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WO2003012290A1 - Machine rotative planetaire amelioree utilisant des volutes ajourees et des joints renforces par fibres continues - Google Patents

Machine rotative planetaire amelioree utilisant des volutes ajourees et des joints renforces par fibres continues Download PDF

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Publication number
WO2003012290A1
WO2003012290A1 PCT/US2002/023965 US0223965W WO03012290A1 WO 2003012290 A1 WO2003012290 A1 WO 2003012290A1 US 0223965 W US0223965 W US 0223965W WO 03012290 A1 WO03012290 A1 WO 03012290A1
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WO
WIPO (PCT)
Prior art keywords
rotor
housing
intake
exhaust
ports
Prior art date
Application number
PCT/US2002/023965
Other languages
English (en)
Inventor
David B. Manner
Kevin R. Kirtley
Brooke Schumm, Iii
Original Assignee
Manner David B
Kirtley Kevin R
Brooke Schumm, Iii
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Manner David B, Kirtley Kevin R, Brooke Schumm, Iii filed Critical Manner David B
Publication of WO2003012290A1 publication Critical patent/WO2003012290A1/fr

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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
    • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B2053/005—Wankel engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2244/00—Machines having two pistons
    • F02G2244/50—Double acting piston machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2250/00—Special cycles or special engines
    • F02G2250/03—Brayton cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2270/00—Constructional features
    • F02G2270/10—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • a planetary motion machine which one inventor characterized as: "a rotating piston arrangement where a motor is guided by a gear mechanism meshing with a toothed reaction wheel in such a way that the rotor can move into or out of one or more consecutively following work chambers which accommodate rotor and are in a stationary casing."
  • a planetary motion machine offers the benefit of fewer moving parts than a typical machine using cyclical motion, valves, or conversion from rotary to linear motion or vice versa to exert or receive pressure.
  • a planetary motion machine may be a pump (that is taking in a fluid stream and compressing it to be exhausted at higher pressure), or a turbine (utilizing pressure to drive a rotor circularly to a lower pressure exhaust, and generating rotary mechanical power in a rotating shaft).
  • a planetary motion machine has less eccentric motion than a typical straight piston machine. It has fewer moving parts in part because the machine is inherently a rotary machine and need not convert linear motion to rotary motion. Its disadvantages are that traditionally the classic planetary motion machine has only one compression per rotor cycle, and at high speed, there can be problems maintaining a seal of the compression chambers.
  • a classic planetary motion machine is illustrated in Figure 2.
  • the basic shape of the chamber looking at the chamber from the "top” parallel to the axis of the rotating parts, is that of a symmetric peanut, though the "waist" of the peanut is barely narrowed.
  • the peanut shape is called a peritrochoid in mathematics.
  • the rotor looks like an equilateral triangle with symmetric bulged sides. In essence, the rotor, to use a layperson's description, rolls around in the inside of the peanut with each apex in contact with the peanut. If an engine is placed on the drive shaft of the planetary machine, it will cause the rotor to spin, and the action of an alternating increase and decrease in volumes of the working chambers in combination with alternate occlusion and exposure to intake and exhaust ports will cause fluid to be pumped.
  • pressurized fluid is allowed into a chamber to force the rotor to turn, then the drive shaft will be forced to rotate and will produce mechanical power at the shaft.
  • pressurized fluid is allowed into a chamber to force the rotor to turn, by changing the position of the intake and exhaust ports for a different chamber, that different chamber can be used to compress fluid, effectively permitting the rotary machine to be a compressor and turbine simultaneously.
  • the fluid can be liquid or gas or a combination.
  • the machine in the present invention is a double pumping or double action planetary machine, meaning that for each planetary cycle, the machine can have one chamber perform a function of compression/exhaust or intake/expansion, while another chamber performs another function of either compression/exhaust or intake/expansion, and therefore the cycle of at least one chamber consists of a) two motions of intake/compression/exhaust, b) two motions of intake/expansion/exhaust or c) one action of each of intake/compression/exhaust and intake/expansion/exhaust.
