WO1999028629A1 - Rotary piston pump and method of operation - Google Patents
Rotary piston pump and method of operation Download PDFInfo
- Publication number
- WO1999028629A1 WO1999028629A1 PCT/NZ1998/000175 NZ9800175W WO9928629A1 WO 1999028629 A1 WO1999028629 A1 WO 1999028629A1 NZ 9800175 W NZ9800175 W NZ 9800175W WO 9928629 A1 WO9928629 A1 WO 9928629A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- shaft
- housing
- work unit
- recess
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/36—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movements defined in sub-groups F01C1/22 and F01C1/24
Definitions
- a work unit (as herein defined), including a housing, a shaft rotatable about an axis within said housing, at least one piston having a stationary orientation relative to said axis but which rotates with said shaft about said axis, the or each said piston being part cylindrical and being concentrically mounted relative to the, or a respective, part cylindrical recess provided in said shaft so that an external arcuate surface of said piston cooperates with an internal arcuate surface of said shaft recess as the piston and shaft move relative with one another, a recess in said piston which forms a chamber for at least part of a cycle of the work unit to receive a charge of a fluid, an internal arcuate surface of said housing being concentrically provided relative to the said axis, so that as the shaft rotates, the arcuate external surface of the piston can cooperate with the internal arcuate surface of said housing as work is performed.
- a work unit as defined in the paragraph immediately above has said piston recess with an additional recess to retain said charge of fluid for an expansion part of said cycle.
- a work unit is as defined in either of the paragraphs immediately above wherein the or a further recess of said piston is adapted to receive a charge of fluid in one cycle or part of a cycle and to transfer it to an opposite side of the housing on the next cycle or part of a cycle.
- a method of operating a work unit including providing a housing and mounting a shaft to rotate about an axis within said housing, providing at least one part cylindrical piston and mounting the piston to rotate with the shaft while maintaining a stationary orientation relative to the axis, concentrically mounting the piston relative to a part cylindrical recess provided in the shaft so that an external arcuate surface of the piston can cooperate with an internal arcuate surface of the shaft recess as the piston and shaft move relative with one another, providing a recess in the piston which forms a chamber for at least part of a cycle of the work unit to receive a charge of fluid, further providing an internal arcuate surface for the housing concentric relative to the axis which can cooperate with the external arcuate surface of the piston as the piston moves relative to the housing with the shaft and work is performed.
- a method as defined in the paragraph immediately above includes providing the or each piston with a pair of said recesses, one of which is adapted to provide a portion of a fluid being exhausted to form part of a fluid which has been induced and to provide a portion of said fluid which has been induced as part of said fluid being exhausted.
- a work unit (as herein defined) and/or a method of operating a work unit (as herein defined) is substantially as herein described, particularly, but not exclusively, with respect to the accompanying drawings.
- FIGURE 1 shows diagrammatically a cross sectional view of a work unit operating as an engine according to one possible embodiment of the invention
- FIGURE 2 shows diagrammatically an end view of an engine of
- FIGURE 3 shows diagrammatically an end view of an engine according to one possible embodiment of the invention including the gearing which may be utilised;
- FIGURES 4-15 show very diagrammatically the operation of an engine according to one possible embodiment of the invention.
- FIGURE 16 shows very diagrammatically the operation of a pump or compressor according to one possible embodiment of the invention
- FIGURE 17 shows diagrammatically an exploded view of the pump or compressor of Figure 1 6;
- FIGURE 18 shows diagrammatically front and cross-sectional views of the pump or compressor of Figure 1 6 and 17;
- FIGURE 19 shows diagrammatically a side exploded view of the pump or compressor of Figures 1 6 to 1 8;
- FIGURE 20 shows diagrammatically a front view of the gearing assembly of Figure 1 9. DESCRIPTION OF POSSIBLE EMBODIMENTS OF THE INVENTION
- an engine referenced generally by arrow 50 has a main housing 5 and end housings 27.
- a main shaft 1 extends through the housing 5 between main shaft ends 2 and is provided with main shaft bearings 6.
