GB2254888A

GB2254888A - Rotary positive-displacement pumps and engines.

Info

Publication number: GB2254888A
Application number: GB9104581A
Authority: GB
Inventors: Ian Alexander Giles
Original assignee: Individual
Current assignee: Individual
Priority date: 1991-03-05
Filing date: 1991-03-05
Publication date: 1992-10-21
Anticipated expiration: 2011-03-05
Also published as: GB2254888B; GB9104581D0

Abstract

In a pump cylinder with an inlet port 5 and an outlet port 6 a rotary piston 9 is arranged to rotate, the piston having an annular channel in which a dam 8 is fitted to pump material. A stop valve 3, 4 mounted on the circumference of the cylinder closes off the annular channel at a point contiguous to the outlet port 6 to enable the dam 8 to force the material through the outlet port. At the end of the pumping cycle, the stop valve is raised to allow the dam to pass and return to the closed off position, to start another pumping cycle when the dam passes the inlet port. The dam 16, Fig. 5 may form the floor of the channel. A rotary piston engine with external combustion chamber (24, Fig. 10) has compressed air provided from a compressor mounted on a common drive shaft. Rotary values (25, Figs. 11-15) may be used and two rotary piston engine units may be fed with compressed air from a central twin rotary air compressor (Fig. 15). <IMAGE>

Description

Rotary Positive-displacement Pump with adaptions to convert to Rotary piston engines This invention relates to a Rotary Positive-displacement pumn for pumping viscous materials such as food, paper pulp, slurry and sewage, non-viscous materials such as oil, water, chemicals, gas and air. This invention also relates to Rotary Piston engines based on the sarne concept and principal components and action.

Conventional Pumps for pumping such materials generally push by soe device operated by a mechanical or air arrangement, the material from. the inlet port to the outlet tort, whereas this invention using annular channel with darn will partly carry the material which will reduce friction and wear on the pump, making the pump more economical in energy. to operate in comparison with other pumps. As with existing rumps i.e.Piston pumps, this can be converted to for a Rotary piston engine by means of various "Stop Valve" arrangements with the provision of fuel injection and/or spark ignition and compressed air to form the timed combustion to drive the Rotary Piston on each power revolution.

According to the present invention there is provided a pump for pumping viscous and non-viscous materials which pump comprises a cylinder provided with an inlet nort for the materials to be pumped and @n outlet port for the material, in which a cylinder is arranged to rotate concentrically a rotary piston having mounted on it a annular channel in which is fitted a day. which will convey the material fror the inlet port to the outlet port. A stop valve mounted on the circurference of the cylinder will close off the annular channel at a point contiguous to the outlet port to enable the dan in the annular channel to force the material through the outlet tort. t the end of the pumping cycle the stoD valve will be raised to allow the dam in the rots tin channel to pass and return to the closed off position immediately afterwards to start another pumping cycle when the dam passes the inlet port.

The stop valve can be operated by a) cam operated lever e.g. flap valve 13 as in fig2 and fig3 (b) Hydraulic control with cam operated plunger e.g. flap valve 13 as in fig4 (c) Spring loaded plunger controlled by cam floor of annular channel fig 5,6,7,8,9 (d) a Rotary stop valve driven and timed from drive shaft by gears, drive chain or serrated belt fig 11,12,13,14 and 15.

The pump may include two or more cylinders arranged in parallel end pistons mounted upon a common drive shaft, thus to provide for continuous discharge of pumped material from the pump.

The pumD may also include two or more annular channels on the same rotary piston, to provide continuous discharge as in fig 8 and 9 and for the purpose of generating air compression to feed internal and external conbustion engines as in fig 10,13,14 and 15 which maybe mounted on the same- rotary piston or built in tandem with separate cylinder and rotary piston on common drive shaft.

A specific embodiment of the invention will now be described by way of examples with erference to the accompanying drawings in which: Fig.1 shows in perspective the outside of the pump with one end.

plate 2 fixed and valve cover 3 for Reciprocating flap stop valve assembly 13 as in Fig 2,3 and 4.

Fig.2 is an illustrated drawing of tbe Rotary piston and Reciprocating flap stop valve 13 with the dam 8 in annular channel approaching the start of the pumping cycle.