  • the cycle of at least one chamber consists of a) two motions of intake/compression/exhaust, b) two motions of intake/expansion/exhaust or c) one action of each of intake/compression/exhaust and intake/expansion/exhaust.
  • the advantage of the present invention is that a working chamber is nearly totally evacuated from a maximum volume.
  • Whitestone particularly as the geometry of his proposed rotor veered away from the three lobed rotor in a square cavity in Figure 2,
  • Whitestone' s invention faces one of two efficiency difficulties.
  • Whitestone's porting shown in Whitestone '054 Figure 9a, which is the identical rotor position to Whitestone '054 subfigure CF of Figure 13, particularly for a solid rotor which eliminates volume 25f of Figure 9E, shows the traditional geometric difficulty faced by Maillard, United Kingdom (British) Pat. No. 583,035 issued 2 Jan 1947, and prior art rotary pumps of either a) maximizing intake volume for the beginning of compression, but also enlarging the volume being compressed at time of exhaust, as in Whitestone '054, or b) lessening intake volume for the beginning of volume, and lessening the volume being compressed at time of exhaust.
  • An example of the latter is Maillard UK Pat. 583,035 and Juge, U.S. Pat.
  • Non-electric gyroscopes are powered by an air stream that expands through a small turbine that drives the gyroscope. Failure of the pump interrupts the flow of air and causes the gyro to slow down and tumble. Slow or tumbling gyros will deliver incorrect navigational information.
  • a typical pump using sliding vanes made of carbon graphite is seen in Kaatz, 3,191,852, June 29, 1965, and Bishop, U.S. Pat. 5,181,844, Jan. 26, 1993, U.S. Pat. 4,820,140.
  • Apex seals may be kept in close contact with a roughly orthogonal surface using centrifugal force as seen in Kaatz, 3,191,852, June 29, 1965, and Bishop, U.S. Pat. 5,181,844, Jan. 26, 1993, U.S. Pat. 4,820,140, or using a technique of feeding pressured air in behind the vanes as seen in Smart et al, U.S. Pat. 4,804,313, Feb. 14, 1989. Springs can also be used.
  • Optimum self-lubricating materials can be seen in any number of patents using polytetraflouroethylene (PTFE), or better yet using carbon fiber reinforced polyetheretherketone (PEEK), particularly continuous carbon fiber reinforced PEEK.
  • PTFE polytetraflouroethylene
  • PEEK carbon fiber reinforced polyetheretherketone
  • continuous carbon fiber reinforced PEEK is focused on polyetheretherketone, and a close material cousin PEKK, polyetherketoneketone, but the term includes a compound selected from the group of polyaromatic compounds having amorphous crystal structure corresponding in intermolecular distance to the intermolecular distance of continuous carbon graphite crystal structure such that upon melting of said polyaromatic compound having amorphous crystal structure in the presence of continuous fiber carbon graphite, said combination results in carbon crystal lattice reinforcement of said polyaromatic compound.
  • This invention has three major features yielding improved performance.
  • By proper arrangement of the location of the inlet parts, duct and exhaust parts no new moving parts are introduced beyond the classic rotary machine design, yet a double action pump is created with substantially improved compression ratio. If pressured air is delivered to the invention with a differential lower pressure on the "opposite" side of the pump, a double pumping turbine yielding power to a drive shaft results with a favorable compression ratio.
  • a volute is a spiraled air pipe that improves the intake and outflow characteristics when collecting and delivering air to the working volumes of the planetary pump.
  • the volute reduces losses caused by turbulence at sharp corners, elbows, etc. and losses caused by sudden expansion.
  • the invention achieves a variety of objectives by this design.
  • the invention can be a pump when an engine or other rotating device is connected to the machine and causes the rotor to rotate, forcing fluid through the parts of the machine.
  • One preferred use is a vacuum air pump with the drive shaft driven by an airplane engine causing the rotor to turn, which draws air through a gyroscope.
  • the invention may be a turbine when pressurized fluid drives the machine, or an engine when combustible mixture is ignited in the working chambers.
  • the invention will be described in terms of a pump, understanding the claims are no limited to a pump and that if, a pressure differential between the intake and exhaust side of the pump exists, the machine will function as a turbine.