- a pair of pistons 3 are in this embodiment (one, or more than two, pistons 3 could be used in other embodiments) are mounted diametrically opposite about the main shaft 1 on respective piston shafts 4 and with piston shaft bearings 7. Seals 8 and 9 are respectively provided for the main shaft 1 and the piston shafts 4.
- the main shaft 1 is provided with gearing 10 which in this embodiment is connected through spur timing gear 1 2 with piston shaft gearing 1 1 .
- a gear cover 1 4 provided with a gear cover seal 1 5 is secured in position by gear cover studs 1 3.
- Lubrication for the gearing is provided through oil lubrication inlet 1 6 with the lubrication oil then leaving through oil lubrication outlet 1 7 for filtering and return.
- the oil provides main bearing lubrication at 1 8 and gear lubrication at 1 9 with pipe 20 providing for lubrication to be directed to an oil centrifuge chamber 21 to provide rotor bearing lubrication at 22 utilising rotor centrifuge oil hole 23.
- Rotor centrifuge gas hole 24 allows the escape of any build up of gases and any oil which passes centrifuge hole 23 and seal 9.
- An oil collection gallery 25 provides a sump from which oil can be recovered by means of scoop 26.
- the engine 50 has inlet ports 28 positioned adjacent outlet ports 29.
- Aperture 30 provides a gas bypass outlet through the end housings 27.
- the main shaft 1 in this embodiment has a pair of opposed radial cuts or part cylindrical recesses 55 in it to accommodate respective concentric part cylindrical pistons 3 which can rotate with the shaft 1 , with a prescribed tolerance between the arcuate external surfaces of the pistons 3 and the recesses 55 as relative movement between those surfaces occur, the shaft 1 and the rotor pistons 3 all operating within the chamber defined within the main housing 5.
- the pistons 3 are in the nature of rotors in that they have a rotational movement relative to the main housing 5 and there is rotational movement of the shaft 1 relative to the pistons 3.
- the pistons 3 are each part cylindrical with arcuate diametrically opposed recesses 51 , 52 and arcuate external surfaces R4 which can cooperate with the concentrically radiused arcuate internal surface R5 of the recesses or chambers 55 on opposed sides of the main shaft 1 .
- part cylindrical is used throughout the specification to define a shape which is essentially cylindrical but has had portions removed or omitted.
- the internal surface R5 sweeps past the surfaces R4 of the pistons 3 to work on the fluid contained within the chamber defined at any time between the respective piston 3 and the shaft 1 .
- the chamber 5 on both of its opposite sides in the embodiment shown in Figure 2, itself has respective radiused arcuate surfaces R3 concentric relative to the axis of the shaft 1 so that, (see Figure 9 for example) the arcuate surface R4 of the piston 3 can sealably cooperate with the arcuate surface R3 in moving the fluid charge before it in the embodiment of Figure 2.
- Additional radiused surfaces R1 and R2 are provided on each side of the radius surface R3, and each side of the blades or projections 53, 54, to sealably engage with the edges or tips 48 of the rotor pistons 3 as they sweep around the internal surfaces R ⁇ and R ⁇ .
- the blades or projections 53, 54 are required to sweep the chambers formed by the recesses 51 , 52 as they move past.
- the radial relationship between the radii of recesses 51 , 52, the radii, R1 , R2, R3, the piston radius R4 and the spacing of the axes of shafts 2 and 4 is, therefore, important.
- the radii R1 and R2 will also equal the distance X with the center of curvature moved vertically and rotated by a few degrees relative to the axes defined by the piston tips or edges 48.
- the top surface of piston recess 51 is shown to extend deeper towards the shaft 4 so that a clearance is provided between the upper surface of the piston 3 as it passes the top blade 53. This again retains some volume in the top recess 51 despite the sweeping action of the top blade 53.
- the additional recess 56 can be of any shape or size extending to be within the boundary defined by the piston tips 48. It will be appreciated that no such additional recess
- the main shaft 1 has its main shaft ends 2 supported by bearings 6 within its end housings 27, the bearings 6 being lubricated and cooled by the lubrication channel 1 8.