Fig.3 is a sectional end elevation of the rotary piston as in Fig.2 and cylinder 1 with the dam 8 passing through the Reciprocating fl@p st@@ valve assembly 13 in the raised @@siton.

Fig.4 is a sectional end elevation of the rotary piston and cylinder with the da@ 8 half-way through the pumping cycle, with Reciprocating fla@ stop valve hydraulically controlled by cam operated @lunger.

Fig.5 is an illustr@ted drawi g of the rotar@ piston with annular chan@el with cam floor forming dam 16 operating spring loaded plunger stop valve 17 shown in the raised position.

Fig.6 is a sectional end elevation of the Rotary piston with cam floor f@@@ing da@ 16 half-way through pumping cycle shown with a @@ring loaded Roller stop valve 18.

Fig.7 is a sectional end elevation of the Rotary piston with car.

floor forming dam 16 raising te spring loaded Wheel StOD valve 19 approaching the start of another pumping cycle.

Fig.8 is a sectional end elevation of the Rotary piston with two annular channels with cam floors forming dams 16 and two Spring loaded plunger stop. valves 17 set at 180.

Fig.9 is a sectional side elevation of Fig.8 of the Rotary piston With two annular channels showing one Spring lorded plunger stop valve in raised position and the other kalf-way through pumping cycle in closed off position.

Fig.lO is a sectional end elevation of a Rotary piston engine With an external combustion chamber 24 shown with a Spring loaded stop valve and cam floor of annular channel forming dam 16 at the maximum air compression and combustion stage of firing stroke position.

Fig.ll is a sectional end elevation of a pump with a Rotary piston and dam 8 approaching start of another pumping cycle with Rotary stop valve unit 25.

Fig.12 is a sectional end elevation of the Rotary piston with dan 8 at end of pumping cycle with Rotary stop valve 25 shown at corresponding position.

Fig 13 is a sectional end elevation of a Rotary piston engine with an internal combustion chamber shown with Rotary stop valve 25 and dam 8 in annular channel at the maximum air compression and combustion stage of firing stroke position.

Fig 14 is a sectional end elevation of a Rotary piston engine with Rotary stop valve 25 as in Fig 13 shown here half-way through power stroke cycle.

FIg. 15 is a sectional side elevation of a Rotary piston engine with two outer power Rotary pistons fed by inner Rotary air compressor with twin annular channels on Rotary piston fixed to common drive shaft. Rotary Stop valves 25 are shown timed and fixed to valve shaft 4 which is driven and tired by gears 27 fro main Drive shaft 10.

Ref erring to Figs which is an outline of the pump showing the Cylinder 1 with a Valve cover 3. fixed to seal and carry Reciprocating Flap Stop valve assembly 13 as shown in Fig.2.

The Stop valve shaft 4 is shown projecting in transverse position to carry te disc being the part of the Spring loaded lever assembly 12 as shown in Fig.2. The disc is fixed to the Stop valve shaft 4 by means of a key or serrated shaft and the Stop valve asser.rbly is actuated b lever assembly 12 anchored with a pivet on the end plate 2 which is secured to the cylinder by means of studs 7.

Fig.2 is an illustrated drawing portraying the action of the Rotary piston 9 and Reciprocating flap stop valve assembly 13 at the start of the nurr.in cycle. The da 8 in the annular channel has passed under the Stop valve, the Stop valve is actuated by the cam fixed on the main drive shaft'10 vilich lifts the lever mechanisn: to turn tile flap stop valve clear of the passing darn. The Flap stop valve 13 is then returned to the pumping position by return spri @@ lever ar@ 12, which is anchored to the end plate 2.

FIg.3 is a sectional end elevation of the Rotary piston 9 and Reciprocating flap stop valve assembly 13 positioned inside the cylinder 1 as shown in Fig.1. The dam 8 is shown passing under the Flap valve 13 which is lifted by cam 11 shown at its highe@t point in relation to the Spring l@@aded lever assembly 12. The lever mechanism o@erates the end dise fixed to the Flap valve shaft 4 causing the Flap valve to lift clear and return to the annular channel as the Rotary piston revolves.