  • the general characteristic of the preferred embodiment is somewhat like a two rotor NSU-- Wankel internal combustion engine found in some automobiles and aircraft except that the preferred embodiment of the invention disclosed herein is in the form of a mechanically driven pump which delivers air to or from air-driven gyroscopic attitude instruments for piston engine powered aircraft.
  • the pump is composed of a forward stationary side plate with mounting fixture, a two-lobe peanut-shaped peritrochoid stator shroud within which rotates a three-face triangular-shaped rotor, a port plate with intake and exhaust orifices, a volute for ducting the air to and from the external pump connections and the working volumes, a second port plate, stator and rotor combination, followed by a rear stationary side plate.
  • the entire unit is held together by four symmetrically placed bolts.
  • the center of each cam is displaced eccentrically from the center of the driving shaft.
  • Each cam rotates within a hole machined into the center of each rotor and drives, in the preferred embodiment, continuous carbon fiber reinforced PEEK bearings fit into each rotor, which action in turn causes rotor rotation as later described. While reference is made to PEEK in the preferred embodiment, PEKK (polyetherketoneketone) has similar properties.
  • the invention preferably utilizes for either the bearings and/or or the rotor apex tips as described a compound selected from the group of polyaromatic compounds having amorphous crystal structure corresponding in intermolecular distance to the intermolecular distance of continuous carbon graphite crystal structure such that upon melting of said polyaromatic compound having amorphous crystal structure in the presence of continuous fiber carbon graphite, said combination results in carbon crystal lattice reinforcement of said polyaromatic compound. Enhancements to strength and lubrosity occur upon curing, including curing under pressure. Such compound, including PEEK and PEKK, achieving carbon crystal lattice reinforcement in such manner will be referred to a continuous carbon fiber reinforced polyaromatic compound.
  • continuous carbon fiber reinforced polyaromatic compounds as defined, and those elastomer reinforced polymeric compositions referenced in Davies, U.S. Pat. No. 5,750,620, will be referred to collectively as carbon fiber reinforced polymeric compositions.
  • Materials such as scintered bronze impregnated with PTFE along with carbon fiber reinforced polymeric compositions, or even hydrocarbons in certain applications, will be the broadest category of suitable materials and will collectively be called self-lubricating materials. All of these may be used, but the optimum selection for use is a continuous carbon fiber reinforced polyaromatic compound such as continuous carbon fiber reinforced PEEK.
  • the preferred embodiment of each rotor has three apices, and therefore three faces corresponding to the number of apices.
  • Each set of two adjacent apices and the intervening face can be referred to generically as a lobe and will have a working chamber of varying volume opposite that lobe which will be moving rotationally and varying volume simultaneously.
  • the rotor is composed of hardened aluminum, e.g., 6061-T6 and machined to the desired contour of three triangularly placed arcs.
  • Each of the three faces of said rotor is penetrated by one of the important innovations of the claimed invention: namely a single duct machined or molded through the rotor face which pierces the side of the rotor which is orthogonal to the face. The duct then forms an aperture through which air flows undisturbed when both ends are not obstructed.
  • the rotor also contains an annular timing gear affixed to either side.
  • This annular gear meshes with a stationary sun or spur gear fixed to the non- rotating forward and rear side plates of the pump and constrains the rotor motion to the desired planetary cycle, much like the Wankel design (The gears could be replaced by a guide similar to Grey's invention U.S. Patent No. 3,884,600, May 20, 1975.
  • each apex of the rotor is machined with a groove to accept an apex seal.
  • the apex seal is a rectangular strip composed of a self-lubricating continuous carbon fiber reinforced PEEK material. The apex seal can be pressed against the shroud by way of compression springs.
  • the spring constant and the amount of compression are chosen such that the mechanical properties of the PEEK apex seals are not exceeded.
  • the apex seal forms a zero clearance sliding contact point with the stationary peritrochoid shroud which guarantees that each working volume defined by each rotor face operates independently with minimal exchange of air.