- the pistons 3 are mounted on the piston shafts 4 provided with the piston shaft bearings 7 and held by the main shaft ends 2.
- the piston bearings 7 are lubricated and cooled by the oil fed by centrifugal action fed through a lubrication pipe 20, spun into the centrifuge chamber 21 and passing through the rotor centrifuge oil hole 23.
- the seal 9, which may be of ceramic or other material, can control the oil so that the oil flow is centrifuged out of the oil hole 23 to form the chamber, from which any oil seepage can be centrifuged through gas hole 24, together with any blow by gas from within the housing 5.
- the oil lubrication for the gearing may be derived from the main shaft gear 1 0 to be spread to all the other gears and to be finally centrifuged to the gear box cover 1 4. All the oil may suitably enter the gear box through the oil inlet 1 6 to be collected in the oil collection gallery or sump 25 and to be picked up by the oil recovery scoop 26 and drawn out into the oil suction pipe 1 7.
- the engine 50 is shown provided with a spark plug 43 and a fuel injector 44. Of course, a plurality of spark plugs and fuel injectors may be used in alternative embodiments. In this particular embodiment, the engine 50 may be liquid cooled through cooling ducts 46.
- the engine 50 in this particular embodiment may operate as a two stroke engine being piston ported but firing twice for every rotation per cylinder instead of only once. Alternatively, the engine may fire as many times per cylinder as may be required. As will also be appreciated from the description herein below particularly, tuning for the induction and exhaust may be unnecessary in that the engine 50 operates with positive induction and the exhaust gases are swept out from the engine 50 by the pistons 3.
- the present invention provides a non-reciprocating engine 50 and as will be appreciated by those skilled in the engineering arts, the engine 50 may, therefore, be considered as being an Otto engine, but with the main shaft 1 replacing the normal crank shaft and with the usual con rods and cylinders omitted. It will also be appreciated that as the main shaft 1 of the engine 50 may extend the entire length of the engine it may be driven or drive from either end. Additionally, as will be appreciated from the brief description of the lubrication of the engine 50, in a preferred embodiment, it is substantially an oiless engine in that the pistons 3 are not required to contact the shaft 1 or the inner surface of the housing 5, but instead can operate with prescribed clearances, relying on the fluid flow through the engine to effectively provide seals between the component parts. These clearances may be maintained as appropriate and by appropriate cooling of the engine 50 such as by liquid cooling through ports 46 in the present embodiment.
- the engine 50 can allow the cylinder pressure to maintain a squared position back to the main axis of the shaft 1 for most of the working or power stroke.
- the pistons 3 uncover or expose the side of the piston 3 to enable the pressure to maintain a good angle for conversion of that pressure into mechanical work.
- the pistons 3 are each shown provided with respective radiused recesses or scallops 51 , 52 on opposed sides of the rotor pistons 3. Each of the pistons 3 is held by gearing so as to maintain its substantially horizontal position or orientation relative to the axis of the shaft 1 and housing 5.
- the pistons 3 engage with prescribed clearances, with the respective concentric radiused part cylindrical recesses 55 provided on opposed sides of the main shaft 1 , and with the arcuate inner surfaces R1 , R2, R3 of the housing 5.
- the engine 50 is therefore achieving a transfer of fresh air between the induction and exhaust sides of the engine and is thereby enabling a contribution to the exhaust of the fresh air. This will be substantially reducing, at least in respect of the relevant ratios, the unwanted components of the exhaust emissions.
- FIG 1 1 the ignited charge 39, together with the second fresh air charge 33, are shown being moved through the right hand cylinder space 47 as the charge 39 expands.
- the object of good combustion chamber design is to create the condition in the cylinder for the air and fuel to be thoroughly mixed and then excited into a highly turbulent state so that the burning of the charge will be completed in the shortest possible time and to burn as completely as possible.
- the beginning of turbulence begins after the induction port is completely sealed and during the start of the compression phase, when the pocket of pressurized exhaust gas exits into the induction charge creating vortices that interact to cause viscous shear interaction which will speed up the rate of heat transfer and fuel mixing.