Fig.4 is a sectional end elevation of a Rotary piston urrp as shown in Fig 3 with the darn 8 half-way through the pumping cycle. The Reciprocating flap stop valve 13 is shown in the pumping position and in this case is operated by a Hydraulic control system 14 actuated by the cam 11 fixed to main drive shaft 10. When the cam is fully extended the plunger in the first Hydraulic barrel forces fluid into second barrel pushing plunger rod to move disc 9 Reciprocating flap stop valve assembly 13 to raised position. As the cam rotates return springs in Hydraulic barrels return stot valve into annular channel to start another pumping cycle.

Fig.5 is an illustrated drawing portraying the action of the Rotary piston 9 and the Spring loaded plunger stop valve 17 approaching the start of the pumping cycle. The Spring loaded stop valve is lifted by the Channel with cam floor 16 which also forms dam to push and draw liquid etc. around annular channel in each revolution of the Rotary piston. In this example annular seals 15 are shown positioned next to annular channel wall to create maximum pressure with least friction.

Fig.6 is a sectional end elevation of the Rotary piston 9 positioned inside the cylinder 1. Spring Icaded roller stop valve 18 is shown: in pumping position. The channel with cam floor forming dam 16 is shown half-way through pumping cycle drawing liquid through inlet port 5 and pushing liquid through outlet port 6.

Fig 7 is a sectional end elevation of the Rotary piston 9 positioned inside the cylinder 1 and the Spring loaded Wheel stop valve 19 in raised position. The Annular channel with cam floor forming dam 16 is shown at the point approaching the next pumping cycle with Wheel stop valve 19 fully lifted by cam floor of channel. The Rotary piston action is exactly the same as in Fig 6.

Fig 8 is a sectional end elevation of a pump with twin Annular channels with cam floors forming dams 16 which operate two Spring loaded. stop valves 17 positioned at 180 interval to allow continuous pressure delivery. The top Spring loaded plunger stoD valve 17 in the first Annular channel is shown at start of pumping cycle with the Spring loaded plunger valve 17 in fully lifted position. At the same time the Spring loaded plunger stop valve 17 in the second Annular channel is half-way through its pumping cycle with the plunger valve shown in channel in pumping position drawing liquid etc through inlet port 5 and pushing liquid through outlet port 6,there is an inlet port and outlet port for each channel.

The Spring loaded plunger stop valves 17 in this example run in a sealed casing with seals, guides and a grease cap for lubrication.

This dual Annular channel Rotary piston works principly the same as the Rotary piston in Fig 5 only with an extra channel starting pumping cycle 180 after first channel.

Fig 9 is 2 sectional side elevation of Fig 8 showing the Rotary piston 9 in the same position. The Rotary piston is fixed to the main drive shaft 10 by serrated spline or key and held in position within cylinder casing 1 by bearings 20 in qd plates 2.

As in Fig 8 te first plunger valve 17 is shown in raised position and the second plunger valve 17 is 3h0'!n in pumping position.

Annular seals can be used between Rotary piston 9 and Cylinder casing 1 to allow maximum pressure with minimum friction, the said can be fixed in Annular grooves as near as possible to edge of Annular channel.

Fig 10 is a sectional end elevation of a Rotary piston engine with an external combustion chamber.

The Rotary piston 9 in this example works in the sare way as in figures 5,6,7,8 and 9 with the ssme Spring loaded plunger stop valve 17. At the inlet port position an External combustion chamber 24 is fixed to the outer cylinder wall 1. At the head of the combustion pot is positioned a spark plug 22, a Fuel invention surly 21 and a compressed air supply 23. Air pressure is fed from the second Annular channel as sho'.vn in Fig 9 and timed to be released into the Combustion chamber pot 24 when the Rotary piston is at the stage shown in this elevation i.e. minimum distance between plunger stop valve 17 and dam. formed by cam floor in channel 16 and allowng @g ull clearence of combustion port below the Combustion pot 24 to produce maximum thrust onto drive channel da.

At this point of maximum compression fuel is injected by fuel supply 21 and ignited by timed spark plug 22. Combustion takes place and drives the Rotary piston around on its fire stroke.

As the Rotary piston revolves exhaust is pushed out through the outlet/exhaust port 6.

It is possible to have a fire stroke in every revolution of the Rotary piston. It maybe desirable to have a fire stroke on every second or third or fourth revolution, this is flexible according to how manly combustion chanbers are used on the corresponding Annular channels in the same Rotary piston or run in parellel in separate cylinder cases on common drive shaft 10.

