Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
  • F01C3/06—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
• • 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
  • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
  • F02B53/02—Methods of operating
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B75/00—Other engines
  • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
  • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
  • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/12—Improving ICE efficiencies

Definitions

• the present invention relates to a mechanism, and in particular a mechanism capable of being used as an engine, a motor, a pump and/or a speedlimiting device (dampers).
• the present invention utilizes a specific action or motion to relate to variable volume engines which operate on a working fluid or gas such as compressors, pumps, expanders, steam engines, compressed air engines, hydraulic engines, internal combustion engines and dampers.
• a working fluid or gas such as compressors, pumps, expanders, steam engines, compressed air engines, hydraulic engines, internal combustion engines and dampers.
• Variable volume engines are generally complex mechanical devices which generally fall into several broad classes namely reciprocating piston engines, trochoidal engines, rotary engines, slant axis or Z shaft engines, and numerous other designs involving various excentric or otherwise convoluted motions, all these engines remain complex in manufacture and assembly, large in proportion to displacement and are subject to large dynamic stresses due to the excentric or otherwise convoluted actions of their various moving parts. Additionally those engines which fall into the loosely defined rotary classes generally have a compression and expansion ratio which is limited by the various geometries employed. Additionally the displacement of these engines are generally fixed as are the compression and expansion ratios.
• the present invention is intended to overcome the above problems by providing in a preferred embodiment a variable volume engine which employs two major moving parts of simple shape which cooperate in a pure rotary action which remains mass balanced in respect of all axes of rotation and which according to configuration may have a compression/expansion ratio limited only by mechanical tolerances. Additionally in certain configurations the engine allows for variable displacement and variable compression/expansion ratios. Additionally in certain configurations the engine allows for a total displacement which is greater than the physical size of the engine.
• the present invention is a mechanism comprising a chamber defined by a spherical or part spherical internal surface, and a disk member rotatable in a fixed plane diametral to the said internal surface and in sealing relation therewith, at least one vane rotatable about an diametral axis to the said internal surface and said axis being inclined to said fixed plane, the disk member and plane dividing the chamber into a plurality of working chambers which vary in volume as the vane and disk member rotate, the vane being in sealing relation to the internal surface and the disk member throughout the rotary movement.
• the chamber has a part spherical internal surface so that a preferably flat surface or surfaces can be incorporated for valve ports etc. or as a base.
• a preferably flat surface or surfaces can be incorporated for valve ports etc. or as a base.
• Any spherical section centered upon the axis of rotation of the vane which does not intersect the plane of the disk member can be used as a flat plane to modify the internal shape of the spherical chamber without affecting the mechanical motion of the engine. Should such flat internal surfaces be required the said vane is appropriately modified in its shape to maintain the necessary sealing relation.
• the number of working chambers depends on the shape of the vane and the chamber. If the vane has a shape that protrudes through the disk member at a line of intersection, four working chambers will be created.
• the vane has a shape that meets the disk member at the line of intersection and does not protrude beyond the plane of the disk member beyond the extent necessary to maintain a sealing relationship with the disk member during one entire rotation, two working chambers will be created.
• the hemisphere not used as working chambers can be utilized as a holding, process or transfer chamber for the working fluids or gases of the _ _ engine .
• the rotatable vane(s) and rotatable disk rotate on separate intersecting axes which are inclined to each other. Rotation of this configuration causes each of the chambers created by the assembly to vary in volume as each point on ⁇ c the disk cyclically converges on and diverges from the vane axis.
• the right spherical triangle in question is defined by the intersection of three planes diametral to the spherical or part spherical chamber and which for the purpose of initial discussion here shall have no thickness. 2 ⁇ With reference to Figure 1 the three diametral planes are:-
• This configuration defines four separate variable volume chambers within the said closed chamber. Zero degrees of rotation is considered to be the point at which the circumferences of the three planes intersect at one point and at which time two of the four chambers have minimum volume values and the other two have maximum volume values. At this point no spherical triangle is present.
• Rotation of the vane/disk assembly gives the spherical triangle A, B, C, and trihedral with face angles D, 0, Z, (Fig. 1).
