and the sealing seat 52j.
  • the cylinder poppet valve 47h,47i,47j confers significant advantages with regard to fluid flow within the device 10.
  • the cylinder poppet valve 47h coacts as the internal wall of the primary 28 and secondary chambers 22 whilst enabling the valve means to shut off the inlet or exhaust port in the cylinder head.
  • the cylinder poppet valve 47h may also coact as a 'sleeve valve', of which, there is a branch of knowledge accessible in the prior art base if it is equipped with appropriately spaced or situated port means which can be brought into fluid registration with passage ways leading in or out or within the device 10, in other words the intake, exhaust or transfer port and passage means.
  • the motion of the cylinder poppet sleeve valve 47h may uncover the transfer port opening or openings leading into a passageway joining fluidly from a secondary chamber to a primary chamber of engine device 10.
  • a sleeve valve port may extend through the wall of the cylinder portion of the cylinder poppet sleeve valve wall which is the chamber wall surface of at least one of the chambers of the device 10 to act as both a passage and gate of a corresponding passage leading either in to the greater environment directly or to another volume in the device from whence it is later discharged.
  • the cylinder valve be actuated by a surface associated with common crank 90. It is preferable that said surface is a cam surface. Other valve actuation strategies may be adapted without diminishing the scope of the invention.
  • valve 47h By means other than purely mechanical means, some alternates would include the use of electromagnetics, pneumatics, hydraulics, bar linkages, also mechatronics and all sorts of other lift or displacement means suitable for the purpose. It is possible to replace the return spring with other return means adapted from the list of actuation means adapted to reciprocate the or a piston in a chamber of the engine 10.
  • FIG 1 Oa can be seen a arrow indicating the direction the cylinder poppet valve must be lifted or moved in order that the valve be lifted off its seat in the cylinder or chamber head of volume 28 it is also of note that the arrow also serves to indicated the return direction also as it is opposite to the arrow.
  • engine or pump 10 may also include transfer port and chamber valve means in situated in and passing through the primary piston 70 body.
  • transfer port and chamber valve means in situated in and passing through the primary piston 70 body.
  • poppet valve in the piston arrangement into the device.
  • this valve may open and close according to conventional two stroke principles in this instance acting as a transfer port with some where near conventional valve actuation timing or it maybe that the valve be opened much closer to TDC of the primary piston.
  • the arrangement of the embodiment is similar to the preceding embodiments with the exception that the axial poppet valve 72h seated in the primary piston 7Oh is not present and the dual piston arrangement is similar to the second embodiment.
  • the complete compliment of valve means,, ports and passage means, etc. are not always depicted, this has been done to unclutter the images to some extent.
  • Figure 11 there is shown a schematic top plan view of the respective paths of the crank shaft surfaces of the fourteenth embodiment that drive the first and second pistons 7Oi 5 IOOi and the cylinder poppet valve 47i.
  • the first path 62i corresponds to the path of the primary scotch yoke 6Oi
  • the second path 63i corresponds to the path of the second scotch yoke slider 82i
  • the third path 61i corresponds to the path of a cam 56i mounted on the crank rotating about the crank axis 9 Ii.
  • FIGs 12a-12d shows a U shaped or kidney shaped secondary piston similar to that described with reference to other examples disclosed herein of this feature figure 12b is an isometric view of figure 12a in 12b one may see the nature of the recess 101b in the secondary piston 100b, this recess may be used to allow a shank 71 of a primary piston 70 to pass by on its way to the primary piston 70 as disclosed elsewhere herein.
  • the secondary piston 100b includes a recess 101b to slidingly receive the primary piston shank 71b of the primary piston 70b. The shank fills the recess.
  • the irregular shape of the primary piston head 70b and the secondary piston 100b means that the axial centre of balance of the secondary piston 100b is offset from the cylinder axis 21b.
  • the piston axes will be taken to be co-axial with the cylinder axis 21b, the piston axis being used to broadly refer to the axial path along with the primary and secondary pistons 7Ob 5 IOOb travel within the cylinder 20b.
  • FIG. 13a there is shown a doughnut or cylindrical shaped secondary piston 100 similar to that described with reference to the first embodiment.
  • the secondary piston 100 has a cylindrical outer wall and a central void or bore 101.
  • the central bore 101 may be co-axial with the cylinder axis 21 or may be parallel but offset relative thereto, without having a common boundary with the outer wall 108.
  • a co-axial bore 101 is better balanced to withstand compressive forces than an offset void and therefore the primary piston shank 71 may be smaller in cross section to save on materials and/or to reduce weight of the shank 71.
  • FIG 13c is a iso metric view of a primary piston 70 and a yoke 60 and shank 71.
  • a secondary piston with its central through void
  • a dual cylinder device 10k having an opposed pair of coaxial primary 70ka, 70kb and secondary pistons lOOka, 100kb, a common crank, having a main axis 90k and a primary big end 80k and secondary big ends 81ka,81kb.
  • the device 10k differs slightly from other embodiments of the invention in that the secondary pistons 100ka, 100kb are operatively engaged via secondary scotch yokes 82ka,82kb and secondary big end mounted drive blocks 180ka and 180kb respectively whilst the primary piston 70ka and 70kb are slidingly engaged by an offset scotch yoke connection 160ka, 160kb.
  • the reader is directed to our published specifications referred to herein with respect to the state of play vis a vis offset scotch yoke connectors. Another useful resource for the reader is the information stored on and viewable from www.sliderengine.com
  • Figure 15 is a boxer layout of the invention, it is a two cylinder, 4 chamber, four piston version of the invention disclosed herein. It discloses the reciprocation of a piston in the device by the use of two secondary crank pins or big ends of the crank 90. The bigends sharing a common big end axis. The mass and motions of the pistons can be balanced as otherwise outlined herein.
  • the secondary pistons each have shanks 711 which are equipped with parallel guidance surfaces the surfaces being parallel to the piston axis 21 and the axis along which said shanks extend along from the secondary piston underside to which they are joined to the offset scotch yoke connection 160ka.
  • the pistons of the device figure 15 may be equipped with cylinder and chamber seal means as is common in combustion engine art.
  • Fig. 16a the pair of pistons 701,1001 in a cylinder 201 are shown by a drawing direction arrow as located to one side of the crank 901 and the big end axis 1811, their axial reciprocating travel guided by a tail guide 941.