- the three offending pollutants released by an engine in the atmosphere are CO, HC and NOx.
- CO carbon monoxide and hydrocarbon products of combustion
- NOx oxides of nitrogen increasing.
- Further leaning of the mixture to around 20: 1 while that brings about a reduction in the production of NOx, creates instability in combustion.
- the stoichiometric values can be kept to assist with the reduction of CO and HC while at the same time reducing the production of NOx.
- pistons 3 are shown in this embodiment, it is envisaged that in its various possible embodiments as envisaged by the applicant, a single piston 3 or more than two pistons 3 could be used.
- a further embodiment of the invention operates as a pump or compressor and is particularly suitable for use as a supercharger for an engine.
- superchargers are used in various types of engines to supply air or a charge of fuel at a higher than atmospheric pressure.
- the present invention may have a cylinder or chamber with a volume less than the volume being displaced per rotation.
- a pump or compressor of the present invention can be of a substantially small size with the ongoing benefits that this can, therefore, provide, particularly as in an automobile engine compartment, space is at a premium.
- a supercharger according to the present invention could be, for example, no larger than a typical automobile alternator.
- a pump or compressor according to one embodiment of the invention is shown very diagrammatically with its main shaft 100 extending through a housing 1 50 and with a pair of part cylindrical pistons 1 03 mounted on respective rotor shafts 1 04.
- Each piston 103 is mounted within a respective opposed radial cut or part cylindrical recess 1 55 provided in the main shaft 100 and is held in its stationary orientation relative to the axis of the shaft 100 engaging the arcuate surfaces of the recess 1 55 and/or the housing 1 50, with the appropriate working clearances, as the main shaft 1 00 is rotated.
- Figure 1 6 illustrates diagrammatically the positioning of the pistons 1 03 relative to the main shaft 100 through one half of revolution of the main shaft 100. The sequence is illustrated from left to right and from top to bottom in Figure 1 6. It is seen that as each piston 1 03 moves relative to the main shaft 100, from an initial position shown at the top left hand illustration, the volume of fluid on each side of the housing 1 50 introduced through a respective one or more inlets 1 60 will be swept in front of a respective leading face of a piston 103 to exit through a respective one or more exhaust ports 1 61 . A complete revolution of the main shaft 100 will, therefore, result in both sides of the housing 1 50 being swept by a respective piston 103. The pump or compressor is, therefore, displacing its capacity in half a revolution, so that in one revolution, it has displaced twice its capacity.
- FIG. 7 one particular embodiment of the invention is shown diagrammatically in an exploded view with the pistons 103 positioned for rotation with the main shaft 100 and within a housing 1 50.
- One set of exhaust ports 1 61 are shown provided with the inlet ports 1 60 being diametrically opposite and an outlet pipe 200 and an inlet pipe 201 being able to be mounted either side of the housing 1 50.
- a front cover 202 is also shown provided with air flow ports 203, 204.
- a front shaft assembly 205 includes bearings 206 for the respective piston shafts 104 and is provided with appropriate bolt holes 207 to enable the front assembly to be bolted to the centre shaft 1 00.
- FIG. 1 8 the front and side cross-sectional views show the front manifold 208 with the inlet and outlet pipes 201 and 200 and with the back manifold 209 extending around a gear assembly 21 0 with rotor gears 21 1 connected with respective pistons 103 and a main gear 21 2.
- Air seals may suitably be provided in the areas referenced generally by arrow 21 3.
- the piston gears 21 1 mesh with rotating spur gears 21 4 and with a stationary main gear 21 2.
- the gearing connecting the pistons with the main shaft in this and the earlier embodiments is not being used as a drive mechanism but merely to maintain the orientation of the pistons.
- This gearing therefore, ensures that the pistons 103 will, as shown particularly in Figure 1 6, maintain a fixed disposition, substantially horizontal as shown, relative to the housing 1 50, as the main shaft 100 rotates.
- a main bearing is provided for the rear shaft assembly 21 6 and appropriate bearings provided for the shafts associated with the other gears.