  • the apex seal can be pressed alternatively or additionally against the shroud by means of compressed air fed in behind the apex seal in the manner suggested by Smart, U.S. Pat. 4,616,985, Oct. 14, 1986, again such a way that the mechanical properties of the PEEK apex seals are not exceeded. Smart proposes that air be fed in behind the sliding vanes in his pump for purpose of equalizing pressure.
  • the peritrochoid shrouds are made of hardened aluminum like 6061-T6, preferably with hard- coat anodizing, and with the next-described side plates form the cavity within which each rotor rotates.
  • the peritrochoid shroud and rotor lie between two side plates, either of which may be ported, but for purposes of the best mode, one of which is a port plate and the other an unported side plate. There can be two port plates as an alternative.
  • the side plates are disposed in conjunction with the shroud such that the side plates are in sliding contact with the rotor.
  • the side plates on which are disposed the stationary sun gears are also made of aluminum and mate with the peritrochoidal shrouds.
  • the side plates could be made of or coated with a self-lubricating material such as PEEK, particularly where there is relatively high speed relative motion between the side plates and the rotor.
  • the side housing could be of PEEK, but this is a less desirable equivalent than the vanes being made of PEEK which are much smaller, and the side housing not being made of PEEK.
  • the sun gears, peritrochoidal shrouds, annular gears and rotors are specifically oriented such the planetary motion of the rotor apices is exactly contained by the shroud.
  • the side plates, including the port plate(s) can be made from continuous carbon fiber reinforced PEEK similar to the apex seal material.
  • the port plates which contain two intake ports symmetrically placed about the central axis coincident with the driving shaft and the shroud longitudinal center line and two exhaust ports also symmetrically placed about the central axis.
  • the intake and exhaust ports are of sufficient cross sectional area that the air flow will not choke (reach Mach 1) during normal operation which would reduce performance.
  • the position of the ports is determined to maximize the flow rate performance but generally, in a pump where the fluid will be exhausted from a working chamber and out through a duct in the rotor face to an exhaust port in the side plate, the intake port on a side plate is positioned and configured in such a way that:
  • the intake port is covered by the rotor side at all times except between the "intake port open” and the “intake port closed” rotor position at which time there exists an unobstructed path for air to flow from the intake volute to the working volume formed by the shroud, the side plates, and the rotor face exposed to the intake port.
  • the ports in this configuration are located inside the outer bound of the rotor, but outside the innermost trace of the face of rotor during the rotation cycle.
  • the "intake port open” rotor position is that rotor position where the working volume is near its minimum and the exhaust port is closed or occluded.
  • the "intake port closed” rotor position is that rotor position where the working volume is near its maximum and the exhaust port is closed or occluded.
  • the exhaust port is positioned and configured in such a way that:
  • the exhaust port is aligned with the rotor side aperture formed by the claimed invention of a duct piercing the rotor face previously exposed to the intake port.
  • the alignment is such that an unobstructed path is formed for air to flow from the working volume to the exhaust volute and subsequently out of the device entirely.
  • the "exhaust port open" rotor position is a position after the working volume is near its maximum and the intake port is closed, and some contraction of the working volume has occurred so that the desired pressure is created.
  • each port plate covers one side of the volute.
  • Each side of the volute contains two scroll-like channels which direct air to the two intake ports and from the two exhaust ports.
  • Each volute channel provides an unobstructed, smooth conduit from the ports to the external connections of the pump.
  • the volute is machined from aluminum and also contains a centrally located longitudinal hole through which the driving shaft rotates.
  • the driving shaft can be supported here too by means of a self-lubricating bearing fit into the volute piece.
  • the intake port is uncovered by the rotor side exposing the minimum working volume and a trailing rotor face to the intake volute.
  • the rotor rotation produces an expanding volume which in turn produces a lower-than-inlet pressure which pulls air into the working volume through the intake volute. Air ceases to flow into working volume as the intake port is occluded by the rotor side prior to the working chamber volume contraction due to rotor rotation. As rotor rotation continues, the air is compressed in a now fully enclosed working chamber until the "exhaust port open" position when a clear path forms from the working volume to the exhaust port via the duct from the rotor face to the rotor side.
