US20130071280A1

US20130071280A1 - Slurry Pump

Info

Publication number: US20130071280A1
Application number: US13/535,355
Authority: US
Inventors: James Brent Klassen
Original assignee: Individual
Current assignee: Genesis Advanced Technology Inc
Priority date: 2011-06-27
Filing date: 2012-06-27
Publication date: 2013-03-21

Abstract

A fluid transfer device, comprising an outer housing having an inward facing cylindrical or partially cylindrical surface, an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis, a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor; an inner rotor secured for rotation about an axis within the carrier, the inner rotor having an outward facing surface plane perpendicular to the inner rotor axis and outward projections arranged around the outward facing surface configured to operate as a pump.

Description

BACKGROUND

A new pump design uses the same sealing geometry as in U.S. Pat. No. 7,111,606 with some important modifications.

SUMMARY

In various embodiments, there may be included any one or more of the following features:
A pump, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface.
an outer rotor with radial inward projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
an inner rotor secured for rotation about an axis within the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface;
the inward projections projecting inward and the outward projections projecting outward to mesh with each other and define variable volume chambers between the inward projections and the outward projections as the inner rotor rotates within the carrier;
the outward projections each having a leading edge and trailing edge;
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers; and
the outer rotor is connected to be driven with a rotary shaft input, and convex trailing contact surfaces of the outward projections of the inner rotor contact the leading contact surfaces of the inward projections, the leading surface of each inner rotor outward projection does not seal and can be any shape as long as it prevents the rotors from locking up when the pump is freespinning or backturning.
A pump, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface.
an outer rotor with radial inward projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured for rotation at least partly within the outer housing;
an inner rotor secured for rotation about an axis within the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface;
the inward projections projecting inward and the outward projections projecting outward to mesh with each other and define variable volume chambers between the inward projections and the outward projections as the inner rotor rotates within the carrier;
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers; and
other advantages of driving the outer rotor include the ability to drive subsequent stages with a drive shaft that extends from both ends of one or more outer rotors to drive multiple similarly constructed outer rotors, coaxial stator shaft through the center of the drive shaft would be supported (at the opposite end from the drive shaft input) to the pump casing and would prevent the inner rotor housings from spinning
A pump, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface.
an outer rotor with radial inward projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured for rotation at least partly within the outer housing;
an inner rotor secured for rotation about an axis within the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface;
the inward projections projecting inward and the outward projections projecting outward to mesh with each other and define variable volume chambers between the inward projections and the outward projections as the inner rotor rotates within the carrier;
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers; and
in one configuration of the pump, it is designed to handle the admission and pumping of breakable solids such as but not limited to methane hydrate ice crystals, it does this with a combination of features such as sharp leading edges on spinning components and sharp trailing edges on stationary components which will slice the ice as it flows into and through the pump. It is also designed to minimized areas where ice could become wedged and restrict the flow by using increasing cross sections along the flow path.
A pump, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface.
an outer rotor with radial inward projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured for rotation at least partly within the outer housing;
an inner rotor secured for rotation about an axis within the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface;
the inward projections projecting inward and the outward projections projecting outward to mesh with each other and define variable volume chambers between the inward projections and the outward projections as the inner rotor rotates within the carrier;
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers; and
by providing fluid pressure to the outlet port of the pump configuration described above and shown in the drawings, the device can also be used in reverse rotation as a hydraulic motor. In this case, the leading convex edges of the inner rotor feet contact the flat or substantially flat trailing surface of the outer rotor which drives the output shaft.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface.
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor;
an inner rotor secured for rotation about an axis within the carrier, the inner rotor having an outward facing surface plane perpendicular to the inner rotor axis and outward projections arranged around the outward facing surface, and a trailing convex surface on each outward projection, the leading face of the radial projections and the trailing convex face of the outward projections mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections each having a leading edge and trailing edge;
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers.
Method of using a pump of any preceding claim in which the pump is ideally suited to pump gases entrapped in a compressible fluid as follows: Gas bubbles that enter the pump are centrifuged to the innermost area of each outer rotor cylinder chamber; When the inner rotor foot rapidly enters the chamber in the discharge port zone, it will create an acceleration force on the fluid which is in the opposite direction of the centrifugal force on the fluid up to that point; This causes the higher density fluid to swap radial positions with at least some of the entrained gas, effectively pushing a bubble of gas out ahead of (radially outward from) the fluid as it exits the rotating chamber. The flow reliefs on the inner rotor are shown as being on the bottom but may be top, bottom or center.
A gas compatible design as described above, in which the rotational axis is preferably (but not necessarily) vertical and the inner rotor has a flow relief (which exists between the trailing convex contact surfaces of each subsequent inner rotor foot) only on the bottom of the inner rotor so gravity can bias the higher density liquid to the bottom of the chamber and the gas to the top of the rotating chamber as it moves from the input to the output area of the pump; the top sealing surface of the inner rotor is therefore more adequately sealed against gas leakage (by virtue of it spanning a greater circumferential span of the chamber) and is capable of pushing at least part of the entrained gas out of each chamber during each rotation.
A fluid transfer device, in which in the case of entrained gas, it is preferable to not push all of the gas out of the chamber at once, this will reduce input torque and pressure variations for smoother operation and longer service life.
A fluid transfer device, in which the pump is also ideally suited to pump grit such as sand. In this case, the port leading up to a pumping stage is preferably curved along an arced or helical path to centrifuge the heavier sand to the outer surface of the flow path. The will bias the higher density sand and/or other abrasives away from the intake rotor sliding interaction with the outer rotor. The sand then travels around the outer perimeter of the casing and cylinder volume to the discharge port where centripetal force ejects and biases it away from the rotor sliding interaction. The multiple seal of the cylinder wall outer surfaces and casing wall inner surface allows the perimeter area (where the sand will be sliding) to have a larger gap clearance while still preventing high leakage rates.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor;
an inner rotor secured for rotation about an axis within the carrier, the inner rotor having an outward facing surface plane perpendicular to the inner rotor axis and outward projections arranged around the outward facing surface, and a trailing convex surface on each outward projection, the leading face of the radial projections and the trailing convex face of the outward projections mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections each having a leading edge and trailing edge;
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the radius of the trailing convex surface on the inner rotor is substantially equal to the offset distance of the leading face of the radial projections on the outer rotor from the radial line form the axis of the outer rotor.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor;
an inner rotor secured for rotation about an axis within the carrier, the inner rotor having an outward facing surface plane perpendicular to the inner rotor axis and outward projections arranged around the outward facing surface, and a trailing convex surface on each outward projection, the leading face of the radial projections and the trailing convex face of the outward projections mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance than the trailing surface such that fluid pressure is allowed to communicate with the chamber ahead of it.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a partially cylindrical inward facing surface;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, and a trailing convex surface on each outward projection, the leading face of the radial projections and the trailing convex face of the outward projections mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance than the trailing surface such that fluid pressure is allowed to communicate with the chamber ahead of it, and the outer cylindrical surface of each projection of the inner rotor is substantially cylindrical and in sealing proximity to the inward facing cylindrical surface of the carrier for part of the rotation, and the rotational power to the device is input to the outer rotor.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a inward facing surface that is at least partially circular along any plane perpendicular to the inner rotor axis;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, and a trailing convex surface on each outward projection, the leading face of the radial projections and the trailing convex face of the outward projections mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance than the trailing surface such that fluid pressure is allowed to communicate with the chamber ahead of it up to the contact between the trailing convex surface of the preceding inner rotor projection contact with the leading offset radial surface of the preceding radial projection of the outer rotor;
and the outer surface of each projection of the inner rotor is at least partially substantially circular along any plane perpendicular to the center axis of the inner rotor and in sealing proximity to the inward facing surface of the carrier for part of the rotation, and the carrier is secured from radial movement by a shaft which is coaxial with the outer rotor rotational axis and a bearing between the carrier shaft and the outer rotor. [0079]
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a inward facing surface that is at least partially circular along any plane perpendicular to the inner rotor axis;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, and a trailing convex surface on each outward projection, the leading face of the radial projections and the trailing convex face of the outward projections mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance than the trailing surface such that fluid pressure is allowed to communicate with the chamber ahead of it up to the contact between the trailing convex surface of the preceding inner rotor projection contact with the leading offset radial surface of the preceding radial projection of the outer rotor;
