AU5188501A - A fluid, electric and magnetic machine - Google Patents

Description

APLICANTS:

NUMBER:

FILED:

JOSEPH KARL BOUDEWYNS JOHN WHITFORD-SMITH.

AUSTRALIA

THE PATENTS ACT 1990 PROVISIONAL SPECIFICATION FOR THE INVENTION ENTITLED A FLUID, ELECTRIC AND MAGNETIC MACHINE" The invention is described in the following statement: '.00 0 06 00 a 0 *0

TITLE

S-

A Fluid and Electric Machine The present invention relates to a fluid or electric machine having a plurality of piston and cylinder assemblies positioned radially around, and rotatable about, an axis of rotation.

Rotary radial piston engines were well known in the early part of this century and were commonly used as aeronautical engines. The use of rotary radial piston engines later declined, and ultimately disappeared from aviation, as competitive stationary engines became available.

With rotary radial piston engines, it was common to deliver a combustible mixture of fuel and air to the combustion chambers by drawing the mixture through a long hollow crankshaft to the crankcase, which was used as a distribution chamber, from where the mixture was fed through individual radial manifolds to each cylinder. This 15 arrangement had the disadvantage of providing a long passageway for delivery of the combustible mixture of fuel and air, which was deleterious to performance of the engine.

The present invention seeks to provide a machine which overcomes, or at least reduces, the disadvantage outlined above in relation to previously known rotary radial engines.

In accordance with a first aspect of the present invention, there is provided a fluid machine comprising: a rotor mounted for rotation about a first axis; eoe.

a plurality of piston and cylinder assemblies provided in the rotor radially about the first axis; each piston and cylinder assembly comprising a cylinder in the rotor and a piston mounted for reciprocation in the cylinder; each piston and cylinder assembly defining a working space which varies in volume with reciprocation of the piston in the cylinder; fluid intake means for admitting fluid to the working spaces and fluid exhaust means for discharging fluid from the working spaces; the fluid intake means comprising an intake chamber within the rotor for receiving fluid, and an intake control means within the rotor for allowing controlled communication between the intake chamber and each working chamber in timed Ssequence with reciprocation of the piston in the cylinder.

Because the intake chamber and the intake control means are within the rotor, improved efficiencies may be achieved in delivery of the fluid from the intake chamber to the respective cylinders in comparison to the prior art arrangements described above.

15 The intake chamber preferably extends around the first axis and is displaced axially o•••o along that axis from the piston and cylinder assemblies.

In one arrangement, the control means may comprise an intake duct extending •OO.oi between the intake chamber and each cylinder, and a valve means defining an intake port, the rotor being rotatable relative to the valve means with the intake chamber in communication with the intake port, the intake duct of each cylinder registering with the intake port in timed sequence with reciprocation of the piston in the cylinder for delivery of fluid into the working chamber.

4 With this arrangement, fluid in the intake chamber can enter each working chamleri.

during the intake stroke of the piston when the intake duct of the cylinder registers with the intake port.

The valve means may comprise a disc valve which is stationary with respect to the rotor. The intake port may comprise an arcuate slot in the disc valve.

The fluid may be delivered to the intake chamber through a stationary central stator about which the rotor is rotatable.

The stationary central stator may have a delivery passage with an inlet section for relieving a supply of the fluid and an outlet section which communicates with the io intake chamber and about which the intake chamber rotates with the rotor. The outlet section of the delivery passage may include one or more outlet ports opening onto the intake chamber.

The fluid exhaust means may comprise an exhaust chamber which is stationary and exhaust control means for allowing controlled communication between each cylinder 15 and the exhaust chamber.

The exhaust control means may comprise an exhaust duct opening at one end onto each cylinder, each exhaust duct being open and closed at the other end to communication with the exhaust chamber by valve means in timed sequence with reciprocation of the piston in the cylinder.

go ooo 2o The valve means may comprise an exhaust port which is stationary and with which the exhaust ducts register in timed sequence with reciprocation of the pistons in the cylinder.

The exhaust chamber preferably extends around the first axis and is displaced axially from the rotor along that axis.

Preferably, the exhaust chamber is on the opposed side of the piston and cyline.

assemblies to the intake chamber.

This fluid machine preferably further comprises a stationary housing in which the rotor is rotatably supported.

The exhaust chamber is conveniently located in the stationary housing.