  • Air continues to flow out of the contracting volume tlirough the duct and into the exhaust volute until the "exhaust port closed" position is reached.
  • This sequence also occurs in the second lobe of the peritrochoid shroud, albeit out of phase. Since the apex seals and side plates produce nearly zero clearance or actually zero clearance, there is little flow communication between the two lobes.
  • the intake and exhaust ports can be utilized or be occluded based on maximizing volumetric efficiency rather than observing the geometric constraints found in the Maillard, United Kingdom Pat No. 583,035, 2 Jan 1947 and Schwab, U.S. Pat. 4,551,073, Nov. 5, 1985 designs.
  • the intake ports instead of being in the side plates, could be in the shroud, but the volumetric efficiency of the machine is significantly less.
  • the turbine can accept fluid to an expanding chamber immediately after minimal volume is achieved, cease accepting fluid to that chamber at maximum volume or in desired quantity, and have the chamber commence access to an exhaust port after an intake port is occluded, and after maximum volume has been achieved. Exhaustion of a chamber can continue until just before an apical tip is at a position where minimal volume is achieved.
  • the system can be a two rotor system which is statically balanced, and/or counterweights or cams may be added for dynamic balance.
  • each lobe must have its own separate exhaust duct and port; the above description of porting locations applies for each chamber, but to separate the exhaust streams, there must be more planning of the relative location of the exhaust ducts.
  • Each duct must intersect the rotor side on a separate peritrochoidal track so that a particular duct only vents to a particular track. If a volute is desired, a volute for each duct and its corresponding track must be created. There is no requirement in the invention that the duct through the rotor face be used for exhaust.
  • the construct of the planetary machine may be inverted.
  • the intake ports may be designed to be covered by the rotor side at all times, and located to be alternately exposed to an intake duct from the rotor side to the rotor face to a working chamber, with the exhaust ports alternately exposed to the working chamber when the intake ports are not exposed to the duct to the working chamber.
  • the invention has superior wear properties as a result of the continuous carbon fiber reinforced PEEK used.
  • Intake and exhaust ducts may be used carry fluid to or from intake and exhaust ports, rather than having ports opening during parts of the cycle directly to a working chamber. In this mode of invention, all ports will then be located inside the innermost trace in each chamber of the face of the rotating rotor.
  • the rotary machine can be set up by appropriate porting to be a pump and turbine, meaning one working chamber is pumping (intake from lower pressure and exhaust at higher pressure), while another is acting as a turbine (intake from higher pressure and exhaust at lower pressure).
  • the pumping side will have an early close of intake in the rotor face motion for the working chamber acting as a pump and later opening and closing of exhaust, while the turbine side will have a relatively later close of intake in the rotor face motion for the working chamber acting as a turbine and later opening and closing of exhaust.
  • the separation of the exhaust streams are separated, and, the intake streams are separated, there can be independent inputs and outputs for each respective working volume for specialized applications.
  • the intake and exhaust ports for one chamber can each have their own fluid source and exhaust outlet, and the intake and exhaust ports for an opposite chamber can each have their own fluid source and exhaust outlet.
  • one "side" or chamber can be acting as a compressor, with the other side acting as a turbine using the same previously- described principles for locating ports to achieve these effects.
  • the equations which describe the shape of the peritrochoid and the faces of the rotor are well developed in the open literature, Kenichi Yamamoto, Rotary Engine, Sankaido Co. Ltd. (1 st ed. 1981), therefore only the results as they pertain to this embodiment are presented.
  • the shape of the peritrochoid can be represented in orthogonal coordinates x and y by:
  • a is the position angle of the main driving shaft and generates periodic motion every 1080 degrees of driving shaft rotation
  • e is the eccentricity, meaning the amount the rotor axis is displaced from the driving axis
  • R is the radius of the rotor, meaning the distance from the rotor axis to the rotor apex.
  • FIG. 1 A generic rotor with the features of the present invention utilized as a pump is presented in FIG. 1.