• Spherical triangle sides AD, AO, AZ are the intercepted arcs of trihedral face angles D, O, Z, respectively.
• Angle O is the angle of rotation of the vane disk assembly.
• Angle D is the angle between the line of intersection of the vane/disk and line of intersection of the vane/imaginary plane.
• Angle A is the set angle between the imaginary plane and the plane of the disk and is constant.
• Angle C is the angle between the imaginary plane and the plane of the vane and is a constant right angle.
• Angle B is the angle between the plane of the vane and the plane of the disk and varies with rotation of the vane disk assembly.
• Resolving angle B (Cos B « Cos 0 Sin A) enables a calculation of the volume of each chamber for each value of 0.
• the chamber within which B falls and its opposite chamber each have a volume of (V/360)B with each adjacent
• Resolving angle D (COS D » COS A/SIN B) enables a calculation of the moment of each chamber about the vane axis for each value of 0, (as discussed below). ,.,- It will be seen that a pressure within any one chamber will cause both the vane and the disk to have an equal but opposite moment about the line of intersection of the vane and disk.
• the moment vector of the vane originates at the point which bisects the arc of the segment of the vane within the chamber in question.
• the angle of arc of the vane segment between this point and the axis of the vane is equal to trihedral face angle D.
• the torque at the vane axis is (vane moment * Sin D).
• the moment of the disk is transferred to the sphere casing and imparts on the casing a moment about the vane axis which is manifest as reactive torque.
• the reactive torque is (Disk moment * Sin D).
• the change in the value of Angle B relates to the sweep of a conventional piston.
• Vane moment relates to piston force.
• a cycle or stroke of the present engine can be described as being 180 degrees of revolution of the vane/disk member assembly relative to the chamber beginning with the point at which a working chamber has its maximum volume value and ending where the same working chamber has its minimum volume value.
• the vane may be coupled to a drive shaft co-axial with the axis of rotation, and preferably the axis of the vane is so utilized, in this preferred form, the drive shaft fixedly locates the vane within the closed chamber.
• the perimeter of the disk member can with gearing act as the drive. If the chamber is maintained stationary, both the vane and the disk member respectively can be coupled to drive means to obtain or apply drive.
• the disk member is retained in a fixed plane with respect to the internal surface by being located within a circumferential groove along the internal surface.
• the line of intersection where the vane meets or protrudes through the disk member can incorporate a flexible membrane to maintain a sealing relation between the vane and disk member during the motion of the engine.
• the disk' member can incorporate a core along the line of intersection, said core preferably having a smooth and cylindrical or part cylindrical outer surface so that the
• vane can be slideably attached to the core and the relative motion of the disk member with respect to the vane is maintained about this said core.
• the ratio of change of volume is fixed by the angle at which the plane of the disk member is set in relation to m m. the axis of rotation of the vane.
• the change in volume can be further enhanced by shaping the disk member or vanes.
• the disk member has flaring outwards from the line of intersection with the vane.
• Sealing means can take several forms as outlined below. In all constructions these sealing means define a
• the core sealing means is provided in the form of a bar of circular section which is diametrally incorporated into the disk member such
• the bar is slotted such that the vane may pass through the bar and form a sealing relationship therewith.
• the core radius and volume is constant.
• a linear seal interposed between the vane and a slot in the disk member to receive the vane.
• This linear seal is mounted in a groove in the disk slot and held against the vane face by spring means.
• the core radius and volume is not constant and varies between a minimum when the disk member plane is perpendicular to the vane plane and a maximum when the plane of the disk member is at its maximum slant to the plane of the vane.
• a linear seal as described above except that the seal maintains a constant relationship to the disk member and a sinuous groove is provided in the face of the vane to accommodate the change in angle between the planes of the vane and disk member. In this instance the core radius and volume remains constant.
• seals of a compressible and or flexible nature there is provided seals of a compressible and or flexible nature and one skilled in the art will appreciate that a variety of sealing means may be applied without departing from the essence of the invention.