  • Fig 16b shows the yoke path perimeter 611 in plan view and it is shown as being transverse or across the piston and extending out of the axial foot print of the piston perimeter, it is also shown as extending through the axis 21 of cylinder 20.
  • a scotch yoke device 10m has two primary pistons 70ma,70mb on a primary yoke 60m and two secondary pistons lOOma, 100mb on secondary yoke 82m.
  • the pistons 70ma,100ma are parallel to the pistons 70mb, 100mb and to a plane perpendicular to the crank axis 91m, a common crank being employed to drive pistons 70ma,70mb,100ma, 100mb via scotch yoke slideways as outlined elsewhere herein.
  • the respective big ends are 180 degrees apart around the main axis of crank 90 to which they are mounted on and form a part of.
  • FIG. 18 another multiple piston per scotch yoke variation is shown in device 1On.
  • the device 1On includes four pistons per yoke, including four primary pistons and four secondary pistons 10On.
  • the pistons are parallel and they reciprocate parallel to each other along piston and cylinder axis 21, they are not necessarily coaxial in some preferred embodiments. More than one piston per yoke can be used and embodiments so configured lie squarely within the scope of the invention.
  • the yokes 60n,82n and guides of the pistons 71n preferably fit within the projected axial footprint of the cylinder 2On or pistons 7On.
  • the side of the path of the drive blocks 65n,161n may lie within the footprint. However, the distal ends of the pathway may escape the said footprint.
  • piston guidance we generally mean yoke and piston guidance, however it is possible for the yoke and the piston to have separate guides and guideways enabling them to be guided independently of each other.
  • a pre-charge part supply single cylinder firing Vee mechanism 1Oo is shown.
  • the mechanism 1Oo may use one or more timed or indexed valves such as rotating disc valve 4Oo .
  • a first piston J has a long skirt and another piston W has a short skirt which is compensated by counterweight CW to balance the piston W and on the conrod 20Oo .
  • the mechanism 1Oo provides positive displacement of charge and is fully balanced at least on one plane.
  • the pistons J 5 W are axially guided by block mounted guides.
  • cylinder K is shown at 1 A stroke in the cycle.
  • a scotch yoke engine 1Op that includes a primary piston 7Op and a secondary piston lOOp that are coaxial, and reciprocate in cylinder 20 and driven by a common crank shaft 9Op and are at right angles thereto.
  • the secondary scotch yoke 82p is rigidly attached to the secondary piston lOOp via its shank 109 ⁇ .
  • the secondary piston 10Op has, in plan view, a kidney shaped perimeter profile and as can be seen in figures 20a, 20,b, 20c, and will therefore require a kidney shaped ring or seal. It is noted that multipart and multilayer rings are not proscribed. It is possible to use one piece rings or multi part rings and sealing means to seal the chambers of the invention.
  • Figs. 21a and 21b show two views of scotch yoke engine and pump 1Oq featuring a secondary piston 10Oq which is pivotably linked to one end of a conventional style connecting rod by way of a gudgeon pin 106q the connecting rod 11 Iq other end being pivotably connected to a secondary big end 81 of the crank 90.
  • the crank 90 also includes a primary bigend which is connected by scotch yoke means to the primary piston of the device 10.
  • the primary big end and the secondary big ends of crank 90 are preferably spaced 180 degrees apart as in some other embodiments of the invention.
  • the crankshaft of the invention may be operatively connected to the secondary piston of the engine by means other than a scotch yoke type slideway system.
  • the use of a conventional connecting rod has some important advantages.
  • the motion of the secondary piston when driven by a conventional connecting rod arrangement is not simple harmonic motion, it is a quasi-sinusoidal motion, the two pistons of the device cooperate as in the previous disclosed embodiments.
  • the yoke and pistons of the device can be guided by guide ways as is common in the art, depicted is one possible guidance method involving tail guide 94q and block mounted guide 95ka.
  • the mass and motions of the primary piston 70 and the secondary piston 100 can be balanced to some extent across the crank main axis 9 Iq.
  • engine 10 includes; a crank 90 mounted for rotation about its main axis 91 the crank having a first or primary big end 80 and a second or secondary big end 81, a cylinder 20 having a cylinder head 29; a primary piston 70 reciprocatable within said, cylinder 20 along said cylinder axis 21, a primary chamber 28 defined at least by the primary piston 70 and the cylinder head 29, said primary piston 70 including a crown portion 72 a primary shank 71 which extends from the underside of said crown 72 to a first scotch yoke 60, said first scotch yoke 60 slidingly engaging said primary big end 80 whereby linear reciprocal motion of primary piston 70 is converted into the rotational motion of said crank 90 about said crank main axis 91 said device 10 further includes a secondary piston 100 reciprocatable within said cylinder 20; the secondary piston being in operative connection to said crankshaft 90 by way of a conventional type connecting rod pivotably linking it to said secondary big end 81 of crank 90, said secondary bigend 82 being
  • the motion direction of the pistons 70, 100 being opposite.
  • the gate being a fluid valve means and being openable and closable according to engine pumping cycle requirements in a synchronous manner in relation to crank 90 angle.
  • the two chambers 22,28 cooperating to pump fluid or gases through the chambers of the device 10.
  • the chambers 22,28 having inlet and or outlet passages and valve means.
  • FIG 23 can be seen the basics of the engine 10, it is a scotch yoke type engine and it includes; a crank 90 mounted for rotation about its main axis 91 the crank having a first or primary big end 80 and a second or secondary big end 81, a cylinder 20 having a cylinder head 29; a primary piston 70 reciprocatable within said cylinder 20 along said cylinder axis 21, a primary chamber 28 defined at least by the primary piston 70 and the cylinder head 29, said primary piston 70 including a crown portion 72 a primary shank 71 which extends from the underside of said crown 72 to a first scotch yoke 60, said first scotch yoke 60 slidingly engaging said primary big end 80 whereby linear reciprocal motion of primary piston 70 is converted into the rotational motion of said crank 90 about said crank main axis 91 said device 10 further includes a secondary piston 100 reciprocatable within said cylinder 20; the secondary piston like wise in operative connection to said crank by way of a secondary big end 81 of crank 90
  • the motion direction of the pistons 70, 100 being substantially opposite.