the outer surface of each projection of the inner rotor is at least partially substantially circular along any plane perpendicular to the center axis of the inner rotor and in sealing proximity to the inward facing surface of the carrier for part of the rotation, and the carrier is secured from radial movement by a shaft which is coaxial with the outer rotor rotational axis and a bearing between the carrier shaft and the outer rotor, and the rotational power to the device is input to the outer rotor.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a partially cylindrical inward facing surface;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, the outward projections each having a cylindrical outward facing surface and a trailing convex surface, the leading face of the radial projections on the outer rotor and the trailing convex face of the outward projections on the inner rotor mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance and/or a relieved area proximal to the trailing face of the outer rotor radial projection preceding it such that fluid pressure in that chamber is allowed to at least partially equalize with the fluid pressure in the chamber preceding it between the outward and trailing surfaces of the preceding inner rotor projection and the forward facing face of the preceding outer rotor radial projection up to the contact between the trailing convex surface of the preceding inner rotor projection and the leading offset radial surface of the preceding outer rotor projection, and the outer cylindrical surface of each projection of the inner rotor is in sealing proximity to the inward facing cylindrical surface of the carrier for part of the inner rotor rotation.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a partially cylindrical inward facing surface;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, the outward projections each having a cylindrical outward facing surface and a trailing convex surface, the leading face of the radial projections on the outer rotor and the trailing convex face of the outward projections on the inner rotor mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance and/or a relieved area proximal to the trailing face of the outer rotor radial projection preceding it such that fluid pressure in that chamber is allowed to at least partially equalize with the fluid pressure in the chamber preceding it between the outward and trailing surfaces of the preceding inner rotor projection and the forward facing face of the preceding outer rotor radial projection up to the contact between the trailing convex surface of the preceding inner rotor projection and the leading offset radial surface of the preceding outer rotor projection, and the outer cylindrical surface of each projection of the inner rotor is in sealing proximity to the inward facing cylindrical surface of the carrier for part of the inner rotor rotation and the rotational power to the device is input to the outer rotor.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a partially cylindrical inward facing surface;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, the outward projections each having a cylindrical outward facing surface and a trailing convex surface, the leading face of the radial projections on the outer rotor and the trailing convex face of the outward projections on the inner rotor mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance and/or a relieved area proximal to the trailing face of the outer rotor radial projection preceding it such that fluid pressure in that chamber is allowed to at least partially equalize with the fluid pressure in the chamber preceding it between the outward and trailing surfaces of the preceding inner rotor projection and the forward facing face of the preceding outer rotor radial projection up to the contact between the trailing convex surface of the preceding inner rotor projection and the leading offset radial surface of the preceding outer rotor projection, and the outer cylindrical surface of each projection of the inner rotor is in sealing proximity to the inward facing cylindrical surface of the carrier for part of the inner rotor rotation and the rotational power to the device is input to the outer rotor, and the sealed chamber is partially defined by planar side faces of the outer rotor.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a partially cylindrical inward facing surface;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, the outward projections each having a cylindrical outward facing surface and a trailing convex surface, the leading face of the radial projections on the outer rotor and the trailing convex face of the outward projections on the inner rotor mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance and/or a relieved area proximal to the trailing face of the outer rotor radial projection preceding it such that fluid pressure in that chamber is allowed to at least partially equalize with the fluid pressure in the chamber preceding it between the outward and trailing surfaces of the preceding inner rotor projection and the forward facing face of the preceding outer rotor radial projection up to the contact between the trailing convex surface of the preceding inner rotor projection and the leading offset radial surface of the preceding outer rotor projection, and the outer cylindrical surface of each projection of the inner rotor is in sealing proximity to the inward facing cylindrical surface of the carrier for part of the inner rotor rotation and the rotational power to the device is input to the outer rotor and the sealed chamber is partially defined by a planar side face of the outer housing.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;.
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a partially cylindrical inward facing surface;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, the outward projections each having a cylindrical outward facing surface and a trailing convex surface, the leading face of the radial projections on the outer rotor and the trailing convex face of the outward projections on the inner rotor mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance and/or a relieved area proximal to the trailing face of the outer rotor radial projection preceding it such that fluid pressure in that chamber is allowed to at least partially equalize with the fluid pressure in the chamber preceding it between the outward and trailing surfaces of the preceding inner rotor projection and the forward facing face of the preceding outer rotor radial projection up to the contact between the trailing convex surface of the preceding inner rotor projection and the leading offset radial surface of the preceding outer rotor projection, and the outer cylindrical surface of each projection of the inner rotor is in sealing proximity to the inward facing cylindrical surface of the carrier for part of the inner rotor rotation and the rotational power to the device is input to the outer rotor and the sealed chamber is partially defined by a planar side face of the outer rotor perpendicular to the axis of the outer rotor and a planar face of the perpendicular to the axis of the outer rotor.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a partially cylindrical inward facing surface;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, the outward projections each having a cylindrical outward facing surface and a trailing convex surface, the leading face of the radial projections on the outer rotor and the trailing convex face of the outward projections on the inner rotor mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance and/or a relieved area proximal to the trailing face of the outer rotor radial projection preceding it such that fluid pressure in that chamber is allowed to at least partially equalize with the fluid pressure in the chamber preceding it between the outward and trailing surfaces of the preceding inner rotor projection and the forward facing face of the preceding outer rotor radial projection up to the contact between the trailing convex surface of the preceding inner rotor projection and the leading offset radial surface of the preceding outer rotor projection, and the outer cylindrical surface of each projection of the inner rotor is in sealing proximity to the inward facing cylindrical surface of the carrier for part of the inner rotor rotation and the rotational power to the device is input to the outer rotor and the sealed chamber is partially defined by a planar side face of the outer housing, and the outer rotor is supported for rotation at both axial ends.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a partially cylindrical inward facing surface;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, the outward projections each having a cylindrical outward facing surface and a trailing convex surface, the leading face of the radial projections on the outer rotor and the trailing convex face of the outward projections on the inner rotor mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance and/or a relieved area proximal to the trailing face of the outer rotor radial projection preceding it such that fluid pressure in that chamber is allowed to at least partially equalize with the fluid pressure in the chamber preceding it between the outward and trailing surfaces of the preceding inner rotor projection and the forward facing face of the preceding outer rotor radial projection up to the contact between the trailing convex surface of the preceding inner rotor projection and the leading offset radial surface of the preceding outer rotor projection, and the outer cylindrical surface of each projection of the inner rotor is in sealing proximity to the inward facing cylindrical surface of the carrier for part of the inner rotor rotation and the rotational power to the device is input to the outer rotor and the sealed chamber is partially defined by a planar side face of the outer housing, and the inner rotor is supported for rotation at both axial ends.
A fluid transfer device, comprising:
an outer housing having an inward facing cylindrical or partially cylindrical surface;
an outer rotor with radial projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;
a carrier secured to prevent rotation relative to the outer housing at least partly within the outer rotor, the carrier having a partially cylindrical inward facing surface;
an inner rotor secured for rotation about an axis within the cylindrical inward facing surface of the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface, the outward projections each having a cylindrical outward facing surface and a trailing convex surface, the leading face of the radial projections on the outer rotor and the trailing convex face of the outward projections on the inner rotor mesh with each other and define variable volume chambers between the leading offset radial face and the trailing convex face of the outward projections as the inner rotor rotates within the carrier;
the radial projections on the outer rotor each having a leading face and trailing face;
the outward projections of the inner rotor each having a leading surface and trailing surface
fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers and the leading surface of the inner rotor projections has a larger gap clearance and/or a relieved area proximal to the trailing face of the outer rotor radial projection preceding it such that fluid pressure in that chamber is allowed to at least partially equalize with the fluid pressure in the chamber preceding it between the outward and trailing surfaces of the preceding inner rotor projection and the forward facing face of the preceding outer rotor radial projection up to the contact between the trailing convex surface of the preceding inner rotor projection and the leading offset radial surface of the preceding outer rotor projection, and the outer cylindrical surface of each projection of the inner rotor is in sealing proximity to the inward facing cylindrical surface of the carrier for part of the inner rotor rotation and the rotational power to the device is input to the outer rotor and the sealed chamber is partially defined by a planar side face of the outer housing, and the inner and outer rotors are supported for rotation at both axial ends.
These and other aspects of the device and method are set out in the claims, which are incorporated here by reference.