The rotor may be accommodated in a cavity within the housing, there being a spacing defined between the rotor and at least part of the perimeter of the cavity, the spacing being occupied by a fluid such as oil. The fluid provides lubrication and may assist in cooling. The fluid may be circulated between the cavity and a heat exchanger to assist Io in dissipation of heat.

The fluid may also occupy the region in the rotor radially inwardly of the cylinders.

Preferably, the fluid machine further includes a shaft drivingly connected to the rotor.

The shaft may be rotatably supported in the stationary housing.

Preferably, the fluid machine still further includes a control shaft mounted for rotation about a second axis parallel to and offset from the first axis.

The control shaft may be rotatably supported in said stationary central stator about which the rotor is rotatable.

A connecting means (such as a connecting rod) preferably connects each piston to the control shaft, the connecting means associated with one of the pistons being pivotally 20 connected to the piston and being fixedly connected to the control shaft for rotation therewith about the second axis, and the connecting means associated with the or each other piston being pivotally connected to the piston and pivotally connected to the control shaft about said second axis.

The fixed connection between the connecting means of said one of the pistons and th control shaft causes rotation of the control shaft with the rotor. The other connecting means can move angularly back and forth about the second axis on rotation of their respective piston and cylinder assemblies with the rotor about the first axis.

The offset between the first and second axes causes rotation of the rotor about the first axis upon reciprocation of the pistons in the cylinders, as would occur where the machine is an internal combustion engine, fluid (hydraulic) motor or electric motor.

Similarly, the offset causes reciprocation of the pistons in the cylinders upon rotation of the rotor, as would occur where the machine is a fluid pump, compressor or generator.

The machine according to the invention has been devised particularly as an internal combustion engine in which case the working chambers comprise combustion chambers, and the fluid admitted thereto comprises a combustible mixture of fuel and "air, or at least air.

Preferably, the internal combustion engine operates on a two-stroke principle.

In accordance with a second aspect of the present invention, there is provided a fluid or electric machine comprising: a rotor mounted for rotation about a first axis; a plurality of piston and cylinder assemblies in the rotor radially about the first axis; 20 each piston and cylinder assembly comprising a cylinder in the rotor and a piston mounted for reciprocation in the cylinder; an output shaft drivingly connected to the rotor; a control shaft mounted for rotation about a second axis parallel to and offset from the first axis; a connecting means (such as a connecting rod) connecting each piston to the suppoq shaft, the connecting means associated with one piston being pivotally connected to the piston and being fixedly connected to the control shaft for rotation therewith about the second axis, and the connecting means associated with the or each other piston being pivotally connected to the piston and being pivotally connected to the control shaft about said second axis; wherein the offset between the first and second axes causes rotation of the rotor about tile first axis upon reciprocation of the pistons in the cylinders, the fixed connection between one of the connecting means and the control shaft causing rotation of the control shaft with the rotor.

The invention also provides a machine comprising a housing defining a cavity, and a rotor accommodated in the cavity, there being a spacing defined between the rotor and at least part of the perimeter of the cavity, the spacing being occupied by a lubricating fluid.

In accordance with a third aspect of the present invention, there is provided an electric machine comprising; a rotor mounted for rotation about a first axis; a pl_._ality of piston and cylinder assemblies; ••co each piston and cylinder assembly comprising a cylinder including a coil and a piston, 2o each piston being magnetised such that providing current to the coils generates magnetic fields within the cylinders which interact with the pistons causing reciprocation of the pistons within the cylinders.

The invention will now be described by way of example, with reference to the accompanying drawings in which: 8 Figure 1 is a front cross-sectional view of an internal combustion engine in accordance with the first and second aspects of the present invention; Figure 2 is a side sectional view of the internal combustion engine of Figure 1; Figure 3 is a front view showing the connection arrangement between the inner end of connecting rods and a control shaft of the engine of Figure 1; Figure 4 is a side cross-sectional view of the first connecting rod of Figure 3; Figure 5 is a side view of the second connecting rod of Figure 3; Figure 6 is a side view of the control shaft of the internal combustion engine of Figure io Figure 7 is an end view of the control shaft of Figure 6; Figure 8 is a side cross-sectional view of a connecting rod securing collar; Figure 9 is a front view of the securing collar of Figure 8; Figure 10 is a view similar to Figure 1 with the exception that an intake port arrangement is shown for induction of a combustible mixture into the combustion chambers; Figure 11 is a side view of an inlet disc valve for the engine of Figure 1; Figure 12 is a front view of an exhaust disc valve for the engine of Figure 1; oo" FiguFe 13 is a side cross-sectional view of an engine with an alternate arrangement of a control shaft; Figure 14 is a front cross sectional view of an electric machine in accordance with the third aspect of the present invention; and Figure 15 is a side sectional view of the electric machine of Figure 14.