  • the letter “A” denominates the depiction of the aperture through the rotor with its entrance on the rotor face "B,” and the aperture's exit on the rotor side opposite to the point indicated by the letter “D” in this embodiment of the invention.
  • the letter “C” indicates the journal bearing hole into which an eccentric drive shaft (normally made eccentric by a cam) is placed which provides power to the rotor.
  • FIG. 2 illustrates the locations of the typical intake ports and exhaust ports within the peritrochoid shape.
  • the intake ports must at least intermittently be within the outer bounds of the trace of the rotor face, and at least intermittently outside the interior trace of the rotor face.
  • FIG. 3 displays four positions of the rotor with the intake and exhaust ports and the manifold of apertures (three) overlaid.
  • working volume A which is defined by the housing and rotor face A, is beginning the intake stroke as the intake port I is just starting to be uncovered.
  • the exhaust duct adjacent to the rotor face conesponding to working volume A is not juxtaposed to the exhaust port so as working volume A expands, fluid will be admitted at the ambient pressure at the intake port.
  • working volume B is in the midst of a compression and exhaust stroke as a clear path exists from volume B to the exhaust port E via the aperture and duct through the rotor.
  • Volumes A and B are sealed from each other by a zero clearance apex seal and the rotor being placed sealingly adjacent to the side plate of the pump.
  • volume C is completing its intake stroke as the working volume is near maximum and intake port I is beginning to be occluded as the rotor side slides over it.
  • working volume A is midway through its intake stroke.
  • the working volume B is completing its compression and exhaust stroke.
  • Working volume C is just beginning its compression stroke with the exhaust port just beginning to be exposed to the exhaust duct through the rotor.
  • working volume A is near maximum volume and the intake port is now blocked by the rotor side.
  • Working volume B is still expanding and the rotor side has just begun to close off the intake port adjacent to rotor face adjacent to working volume B while working volume C is nearing its minimum volume point.
  • the invention allows the designer to guarantee that the exhaust port is not open while the intake port is open so timing can be completely optimized for maximum performance.
  • working volume A is midway through its compression and exhaust stroke.
  • the intake port is almost occluded by the rotor side as to working volume B while the exhaust port is not yet exposed to working chamber B.
  • the rotor side adjacent to working volume C is just uncovering the intake port and the expanding volume admits air from the intake volute.
  • volute FIG. 4 in the top half, displays a simple representation of the separated flow, with its potential for large fluid dynamic loss encountered in a poorly designed plenum.
  • the largest loss occurs as high speed flow from the working volumes of the pump diffuses rapidly to a nearly quiescent state within a plenum. This high loss flow is then accelerated into the external connection of the pump increasing the loss further.
  • a large degree of turning over a short distance produces a large loss when streamlines turn away from the mainstream in a diffusing action.
  • these loss mechanisms can be effectively attenuated.
  • a passage with these properties will appear as a scroll-like volute channel.
  • the exhaust volute starts with a cross sectional area which is equal to the area of the aperture cut through the rotor face and is smoothly varied to the area of the conduit which carries the fluid from the pump unit.
  • the rate at which the cross sectional area varies is set below a critical value where fluid dynamic energy loss from diffusion increases rapidly.
  • the alignment of the exhaust volute is coincident with the alignment of the aperture when the exhaust port is open and turns to parallel to the exiting conduit. By maintaining proper alignment, the exiting air will not need to turn sharply thereby promoting smooth flow with a commensurate reduction in pressure loss and secondary flow action.
  • FIG. 5 shows a cross section along the line of the driving shaft. Description of the mechanical parts A description of the interrelationship of the parts is as follows referring to the numbers in FIGURE 5:
  • the driving shaft (1) transmits the mechanical power from an engine to the pump.
  • the shaft is supported by at least two bearings (2) composed of any self-lubricating material such as PEEK or PTFE or scintered bronze impregnated with lubricant.
  • the bearings are set in the side plate (4).
  • Fixed to the driving shaft are two cams (5) which ride inside continuous carbon reinforced PEEK bearings fit into each rotor and which drive the rotor rotation.
  • Each rotor (6) has three-lobes with the claimed invention of an aperture (7) connecting each rotor face with the rotor side.