BRIEF DESCRIPTION OF THE FIGURES

Embodiments will now be described with reference to the figures, in which like reference characters denote like elements, by way of example, and in which:

FIG. 1 is an isometric view of a design according to U.S. Pat. No. 7,111,606 (the '606 design);

FIG. 2 is a top view of an outer rotor and inner rotor of the '606 design;

FIG. 3 is a top view of a housing for the first embodiment of the '606 design;

FIG. 4 is a first view illustrating a progressive cycle of compression of a compression chamber of the '606 design;

FIG. 5 is a second view illustrating a second position of a cycle of compression of a compression chamber where the base of a foot begins displacing the gas contained therein of the '606 design;

FIG. 6 is a third view illustrating a third stage and a compression cycle of a compression chamber where a portion of the compression chamber is exposed to and exit passage of the '606 design;

FIG. 7 is a fourth view illustrating the progression of a compression cycle of the '606 design;

FIG. 8 is at this view illustrating the final phase of a single compression cycle for a compression chamber of the '606 design;

FIG. 9 is a schematic view illustrating the geometries for the outer circle and inner circle of the '606 design;

FIG. 10 shows the outer circle and inner circles superimposed upon the outer rotor and inner rotor respectively of the '606 design;

FIG. 11 shows the geometric relationship of the inner and outer rotor where the method of defining the contact surfaces for the legs of the inner rotor and the fans of the outer rotor a shown of the '606 design;

FIG. 12 shows a day modification to the first embodiment where to interior rotors are employed wall maintain an aspect ratio of two to one with respect to the outer and inner reference circles of the '606 design;

FIG. 13 is an exploded view showing the method of calculating the contact surface for the leg of the inner rotor of the '606 design;

FIG. 14 shows an isometric view of the preferred embodiment where a plurality of interior rotors are employed of the '606 design;

FIG. 15 is an isometric view showing a backside of the preferred embodiment shown in FIG. 18 or a scoop section is shown of the '606 design;

FIG. 16 is an isometric view showing a modification to the embodiment in FIG. 18 where the casing provides openings for a pump configuration of the '606 design;

FIG. 17 is an isometric view showing the casing of the pump configuration of the '606 design;

FIG. 18 is an isometric this of the pump configuration of the preferred embodiment with the outer rotor placed inside the housing of the '606 design;

FIG. 19 is an isometric view of the end cap of the '606 design;

FIG. 20 is an isometric view of a close up an interior rotor of the preferred embodiment of the '606 design;

FIG. 20 a is a second isometric view of the interior rotor engaging the fins of the exterior rotor of the '606 design;

FIG. 21 is a front view showing the geometric relationship of the reference circles the inner and outer rotors of the '606 design;

FIG. 22 is a close of the view in FIG. 21 and shows the perpendicular distance from the outer reference radii to the endpoints of the inner rotor change with respects to rotation of both reference circles while maintaining a constant velocity at the intersect point of the '606 design;

FIG. 23 shows the geometric relationship with the forward surface of the toe region and the reference axis of the outer rotor that extends through an outer rotor fin of the '606 design;

FIG. 24 shows an isometric view of a foot region of an inner rotor and the surface of a fin that is adapted to engage the surface of the toe region of the foot of the '606 design;

FIG. 25 is a front view of the outer and inner reference circle showing various variables that are used to mathematically define the first and second surfaces of the fins of the '606 design;

FIG. 26 is a simplified top view of the prototype configuration of an embodiment of the present invention with transparent casing;

FIG. 27 is a simplified top view of an embodiment of the present invention with no top casing, in which the arrow shows the rotational direction of the rotors when operated as a pump (as a hydraulic motor, rotation would be in the opposite direction);

FIG. 28 is a simplified iso view of an embodiment of the present invention with no top casing;

FIG. 29 is a simplified iso view of an embodiment of the present invention with no casing;

FIG. 30 is a simplified top view of an embodiment of the present invention with no casing (fasteners not shown in any views);

FIG. 31 is a simplified schematic bottom view of the discharge port of an embodiment of the present invention with no casing showing entrained gas handling capability (when inner rotor foot enters the chamber, the acceleration on the fluid is in the opposite direction and all or part of the lighter gas is pushed out of the chamber first);

FIG. 32 is a simplified top view of an embodiment of the present invention with bottom casing only, the casing showing entrained sand handling capability (white arrows show path of denser particles that enter the pump on a helical path and are biased away from the inner rotor sliding interface by centripetal force); and

FIG. 33 is a simplified schematic iso section view of an embodiment of the present invention showing coaxial multi stage configuration (no casing shown).