  • the gate being a fluid valve means and being openable and closable according to engine pumping cycle requirements.
  • the bigends of the device 10 may further include scotch yoke drive block and or offset sliding connection means common to such variants of the scotch yoke family.
  • the two chambers 22,28 being linked by passage ways and port means, said passage way being a gated or valved passage.
  • the gate being a fluid valve means and being openable and closable according to engine pumping cycle requirements in a synchronous manner in relation to crank 90 angle by actuation means further included in the device.
  • crank 90 cooperating to pump fluid or gases through the chambers of the device 10. It is clear that rotation of the crank 90 about its main axis 91 will result in both the primary piston and the secondary piston being displaced along the cylinder axis 21 and that the directions of the two pistons travel along the axis 21 will be substantially opposite each other. In some embodiments of the invention primary big end and secondary bigend of crank 90 are opposed at less than 180 degree.
  • a scotch yoke engine 1Ov having a reciprocating cylinder or sleeve valve 47v which is also the cylinder wall of the primary chamber 28v and the secondary chamber 22v of the fluid engine 10.
  • the sleeve valve performing the dual functions of forming the internal cylinder wall surface of chambers 28 v and 22v and providing valve means to inlet port 34v and outlet 35v.
  • the sleeve valve 47v provides inlet/outlet access when its ports 15Ov line up in registration with the inlet/outlet ports 34v, 35v and the port passageways 12Ov.
  • the movement of the second piston 10Ov is controlled by its fixed attachment to the internal wall of the sleeve valve 47v.
  • the secondary piston 10Ov may be formed integrally with the sleeve valve 47v or may be fixedly attached thereto. In any case, the secondary piston 10Ov reciprocates in cylinder 20v as one with the sleeve valve 47v. This movement is opposite that of the primary piston 7Ov.
  • the combined secondary piston reciprocating sleeve valve 47v is, operatively connected to a secondary bigend of crank 90 by scotch yoke means.
  • the reader will note that there are a number of secondary piston drive means outlined in this specification which may be adapted to drive the secondary piston of the invention, including the use of a conventional connecting rod and link pin or gudgeon pin set up.
  • the device 10 features in this embodiment a poppet valve in the primary piston 70, its stem extending down the shank 71 of the primary piston 70 to be actuated by a cam associated with the secondary big end of crank 90.
  • the secondary big end being a minimum parts type arrangement with the big end journal bearing directly onto the secondary slideways surfaces.
  • the big end carries a rotatable circular connecting member as elsewhere seen in the art which is able to turn about the secondary axis. Basically a replacement for the minimum parts type big end centred non rotating drive surface disclosed elsewhere in this application.
  • a common cylinder, two piston common crank scotch yoke engine or pump 10x is shown with its crank case 98x in which are included block mounted guides 95x to guide the axial reciprocal movement of the secondary tail guide HOx.
  • the cylinder block 32x has an aperture and passage which are covered and uncovered as the sleeve cylinder valve 47x reciprocates.
  • the inlet 35x includes reed valves or other suitable valves that are variably timed or of fixed timing.
  • Both the upper and lower chambers 28x, 22x may be combustion chambers where the valves are suited for such an arrangement as shown in Figure 31b.
  • the primary piston shank 7 Ix may include cooling means to cool the primary piston 7Ox or to cool the lower chamber 22x or the primary piston shank71x
  • the primary piston shank 7 Ix may also be used to carry electrical transmission means such as wiring to ignition means or sensor means imbedded or otherwise carried by the primary piston.
  • the sleeve valve 47x is slidingly received in carrier or guide bearings which are part of the engine or cylinder block 32x.
  • the sleeve valve and secondary piston 47x is reciprocated by sliding engagement with a secondary big end of crank 9Ox.
  • the primary piston 7Ox is also driven by the same crankshaft 9Ox by a form of scotch yoke connection called a donkey cross head scotch yoke connection.
  • the upper end of the sleeve valve 47x is received in an receiving portion or slide chamber V83 of the cylinder head 29x the slide chamber forming an annular slot into which can extend the upper end of the slide valve in order that the cylinder wall sealing surfaces of the sleeve valve, whether they be internal or external may be sealed against unwanted . fluid leakage.
  • the sleeve valve 47x may have sealing and bearing means about its longitudinal surfaces in order that leakage does not occur.
  • the primary piston 7Ox of the device 10 is shown with transfer port and passage means and poppet valve means as otherwise described herein.
  • FIG. 32a 32b, 32c there is shown three different views, (an end view, a side view, a top or plan view,) of a scotch yoke engine 1Oy having a primary chamber 28y above a primary piston 7Oy, a secondary chamber 22y defined by a secondary piston combined cylinder 47y and the underside of the primary piston 7Oy.
  • the primary piston 7Oy includes an axial shank 7 Iy that is rigidly connected to primary scotch yoke 6Oy that reciprocates up and down along the cylinder axis 2 Iy in sliding engagement with a drive block 92y mounted on the big end 8Oy.
  • the reciprocating motion of the working surface of the secondary big end 8 Iy within the scotch yoke slideways of provides for linear reciprocal motion of the cylinder poppet valve and secondary piston combination 47y.
  • the paths travelled by the drive surfaces or drive blocks is parallel to a plane which is perpendicular to the crank axes 9 Iy.
  • Valving and gating of the chambers 28y, 22y can be two or four-stroke and variance of these including, but not limited to: Miller cycle, Atkinson cycle and combinations of cycles.
  • the reciprocating guides HOy preferably lie within an axial projection of the perimeter 17Oy of the projection of the piston/ cylinder.
  • figures 32a, 32b, 32c can be seen an ideal layup of the device in terms of relationships between key components of the invention. It can be seen in 32a that it is preferred that the yoke slideways of the invention are in a plane which is perpendicular to the crank main axis 9 Iy.
  • Figure 33 shows an engine or pump 1Oz in a 90° V formation incorporating the novel piston pairs and utilising scotch yoke type connections. Note that a variety of angles are contemplated within the scope of the. invention.
  • the pump or engine 1Oz includes a common crank having a main axis 91z that drives all yokes from the two or more separate big ends.
  • the device 1Oz shown has four yokes, four pistons and, at least two cylinders and two big ends.