Air pressure may also be developed by an independent compressor with timed outlet valve to serve combustion chambers 24. However floor economy and efficiency reasons compressed air pressure can be more easily produced by using Annular compression channel with the same or piston and com.r:on drive shaft, or produced in separate cylinder case on common drive shaft with separate Rotary piston carrying Annular air compression channel.

The compression ratio developed will be according to the volume inside air compression Annular channel or channels relative to the Tower @ annular charnel it is supplying.

Fig 11 is a sectional end elevation of a pump showing Rotary piston 9 with dam 8 approaching start of pumping cycle. The Rotary stop valve 25 is geared and timed to main Drive shaft 10 on a 1:1 ratio allowing the dam 8 to pass through the valve to start another pumping cycle this valve :::ay also be drIven by a tired Drive chain or a tied Serrated belt principle the Rotary piston is designed@and or in the same way 9 1n 1 2,3 nd 4 taking material in through inlet port@5 and pushing material through outlet port 6.

One way valve maybe used in@outlet pipe or inlet pipe to stop return oressure of pumped material.

Fig 12 is a sectional end elevation of the same tyne of pump as in Fig 11 with a modified Annular chancel which has been cut away on one side wall immediately infront of dam 8 to allow the compressed air to be released at maximum pressure through outlet port 6 to feed combustion chamber in votary engine at the stage shown in Fig 13 and 15 at a point just preceding ignition.

The dam a in Rotary piston 9 is shown at the end of its pumping cycle and is releasing the compressed air through Orifice 26 as it rotates by outlet port 6, which is positioned off channel centre to match up with Orifice 26. This valve allows the compressed air produced in Rotary air pump to be transferred to te power channel at the right time to create maximum compression for combustion as shown in Rotary engines nig 13 and 15.

Fig 13 is a sectional end elevation of a Rotary piston engine based on the Rotary pump model Fig 11 and 12, at this stage the Rotary piston is shown in the firing position where the dam 8 is at the optimum compression stage i.e. minimum distance between stop valve 25 and dam 8 but allowing clearance of compressed air supply 23 and fuel injection 21. At this point of maximum compression fuel is injected by fuel supply 21 and ignited by timed spark plug 22. Combustion takes place and drives the Rotary piston around on its fire stroke.

It may be possible on high compression models to use a fuel injection ignition without the use of a spark plug. As the Rotary piston revolves exhaust is pushed through the outlet/exhaust port 6.

It is possible to have a fire stroke in every revolution of the Rotary piston. It may be desirable to have a fire stroke every second, third or fourth revolution according to the number of annular combustion channels d their corresponding stop valves positioned on the same Rotary piston or separate cylinder cases, in line, on common drive shaft.As explained in Fig 10 the same flexibility applies the air pressure may be developed by a compressor driven from drive shaft or b air compression annular chunnel on same Rotary piston or produced y senarsts rotary air pump on @@@@@n drive shaft.

Fig 14 is a sectional end elev@tion of the sa@@ Rotary @@@ engine shown in Fig 13 with the @ @ @ half-way through its @@@ cycle, pushing the exhaust through outlet/exhaust port 6.

Fig 15 Is a sectional side elevation of a Rotary oiston engine. The first Rotary piston with power channel is shown at firing stage as shown in Fig 13. Compressed air has been delivered fro the left hand channel of the central Rotary air compressor and is shown t same stage as in Fig 12. Fuel is injected from fuel supply 21 and ignited by spark plug 22.

As can be seen in this example the central Rotary piston producing air pressure from two Annular channels is timed to release compressed air at the right time through Orifice 26.

The first air channel is releasing air which is compressed for combustion in the first rotary power piston, as the second air channel is almost half-way through its pumping cycle to deliver compressed air for combustion in the second Rotary power piston 180 after the firing of the first Rotary power piston i.e. dams8 on the two Rotary power pistons are set at 180 intervals and dams 8 on the two Annular channels on central Rotary compressor piston are set at 180 intervals to match up with their corresponding Rotary power pistons.

In other Rotary engines of this type it may .e desirable to have a Air release valve between compressor and combustion chamber timed to particular firing order.

The Rotary stop valves 25 are keyed onto Stop valve shaft 4 in positions shown,as in Fig 12 for first channel in central Rotary compressor, as in Fig 13 for first Rotary power piston.