DETAILED DESCRIPTION

The following description is extracted from U.S. Pat. No. 7,111,606.
Throughout this description reference is made to top and bottom, front and rear. The device of the present invention can, and will in practice, be in numerous positions and orientations. These orientation terms, such as top and bottom, are obviously used for aiding the description and are not meant to limit the invention to any specific orientation.
To a description of the apparatus 20, an axis system 10 is defined as shown in FIG. 1 where the transverse axes is indicated by arrow 12, arrow 14 is referred to as the crossword axis and is aligned to pass through centerpoints 50 and 26. Finally, the axis orthogonal to both axes 12 and 14 are referred to as the wayward axis indicated by arrow 16.
The term fluid is defined as compressible and incompressible fluids as well as other particulate matter and mixtures that flows with respects to pressure differentials applied thereto. Displacing a fluid is defined as either compressing a fluid or transfer of an incompressible fluid from a high to low pressure location or allowing expansion of a fluid in a chamber. Engagement is defined as either having a fluid film or fluid film seal between two adjacent surfaces or be in contact or having interference between two surfaces where forceful contact occurs for a tight seal.
In the following text, there will first be a description of the first embodiment with a detailed description of the geometries necessary to prevent surface interference between the inner rotor 24 and the outer rotor 22. Finally, there is a description of several other preferred embodiments that utilized numerous internal rotors, which have inner reference circles that are at a ratio of number of legs (Λ) divided by the number of chambers (X) defined by the fins is equal to the radius of the inner reference circle r_idivided by the outer reference circle r_o(i.e. Λ/X=r_i/r_o) and r_i/r_ois <½.
As seen in FIG. 1, there is shown a first embodiment of the apparatus 20 comprising a rotor assembly 21 and a housing 25. Shown in FIG. 1, the rotor assembly 21 comprises an outer rotor 22, and an inner rotor 24. The outer rotor 22 has an outside diameter d (FIG. 2) and a center point indicated at 26 that indicates the location of the axis of rotation for the outer rotor 22. The outer rotor further has a plurality of fins 28 discussed further herein. As shown in FIG. 10, the outside rotor further has an outer reference circle 80 and the inner rotor 24 has an inner reference circle 82 that is one half of the diameter of the outer reference circle 80. The significance of this geometrical integer ratio requirement is discussed further herein.
Now referring back to FIG. 2, the fins 28 each have a central axis 30 that extends through the center point 26. The fins 28 further comprise a forward surface 32 and a rearward surface 34. It should be noted that surfaces of 32 and 34 are substantially flat and aligned to the transverse axis. The outer rotor 22 further comprises the surface 40 that is located in the transverse plane and partially defined sealed chambers discussed further herein. As seen in FIG. 2, a semi chamber (or semi chamber region) 42 d is defined as surface 40 d, forward surface 32 d, and rearward surface 34 c. Located in the radially outward portion of the outer rotor 22 is a peripheral edge portion 44 that defines a circle about center point 26. The peripheral edge 44 is adapted to intimately engage the housing 25 to form a compression chamber discussed further herein.
The inner rotor 24 has a center of rotation indicated at 50 and a plurality of legs 52. Each leg has a foot portion 54 that has a toe portion 58. The foot 54 further comprises a radially outward surface 60. The toe portion 58 has a toe surface 64 that as adapted to engage the forward surface 32 of the fins 28.
Each leg 52 further has a rearward surface 65 and a forward surface 66. Opposing forward and rearward surfaces 65 and 66 facing one another (e.g. 66 d and 65 c) define an inner rotor chamber 67.
There will now be a discussion of the geometric relationship between the inner rotor 24 and the outer rotor 22. As previously mentioned above, FIG. 2 shows an embodiment where the rotor 24 has nine legs 52 with nine corresponding foot portions 54. The radially outward surface surfaces 60 of the foot portions 54 define at least in part a circular cylinder in the transverse axis about center point at 50. As shown in FIG. 2, there are twelve semi chamber regions 42 of the outer rotor 22. The number of semi chamber regions in the outer wheel in the embodiment shown in FIG. 2 is twice the number of legs 52 of inner rotor 24.
As previously mentioned above, in the first embodiment the circumference the outer reference circle 80 of the outer rotor 22 is exactly twice the circumference of the inner reference circle 82 of the inner rotor 24. Therefore, as the inner rotor wheel 24 rotates about center point 50, the inner rotor's rotations per minute is exactly twice the rotations per minute of the outer rotor 22. The ratio between the circumferences of the inner rotor 24 and the outer rotor 22 is a factor of two. As discussed further herein the ratios between the inner rotors and the outer rotor will be the ratio of the number of legs 52 and fins 28 of the inner and outer rotors as a direct relationship with ratio of the inner and outer radii of the inner and outer rotors 24 and 22. In other words the number of legs (Λ) divided by the number of chambers (X) defined by the fins is equal to the radius of the inner reference circle r_idivided by the outer reference circle r_o(i.e. Λ/X=r_i/ r_o).
Of course there is a linear relationship between the radius, diameter, and circumference of a circle. Therefore, the ratios between the diameter of the inner rotor 24 and the diameter of the outer rotor 22 is the same as the ratio between the circumference of the inner rotor 24 and the circumference of the outer rotor 22.
There will now be a discussion of the forward surface 32 of the outer rotor 22 with reference being made to FIGS. 9-11. FIG. 9 shows an outer reference circle 80 and an inner reference circle 82. The outer reference circle has sixteen pie sections spaced at twenty two and a half degrees defining outer reference points 84 a-84 p. The inner reference circle 82 has eight evenly spaced pie sections at forty-five degrees defining inner reference points 86 a-86 h.
The center point 26 shown in FIG. 9 is the center of outer reference circle 80, and center point 50 is the center of inner circle 82. The radius of the outer circle indicated by r_ois exactly twice see inner radius r_i. The circumference of a circle is a linear relationship with respects to the radius. The well-known equation is c=2πr. Therefore, one-half of a radius yields exactly one-half the circumference. Further, forty-five degrees of circumference section 88 for the inner circle 82 yields exactly one-half of the circumferential distance of forty-five degrees circumference section 90 for the outer circle 80. Therefore, twenty two and a half degrees (½ of forty five degrees) circumferential section 92 for the outer circle 80 yields the exact same circumferential distance as a 45 degree circumferential length 88 for the inner circle 82. So as the outer circle 80 rotates about center point 26 and the inner circle 82 rotates about center point 50 and the perimeters of each circle at point 84 a move at the same speed, the inner circle 82 will rotates at exactly twice the rotational velocity of the outer circle 80. This rotational scheme is defined as the dual rotation.
By having the inner radius r_ione-half the length of the outer radius r_othere is an interesting mathematical phenomena where points 86 define linear lines on the outer circle 80 during dual rotation. In other words, as the circles rotate in the dual rotation fashion point 86 d defines straight line 84 d. Likewise, all of the points about the circumference of the inner circle define straight lines radially extending from the center point 26 are the outer circle 80.
With the foregoing geometric relationships in mind, reference is now made to FIG. 10 where the inner and outer circles 80 and 82 are superimposed upon the rotor assembly of the first embodiment. The point 86 a is located on the toe portion of leg 52 a and point 84 a is at the exact same location. This location is referred to as the contact point where the circumference is of the inner circle 82 and the outer circle 80 cross. The line 84 a′ extends to point 86 a when point 86 a is in the contact point position. The toe surface 64 is defined by a semi-circle having a center point at 84 a and a radius of 90 a (see FIG. 11). The center of toe surface 64 is point 86 a. Therefore all points along toe surface 64 are equidistant from the point 86 a at a distance 90 a. To reiterate the geometric relationship phenomenon, as the inner and outer rotors 24 and 22 rotate in the dual rotation scheme described above, the point 86 a will travel along the line 84 a′. Therefore, rearward surface 32 a must be parallel to line 84 a′. In other words, as point 86 a travels radially inwardly along line 84 a′ during the dual rotation scheme, the surface 32 a must be parallel to radially extending line 84 a′ to avoid interference between the surface 32 a and the toe surface 64.