  • Valving or gating means are provided in passages linking the chambers of one piston pair to the chambers of a different piston pair.
  • the chambers and pistons in this device 1Oz may be configured to pump fluids such as gases to chambers housing other piston pairs. The fluids and gases pumped or intended to be pumped in or out of a
  • each cylinder 2Oz includes a passage 121 z linking respective secondary or primary chambers 22z, 28z. Valving or gating means 4Oz is provided intermediate the length of the passage 12 Iz.
  • the device 1Oz includes an offset scotch yoke with slideways 6Oz that slidingly engages with the offset scotch yoke connection means 65z. its a Vee engine with primary and secondary chambers in accordance with our inventive concept.
  • Figs. 34a - Figs. 35b shows devices 390a,390b having height adjustable means 391a,391b to adjust the valves 392a,392b with respect to timing and occurrence as the piston reciprocates.
  • Fig. 36 shows a device 10za having a primary piston 70za with a piston head 72za in which is housed a rotary valve 73za. The operation of the rotary valve 73za is controlled by lever 393za in turn governed by guide way 394za via a cam follower at the lever's 393za distal end 395za.
  • the axial reciprocation of the primary piston 70za is guided by the sliding engagement of a piston guide in the form of a longitudinally aligned ridge of the piston shank 71za and a block mounted guide means 95za.
  • the distal end 76za of the piston shank 71za is slidingly engaged within an offset scotch yoke slider connection 60za.
  • the rotary valve 73za is supplied via a port passage 396za extending from a side wall of the piston shank 71za upwardly to the rotary valve 73za.
  • the secondary piston lOOza can form part of this type of arrangement, but is omitted from this drawings for the sake of clarity.
  • a scotch yoke device 10zb having parallel cylinders 20Zb operatively linked by cooperating gears 190zb, 191zb.
  • the gears 190zb,191zb are meshed directly although, as shown in Fig. 37b, an intermediate gear 192zb may be used.
  • the gears 190zb, 191zb are preferably circular as shown but may just as equally be elliptical or irregular (e.g. kidney shaped) and configured to remain enmeshed for varying shaft speed and so on
  • Fig. 38 provides a device lOzc in which secondary cranks rotating about second crank axes 397zc are driven at non-uniform angular velocity by elliptical gears 390zc.
  • the device 10zd in Fig. 39 is similar to device 10za described in Fig. 36, in that the primary piston head 72zd includes a rotary valve 73zd the operation of which is controlled by a lever 393zd. However, instead of a port passage extending into the piston shank 71zd, the port passage 396zd opens at the underside of the piston head 72zd and continues, via the rotary valve 73zd, out the top of the piston head 72zd through the piston crown 398zd.
  • the piston head 72zd includes a floating piston crown 398zd in which the crown moves and down along the line of retaining means axially and parallel to the piston axis 21zd in the form of a pair of guide pins 399zd trapped in recesses 400zd within the head 72zd.
  • the guide pin is fastened to the base of the piston head 72zd, preferably by threaded means.
  • the distance "4" shows the distance of travel of the cam follower 401zd as it reciprocates.
  • Fig. 40 shows a scotch yoke device 10ze, having a piston crown 402ze or head fixed in both ends of a floating internal cylinder 47ze.
  • the cylinder 47ze reciprocates within a cylinder block 32ze whereby cylinder wall ports 403ze corresponding to cylinder block ports 120ze move into and out of registration therewith.
  • the head 402ze.of the primary chamber 28ze, the walls of the cylinder 47ze and a secondary piston lOOze are all connected and reciprocate together within the cylinder block 32ze.
  • a device 10zf has a primary piston 70zf operably connected to a primary yoke 60zf and a secondary piston operably connected to a secondary yoke 82zf by a pair of arms 105zf.
  • the inner cylinder wall 47ze comprises a piston crown 402zf and the secondary piston lOOzf
  • a rack 407zg is mounted on a big end centred drive block or surface and via an intermediate gear 408zg imparts rotary motion to a rotary valve situated in the piston which has a gear centred on its axis enabling the opening and closing of a passage leading from a volume below the piston crown to above the piston crown.
  • a device 10zh has a reciprocating cylinder 47zh that is closed at both ends with a top head 152zh and a base 153zh, has a cylinder wall 154zh, reciprocates within a cylinder block (not shown) and houses a first piston crown 70zh and a second piston crown.
  • the first piston crown is fixed to block mounted guides 95zh by brackets 193zh extending through the cylinder wall 154zh through a sealed slot 194zh.
  • the cylinder head 152zh is operatively connected, via a shank 155zh extending down the outside of the cylinder wall 154zh to the engine block/the drive block or surface 65zh operatively engaged in sliding relationship to a scotch yoke 60zh.
  • Figs. 44a and 44b show a another preferred embodiment of fluid device 10 it can be readily seen that it is a Boxer or pancake embodiment of the engine.10 in which primary pistons 70zi and secondary pistons lOOzi meet and retreat within a shared cylinder 20 along cylinder axis 21.
  • the primary pistons 70zi and the secondary pistons lOOzi axes are 180° apart about a main axis 91zi of crank 90.
  • a rotary valve 40zi is controlled by a cam lobe 41zi in turn controlled by a push rod 42zi actuated by a rocker actuator 43zi driven by a poppet valve 44zi located in the cylinder block head 29zi to control the exhaust port 34zi.
  • This head arrangement may be provided at each end of the device 10zi.
  • the rotary valve 40zi rotates at engine speed. It may provide one valving event per rotation.
  • the device lOzj is an example of how to lay out a Boxer engine with applicant's improved underside piston pumping arrangement.
  • the piston axes are preferably parallel with the cylinder axis 21zi and the cylinders 20zi are coaxial.
  • the primary piston 70zi preferably includes valve means shown as poppet valve 74zi.
  • the cylinders 20zi or portions thereof have valve means and as described above the cylinder head 29zi includes valve 44zi.
  • the valves are actuated according to fluid pump and/or engine parameters.
  • the actuation means 42zi,43zi is variable in its effect on the inlet valve 40zi so that the valve 40zi is adjustable in relation to its flow rate/timing and so on.
  • Actuation means may be driven directly by the crank that has a main axis 91zi or by other means as described with regard to equivalents as the skilled person appreciate.