- a main bearing 21 5 displaced from its actual position is shown also provided for the front shaft assembly 205 including the drive shaft 21 7.
- the ducting of the inlet and outlet fluid flow paths can be arranged as appropriate, so as to accommodate various types and sizes of engines for example. Where particular ducting and ports are required for a particular type of engine such as a V6 or V8, then the internal ducting of the housing 1 50 and the ducting of the front and back manifolds 208, 209 will be arranged accordingly. Where in the foregoing description, reference has been made to specific components or integers of the invention having known equivalents then such equivalents are herein incorporated as if individually set forth.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NZ504724A NZ504724A (en) | 1997-11-27 | 1998-11-25 | Rotary piston pump or non-reciprocating Otto engine and method of operation |
AU16967/99A AU737023B2 (en) | 1997-11-27 | 1998-11-25 | Rotary piston pump and method of operation |
EP98961704A EP1034374A4 (en) | 1997-11-27 | 1998-11-25 | Rotary piston pump and method of operation |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NZ329274 | 1997-11-27 | ||
NZ32927497 | 1997-11-27 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1999028629A1 true WO1999028629A1 (en) | 1999-06-10 |
Family
ID=19926539
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/NZ1998/000175 WO1999028629A1 (en) | 1997-11-27 | 1998-11-25 | Rotary piston pump and method of operation |
Country Status (6)
Country | Link |
---|---|
EP (1) | EP1034374A4 (en) |
JP (1) | JPH11182201A (en) |
AU (1) | AU737023B2 (en) |
TW (1) | TW362127B (en) |
WO (1) | WO1999028629A1 (en) |
ZA (1) | ZA9810871B (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103452846A (en) * | 2013-10-08 | 2013-12-18 | 李锦上 | Plug rod compressor |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4521785B1 (en) * | 2009-07-30 | 2010-08-11 | 清 野口 | Rotating piston machine |
JP5065532B1 (en) * | 2012-02-10 | 2012-11-07 | 泰朗 横山 | 3 cycle gas fuel engine |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1362686A (en) * | 1972-10-20 | 1974-08-07 | Cheshire Software Ltd | Rotary piston machines |
US4741308A (en) * | 1986-08-15 | 1988-05-03 | Ballinger Michael S | Rotary internal combustion engine and method of operation |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3363606A (en) * | 1965-11-04 | 1968-01-16 | James E. Robertson | Single-rotor type internal combustion engine |
FR1489283A (en) * | 1966-08-04 | 1967-07-21 | Improvements to rotating piston machines |
-
1998
- 1998-04-10 TW TW087105494A patent/TW362127B/en active
- 1998-04-20 JP JP10998998A patent/JPH11182201A/en active Pending
- 1998-11-25 WO PCT/NZ1998/000175 patent/WO1999028629A1/en not_active Application Discontinuation
- 1998-11-25 AU AU16967/99A patent/AU737023B2/en not_active Ceased
- 1998-11-25 EP EP98961704A patent/EP1034374A4/en not_active Withdrawn
- 1998-11-27 ZA ZA9810871A patent/ZA9810871B/en unknown
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1362686A (en) * | 1972-10-20 | 1974-08-07 | Cheshire Software Ltd | Rotary piston machines |
US4741308A (en) * | 1986-08-15 | 1988-05-03 | Ballinger Michael S | Rotary internal combustion engine and method of operation |
Non-Patent Citations (1)
Title |
---|
See also references of EP1034374A4 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103452846A (en) * | 2013-10-08 | 2013-12-18 | 李锦上 | Plug rod compressor |
CN103452846B (en) * | 2013-10-08 | 2016-08-03 | 李锦上 | Plug rod compressor |
Also Published As
Publication number | Publication date |
---|---|
EP1034374A1 (en) | 2000-09-13 |
ZA9810871B (en) | 1999-05-27 |
EP1034374A4 (en) | 2001-01-31 |
AU737023B2 (en) | 2001-08-09 |
AU1696799A (en) | 1999-06-16 |
TW362127B (en) | 1999-06-21 |
JPH11182201A (en) | 1999-07-06 |
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