The same analysis can be conducted for all of the fins 28 with the respective legs 52 lined adjacent thereto.
It should be noted that the preferred surface for the first embodiment toe heel surface 64 is a semi-circle about a point. The semi-circle allows the fins to have non-curved surfaces that radially extend from the outer reference circle 80. Other circular shapes for the toe surface 64 could be employed with a varying radius.
In addition to having the reference circles 80 and 82 radii (and circumferences) a ratio of two to one, it is just as important to have the number of fins 28 line of the outer rotor twice in quantity as the number of legs 52 line of the inner rotor (see FIGS. 9-11). This integer ratio is crucial for having continuous rotation of the inner and outer rotors free from having a leg crashed down upon a fin for the first embodiment.
There will now be a discussion of the rotor assembly mounted in the housing 25 along with the various components of the apparatus 20 followed by a description of the pumping or displacement scheme.
FIG. 1 shows the rotor assembly with the housing 25 in conjunction with the inner rotor 24 and the outer rotor 26. As seen in FIG. 3, the housing 25 is preferably a unitary designed having a central area 94, an exit/entrance portion 96, a discharge region 98, an entrance region 100, an outer rotor annular slot 102, an inner rotor annular slot 104, a high compression region 106, an expansion region 108 and finally an annular support region 110. The outer rotor annular slot 102 is adapted to house the outer rotor 22 (see FIG. 2). The outer rotor 22 can rotate therein slot 102 and press upon the inward annular surface 112 and the outward annular surface 114. Further, the annular slot has a surface 116 adapted to support the lower surface of the outer rotor 22. The inner rotor annular slot 104 is defined by radially inward facing surface 118 and a radially outward facing surface 120. The radially outward facing surface 120 is adapted to position the inner rotor 24. Further, the radially inward surface 118 is in close engagement with the radially outward surface 60 of the inner rotor 24. Therefore, surfaces 118 and 120 independently cooperate to hold inner rotor 24 and place to rotate about center point 50.
The outer rotor annular slot 102 and inner rotor annular slot 104 cooperate to assist in positioning the outer rotor 22 and inner rotor 24 so both rotors rotate about centerpoints 26 and 50 respectively.
The airflow into and out of the rotor assembly 20 is accomplished by the exit/entrance portion 96, the discharge region 98, and finally the entrance region 100. The exit/entrance portion 96 comprises an exit passage 122 and an entrance passage 124. The exit passage 122 comprises a first surface 126, a second surface 128 and upper and lower surfaces 130 and 132. A boundary corner is defined at numeral 134 and a second corner portion is indicated at 136. The entrance passage 124 comprises a first surface 138, a second surface 140, an upper and lower surfaces 144. A corner portion 146 is located at the juncture between surface 112 b and first surface 138.
To properly understand the air flow scheme of the apparatus 20 there will first be a discussion of the chamber volume displacement. In general, a compression chamber 148 is defined by the radially outward surface 60 a, the forward surface 32 a, the rearward surface 34 b the radially inward surface 112 a and finally the upper and lower surfaces of the outer rotor 22.
The gas entrance phase will now be discussed with reference again made to FIGS. 4-8.
As seen in FIG. 4, gas enters in entrance passage 124 and enters into expansion chamber 150. The expansion chamber 150 is defined as the particular inner rotor chamber 67 that is in communication with entrance passage 124.
As seen in FIG. 6, the inner rotor chamber 67 b is not directly in communication with exit passage 122; however, the seal between fin 28 c and toe portion 58 c of leg 52 c is not a perfect seal and some higher pressure gas can seep into chamber 67 b.
As the inner and outer rotors 22 and 24 are positioned in the matter shown in FIG. 5, inner rotor chamber 67 b is now substantially sealed from exit passage 122 and entrance passage 124. However, the pressure in chamber 67 b may be slightly greater than the pressure in entrance passage 124.
As seen in FIG. 5, the leg 52 c is near the radially inward portion of entrance passage 124. Shown in FIG. 6, the inner rotor 24 has rotated additional degrees clockwise and the expansion chamber 150 is increasing in volume. It is important to note that it is undesirable to have the expansion chamber 150 sealed and not be in communication with the entrance passage 124. If the expansion chamber was substantially sealed between surfaces 112 c, 34 d, 32 c and 60 c as the chamber 150 increases in volume corresponding to the clockwise rotation of rotors 22 and 24, the low-pressure therein would create a counter clockwise force as a result of the tangential surface difference between rearward surface 34 d and forward surface 32 c.
As seen in FIG. 7, the expansion chamber 150 has increased in volume with respect to the location in FIG. 6. The distance dr₁indicates the amount of surface area exposed in the radial direction (presuming a finite amount of depth). The distance dr₂represents the amount of surface area in the radial direction for the fin 28 d. It is therefore apparent that a positive clockwise torque is created upon the outer rotor due to the increase in surface area of distance dr₂over dr₁.
In FIG. 8 the expansion chamber is fully expanded and now defined by the surfaces 112 c, 114 b and forward surface 32 c and rearward surface 34 d. Finally, the air is subjected a centrifugal force and ejected through the discharge region 98.
There will now be a discussion of how air enters into the semi chamber regions 42 of the outer rotor 22. As seen in FIG. 1, as the outer rotor 22 rotates in the direction indicated by arrow 151. The air is drawn in through the entrance region 100. The entrance region 100 comprises glide surface 152 having generally downward slope in the radial outward and tangentially clockwise direction. As discussed above, the rotations per minute of the outer rotor 22 are in the order of magnitude in the thousands to hundreds of thousands with certain materials in certain configurations. At this high-speed air channeled through the entrance region 100 is “pre-compressed” into the semi chambers 42. The compression at this phase is similar to a centrifugal compressor. When the rearward fin 28 of semi chamber 42 passes the position 154 (FIG. 3) the semi chamber is now substantially sealed and ready for the gas contained therein to pass to the high compression region 106.
We have thus far discussed one embodiment of the present invention, which employs a single outer rotor 22 and a single inner rotor 24. There will now be a discussion of a second embodiment employing two inner rotors while still maintaining a two to one ratio between the outer reference circle 380 of the outer rotor 322 and the inner rotors 324. The numerals designating the components of the second embodiment will correspond, where possible, to the numerals describing similar components except the numeric values will be increased by three hundred.
As shown in FIG. 12, the rotor assembly 321 comprises an outer rotor 321, a first inner rotor 324 and a second inner rotor 324′.
The outer rotor 321 is very similar to the outer rotors 22 in the first embodiment except for different angles of the forward and rearward surfaces 332 and 334. The center point 326 is the center of rotation for the outer rotor 322. The reference circle 380 for the outer rotor coincides with the peripheral edge 344 also having a center point 326.
The inner rotors 324 and 324′ are substantially similar and hence inner rotor 324 will be described in detail with the understanding the description also relates to inner rotor 324′.
The inner rotor 324 comprises a plurality of legs 352 where each leg has a foot portion 354. The foot portion 354 comprises a toe portion 358 and a radial outward surface 360. The radial outward surface 360 defines a circle about point 350. The inner reference circle for the inner rotor 324 is indicated at 382 and coincides with the circle defined by radially outward surface 360.