  • Each apex of each rotor contains the claimed invention of an apex seal composed of continuous carbon fiber reinforced PEEK (8).
  • the apex seals are in sliding contact with a two-lobe peritrochoid shroud (9) and forced against the shroud by means of small compression springs.
  • the planetary motion of the rotor is maintained by an annular gear (10) fixed to each rotor by means of screws or pins and a stationary sun gear (11) fixed to the side plate by means of screws.
  • the working volumes of the pump (12) are then formed by the rotor face and the side plates composed of continuous carbon fiber reinforced PEEK (13) and (14).
  • the inner-most side plates (14) contain the intake and exhaust ports (15) and (16), respectively.
  • the intake and exhaust ports expose portions of the claimed invention of intake and exhaust volutes (17) which deliver and collect air from the working volumes to and from the separate intake and exhaust external pump connections (18).
  • the entire unit is held together by means of bolts symmetrically placed about the driving shaft and parallel to it.
  • the external connections of the invention pump mate with threaded pipe connectors which are attached to flexible hoses. These hoses are connected to filters, regulators, and other devices used in fluid transfer and flow. If used on an aircraft, such hoses would be ultimately attached to the gyroscopic instruments fixed to the aircraft.
  • One added benefit of the preferred embodiment is that, in using low friction, high flexural strength continuous carbon fiber reinforced PEEK seals and side plates, the potential for catastrophic failure of the unit is minimized. The likely failure mode is a detectable, graceful degradation which perceptive pilots will recognize early as a small pressure drop across the gyroscopic instruments indicating low flow rate.
  • the invention has other advantages as a result of the thermodynamic and kinetic effects of the fluid being handled and the arrangement and shape of the ports.
  • the ports may be varied to avoid, or to encourage "choking", where fluid speed has reached Mach 1, and to smooth or vary the characteristics of fluid flow through the machine.
  • Those reasonably skilled in the art will recognize that because of kinetic and thermodynamic effects, there are alternate modes available for operation, and while the working chamber is expanding, there could in fact be a short interval of compression, and conversely, while the working chamber is contracting, there could in fact be a short interval of expansion.
  • the invention does not link the entire compression phase with contraction of the working chamber, nor does the invention link the entire expansion phase with increase in volume of the working chamber. Rather, three fluid action phases are referred to.
  • the arbitrarily selected first phase is the expansion phase which would include an intake phase and a compression phase which would include an exhaust phase, and an interphase at which there would be no intake or exhaust.
  • ducts through the rotor that enable fluid pressure to be applied behind sliding apical tips or springs behind sliding apical tips if greater pressure of the apical tips against the side housing is desired.
  • Another mode of the invention particularly useful where it is important to separate fluid streams flowing through the planetary machine uses independently "tracked" exhaust and intake ducts for each vane face.
  • the pump yields a novel feature of double pumping of three separate streams of fluid. While all ports could be on one side of the rotor and the six tracks can be fit to correspond to the intake and exhaust porting arrangement, it is easier to have one side be the intake side and the other the exhaust side.
  • the chamber can be foreclosed from the intake or exhaust duct for that face communicating with any ambient fluid.
  • the exhaust duct can communicate with the exhaust track corresponding to the exhaust port, and as the chamber contracts to minimal volume, the fluid inside the working chamber corresponding to the first vane face is exhausted.
  • the second face will be ready to turn again to the compression and exhaust phases.
  • the invention as described is particularly useful for external combustion engines, including Stirling and Ericsson cycle engines, because the planetary pump converts heat energy to rotational work in a simple mechanism in the expansion phase of the working chamber.
  • the volumetric characteristics of this planetary machine are such that combined with a tandem and like machine, the machines cooperating together can have a corresponding working chamber working in tandem such that the sum of the volumes of working chamber 1 in the first machine plus an arbitrarily selected working chamber 1 in the second machine can be set to be a virtual constant.
  • the invention also enables effective sealing because of the PEEK and more precise machining and cam function the lack of which effective parts has been the traditional impediment to utilizing a planetary machine for an external combustion cycle machine.