The internal combustion engine shown in Figures 1 to 14 is one operating on a twostroke principle.

Referring to Figures 1 to 14 of the drawings, there is shown an internal combustion engine comprising a stationary housing 11 having a cylindrical side wall 13, and first and second end walls 15 and 17 between which the cylindrical side wall 13 is positioned. Each end wall 15, 17 is detachably mounted onto the cylindrical side wall 13 by removable fastening means 19 such as machine screws.

A cavity 21 is provided in the stationary housing 11. The cavity 21 includes a cylindrical side wall surface 23.

The housing 11 incorporates an inlet duct and an outlet duct, for circulation of a lubricating fluid through the cavity 21, as will be explained in more detail later.

1t A stationary central stator 31 is mounted on the first end wall 15 of the housing and extends into the cavity 21, terminating at an end face 33.

A rotor 40 is rotatably supported within the cavity 21 of the housing 11 for rotation about a first axis 41. The rotor 40 has a section thereof rotatably supported on the stationary central stator 31 by way of a bearing 43. The rotor 40 is also supported on 15 the inner end of a drive shaft 45 which is rotatably supported on the second end wall 17 of the stationary housing 11 by way of a bearing 47. The drive shaft 45 has a mounting flange 49 which is secured to an end face 51 of the rotor 40 by way of fastening means 53 in the form of machine screws. The drive shaft 45 extends beyond the stationary housing 11 and supports a fly wheel 55 in conventional manner.

20 A control shaft 61 is rotatably supported within a passage 63 extending axially through the stationary central stator 31. The control shaft 61 is rotatably supported on bearings 65 housed in the axial passage 63. The control shaft 61 is rotatable about a second axis 62 which is parallel to and offset from the first axis 41 about which the rotor 40 is rotatable.

The control shaft 61 has an inner end section 67 which extends into a cavity 69 within the rotor 40. The control shaft 61 has an outer section (not shown) coupled to ah extension shaft which is rotatably supported in a bearing housing mounted on the first end wall 15 of the stationary housing 11.

The rotor 40 is provided with a plurality of piston and cylinder assemblies 80 radially disposed about the first axis 41. In this embodiment there are four piston and cylinder assemblies 80, but any other suitable number can be used. Each piston and cylinder assembly 80 comprises a cylinder 81 and a piston 83 mounted for reciprocation in the cylinder. Each piston and cylinder assembly 80 defines a working space 85 which comprises a combustion chamber. An ignition means 87 in the form of a spark plug is provided for igniting a combustible mixture in each chamber The .cylinders 81 open at their inner end onto the cavity 69 within the rotor Each piston 83 is connected to the inner end section 67 of the control shaft 61 by way .o of a connecting rod 91 having an inner (big) end 93 and an outer (little) end 95. One 15 particular piston 83a is connected to the control shaft 61 by way of connecting rod 91 a, and each other piston 83b is connected to the inner end section 67 of the control shaft 61 by a connecting rod 91b, as shown in Figure 1.

The _connecting rod 91a is pivotally connected at its outer end to piston 83a in a conventional manner. The connecting rod 91a is fixed to the inner end section 67 of 20 the control shaft 61 in a manner such that rotation of the connecting rod 91a with its respective piston and cylinder assembly 80 within the rotor 40 causes rotation of the control shaft 61 about the second axis 62.

Each connecting rod 91b is pivotally connected at its outer (little) end 95b to the respective piston 83b in conventional manner. Each connecting rod 91b is pivotally 11 connected at its inner (big) end 93b to the control shaft 61 for pivotal movement with respect to the control shaft 61 about the second pivot axis 62.

The manner of connection of .the inner (big) end 93a of the connecting rod 91a and the inner (big) ends 93b of the three connecting rods 91b to the inner section 67 of the control shaft 61 is shown in more detail in Figures 3 to 9 of the drawings.