As seen in FIG. 13, the forward surface 364 of the toe portion 358 is semi-circular about point 386 a. The point 386 a lifelong the inner reference circle 382 (as well as the circle defined by radially outward surfaces 360). The significance of having the reference point at this radially outward extreme location from the center point 350 is discussed further herein.
There is now a description of the forward and rearward surfaces 332 and 334 of the fins 328. The analysis of the forward and rearward surface 332 and 334 is very similar to the analysis of surfaces 32 and 34 of the first embodiment discussed above referring to FIGS. 9-10. The main difference in the third embodiment is the point 386 is located on the radially outward surface 360, whereas in the first embodiment the point 86 is located a distance radially inward from the radial outward surface 60.
The line 386 a′ extends from the reference point 386 a to the center point 326 of the outer reference circle 380 (see FIGS. 12 and 13). When the inner and outer rotors 324 and 322 engage in the dual rotation scheme, the reference point 386 a travels radially inward along line 386 a′. Therefore, forward surface 332 a must be parallel to the line 386 a′. A similar analysis can be conducted for the rest of the surfaces 364 and 362 of the inner rotors 324 and 324′.
By having the outer reference circle 382 coexisting with the radially outward surface 360 or slightly radially outward from radially outward surface 360, the rotor assembly 321 can fit the second rotor 324′ into the housing as well.
In a preferred form, the inner reference circles 382 and 382 a′ are a small tolerance distance from the radially outward surfaces 360 and 360′ to avoid interference between these surfaces at the center point location 326.
The third embodiment is shown in FIG. 14 where four inner rotors are employed. The third embodiment has advantages of allowing a throughput shaft that is attached to the outer rotor 422. As with the previous embodiments, the numerals for the most part correspond with the first embodiment except increased by four hundred.
The apparatus 420 has a rotor assembly 421 that comprises an outer rotor 422 and a plurality of inner rotors 424 a-424 d. The outer rotor has a reference circle 480 and a center of rotation indicated about axis 426. Likewise, the inner rotors 424 have been inner reference circle 482. In a similar manner with the previous embodiments the relationship between the circumference of the inner reference circle and the outer reference circle 482 and 480 is a ratio that is an integer and in this embodiment a ratio of 3-1.
The relationship between the ratio of the number of legs 52 and fins 28 of the inner and outer rotors has a direct relationship with ratio of the inner and outer radii of the inner and outer rotors 24 and 22. In other words the number of legs (Ε) divided by the number of chambers (X) defined by the fins is equal to the radius of the inner reference circle r_idivided by the outer reference circle r_o(i.e. Λ/X=r_i/r_o).
Further, the outer rotor has 18 fins and the inner rotors have six legs (a ratio of 3-1). It should be noted that although the third embodiment discloses four interior rotors 424, there can be one—four interior rotors. However, having four interior rotors as particular benefits of balancing the force upon the central shaft described further herein.
The rotor 422 further comprises a scoop region 431 best shown in FIG. 15 which shows the backside of one of the rotor assembly support 420 of FIG. 14. As seen in FIG. 15, the scoop region 431 comprises a plurality of vanes 433 define channels 435 that channel the air radially inward to the longitudinal extensions 437. Now referring to FIG. 14, the extensions 437 channel air into the chambers 442. The scoop region 431 is connected to and can be a unitary structure with the outer rotor 422. FIG. 14 shows an embodiment where two apparatuses 420 are positioned in a back-to-back arrangement having two outer rotors 422 and eight inner rotors 424.
The apparatus 420 further comprises a central frame member 494 that has a central open region 495 and annular interior surfaces 518 that are adapted to house the inner rotors 424. Further, a radially recessed region 497 allows communication to the longitudinal extensions 437 of the scoop region 431.
Finally, the apparatus 420 has a housing (not shown) that is connected to the front face 499 of the central frame member 494. The housing provides a seal in a similar manner to the housing is shown in FIG. 1, except a plurality of interest and exit ports would be provided for each interior rotor 424.
FIG. 16 shows a pump version for the third embodiment where in general the entry and exit ports are modified to allow exit ports to be communication with any chamber that is displaced in volume to prevent compression of a fluid. The housing 425 is best shown in FIG. 17 and comprises a plurality of entrance ports 520 and exit ports 522. The entrance ports 520 comprise a radial outward slot portion 524, an axial conduit 526, and a toe portion passage 528.
The exit ports 522 comprise a radial outward slot portion 540 a radially extending slot 542 and a toe portion slot 544. The radially extending slot and toe portion slot 542 and 544 are in communication with one another and are in communication with a central annular slot region 546 which is in turn in communication to the axial conduit 548.
As shown in FIG. 18, the outer rotor 560 is similar to the outer rotors discussed above, with the exception a plurality of ports 562 are provided and are adapted to communicate with the toe portion passages 528. FIG. 19 shows an endcap 570 that is adapted to the mounted upon the pump assembly shown in FIG. 16. The endcap 570 has a center crossmember 572 that provides a plurality of surfaces 574 that are adapted to house the interior rotors. The extensions 576 are adapted to extend to the central shaft of the interior rotors and allowing the interior rotors to rotate their around. The central region 578 is open and allows a shaft 580 (shown in FIG. 18) pass therethrough.
The pump embodiment can be used as a flow meter as well. The multi interior rotor embodiment is particularly advantageous because the center shaft can extend therethrough and the load balance upon the shaft is desirable where the primary force upon the shaft is the torque caused by the force of the inner rotors acting upon outer rotor.
The two dimensional nature of the invention allows for variances of the geometries in the transverse direction. In other words in the transverse plane (the plane aligned in the wayword and crossword axes) at a given location in the transverse direction, the points on the inner and outer rotors 24 and 22 remain in the said plane during rotation. This is due to the axes of rotation for each rotor are parallel to each other. Therefore the geometry for the outer and inner rotors 22 and 24 can change with respects to the transverse position coordinate. To run the device in FIG. 14 as an expander the sealed chamber that is formed with a housing similar to that of the first embodiment with a gas entrance passage would receive compressed gas and provide a torque to drive the outer rotor.
There will now be a discussion of the geometric relationships between the inner and outer reference circles for the embodiments where the ratio of r_i/r_ois less than 1/2. For this example we will assume the inner reference circle radius, r_i, is ⅓ of the outer reference circle, r_o.
Referring to FIG. 21, there will now be a discussion of the fundamental geometries that are used to define the engagement surfaces. FIG. 21 is similar to FIG. 9 except when the r_i/r_ois not a factor of ½ then the exterior points on the inner reference circle 482 will not follow the path of the outer reference circle's radii during dual rotation (where velocity of travel is the same at the insect point as both circles rotate about their center axis. The outer reference circle 480 has a r_oof three units and the inner reference circle has an inner radius of r_iof one unit. Therefore the ninety degree circumferential section 481 of the inner circle 482 is equal in circumferential length to the thirty degree circumferential length 483 (see angle references 481′ and 483′). For this example, four points of rotation will be examined in the clockwise direction, 0°, 30°, 60°, and 90° indicated by r_{i 0}, r_{i 30}, R_{i 60}and r_{i 90}for the inner rotor 482 and corresponding angles of 60°, 70°, 80° and 90° indicated by r_{o 60}, r_{o 70}, r_{o 80}and r_{o 90}for the outer rotor 480. The distal points of r_{i 0}, r_{i 30}, r_{i 60}and r_{i 90}intersect the corresponding distal points of r_{o 60}, r_{o 70}, r_{o 80}and r_{o 90}at the intersection location as both reference circles rotate. However, it is apparent that the corresponding radii (e.g. r_{o 60}and r_{i 0}) do not intersect at other rotational positions at the distal point of the inner reference radius such shown in FIG. 9.