  • a side plate in a sense has a groove for each track with the grooves being "open" to the ports at the necessary times of the cycle.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Hydraulic Motors (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Des ouvertures (A) pratiquées à travers chaque face (B) d'un rotor planétaire, des volutes (17) servant à effectuer une alimentation en liquide avec des pertes limitées et un recueil de ces liquides entre les volumes de travail d'une pompe rotative planétaire, d'un compresseur ou d'une turbine et des joints sans jeu en polyétheréthercétone (PEEK) renforcé par des fibres de carbone continues ou d'autres matériaux autolubrifiants améliorent considérablement le débit volumétrique de ces pompes, compresseurs ou turbines rotatifs. Des moyens servant à ventiler chaque volume de travail vers un orifice d'admission (15) ou d'échappement (16) dans des positions arbitraires du rotor, des ouvertures reliant ces volumes de travail aux orifices d'admission ou d'échappement permettent à chaque volume de travail d'une pompe rotative planétaire multilobe de fonctionner de façon indépendante avec une efficacité volumétrique proche du maximum. Des moyens supplémentaires consistant en des volutes hélicoïdales effectuent le recueil du débit d'admission et d'échappement de chaque volume de travail, ainsi que l'alimentation en ce débit, de manière à limiter la perte dynamique du liquide associée aux dilatations et contractions soudaines apparaissant à l'entrée et à la sortie du plénum.
PCT/US2002/023965 2001-07-27 2002-07-29 Machine rotative planetaire amelioree utilisant des volutes ajourees et des joints renforces par fibres continues WO2003012290A1 (fr)

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US30841301P 2001-07-27 2001-07-27
US60/308,413 2001-07-27

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PCT/US2002/023966 WO2003012257A1 (fr) 2001-07-27 2002-07-29 Machine stirling mettant en application un systeme planetaire double action

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CN109159124A (zh) * 2018-09-17 2019-01-08 浙江工业大学 采用快速双幂次终态神经网络的冗余机器人重复运动规划方法

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CZ297785B6 (cs) * 2003-04-01 2007-03-28 Zpusob a zarízení pro premenu tepelné energie na mechanickou
FR2935155B1 (fr) * 2008-08-22 2012-04-20 Sycomoreen Machines a piston rotatif annulaire trilobique avec cycles thermodynamiques de stirling
UA119134C2 (uk) 2012-08-08 2019-05-10 Аарон Фьюстел Роторні пристрої з розширюваними камерами, що мають регульовані проходи для робочого плинного середовища, а також системи, що мають такі пристрої

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US3762842A (en) * 1969-07-03 1973-10-02 L George Expansible fluid rotary engine
US3860365A (en) * 1973-05-03 1975-01-14 William H Bibbens Seals and methods and means of sealing for rotary engines and the like
US4345885A (en) * 1980-03-03 1982-08-24 Briggs & Stratton Corporation Lubrication system for rotary-trochoidal engines
US5305721A (en) * 1989-06-29 1994-04-26 Burtis Wilson A Rotary Wankel type engine

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US5211017A (en) * 1990-09-19 1993-05-18 Pavo Pusic External combustion rotary engine
US5335497A (en) * 1993-02-10 1994-08-09 Macomber Bennie D Rotary Stirling cycle engine

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US3424135A (en) * 1966-02-23 1969-01-28 Yanmar Diesel Engine Co Suction device for rotary piston internal combustion engine
US3762842A (en) * 1969-07-03 1973-10-02 L George Expansible fluid rotary engine
US3860365A (en) * 1973-05-03 1975-01-14 William H Bibbens Seals and methods and means of sealing for rotary engines and the like
US4345885A (en) * 1980-03-03 1982-08-24 Briggs & Stratton Corporation Lubrication system for rotary-trochoidal engines
US5305721A (en) * 1989-06-29 1994-04-26 Burtis Wilson A Rotary Wankel type engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109159124A (zh) * 2018-09-17 2019-01-08 浙江工业大学 采用快速双幂次终态神经网络的冗余机器人重复运动规划方法

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