  • the respective rotary valves 40zi counter rotate.
  • the device 1 Ozi preferably includes masses countering mass imbalances in the crank assemblies.
  • Fig. 45a shows a device lOzj in which the primary piston shank 71zj is operatively fixed to a follower 89zj adapted to travel within a cam guide means being an arcuate track 394zj and to also to a prime slideway ⁇ Ozj.
  • the secondary piston lOzj is connected by a pair of arms shanks 105zj to a secondary slideway 64zj.
  • the primary piston 70zij includes a crown in the form of a disc valve 74zj preferably coaxially aligned with the cylinder and piston axes 21zj.
  • Fig. 45b shows the footprint or axial projection of the path 62zj of the primary slideway 60zj.
  • Fig. 46 guidance is provided in a device 10zk to a first piston 70zk and a second piston lOOzk integrally formed or otherwise made into one fixed structure with a cylinder wall 154zk.
  • the secondary piston is operatively engaged to secondary slideway 64zk by downwardly extending secondary shanks 105zk.
  • the primary piston 70zk reciprocates within the cylinder wall 154zk and divides the internal spaces thereof into a primary chamber 28zk and a secondary chamber 22zk.
  • the movement of the secondary piston 1 OOzk is governed by primary and or secondary guide cylinders rotatable about a guide cylinder axis 411zk whereby its movement defines a composite perimeter 412zk.
  • a crescent shank 416zk is provide with the primary cylinder 410zk.
  • the crescent shank 416zk includes a wall valve passage or port 417zk to act as an inlet or outlet and cooperates with an exhaust port or inlet port 34zk in the block wall 32zk that may come into registration with a corresponding aperture in the cylinder wall 154zk.
  • the pistons 70zk,100zk are driven by a common crank having a main axis 91zk or by cranks whose main axes are coaxial or parallel to each other.
  • the cylinder wall 154zk operates as a valve that is a type of reciprocating sleeve valve.
  • the surface of the shank type 100zk may provide a portion of the primary and/or secondary chamber wall or as shown here may provide the entire wall 154zk, with the exception of the head 152zk.
  • Figs. 47a - 47f show a boxer device 1OzI that can be a 2- or 4-stroke device.
  • Figs. 48a and 48b show a big end support structure 183zm comprising an entrapment slot 184zm.
  • the trapped web 185zm of the big end rests in the slot.
  • the big end rotates about the big end axis 181zm that is offset but parallel to the main axis 91zm.
  • the trapped portion 185zm is free to move only along a path defined by the slot 184zm.
  • Fig, 49 shows a dual piston device 10zn having a reciprocating secondary piston lOOzn which is also the cylinder wall 154zn for both the primary chamber 28zn and the secondary chamber 22zn.
  • a slide or sleeve valve 47zn lies coaxially between the sleeve valve 47zn and the cylinder block 32zn.
  • the sleeve valve 47zn is a non-reciprocating element but its position may be altered up or down to effect timing in the opening of the cylinder wall 154zn as the sleeve valve 47zn reciprocates.
  • the secondary piston lOOzn is connected by secondary shank arms 105zn to a secondary yoke or slideway 82zn.
  • the cylinder 47zn is generally stationary but can be raised or lowered by a rack in mesh gear arrangement 417zn.
  • Figures 50a-50f show various possible piston profiles, including s-shaped, triangular, amoeba, cruciform, c-shaped and t-shaped.
  • Figure 51a is a representation of either a piston, piston shank or cylinder of triangular cross-sectional profile comprising a crown 171zo, a base 172zo and a wall 173zo, the inner surfaces of the crown base and wall defining an internal void 174zo.
  • the void 174zo is sized to receive a correspondingly sized and shaped piston.
  • the wall 173zo will be short and unlike the elongate wall 173zo shown.
  • FIG. 52a there is shown a portion of a cylinder 24zq that defines a central chamber 28zq in which a piston 70 and or 100 may reciprocate along a piston or cylinder axis 21zq.
  • the cylinder wall 24zq includes elongate slots 418zq, 418zqq within each may reciprocate longitudinally or be displaced longitudinally a respective slide valve 419zq and 419zqq.
  • the slide valves have suitable ports 421zq and 421zqq adapted to register with corresponding passages 422zq 422zqq of the engine..
  • the slots 418zq are preferably parallel to the piston or cylinder axis 21zq.
  • the slide valve 419zq can reciprocate in a direction parallel to the piston axis 21zq whereby the opening 421zq aligns in registration with the passage 422zq to enable the ingress or egress of fluid there through into or from a chamber 28zq or 22zq of the two piston in one cylinder engine.
  • the cylinder wall 24zq may also be a reciprocating member eg a combined secondary piston and sleeve valve and therefore may be mounted for reciprocal motion to the cylinder block 32 in bearing ways adapted for the purpose which include linear bearing surfaces which slidingly engage complementary surfaces on the sleeve valve. The complementary surfaces also extending parallel to the cylinder axis 21 (not shown).
  • Figures 53a-53c show a slide valve arrangement according to a variation on the embodiment shown in Figure 52a in which the cylinder wall 24zr is eccentrically shaped in profile across its axis 21zr whereby to accommodate a slide valve 419zr the wall of cylinder 20zr.
  • the slide valve 419zr reciprocates in a slot 418zr extending longitudinally through cylinder wall 24zr and aligned along an axis parallel to the cylinder axis 21zr.
  • the slot 418zr is located within the cylinder wall 24zr of the cylinder block 32, the cylinder wall 24zr defining a cylindrical void for reciprocation therein of a piston along the cylinder axis 21zr.
  • the cylinder 20zr may reciprocate within a cylinder block (not shown),
  • the slide valve 419zr may be actuated by suitable means as described with reference to analogous devices herein. It is preferred that slide valves used in the invention are linked to or rigidly attached to one or other of the piston and yoke sets of device 10. Rotating cam or other actuation is also feasible and use of same could hardly diminish the scope of the invention.
  • the valve opening 421zr may have sealing surfaces 426zr around the periphery of the opening to provide an improved seal or the tolerances of the components may be made to high precision. It can be seen that fluids such as air or gas can be flowed either way through the opening 421zr and passage 422zr when in registration or when they define a continuous passage there through.