Now referring to FIG. 22, additional reference radial are added. For this illustrative example each outer radii r_ois repositioned counter clockwise a fixed amount of degrees (e.g. 8° for this example) and numbered in the same reference degree offset fashion as r_{o 68}, r_{o 78}, r_{o 88}and r_{o 98}. These outer circle reference radii are similar to r_oas shown in FIG. 20. The perpendicular distance d₀is defined as the reference radii r_{o 68}to the distal point of r_i0 indicated at P_i0 and the perpendicular distances d₃₀, d₆₀and d₉₀are defined in a like fashion with reference radii r_{o 78}, r_{o 88}and r_{o 98}and points P_{i 30}, P_{i 60}and P_{i 90}respectively. It is therefore apparent that the perpendicular distances (d₀, d₃₀, d₆₀and d₉₀) increase during the course of rotation.
It should be reiterated that the subscript notations are the angle of rotation of the inner rotor (where 0° is to the right in the wayward axis direction and clockwise rotation is positive).
Now referring back to FIG. 20, it should be noted that distance d′₁, is greater than d′₂. The point 486′ is near the bottom dead center portion of rotation. The point 486′ will continue to travel along the inner reference circle path 482 away from the outer reference circle 480. Therefore as shown in FIG. 20 a, an extension region 481 is provided that is adapted to engage the outer surface indicated at the portion 483. This extension region further supplies an additional advantage by increasing the compression ratio of the device.
It should be noted that the inner reference radius r,_i0is primarily for exemplary purposes of an extreme location because of the difficulty of having a fin extend radially inwardly to engage the arc at that rotational position.
There will now be a discussion of the engagement surface 464 of the toe region 458 with reference to FIG. 23. The toe region arc at the positions indicated at a′₃₀, a′₆₀and a′₉₀are centered about points P_{i 30}., P_{i 60.}P_{i 90}respectively. The indicator lines 469 are ninety degrees from the inner radius reference lines r_iand are helpful for determining the angle of the orthogonal distances d_f. The orthogonal d_f30, d_f60and d_f90increase as the rotors rotate clockwise to the 90 degree position and the d′_f30, d′_f60and d′_f90that are defined as the orthogonal distances d_f30, d_f60and d_f90subtracted by the arc radius of arcs a′ in FIG. 23. It can be observed that the distances d′_f30, d′_f60and d′_f90increase with clockwise rotation. The arc represents the engagement surface 464 as shown in FIGS. 20 a and 24. Therefore with an arc that has a constant radius, the second defined distance d′_fas shown in FIG. 24 increases with respects to the radial location along the second reference radius shown at r_{o 82}and the engagement surface 432 of the fin 428 in FIG. 24 must increase in distance from the outer reference radius r_{o 82}with respects to radially outward travel along r_{o 82}.
Therefore as the perpendicular distance d_fchanges with respects to the rotational position of the inner and outer rotors, the second defined distance 505 of the toe region is collinear with the second defined distance 507 (d′_f) of the second fin 509 and their sum plus a desired gap totals the distance d_fthat changes with respects to the rotational position of the inner and outer rotors.
The distance 471 in FIGS. 23 and 24 roughly indicates the location and magnitude of increased tangential distance between r_{o 82}and the distal portion of surface 432. This accelerated increase in distance is because as seen in FIG. 23 the orthogonal line 473 is above the ninety degree reference line 469 and indicates the shortest path from the reference point 486 to r_{o 82}. However, for clearance among the parts it is advantageous extend the material at extension portion 491 to engage the outer region 473 of the surface 464.
Therefore a preferred method of constructing the first and second surfaces 434 and 432 is sketch out a CAD drawing such as that in FIG. 23 and rotate the inner circle 3 units and the outer circle 1 unit (the aspect ratio to r_o/r_i) and enter in spline points that traces the path of the forward and rearward (second and first) fin surfaces with a desirable gap or interference fit thereinbetween. Then the inner chamber 435 (FIG. 16) should be constructed in a manner to not interfere with the fin during rotation.
To use the preferred embodiment as an expander the exit port is an entrance port and the fluid will fill the expanding sealed chamber. It is therefore apparent that the preferred embodiment utilizes nonlinear surfaces in the radial direction of the fins. It is important to note the desirable balancing loads radial loads upon the outer rotor when a plurality of inner rotors are employed. Further, a center throughput shaft can be attached to the outer rotor in the preferred embodiment.
The mathematical model to define the surfaces of the fin is discussed below.
To ease the explanation the first (toe surface of the fin will be defined using two coordinate systems O₁and O₂. The first coordinate system is referenced to the casing and is located at the center of rotation of the outer reference circle 480 of the outer rotor. Because we are interested in defining the surfaces of a fin of the outer rotor, a second coordinated system is defined at O₂and the Y axis of the second coordinate system extends radially inward along the reference radius 484 which is the reference radius that extends through a point through the fin to be defined.
The relationship between the rotational value θo of the reference circle to the rotational value θi of the inner reference circle is defined by the equation:
$? = \frac{?}{Ro}$ $? indicates text missing or illegible when filed$
The angular location of the center of the toe arc 464′ are denoted by θt where each point 486 are rotationally offset from point 450 by a value θi_t_o for the toe region. These offsets represents the distance the points 486 and 486′ are from the center radius 484 of the fin to be defined. Therefore the resulting equation is:
The position of the toe center point 486 with respects to the first axis O₁are defined by x,y coordinates Xi_{—t and Yi} _{—t where Rip}_t is the distance from the inner circle center point 450. The point 486 lies on the circumference of the outer reference circle. However, the point 486 can be extended beyond the inner reference circle to define the first surface (toe fin surface) 464′:
The x,y location of the second origin O₂in the first coordinate system is defined as:
The second coordinate system O₂is referenced to the center axis 484 of a fin of the outer rotor. Therefore the second coordinate system changes position with respects to the first coordinate system during rotation of the inner and outer reference circles (corresponding to rotation of the inner and outer rotors). To convert from the first coordinate system O₁to the second coordinate system O₂the following functions are used.
Therefore, the arc center points 486 and 486′ in the second (fin) coordinate system is:
which are expanded to the format:
Finally the offset from the center point 486 to the center fin axis in the second coordinate system axis is defined as the equations:
The above equations are for the toe surface where r_t is the radius or radius function for the toe surface arc and gap_t is the gap clearance distance or function to account for a fluid film gap. The expanded full form of the equations are:
Substituting in the variables for θo we get the equation:
$? = (\sin ? - \sin (?) ro) \cos (?) + (- \cos ? + \cos (?) ro) \sin (?)$ $? = (- \cos ? + \cos (?) ro) \cos (?) - (\sin ? - \sin (?) ro) \sin (?)$ $? indicates text missing or illegible when filed$
to have the x,y values be a function of the θi (the inner rotation of the inner reference circle.
It should be noted that the preferred embodiment allows for points of contact between the toe second engagement surface and the second surface of a second fin for a more than an instant point of rotation. The sealed chamber is in effect for more than a finite range of rotation (i.e. certain amount of rotation of the inner and outer rotors). In other words a sealed chamber is maintained for up to 45° of rotation of the inner rotor and possibly higher with longer thinner fins extending radially inwardly.