• Valving and or porting may be achieved by suitable application of ports or any of a variety of well known valves and may be actuated by the rotary action of the various parts or alternatively or in conjunction with the actuation means which is peculiar to this particular mechanism and in particular the sliding action and change in angle between the plane of the disk member and the faces of the vanes or the cyclic convergence and divergence previously described.
• the engine may be utilized as a pump or a compressed air motor or pressurized fluid motor or steam engine or two or four stroke/cycle internal combustion engine or if sealed and containing a suitable fluid or gas and having suitable ports or valves interconnecting the various chambers could act as a rotary speed limiting device or damper.
• the engine may act as a combination motor and pump by having its chambers apportioned between tasks.
• Actuating mechanism for the porting and/or valving and where appropriate ignition may be mounted so as to permit adjustment of timing during operation or to permit the engine to be operated in either direction of revolution or to permit selective redundancy of a portion of the chambers.
• ports may be provided to allow for the ingress and egress of working fluids by providing an opening in the chamber such that it communicates with a variable working chamber during either an entire expansion or compression stroke or any portion thereof. These ports may be bridged or incorporate other related port technology.
• recesses may be provided in the internal walls of the chamber to permit communication between variable volume working chambers during operation.
• rotary valves may be incorporated in and form part of the mounting means or shaft of the vane and be actuated by the revolution thereof.
• ports may be provided in and form part of the mounting means or shaft of the vane or flarings therefrom in conjunction with a further member rotating at half vane speed and incorporating slots or holes which communicate with the ports to facilitate port timing applicable to four stroke/cycle internal combustion engines.
• reed or other one way valves may be provided to permit the ingress or egress of working fluids or be provided such that they communicate with variable volume working chambers through either the disk member or vane to permit transfer of working fluids between working chambers.
• one preferred construction incorporates a spherical chamber 7 with a diametral groove 8 into which is located the perimeter 9a of a rotatable disk member 9 supported within the said groove 8 on bearings 10 and having compression seals 11 and oil seals 12 and core member 13 diametrally located within the disk member on bearings and said core member slotted in such a manner as to permit the vane 14 to pass through the plane of the disk member and linear seals 15 slotted into the core member to seal against the vane face and seals 16 slotted into the disk member 9 to seal against the core member and shafts 17 integral with the vane passing through the walls of the spherical chamber and supported by bearings 18 such that the axis of the shafts and thus the vane is set at an angle to the major axis of the disk.
• the vane has perimeter or circumferential seals 19 sealing against the chamber walls.
• This assembly forms four working chambers 20 which vary in volume as the vane/disk member assembly rotates in relation to the spherical chamber.
• Four ports 21 are provided for the ingress and egress of working fluids. Two of these are inlet and two outlet. The ports are located in such a manner that one inlet and one outlet port is situated on either side of the plane of the disk member and the inlet ports communicate with each working chamber as it expands in volume and the outlet ports communicate with each working chamber as it decreases in volume. Inlet and outlet ports being situated approximately 180 degrees from each other about the vane axis.
• Construction is identical to that described above in relation to the pump/compressor except that the inlet and outlet ports are omitted which results in a completely sealed unit.
• the unit is completely filled with fluid and a variety of valving and bleeding ports (such as reed valves) are provided to communicate the working chambers in order that the fluid may pass through at rates proportionate to the combination of fluid viscosity, valve or port sizes and torque applied to the vane/disk member assembly.
• valving and bleeding ports such as reed valves
• valves between working chambers which are held open by spring or other means against the pressure of the flow of the fluid until such time as the torque applied to the device creates such a pressure that the valves are forced to close which would effectively lock the mechanism.
• the valves could also be designed to close at a certain shaft speed and or gradually close as shaft speed and or torque/fluid pressure increases in which case the effort applied to the vane/disk member assembly would be transferred to the chamber housing and therefore be available at the housing for ongoing transmission once the preset shaft speed and or torque levels had been achieved.
• Construction is identical to that provided above in relation to the pump/compressor except that on one side of the plane of the disk only the inlet port is provided and on the other side of the plane of the disk only the exhaust or outlet port is provided.