  • Figure 54 shows a similar arrangement 10zs to the arrangements shown in Figures 52a- 52c in device 10zq
  • Figure 55 shows the slide valve device 10zr in the context of a scotch yoke engine or pump 10zt in which the slide valve 419zs reciprocates within a slot 418zs whereby its opening reciprocates between a position in which it is in " an exhaust passage 422zs in the cylinder wall 24zs to enable the egress of fluid from a primary chamber 28zs in the cylinder block 32zs and a position where the opening 421zs occludes the passage 422zs.
  • the slide valve 419zs is actuated by a roller or bucket follower mechanism 42zs that cooperates with a cam 41zs mounted about the same axis that a rotary valve 40zs is mounted on, the rotary valve 40zs controlling an inlet 35zs located in the cylinder wall 24zs intermediate its length on one side thereof.
  • the slide valve 419zs reciprocates within the slot 418zs along a path parallel to the cylinder axis 21zs.
  • a crank 90zt having a main axis 91zt and a transverse slot 184zt being a cross-sectional trapezoid shape.
  • a big end 80zt has a big end journal 183zt and a big end web 185zt having a correspondingly sectional trapezoid shape adapted to slidingly engage in the slot 184zt. As shown in Figures 56c and 56d, the big end journal 183zt is moveable relative to the crank main axis 91zt to vary the throw of the big end 80zt.
  • FIGS 57a-57d there is shown another throw-variable moveable big end 80zu having a web 185zu moveable within an internal passage 184zu whereby to vary the length of throw of the crank by means of an hydraulic ram in the passage 184zu.
  • a dual crank arrangement having separate cranks, a first crank 90zvi rotational around its main axis 91zvi and a second crank 90zvii rotational around its main axis 91zvii, the main axes 91zvi,91zvii being parallel if not coaxial relative to each other.
  • 91zvi has a primary main journal 92zvi and the secondary crank on the secondary main axis 91zvii has a secondary main journal 92zvii.
  • the main journal 92zvi there is mounted a first gear 190zvii enmeshed with a second gear 190zvi which is mounted on a transfer shaft 97zv aligned parallel with the main axes 91zvi,91zvii.
  • 92zvii has like wise got a gear which links to a gear on the transfer shaft enabling the separate crankshafts to be kept in register as the rotate.
  • the use of transfer shafts and systems to operatively link separate crankshafts and other rotational components in the device 10 is clearly contemplated.
  • Fig 59 shows an arrangement similar to that shown in Fig. 58a and 58bb, but the transfer shafts are not parallel with crank axes 91zwi,91zwii and bevelled gears are used to drivingly connect to the crank journals 92zvi,92zvii to a transfer shaft.
  • Figs. 60a and 60b show a valve such as a poppet or slide valve having a valve stem 74zx situated in a primary piston having a primary shank 71zx connected to a yoke slideways device 60zx.
  • a valve stem 74zx situated in a primary piston having a primary shank 71zx connected to a yoke slideways device 60zx.
  • Coaxial to the primary piston and cylinder axis 21zx is a doughnut shaped secondary piston lOOzx in part defining a secondary chamber 22zx of a cylinder 20zx.
  • the valve stem 74zx is coaxially aligned to the cylinder axis 21zx by valve guides 75zx:in or on the primary shank 71zx.
  • the valve stem 74zx is biased to an closed position by a compression spring 176zx contained with a spring cover 177zx, the base cap 178zx in which is fixed the distal end of the valve stem 74zx.
  • a swing cam 427zx rotatable about a cam swing axis 428zx within the side profile perimeter of the primary shank 71zx.
  • a roller follower 429zx mounted on a roller follower axis 430zx on the primary shank 71zx coacts with a shallow S-shaped cam surface 431zx.
  • the swing cam 427zx is caused to swing on its axis 428zx, its profile being such that as it swings it lifts the valve stem74zx.
  • the roller follower 429zx is limited to inside the side profile perimeter 71zxi of the primary shank 71zx or it or its support structure may extend from the shank 71zx to the cam surface 431zx.
  • the roller follower 429zx follows the cam path of the cam surface 431zx.
  • roller follower 429zx is rotatably mounted on the swing cam 427zx on an axis 430zx distant from the swing cam axis 428zx, motion of the follower 429zx following an arc centred on the swing axis 428zx, the swing cam's working face effectively axially moves the valve stem 74zx.
  • the cam surface member 431zx is moved up and down by a rack gear arrangement 433zx operable by a lever 434zx to alter the valve timing relative piston motion
  • the valve spring return 176zx may be substituted with other return means such a pneumatic, linkage or roller return.
  • the device 10zx has a main crank rotatable about a main axis 91 zx and a big end rotatable about a big end axis 181 zx.
  • Figs. 61a - 61e a number of variations of the cam surface 431zx of Fig. 60a are shown.
  • a roller or follower 430zy engages a one-sided cam way similar to cam surface 43 lzx.
  • the roller 430zy is connected to an articulated lever 432zy having a working end 435zy to actuate the valve stem 74zx and a pivot point 436zy intermediate its length.
  • the arrangement is similar to that of Fig. 61a, except that the cam way 4.31zz is double sided.
  • Fig. 61c the arrangement is similar to that of Fig.
  • cam way 431ya is a monorail design engaged by a dual roller truck device 430ya.
  • Fig. 61d the arrangement is similar to that of Fig. 61b, except that the double sided cam way 431yb is a engaged by a multiple contact follower device 430yb.
  • Fig. 61 e shows a valve actuating cam arrangement similar to that of Fig. 60a.
  • the swing arm follower being the spring base cap 178zx that directly actuates the valve stem 74zx is preferably coaxial with the piston axis 2 lzx, although other orientations can be made to work.
  • the swing arm follower 178zx preferably lies in a guide way inside the piston shank 7 lzx or shank perimeter 71zxi.
  • Figs. 62a - 62c shows various possible axial orientations of the components of the device lOzx shown in Fig. 60a.
  • the valve stem 74yc is parallel to, but not coaxial with, the piston and cylinder axis 2 lye.
  • valve stem 74yd is coaxial with the piston and cylinder axis 21yd.
  • valve stem 74ye is non-parallel and transverse (but not necessarily intersecting) to the piston and cylinder axis 2 lye.