The Rotary stop valves for second channel of central Rotary compressor and matching second Rotary power piston are timed 180 later, to correspond with dans a in annular channels. The stop valve shaft 4 is driven and timed by gears 27 n-t same sped as main drive shaft 10.

Suitable Seals, Bearings and Gears well on in the art are employed together with conventional lubrication ad cooling means well known in the art.

The model shown in Pig 15 can be easily adapted to a Two stroke diesel engine by timing injectors to fire every second revolution of each Rotary piston and using the air pressure in ' the other revolution to scavenge any surplus exhaust gases let by the previous power stroke. This would assist in cooling and efficient exhaust emIssion control.

In a Four Rotary power piston, Two stroke diesel engine of this type i.e. increasing engine in Fig 15 by two mo@e Rotary power pistons and another matching central Rotary air @@@@@essor, every revolution of the drive shaft would be powered by the capacity e@tal to two rev@lutions of a Rotary power piston. @@@@lly @@ in @ @h@@e Rotary power piston Two stroke diesel engine of this type, one revolution of the drive shaft 10 would be @@@ered by the ca@acity equivalent to one and a half revolutions of a Rotary power piston.

In the examples described (Figures 1 to 15) Annular seals @@@ be used between Rotary piston and cylinder ca@ing @@ @llow minimum friction and create maximum pressure. The seals can be fixed in Annular grcoves as near as possible to edge of Annular channel.

On more simple models compatible materials alone may be used to carry out sealing function e.g. nylon Rotary piston serrated to metal drive shaft housed by metal cylinder casing with a low friction material stop valve.

On some pumps it may be desirable to have a Non return valve in outlet pipe or inlet fire but not essential. 3y fitting a control valve in inlet pipe to regulate intake of raterial the pump can be converted to a variable delivery pump.

All models described can have the various Stot valves interchanged to corresponding rotary pistons with both tyres of dams, to allow flexibility for a wide range of purposes for pumps and Rotary engines.

In Pigs 5,6,7,8,9 and 11 the pumps can be changed to reverse action (clockwise to anti-clockwise) where the material being pumped would be drawn and discharged through opposite ports.

The Rotary pumps and Rotary engines of the above described embodiments of the present invention posesses the following advantages Advantagas of Rotary pump: 1. It is of simple and cheap construction; 2. 3y its design which is a departure from general practice it can be sealed and regulated to give high pressure when required; 3. It can be operated effectively as a surface, submersible, bore hole or well pump; 4.It has a capacity range from rinus 5 G.P.M. hydraulic to 50,000 G.P.M. plus oil end water pump, u'nrer limit being limited only by the power capability to drive pump; 5. A pump for pumping some viscous materials will not require a valve in the inlet Dioe or in the outlet pipe. Other pumps will require @ non-return valve in the outlet pipe and in some cases a regulating valve in the inlet tire; o.It can be used as a constant delivery pump by tha employment of two cylinders with inlet ports positioned 180 from the outlet ports. @ach cylinder with its Rotary piston fitted on a common @rive shaft pumping an alter@ate 180 cycle would give a consta@t discharge from the pump.

7. It can be used as a variable delivery pump by fitting a valve or other arrangement on the inlet pipe to regulate the intake of pumping material.

Advantages of Rotary piston engines; 1. It is of simple and cheap construction; 2. Higher ratio of tower to main drive shaft revolution; 3. Efficiency higher than conventional engines.

4. Adaptable to suit wide range of engine requirments i.e.

small air cooled units to large capacity tower units.

5. By varying the timing and stop valve components it can be adapted to 1,2 and 4 stroke engine; 6. The range of Rotary engines based on same concept encompasses External and Internal combustion engines, Fuel injection, Electric ignition and Fuel ignition (Diesel) engines.

7. Compression ratio can be easily varied to suit engine design requirement.

8. Balanced drive thrust on revolving drive shaft with the advantage of Rotary pistons having "Fly wheel" momentum efficiency effect, as apposed to a crank and connecting rod arrangement in conventional engines .

9. Engines can be designed to run cleaner than conventional engines, with the use of compressed air running through Annular charnel, creating good Exhaust emission control.