• the inlet port communicates with a carburettor, the outlet port communicates with an exhaust conduit.
• Ignition point 22 for a spark plug or the like is positioned to ignite fuel in timed relation with rotation of assembly. Ignition points can be placed in alternative, equivalent positions (not shown).
• the faces of the disk are set so that maximum compression/ expansion ratios are achieved as described above.
• the volume between the faces of the disk is utilized to form two constant volume chambers.
• This construction provides therefore four variable volume chambers and two constant volume chambers. Two of the variable volume chambers on the one side of the disk member plane are utilized as intake/compression chambers and the remaining two variable volume chambers are utilized as expansion chambers.
• each of the two disk member faces between the intake compression chambers and constant chambers and also a port in the core which communicates each constant volume chamber with its adjacent vane face and also recesses in the vane faces which communicates each port in the core with its adjacent expansion chamber.
• This core port and vane face recess permits each constant volume chamber to communicate with its adjacent expansion chamber once in every complete revolution and also permits the timing of this communication to be set to begin and end at any point of the revolution.
• the spark plug provided 22 is fixed into the spherical chamber wall and positioned such that it communicates with the expansion chamber at the required point. There is also provided appropriate spark timing mechanism, lubrication means and other means are also provided all of which are known.
• This explanation follows the operation of one set of working chambers including one constant chamber and its adjacent intake/compression chamber and adjacent expansion chamber.
• Rotation is calculated from the point at which the expansion chamber under discussion has its minimum volume value and no spherical triangle as previously defined is present.
• the disk member faces in this example are set at 60 degrees from the plane of the disk member. The two faces therefore are 120 degrees apart.
• the cohstant volume chambers have a volume equivalent to the swept volume of the variable volume chambers which is 648 cc.
• the compressed mixture in the constant chamber expands into the expansion chamber at a ratio of 20:21 which reflects the ratio between the volume transferred (transfer volume) and the volume of the constant volume chamber.
• Ignition occurs at 25 degrees of vane/disk member revolution at which point angle D is approximately 13.5 degrees or 45% of its maximum 30 degrees. As the moment of a chamber about the vane axis increases with the sine of angle D the moment has reached 46.68% of its maximum at this time.
• the effective compression ratio is the ratio between the swept _ ⁇ volume of the intak-e compression chamber and the total of the unswept volume of the intake/compression chamber and the transfer volume of the expansion chamber.
• Another configuration of an internal combustion engine embodies identical construction except that constant volume chambers are not utilised and therefore the core porting arrangement is also not utilised.
• the compressed mixture is instead compressed into a separate holding tank and introduced via rotary valves actuated by the vane shaft revolution into the expansion chamber.
• the angle between the vane axis and the disk member axis may be altered by adjusting either the vane axis or the disk member axis or both. Any adjustment however must maintain both axis diametral to the spherical or part spherical chamber and also maintain the vane and disk member in diametral relationship to the chamber.
• Means of providing this adjustment on the vane axis may be provided by the vane shaft bearing being situate itself within an excentrically adjustable mounting or slide mounting such that adjustment of both vane shaft mountings maintains the diametral relationship of the vane axis.
• Means of providing adjustment to the axis of the disk member are provided by having the perimeter of the disk member in sealing relation with the spherical or part spherical chamber and located in that position by adjustable means in which case the disk member is not located within a fixed groove in the sphere walls.
• This configuration is _ particularly applicable to hemispherical applications of the engine or spherical applications where only one hemisphere has working chambers.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Rotary Pumps (AREA)

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• 1987
  • 1987-01-28 AU AU68943/87A patent/AU6894387A/en not_active Abandoned
  • 1987-01-28 JP JP62500905A patent/JPS63502444A/ja active Pending
  • 1987-01-28 WO PCT/AU1987/000021 patent/WO1987004495A1/en not_active Application Discontinuation
  • 1987-01-28 EP EP87900789A patent/EP0257043A1/de not_active Withdrawn
  • 1987-09-28 KR KR1019870700876A patent/KR880700890A/ko not_active Application Discontinuation

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