As can be seen in Figure 6, the inner end section 67 of the control shaft 61 includes a connecting rod mounting portion 180. The mounting portion 180 includes a widened portion 182 at a first inner end, a threaded portion 184 at a second, outer end and a central portion 186.

1o The central portion 186 is generally cylindrical and includes a longitudinal slot 188.

Further the widened portion 182 includes a first lip 190 adjacent the central portion 186. The first lip extends around the circumference of the widened portion 182 with the exception of a portion adjacent the longitudinal slot 188.

As can be seen in Figures 3 to 5, each of the connecting rods 91 has a concave portion 192 at an inner end thereof The concave portion 192 is arcuate and has a radius of curvature equal to that of the central portion 186 of the mounting portion 180. The concave portion 192 of each of the connecting rods 91 is arranged to engage the Scentral portion 192 as shown in Figure 3 such that all of the connecting rods 91 are o located in a single plane 200 which is perpendicular to the first axis 41. The o connecting rod 91a has a projection 194 at the inner end thereof arranged to engage with the longitudinal slot 188 such that the connecting rod 91a cannot rotate about the control shaft 61.

.:oo#i Each of the connecting rods 91 has a first groove 196 adjacent the inner end 93 thereof. The connecting rods 91b also have a second opposed groove 198 adjacent the 12 inner ends 93b thereof The second grooves 198 are arranged to engage with the first lip 190 of the widened portion 182. The connecting rod 91a is arranged against the central portion 186 adjacent the part of the widened portion 182 around which the first lip 190 does not extend.

A securing collar 202 is provided to secure the connecting rods 91 to the control shaft 61. The collar 202 is placed over the control shaft 61 once the connecting rods 91 are in place. The securing collar 202 includes a second lip 204 extending around its circumference. The second lip 204 engages with the first grooves 196 of connecting rods 91 to secure the connecting rods 91 to the control shaft 61. This arrangement allows the connecting rods 91b to pivot about the control shaft in a limited angular fashion. A securing nut 206 is placed over the threaded portion 184 to secure the collar 202.

Figure 13 shows an alternative embodiment of the inner end section 67 of the control shaft 61. In this embodiment, the inner end section 67 of the control shaft 61 is secured within bearings contained within the second side wall 17 of the stationary housing 11. This provides additional stability and support for the inner end section 67 of the control shaft 61.

The .ffset between the first axis 41 and the second axis 62 causes rotation of the rotor about the first axis 41 upon reciprocation of the pistons 83 in the cylinders 81.

2( Rotation of the rotor 40 is transferred to the control shaft 61 by the connecting rod 91a fixed thereto as the piston 83a rotates with the rotor.

The pistons 83 rotate about the second axis 62 as they reciprocate within the cylinders 83 which in turn rotate with the rotor about the first axis 41. The offset between the 13 first axis 41 and second axis 62 is accommodated by angular movement of the connecting rods 91b.

The engine is provided with a fluid intake means 110 for admitting a combustible mixture of fuel and air to the cylinders 83, and a fluid exhaust means 130 for discharging spent products of combustion from the cylinders.

The fluid intake means 110 comprises an intake chamber 113 formed in the rotor The intake chamber 113 extends about the stationary central stator 31. A longitudinal delivery passage 114 is formed in the stator 31. The delivery passage 114 has an inlet section 115 adapted in a manner (not shown) to receive a supply of the combustible 1o mixture. The delivery passage 114 has an outlet section 117 which includes radial ports 118 for continual communication with the intake chamber 113 in the rotor. In this way, combustible mixture introduced into the delivery passage 114 is conveyed to the intake chamber 113.

From the intake chamber 113, the combustible mixture is distributed to the cylinders 15 81 in a regulated fashion in timed sequence with reciprocation of the pistons 83 in the cylinders. This distribution is controlled by a control means 111 which includes a respective intake duct 119 extending between the intake chamber 113 and each cylinder 81. The intake duct 119 for each cylinder 81 opens into the intake chamber 113 by way of a port 120, and opens into the cylinder by way of a port 124 in the side wall of the cylinder.

The control means 111 further includes a valve means 123 in the form of a disc valve 125 having an arcuate intake port 127 formed in it. The disc valve 125 is rigidly mounted on the central stationary section 31 so as to be fixed against rotation.