Key to Drawings Figs. 1 to 15 FIG.1 1. Cylinder 2. End plate 3. Valve cover 4. Stop valve shaft 5. Inlet port 7. Studs for End plate fixin FIG.2 4. Stot valve shaft 6. Channel wlth dam 9. Rotary piston 10. Drive shaft 11. Cam 12. Spring loaded lever assembly ( pivoted to End plate ) 13. @@ciprocating Flap Stop valve as: e:: 1. Cylinder 3. Valve cover 4. Stop valve shaft 5. Inlet rort 6. Outlet port e. Channel with Dam 9. Rotary piston 10. Drive shaft 11. Cam 12. Spring loaded lever assembly ( pivoted to End plate ) 13. Reciprocating Flap stop valve assembly 1.Cylinder 5. Inlet port 6. Outlet port 8. Channel with Dam 11. Cam 13. Reciprocating Flap Ston valve assembly 14. Hydraulic control to St6p valv with return springs Key to Drawings Figs. 1 to 15 FIG.5 9. Rotary piston 10. Drive shaft 15. Annular seals 16. Annular channel with Cam floor ( Forming Dam ) 17. Spring loaded plunger Stop valve FIG.6.

1. Cylinder 5. Inlet port 6. Outlet port 9. Rotary piston 13. Drive shaft 16. Annular channel with Car..

floor ( forming Dam ) 18. Spring loaded Roller Stop valve FIG.7 16. Annular channel with Ca@ floor ( Forming Dam ) FIG.8 1. Cylinder 5. Inlet port 6. Outlet port 9. Rotary piston 10. Drive shaft 16. Annular channel with Cam floor ( Forming Dar. ) 17. Spring loaced Plunger Stop valve Key to Drawings Figs. 1 to 15 FIG.9 1. Cylinder 2. End plate 9. Rotary piston 10. Drive shaft 16. Annular channel with Cam floor ( Forming Dam) 17. Spring loaded Plunger Stop valve 20. Main drive shaft bearings FIG.10 1. CyliriEcr 6. Outlet Port (Exhaust) 9. Rotary Piston 10. Drive Shaft 16. Annular Channel with Cam floor ( Forming Dam ) 17. Spring loaded Plunger Stop valve 21.Fuel injection supply 22. Spark plug 23. Compressed air supply 24. External combustion chamber pot PIG.11 1. Cylinder 4. Stop valve shaft 5. Inlet port 6. Outlet port 8. Channel with Dam 9. Rotary piston 10. Drive shaft 25. Rotary Stop Valve Unit FIG.12 5. Inlet Port 6. Outlet Port 8. Channel with Dam 25. Rotary Stop Valve Unit 26. Orifice inside wall of channel, forming air release valve Key to Drawings Figs. 1 to 15 FIG.13 1. Cylinder 6. Outlet Port (Exhaust) 8. Chal-nel with Dan 9. Rotary piston 10. Drive shaft 21. Fuel injection supply 22. Spark plug 23. Compressed air supply 25. Rotary Stop Valve writ 27. Combustion cavity FIG.14 6. Outlet Port (exhaust) 8. Channel with Dam 25. Rotary Stop Valve Unit 1. Cylinder 2. End plate t. Stop Valve shaft 8. Channel with Dam 9. Rotary piston 10. Drive shaft 21. Fuel inJection supply 22. Spark plug 23. Compressed air supply 25. Rotary Stop Valve Unit 26. Orifice inside wall of channel, forming air release valve 27. Gears driving Rotary Stop Valve shaft