  • the valve stem 74ye and swing cam follower 178ye can reside within the shank perimeter 71yei or partly or wholly outside thereof and be on an axis 437ye which is not parallel to the cylinder axis 2 lye.
  • Figs 63a and 63b show a dual crank arrangement lOyf having two crank shafts that are parallel but not coaxial.
  • the arrangement lOyf has a first crank 90yfi with a first big end
  • crankshafts may be operatively connected to the piston arrangement of the invention as other wise disclosed herein
  • Figs. 64a and 64b there is shown a twin or multicrank device which is suitable for inclusion of mechanical links to keep the cranks in register with regard to crank angle.
  • the first crank axis 91ygi is oriented normal to the second crank axis 91ygii.
  • Compound crank shafts of 2:1 or 3:2 annular sun gear: planet gear ratio are useful as actuation devices for primary or secondary pistons.
  • An example of a compound crank mechanism can be found elsewhere in this disclosure and in the references incorporated herein above.
  • Figs. 65a and 65b show a crown 398yh of a floating piston 70yh in respect of which the underside 439yh of the crown 398yh is shaped to match the outer circumference of a rotary valve 74yh mounted within the piston body or base 72yh.
  • the piston body 72yh has an upper cradle 438yh and a lower shank 71yh.
  • the core of the rotary valve 74yh defines a central through bore, hole or slot 440yh that may come into alignment with an aperture in the floating piston body 398yh in the form of a truncated conical aperture 79yh.
  • Seal ring 426yh provides a seal between the piston base 70yh and the floating crown 398yh.
  • the crown 398yh When the pressure in the combustion chamber (not shown) presses upon the top of the crown 398yh, the crown 398yh is pressed against the face of the rotary valve 74yh to stop the flow of gas through the crown 398yh.
  • the rotation of the rotary valve 74yh may be constant or intermittent and in one direction or in either direction. Additional sealing means may be provided to supplement the effect of the crown underside 439yh pressing down on the rotary valve 74yh. Therefore the underside 439yh may include additional sealing means such as rings or lip seals and so forth.
  • the floating crown piston 70yh may be adapted for use in paused piston fluid pumps disclosed in this specification and in the above disclosures incorporated herein by reference.
  • Fig. 66 shows a Boxer layout of the paired piston device lOyj, other non-limiting versions of which are disclosed herein, having a common crankshaft 90yj a first cylinder axis 21yji and a second cylinder axis 21yjii.
  • Each cylinder 20a and 20b has a primary 70 and secondary 100 piston mounted for reciprocal motion therein.
  • the pistons are operatively connected to the common crankshaft as elsewhere disclosed herein.
  • the device 10yj is a Boxer layout of the device, a feature of note being that the cylinders 20a and 20b are not coaxial as is common with boxer engines.
  • Fig. 67 shows a multi parallel piston device lOyk having one or more cranks 90yk parallel to each other or at angles to each other but each main axis 91yk extending along a common plane.
  • FIG 68 can be seen a variable compression ratio version of engine 10.
  • the engine features a primary piston 70 and a secondary piston 100 linked to a crankshaft 90 and functioning as described elsewhere herein.
  • a compression ratio adjustment means 202 comprising a displaceable piston 222 in a cylinder 212, the cylinder 212.
  • the piston 222 being height adjustable within its cylinder 212 with respect of the head region of said cylinder 212 an adjustable volume chamber 232 being created there between .
  • the head region of said cylinder 121 having a port and passageway means extending from cylinder 232 into a chamber of the device 10, that chamber being in this particular embodiment, the secondary chamber 22 of the device 10
  • the gas trapped under the primary piston crown 72 in variable volume chamber 22 may become overly compressed or in another operational situation become under-compressed before being vented by transfer port and passage means into the primary chamber of the device 10.
  • an additional volume or separated volume has be fluidly linked to the chamber, that chamber being the secondary chamber 22.
  • variable volume chambers of the device may be thus variably compressed, furthermore it will be appreciated that a variable volume chamber of the device may have its overall volume altered to achieve variable compression of a particular chamber within the device.
  • FIGS 78a and 78b there is shown a dual piston arrangement in accordance with the invention in which there is a primary piston 70yy and secondary pistons lOOy and lOOyy which are aligned parallel to, but offset from, the cylinder axis 21.
  • the device is similar in almost every respect to those other examples found herein. It can be seen that the secondary chambers of device 10yz are separated from the primary chamber not by the primary piston but by a bottom end wall of chamber 22. Through this end wall or region of chamber 22 extends primary piston shank 71 of primary piston 70 the shank extending parallel the cylinder axis 21 An aperture 252 in the end wall 1001 is adapted to allow reciprocating movement of the shank 71 as is common in many embodiments of the invention.
  • the secondary chambers 441yzi and 441 yzii are joined by port and passage means to secondary chamber 22. It can be seen that in effect, secondary pistons lOOy and lOOyy are the moving lower wall of secondary chamber 22 separated by a wall portion of chamber 22 and in fluid connection thereto by port and passage means.
  • the passage way leading from a secondary chamber 441yzi , 441yzii may be gated by valve means, in this particular embodiment the inventor has opted for ball valve means.
  • The" three secondary chambers of the embodiment in gateable fluid connection.
  • a device 10yz having at least one secondary chamber that does not have as a boundary the primary shank 71yz surface.
  • the device 10yz includes a pair of parallel, spaced additional secondary pistons 112yzi,112yzii in additional secondary cylinders 441yzi,441yzii and having secondary shanks 109yzi,109yzii attached to a secondary scotch yoke slideway 66yz.
  • Fig. 80a shows device 10yz in plan view including the relative positions of the additional secondary cylinders 441yzi,441yzii defining corresponding perimeters and that of the ball valves 446yz.
  • Fig. 80b shows a similar arrangement as in Fig. 80a, except that the ball valves 446xa lie outside the axial projection perimeter of the secondary chamber 441xa but within the larger perimeter 179xa of the cylinder 20xa which also corresponds to the perimeter of a second secondary chamber.
  • Fig. 80c shows another variation in which the ball valves are both located within a first secondary chamber perimeter 441xbi but not within an inner secondary chamber perimeter 441xbii.
