A MECHANISM

Abstract: A mechanism comprising a chamber (7) defined by a spherical or part spherical internal surface, and a disk member (9) rotatable ina fixed plane diametral to the said internal surface and in sealing relation therewith, at least one vane (14) rotatable about an axis diametral to the said internal surface and said axis being inclined to said fixed plane, the disk member and the vane dividing the chamber into a plurality of working chambers (20) 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.

Description: A MECHANISM 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. 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. SUMMARY OF INVENTION 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. Preferably, 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. 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. If however, 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. If a complete chamber is to be used in the two working chamber configuration, 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 . With appropriate porting and or valving and where appropriate ignition the mechanism has the abovementioned technical applications. Before describing specific constructions for particular application and to obtain an understanding of the essential action of the engine. Reference is made to Figure 1 and the discussion below. For explanation purposes only a spherical closed chamber is assumed, however part spherical 10 constructions of the engine maintain the same relationships. 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. An understanding of this action is based upon the resolution of a right spherical triangle and associated trihedral at each point of revolution of the vane/disk 20 assembly. 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 ς With reference to Figure 1 the three diametral planes are:- 1. An imaginary plane (2) diametral to the said closed chamber (1) . 2. The plane of the diametral vane (3) having a 30 diametral axis (6) perpendicular to the imaginary plane (2). 3. The plane of the diametral disk (4) which rotates on its major axis (5) which is inclined to the diametral axis of the vane member (6). 35 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). 10 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. ,c 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. 20 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. 25 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 30 chamber having a volume of (V/360) (180-B) and a swept volume of (V/360)2A per chamber. (V = sphere volume). 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 tendency of these forces is to cause the vane and disk to diverge. The vane and disk however are unable to diverge unless the assembly revolves within the sphere. 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. When the chamber is balanced this point coincides with the vane axis and trihedral face angle D - 0 and no torque is manifest. At any point where angle D is not equal to zero then the moment of the vane is manifest as torque at the vane axis. 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). It should be noted that there is no tendency of the disk to rotate about its own axis in either direction and rotation of the disk totally results from its meshing with the vane. With the action of the engine established it can be seen that for the purpose of comparison the following relationships exist between this and a conventional engine. 1. The change in the value of Angle B relates to the sweep of a conventional piston. 2. Vane moment relates to piston force. 3. Sine D relates to effective moment arm of a conventional crank insofar as torque ■ (vane moment * Sine D) and in the case of a conventional engine torque = (piston force * effective moment). 4. 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. It will be seen therefore that with rotation the entire mechanism remains at all times mass balanced in respect of all axes however with rotation the mass of any one chamber becomes cyclically imbalanced in respect of the vane axis and therefore has a moment about the vane axis. This of course is always balanced by the opposite moment of the adjacent chamber. However if one increases the apparent (but not actual) mass of any one chamber by applying a pressure to the walls of the chamber it is no longer balanced by the actual mass of its adjacent chamber and the moment of the apparent mass is manifest as torque at the vane axis. 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. In an alternative form 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. In yet a further alternative form if the vane and disk member are held stationary, the moment of the disk member manifests itself as reactive torque which is transferred to the chamber causing the chamber itself to rotate. Drive may be applied to or obtained from means meshing with the chamber (this further alternative form might find application, when the chamber is given on its outside surface, propeller blades and an aerofoil shape, as an aircraft engine). Preferably 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. Alternatively, or in association with such a flexible membrane, 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 10 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. Preferably, 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 20 core which reduces the effective volume of the engine. A general statement is that swept volume becomes ((sphere volume - core volume)/360)*2A per chamber (A- Angle A). A further effect of thickness is that the effective disk member and vane area is reduced in that these areas 25 become segments having a height equivalent to the sphere radius less the core radius. In one preferred construction the core sealing means is provided in the form of a bar of circular section which is diametrally incorporated into the disk member such 30 that it is free to rotate on its longitudinal axis and forms a sealing relationship with the disk member. The bar is slotted such that the vane may pass through the bar and form a sealing relationship therewith. In this instance the core radius and volume is constant. 35 In another preferred construction there is provided 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. In this instance 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. In another preferred construction there is provided 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. In another preferred construction there is provided a linear seal as described above except that the seal has near parabolic section and the vane faces remain flat. In this instance the core radius and volume varies as described above. In yet other constructions 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. With suitable porting and or valving and where appropriate ignition, 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. In addition 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. In one preferred method 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. In another preferred embodiment recesses may be provided in the internal walls of the chamber to permit communication between variable volume working chambers during operation. In another preferred method 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. in another preferred method 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. in another preferred method 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. The above valving and porting possibilities are given as non limiting examples and one skilled in the art will realise that many variations of porting and valving are applicable without departing from the essence of the invention. It will be observed that setting the angle between the vane axis and the disk member axis at 45 degrees gives a swept volume equivalent to the chamber volume minus the core volume. This angle may be further increased to the extent that the extra swept volume exceeds both the core volume and the volume of the chamber walls thus achieving an engine with a greater displacement than its physical volume. Preferred embodiments of the mechanism will be further described with reference to the figures as follows. Figure 1 Geometry of mechanism Figure 2 Cross Sectional View of an engine embodiment. A PRACTICAL PUMP/COMPRESSOR Referring to Fig. 2 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. With this construction if it were desired to obtain high compression ratios the faces of the disk member are set at an angle to the plane of the disk member up to a maximum where at the point of closest convergence the face of the disk member and the face of the vane are parallel (as shown) and have the minimum mechanical clearance required to permit free operation. A virtual infinite compression ratio is thereby achievable. A PRACTICAL COMPRESSED AIR/HYDRAULIC ENGINE Construction and porting is identical to that described above in relation to the pump/compressor and the only difference being the method of operation. Pressurized air or fluid is introduced into the engine through the inlet ports creating a pressure within the expanding chamber thereby causing the engine to motor. The exhaust ports maintain the same operation and the spent air or fluid is exhausted through the outlet ports as with the pump/compressor. A PRACTICAL DAMPER/ROTARY SPEED LIMITING DEVICE 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. In this application it is possible to have merely holes in the vane or disk member face communicating the working chambers so that the fluid flows backwards and forwards between adjacent working chambers or alternatively one way valves permitting a one way flow only between adjacent working chambers in which case a flow could be established in either direction around the core. This application and construction also permits the use of 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. A PRACTICAL INTERNAL COMBUSTION ENGINE 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. In this instance 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. There is also provided a reed or similar one way valve in 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. The combination of 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. For the purpose of description only values and further relationships are established as follows. These values are set in a non limiting manner and those skilled in the art will appreciate that all values may be altered within the terms of the relationships established. Closed Chamber Radius = 10 CM Disk Angle - 30 Degrees (Angle A) Core Radius = 2.2 CM Swept Volume - 2592 CC Swept Volume (Per Chamber)* 648 CC Angle Between Disk Faces * 120 Degrees Method of Operation:- 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. 1. Induct the fuel air mixture through the intake port. 2. Compress the mixture through the reed valve situated in the disk member face into the constant chamber. 3. Totally expell all gases in the expansion chamber through the exhaust port by having the unswept volume as near as practicable to zero. 4. Cease exhaust phase. 5. By means of the before entioned core ports transfer part of the compressed mixture being held in the constant volume chamber into the expansion chamber as the volume of the expansion chamber begins to increase. 6. Close core ports. 7. Ignite mixture. 8. Expand the products of combustion to a ratio of approximately 1:19. 9. Open exhaust ports at 155 degrees of rotation. 10. Return phase 1. Notes regarding the above cycle:- 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. For the purpose of this exercise it will be assumed that the cohstant volume chambers have a volume equivalent to the swept volume of the variable volume chambers which is 648 cc. Transfer of the mixture from the constant chamber to the expansion chamber takes place during the first three degrees of expansion (increase of angle B) of the expansion chamber. This would occur during 24.5 degrees of revolution of the vane/disk member assembly. During this period 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. As combustion proceeds angle D and therefore moment continues to increase so that the cycles highest pressures are present during the period of maximum mechanical efficiency. At ignition sweep (Angle B) has only completed 3.05 degrees or 5% of expansion but rapidly increases from this point. Expansion takes place during the following 130 degrees of vane/disk member rotation during which time the expansion chamber expands through a further 54 degrees (Angle B) to a total of 57 degrees of expansion. This then gives an expansion ratio of 1:19 before exhaust begins. Exhaust continues for the next 205 degrees of vane disk revolution during which time the exhaust gases are as near as practicable totally expelled. Once working pressures have been achieved it will be observed that irrespective of constant chamber volume the effective compression ratio is the ratio between the swept _ ζ 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 above practical examples are given by way of non limiting example and it will be seen by those skilled in the art that a variety of porting and valving arrangements and internal combustion engine cycles may be applied to the engine without departing from the scope of the invention. VARIABLE DISPLACEMENT, COMPRESSION/EXPANSION:- It is possible to vary the displacement, compression/expansion ratios of the engine during operation by providing means which alter the angle between the vane axis and the disk member axis. 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.