14 The disc valve 125 is positioned immediately adjacent the ports 120 of the intake ducts 119 for the cylinders such that the ports 120 are sequentially opened and closed by the disc valve 125. Each port 1'20 is opened by the stationary disc valve 125 when the port 120 registers with the arcuate intake port 127 in the disc valve 125. When the port 120 is registering with the intake port 127 (and is thus open), combustible mixture in the intake chamber 113 can be drawn into the particular cylinder 81 with which the open intake duct 119 is in communication.

The arcuate intake port 127 in the disc valve 125 is configured to open the intake duct 119 for each cylinder in timed sequence with reciprocation of the piston in the cylinder. Specifically, in this embodiment the intake duct 119 opens at 550 before bottom dead centre of the piston and closes at 650 after bottom dead centre, as is shown in Figure 11. Other timing arrangements are of course possible.

In the arrangement shown in Figure 1, the intake duct 119 for the lower cylinder is open (the intake port 127 being in register with it) and the intake duct 119 for the 15 upper cylinder is closed.

The fluid exhaust means 130 comprises an exhaust chamber 131 formed in the second end wall 17 of the stationary housing 11. The exhaust chamber 131 extends around the fC-st axis 41 and is an annular arrangement. An outlet duct (not shown) is provided to carry the spent products of combustion away from the exhaust chamber 131, such 20 as to a conventional exhaust system (not shown) including a muffler.

The fluid exhaust means 130 further comprises an exhaust control means 133 for allowing controlled communication between each cylinder 81 and the exhaust chamber 131.

The exhaust control means 133 comprises a respective exhaust duct 135 having a p9.rt 137 opening at one end onto each cylinder 81 and having a port 139 at the other end opening onto the exhaust chamber 131.

The exhaust control means 133 further comprises a valve means 140 having a disc valve body 141 and an arcuate exhaust port 143 in the body.

The valve body 141 is fixed against rotation with respect to the rotor 40 and is located immediately adjacent the ports 139 of the exhaust ducts 135.

The disc valve body 141 is accommodated in a recess 144 having an inner face onto which the ports 139 open. The disc valve body 141 is supported in the recess 144 on support posts 147 mounted on the second end wall 17 of the stationary housing 11.

This support arrangement maintains the disc valve body 141 in a stationary condition while the rotor 40 rotates, there being sliding contact between the inner face of the recess 144 and the disc valve body 141 during relative rotation therebetween.

The ports 139 of the exhaust ducts 135 are sequentially opened and closed by the 15 valve means 140. Each port 139 is opened by the valve means 140 when the port 139 registers with the arcuate exhaust port 143 in the stationary valve body 141. When the port 139 is registering with the exhaust port 143 (and is thus open), spent products of combustion in the respective cylinder 81 can be discharged into the exhaust chamber 131.

20 The arcuate exhaust port 143 is configured to open the exhaust duct 135 for each cylinder 81 in a timed sequence with reciprocation of the piston 83 in the cylinder.

Specifically, in this embodiment the exhaust duct 135 opening at 650 before bottom dead centre of the piston and closing at 650 after bottom dead centre, as is shown in Figure 12. Other timing arrangements are of course possible.

16 Preferably, the support posts 147 are contained within arcuate slots (not showvn, extending through the second side wall 17. The angular position of the disc valve body 141 may then be adjusted by rotating the support posts 147 from the second end wvall 17. This arrangement allows for fine tuning of the outlet exhaust gases.

As can be seen from the port arrangement in Figures 11 and 12, the intake duct 119 for each cylinder 81 opens to admit a combustible mixture into the cylinder before the exhaust duct 135 is closed. This provides a scavenging process which assists removal of residual exhaust gases (spent products of combustion).

A spacing is defined between the cavity 21 and the rotor 40 accommodated in the 1n cavity. A lubricating fluid such as oil is circulated through the cavity 21 so as to occupy the spacing, the lubricating fluid being introduced into the cavity through an inlet duct 25 and being withdrawn through an outlet duct 27. The circulating lubricating fluid flows through a circuit which includes a flow line (not shown) incorporating a heat exchanger. A fan, which is driven from the extension shaft 15 coupled to the control shaft 61, is provided for generating an air flow over the heat i exchanger. With this arrangement, the lubricating fluid also acts as a coolant for the engine.