Claims

Claims WHAT I CLAIM IS: 1. A pump for pumping viscous and non viscous materials which pump comprises a cylinder provided with an inlet port for material to be pumped and an outlet port for the material, in which cylinder is arranged to rotate concentrically a rotary piston having mounted on it a annular channel dam which convey materials from the inlet port to the outlet port. A stop valve fitted on the circumference of the cylinder will close off the channel at a point contiguous to the outlet port to enable the dam in the rotary channel to force material through the outlet port, at the end of the pumping cycle the stop valve lifts to allow the dam in the rotary channel to pass and return to the closed off position immediately afterwards to start another pumping cycle when the dam passes the inlet port.
2. A pump according to Claim 1. wherein said stop valve is a reciprocating flap valve activated by a cam on the main drive shaft as in Fig 2, 3 and 4.
3. A pump according to Claim 1. wherein said stop valve is a spring loaded plunger stop valve activated by annular channel with a cam floor (forming dam), as in Fig 5, 8 and 9.
4. A pump according to Claim 1. wherein said stop valve is a spring loaded roller stop valve activated by annular channel with cam floor (forming dam), as in Fig 6.
5. A pump according to Claim 1. wherein said stop valve is a spring loaded wheel stop valve activated by a annular channel with cam floor (forming dam), as in Fig 7.
6. A pump according to Claim 1. wherein said stop valve is a rotary stop valve, geared and timed to main drive shaft on a 1:1 ratio and driven by gears, chain or serrated belt, as in Fig 11 and 12.
7. A pump as claimed in any preceding claim which comprises of two or more of said cylinder arranged in parallel and having rotary piston mounted on a common drive shaft in a position so as to discharge material from the pump at equal spaced intervals in one revolution of the drive shaft.
8. A pump as claimed in any preceding claims wherein said rotary piston has two or more annular channels with matching inlet and outlet ports, as in Fig 8 and 9.
9. A pump as claimed in any preceding claims which can be used as constant delivery pump by the employment of two or more annular channels in the same rotary cylinders or in separate cylinders with inlet and outlet port with stop valve at 180 degrees interval as in Fig 8 and 9 with each annular channel pumping 320 degrees of its cycle.
10. A pump as claimed in Claim 1. which can be used as a constant delivery pump by the employment of two or more annular channels in the same rotary cylinder or in separate cylinder with inlet ports positioned 180 degrees from their outlet ports each annular channel pumping an alternative 180 degrees cycle to give a constant delivery.
11. A pump as claimed in preceding claim which can be used as a variable delivery pump, by fitting a valve or other arrangement on the inlet pipe to regulate the intake of pumping material.
12. A pump as claimed in Claims 1, 2, 3, 4, 5 and 6 which can be changed to reverse action where the material being pumped would be drawn and discharged through opposite ports, as in Fig 5, 6, 7, 8, 9, 11 and 12.
13. A pump for pumping viscous and non-viscous materials substantially as herein before described with reference to Figs 1, 2, 3, 4, 5, 6, 7, 8, 9, 11 and 12.
14. A rotary piston engine with an external combustion chamber where compressed air is mixed with fuel, and ignited by electric spark plug or by indirect injection in the case of diesel rotary engine. The expansion of the gas mixture when ignited drives the rotary piston with annular channel and dam around one revolution to return to the next fire stroke after pushing the exhaust gas through outlet port and passing under the stop valve. The rotary piston engine is based on the same concept as the pumps described in preceding claims, where different stop valves can be used for different models, as in Fig 10: spring loaded plunger with cam floor (forming dam).

Compressed air in this model can be supplied from rotary air pump driven on common drive shaft.
15. A rotary piston engine with an internal combustion chamber (as in Figs 13, 14 and 15) where compressed air is mixed with fuel and ignited by electric spark plug or by direct injection in the case of diesel engines. The ignition occurs directly in the combustion cavity inside the annular channel between the stop valve and the dam which drives the rotary piston around on each power stroke. Compressed air is provided from rotary piston compressor on common drive shaft and timed to be released into internal combustion chamber at the time just preceding ignition. As in Fig 15, a twin rotary piston power unit is fed from a central rotary twin annular channel compressor, where each air compression output from each compression channel is matched and timed to its corresponding power rotary piston.The rotary stop valve is timed and geared to the main drive shaft on a 1:1 ratio and driven by gears chain or serrated belt.
16. A rotary piston engine as claimed in any preceding claim wherein the number of pistons can be arranged on common drive shaft or in parallel to suit power requirement and the firing stroke can be varied according to design requirement ranging from a power stroke every revolution upwards, including two stroke, three stroke, and four stroke engines.
17. A pump and rotary engine as claimed in any preceding claim, which can have various stop valves interchanged to corresponding pistons with both types of dams to allow flexibility for a wide range of purposes for pumps and rotary engines.
18. A pump and rotary engine as claimed in any preceding claims wherein said construction of components can be made from a wide range of materials - nylon, plastic, ceramics, metal, rubber etc. which are compatible and run with least friction.
19. A pump and rotary engine as claimed in any preceding claims wherein said annular channel seals and stop valve seals can be used to allow minimum friction and create maximum pressure.
20. A rotary piston engine constructed, arranged and adapted to operate substantially as here in before described with reference to the accompanying drawings - Figures 10, 13, 14 and 15.