Claims: THE CLAIMS DEFINING THE INVENTION ARE AS FOLLOWS: 1. 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 axis diametral to the said internal surface and said axis being inclined to said fixed plane, the disk member and vane 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. 2. A mechanism as claimed in claim 1 wherein the shape of the vane and the chamber are adapted to co-operate with the disk member to provide a predetermined number of working chambers. 3. A mechanism as claimed in any one of Claims 1 or 2 wherein working chambers are provided on both sides of the fixed plane of the disk member. 4. A mechanism as claimed in any one of the preceding claims wherein the vane and/or disk member have shapes and/or relative inclination adapted to provide a predetermined volume and compression of the working chambers. 5. A mechanism as claimed in any one of the preceding claims wherein there is provided at the intersection of the vane with the disk member seal means, said seal means including a rotatable core. 6. A mechanism as claimed in any one of the preceding claims wherein drive means operably co-operate with the vane and/or the disk member to effect rotation thereof or be rotated thereby. 7. A mechanism as claimed in any one of the preceding claims wherein the mechanism is used as an engine having inlet and outlet ports located so that the ports selectively communicate with one or more working chambers to regulate the flow of working fluid to and from the working chambers. 8. A mechanism as claimed in claim 6 for use as an internal combustion engine having inlet and outlet ports located either side of the disk member and ignition means located in the closed chamber to communicate with each working chamber as it increases in volume. 9. A mechanism as claimed in any one of claims 1 to 6 for use as an engine, motor, pump, compressor or speed limiting device. 8:8-cp

Inventors: THOMPSON GLENN ALEXANDER, THOMPSON, GLENN, ALEXANDER
Applicants: THOMPSON GLENN ALEXANDER, THOMPSON, GLENN, ALEXANDER
Application year: 1987
Main classification: F02B53
IPC codes: F01C3, F02B53, F02B75, F04C3