The 4ubricating fluid is distributed within the engine through a distribution system, which includes various galleries and ports, to lubricate various parts of the engine S 20 including the piston and cylinder assemblies 80, and bearing surfaces. The distribution system also circulates the lubricating fluid through the cavity 69 within *e Sthe rotor 40 which accommodates the inner end section 67 of the control shaft 61 and the connectin rods 91.

the connecting rods 91.

17 The engine incorporates an ignition system for delivering electrical ignition pulsestq.

the spark plugs 87 in timed sequence with reciprocation of the pistons in the cylinders.

The ignition system includes a sensing means 161 adjacent the flywheel 55 and a set of contact points 170 located on the flywheel 55. Each of the contact points 170 is provided for a respective cylinder 81. Each contact point 170 is located on the flywheel 55 in a position such that it comes into proximity with the sensing means 161 when ignition is required of the fuel in the respective cylinder 81.

Ignition pulses for the spark plugs 87 timed by the sensing means 161 are transferred 1o to the rotor 40 through a brush contact 163 which is mounted on the housing and which is in sliding contact with commutators 165 on the rotor 40. The commutators 165 are insulated from the rotor and are electrically connected to the respective spark plugs 87.

The engine includes various seals for ensuring sealing between cooperating parts, 15 particularly those where one part rotates relative to another part.

o While the engine may operate on various fuels including petrol, it is particularly suitable for operation on gas.

The ngine operates under a conventional two-stroke Otto cycle. As the rotor rotates, the offset between the first axis 41 and second axis 62 causes reciprocation of the T, 20 pistons 83 in the cylinders 81. Each piston 83 performs an expansion stroke and a compression stroke for each rotation of the rotor 40. During these strokes, the combustible mixture is drawn into the cylinders 81 in timed sequence from the intake chamber 113, and spent products of combustion are exhausted in timed sequence from the cylinders 81 into the exhaust chamber 131, as previously explained.

18 Because the intake chamber 113 is located in the rotor 40 in close proximity to the cylinders 81, there is a relatively short passageway for delivery of the combustible mixture of ffiel and air to the cylinders. This provides for efficient operation of the engine.

From the foregoing, it is evident that an internal combustion engine is provided which is of relatively simple construiction yet effective in operation.

Figures 14 and 15 show an electric machine in accordance with the third aspect of the present invention where like numerals denote like parts. In this case, the machine is an electric motor. The motor includes the housing 11, rotor 40, central stator 31, io control shaft 61, pistons 83 and cylinders 81 as previously described. The fluid inlets and outlets and associated parts are not required.

In this embodiment, the cylinders 81 include a coil 210 surrounding the upper portions thereof The coils 210 are connected to a control system which may be timed in a manner similar to that described previously for the ignition system of the internal 15 combustion engine of Figures 1 to 14. The control system provides current to the coils 210 to generate a magnetic field within the cylinders 81. The pistons 83 each include :a magnetic portion to interact with the magnetic field within the respective coil 210.

The-control system is arranged to provide a current to each coil 210 as the respective piston 83 enters the coil 210. The field is provided in a direction to attract the piston 20 83 through the coil 210 and toward the top of the cylinder 81. The current in the coil will be reversed after the piston 83 reaches the top of the cylinder 81 to reverse the magentic field and force the piston 83 back down the cylinder 81.

Further, each piston 83 includes an extendible portion 212. The extendible portion 212 is in the form of a slidable pin member 214 having a head 216 and a shaft 218 19 The head 216 extends across the cylinder 81 and the shaft 218 is slidable withia.an opening in an end of the respective piston 83. The slidable pin member 214 is fixed to the cylinder 81 so that it may not slide completely out of the cylinder 81 and is biased to extend out of the piston 83 by a spring member 220.

When the slidable pin member 214 first enters the coil 210 and the coil 210 is energised, the slidable pin member 214 is pulled up the cylinder 81 and draws with it the piston 83. As the piston 83 approaches the top of the cylinder 81, the slidable pin member 214 is depressed into the piston 83 against spring member 220. This effectively increases the length of the stroke over which power is applied to the piston It) 83.

It should be appreciated that the scope of the invention is not limited to the scope of the embodiments described. The invention may apply to internal combustion engines operating on a four-stroke principle and to machines other than internal combustion engines or electric motors., s DATED THIS 12 TH DAY OF JUNE 2000 JOSEPH KARL BOUDEWYNS 20 By his Patent Attorneys LORD COMPANY PERTH, WESTERN

AUSTRALIA