  • Figs. 81a - 81d show other arrangements in which the relative positions of the piston or cylinder axis 21xci, 21xcii and piston or cylinder perimeter 179xc,441xci,441xcii are varied.
  • Figs. 82a and 82b are top plan view of crescent shank arrangements in which the shank 71xd inner concave face forms part of the cylinder wall for a secondary chamber 22.
  • the combination of the shank 71xd and the secondary piston form a composite perimeter 441xd that defines the boundaries within which it is Figs. 84a - 84e show a paired piston device 10xg with a crescent shank 71xg having in its inner concave wall surface a slot 458xg which receives slidingly and sealingly an sealing ring extension of the secondary piston 100xg in the form of a shuttle seal 459xg.
  • the shuttle seals longitudinal surfaces are parallel to the cylinder axis 21xg.
  • the shuttle 459xg may be formed integrally with an seal ring 103xg in ring lands of the secondary piston lOOxg.
  • the shuttle portion or portions 459xg should intersect at least partially the perimeter of the cylinder ring 103xg.
  • the annular ring 103xg operates as a normal sealing ring but with a shuttle portion 459xg attached that seals the longitudinal gap between the shank face and the cylinder wall and/or the secondary piston and the edge of the shank as it meets cylinder wall 20.
  • the scotch yoke devices of the invention have wide application as motors for driving a main crank, particularly in the automotive industry and particularly where variable compression is advantageous.
  • the word "comprise” and its derivatives is intended to have an inclusive rather than exclusive meaning unless the context requires otherwise.

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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 dispositif pompe ou moteur à excentrique scotch (10) conçu pour faire tourner un vilebrequin (90) autour de son axe principal (91). Ledit dispositif comporte un cylindre (20) ayant une culasse (29); un piston primaire (70) alternatif à l'intérieur dudit cylindre (20); et une chambre primaire (28) définie au moins par le piston primaire (70) et la culasse (29) et le cylindre (20). Ledit piston primaire (70) comporte une couronne primaire (72) et un manchon primaire (71) s'étendant du dessous de ladite couronne primaire (72) en direction d'un premier excentrique Scotch (60) de façon à transformer le mouvement alternatif linéaire dudit piston primaire en mouvement tournant d'une première bielle (80) autour dudit vilebrequin (90) venant fonctionnellement en prise avec elle. Ledit dispositif (10) comporte en outre un piston secondaire (100) alternatif à l'intérieur dudit cylindre (20); le piston secondaire étant également en liaison fonctionnelle avec ledit vilebrequin (90) par le biais d'une bielle secondaire (81) de ce vilebrequin (90), ladite bielle secondaire étant placée du côté opposé par rapport à l'axe du vilebrequin (90). Ledit dispositif (10) comporte en outre une chambre secondaire (22) formée par lesdits pistons primaire et secondaire (70, 100) et la paroi du cylindre (20). Lesdites chambres primaire et secondaire (28, 22) sont à volume variable.
PCT/AU2005/001847 2004-12-06 2005-12-06 Moteur et pompe ameliores WO2006060859A1 (fr)

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FR2921694A1 (fr) * 2007-10-02 2009-04-03 Jean Claude Keromnes Moteur thermique alternatif
WO2010069027A1 (fr) * 2008-12-19 2010-06-24 Claudio Barberato Moteur thermique a trois temps, cycle et composants associes
US8215280B2 (en) 2008-02-28 2012-07-10 Df Reserve, Lc Power linkage assembly for a high efficiency internal explosion engine
US20140261347A1 (en) * 2013-03-15 2014-09-18 Mcalister Technologies, Llc Internal combustion engine and associated systems and methods
WO2015056015A1 (fr) * 2013-10-17 2015-04-23 Cox Powertrain Ltd Moteurs à combustion interne
EP3128127A4 (fr) * 2014-04-04 2017-10-04 Z Mechanism Technology Institute Co. Ltd. Expanseur et appareil de congélation d'air équipé de celui-ci
WO2021006855A1 (fr) * 2019-07-05 2021-01-14 ГАЛЕЦКИЙ, Анатолий Юрьевич Moteur avec mécanisme de manivelle-coulisseau
WO2021151207A1 (fr) * 2020-01-31 2021-08-05 Intelline Inc. Moteurs à combustion linéaire dotés de soupape à l'intérieur de piston

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FR2921694A1 (fr) * 2007-10-02 2009-04-03 Jean Claude Keromnes Moteur thermique alternatif
US8215280B2 (en) 2008-02-28 2012-07-10 Df Reserve, Lc Power linkage assembly for a high efficiency internal explosion engine
US8857404B2 (en) 2008-02-28 2014-10-14 Douglas K. Furr High efficiency internal explosion engine
WO2010069027A1 (fr) * 2008-12-19 2010-06-24 Claudio Barberato Moteur thermique a trois temps, cycle et composants associes
US8215268B2 (en) 2008-12-19 2012-07-10 Claudio Barberato Three-stroke internal combustion engine, cycle and components
US9091204B2 (en) * 2013-03-15 2015-07-28 Mcalister Technologies, Llc Internal combustion engine having piston with piston valve and associated method
US20140261347A1 (en) * 2013-03-15 2014-09-18 Mcalister Technologies, Llc Internal combustion engine and associated systems and methods
WO2015056015A1 (fr) * 2013-10-17 2015-04-23 Cox Powertrain Ltd Moteurs à combustion interne
US9874141B2 (en) 2013-10-17 2018-01-23 Cox Powertrain Ltd Internal combustion engines
EP3128127A4 (fr) * 2014-04-04 2017-10-04 Z Mechanism Technology Institute Co. Ltd. Expanseur et appareil de congélation d'air équipé de celui-ci
US10400599B2 (en) 2014-04-04 2019-09-03 Z Mechanism Technology Institute Co., Ltd. Expander and air refrigeration device with the same
WO2021006855A1 (fr) * 2019-07-05 2021-01-14 ГАЛЕЦКИЙ, Анатолий Юрьевич Moteur avec mécanisme de manivelle-coulisseau
WO2021151207A1 (fr) * 2020-01-31 2021-08-05 Intelline Inc. Moteurs à combustion linéaire dotés de soupape à l'intérieur de piston
US11692478B2 (en) 2020-01-31 2023-07-04 Intelline Inc. Linear combustion engines with valve in piston

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