Therefore it is apparent that the device has numerous applications for converting energy. While the invention is susceptible of various modifications and alternative forms, specific embodiments thereof have been shown by way of example in the drawings and described in detail. It should be understood, however, that it is not intended to limit the invention to the particular forms disclosed, but, on the contrary, the intention is to cover all modifications, equivalents and alternatives falling within the spirit and scope of the invention as expressed in the appended claims.
There will now be a discussion of the geometric relationships between the inner and outer reference circles for the embodiments where the ratio of r_i/r_{o is less than}½.
For this example we will assume the inner reference circle radius, r_i, is ⅓ of the outer reference circle, r_o.
As shown in FIG. 20, the heel portion of 456 a of leg 452 a comprises a surface 462 a that is defined as a circular surface in the transverse plane about heel point 486′. It can be seen that as the inner rotor 424 rotates to a position as leg 452 b the engagement point of surface 462 a is at a more distal location. Further, the perpendicular distance between the heel point 486′ and the outer reference circle reference radius increases in the course of rotation (during the rotation compression phase).
Referring to FIG. 21, there will now be a discussion of the fundamental geometries that are used to define the engagement surfaces. FIG. 21 is similar to FIG. 9 except when the r_i/r_ois not a factor of ½ then the exterior points on the inner reference circle 482 will not follow the path of the outer reference circle's radii during dual rotation (where velocity of travel is the same at the insect point as both circles rotate about their center axis. The outer reference circle 480 has a r_oof three units and the inner reference circle has an inner radius of r_iof one unit. Therefore the ninety degree circumferential section 481 of the inner circle 482 is equal in circumferential length to the thirty degree circumferential length 483 (see angle references 481′ and 483′). For this example, four points of rotation will be examined in the clockwise direction, 0°, 30°, 60°, and 90° indicated by r_{i 0}, r_{i 30}, r_{i 60}and R_{i 90}for the inner rotor 482 and corresponding angles of 60°, 70°, 80° and 90° indicated by r_{o 60}, r_{o 70}, r_{o 80}and r_{o 90}for the outer rotor 480. The distal points of r_{i 0}, r_{i 30}, r_{i 60}and r_{i 90}intersect the corresponding distal points of r_{o 60}, r_{o 70}, r_{o 80}and r_{o 90}at the intersection location as both reference circles rotate. However, it is apparent that the corresponding radii (e.g. r_{o 60}and r_{i 0}) do not intersect at other rotational positions at the distal point of the inner reference radius such shown in FIG. 9. Therefore it is apparent that the engagement surfaces of the heel surface 462 and the forward fin surface 434 must adapt to this varying tangential distances.
Now referring to FIG. 22, additional reference radial are added. For this illustrative example each outer radii r_ois repositioned counter clockwise a fixed amount of degrees (e.g. 8° for this example) and numbered in the same reference degree offset fashion as r_{o 68}, r_{o 78}, r_{o 88}and r_{o 98}. These outer circle reference radii are similar to r_oas shown in FIG. 20. The perpendicular distance d₀is defined as the reference radii r_{o 68}to the distal point of r_{i 0}indicated at P_{i 0}and the perpendicular distances d₃₀, d₆₀and d₉₀are defined in a like fashion with reference radii r_{0 78}, r_{0 88}and r_{0 98}and points P_{i 30}, P_{1 60}and P_{i 90}respectively. It is therefore apparent that the perpendicular distances (d₀, d₃₀, d₆₀and d₉₀) increase during the course of rotation.
Now referring back to FIG. 20, it should be noted that distance d′₁, is greater than d′₂. The point 486′ is near the bottom dead center portion of rotation. The point 486′ will continue to travel along the inner reference circle path 482 away from the outer reference circle 480. Therefore as shown in FIG. 20 a, an extension region 481 is provided that is adapted to engage the outer surface indicated at the portion 483. This extension region further supplies an additional advantage by increasing the compression ratio of the device.
It should be noted that the inner reference radius r,_i0is primarily for exemplary purposes of an extreme location because of the difficulty of having a fin extend radially inwardly to engage the arc at that rotational position.
To ease the explanation the first surfaces (heel surface of the fin will be defined using two coordinate systems O₁and O₂. The first coordinate system is referenced to the casing and is located at the center of rotation of the outer reference circle 480 of the outer rotor. Because we are interested in defining the surfaces of a fin of the outer rotor, a second coordinated system is defined at O₂and the Y axis of the second coordinate system extends radially inward along the reference radius 484 which is the reference radius that extends through a point through the fin to be defined.
The angular location of the center of the heel arc 462′ are denoted by θh where each point 486′ are rotationally offset from point 450 by a value θi_h_o for the heel region. These offsets represents the distance the points 486′ are from the center radius 484 of the fin to be defined. Therefore the resulting equations are is:
The point 486′ lies on the circumference of the outer reference circle. However, the point 486′ can be extended beyond the inner reference circle to define the first and second surface (heel fin surface) 462′ and 464′. In a similar manner the position of the heel center point 462′ in the first axis O₁coordinate system is defined by the equations:
Therefore, the arc center points 486′ in the second (fin) coordinate system are is:
which are expanded to the format:
Likewise for the heel surface, the equation to determine the perpendicular distance from the center point 486′ to the heel surface is defined as:
and the expanded forms are:
Substituting in the variables for θh and θo we get the equation:
$? = (\sin ? - \sin (?) ro) \cos (?) + (- \cos ? + \cos (?) ro) \sin (?)$ $? = (- \cos ? + \cos (?) ro) \cos (?) - (\sin ? - \sin (?) ro) \sin (?)$ $? indicates text missing or illegible when filed$
to have the x,y values be a function of the θi (the inner rotation of the inner reference circle.
The new variables r_h and gap gap_h represent the radius of the heel arc and the desired gap distances (or equations of they vary with respects to rotation).
It should be noted that the preferred embodiment allows for points of contact between the-first engagement surface of the heel and the first surface of an adjacent fin for a more than an instant point of rotation. The sealed chamber is in effect for more than a finite range of rotation (i.e. certain amount of rotation of the inner and outer rotors). In other words a sealed chamber is maintained for up to 45° of rotation of the inner rotor and possibly higher with longer thinner fins extending radially inwardly.
The design uses the basic design as in U.S. Pat. No. 7,111,606 as modified below. The following modifications are shown in the figures.
When used as a pump, the larger outer rotor 622 is driven with a rotary shaft input, and only the convex trailing contact surfaces 678 of the inner rotor 624 contact the flat (or substantially flat) leading contact surfaces of the outer rotor “cylinder” walls. The leading surface 680 of each inner rotor foot does not seal and can be any shape as long as it prevents the rotors from locking up when the pump is freespinning or backturning.
Benefits of this design include the ability of the inner rotor to rotationally “retreat” (as opposed to the more commonly used term “advance”) in relation to the outer rotor 622 as the inner rotor 624 and/or outer rotor contact surfaces wear. This will, in effect, allow the pump to “wear in” for a period of time rather than wear out.
Other advantages of driving the outer rotor 622 include the ability to drive subsequent stages with a drive shaft that extends from both ends of one or more outer rotors 622 f to drive multiple similarly constructed outer rotors. A coaxial stator shaft 694 through the center of the drive shaft would be supported (at the opposite end from the drive shaft input) to the pump casing and would prevent the inner rotor housings from spinning
As Ice Pump
In one configuration of the pump, it is designed to handle the admission and pumping of breakable solids such as but not limited to methane hydrate ice crystals. It does this with a combination of features such as sharp leading edges on spinning components and sharp trailing edges on stationary components which will slice the ice as it flows into and through the pump. It is also designed to minimized areas where ice could become wedged and restrict the flow by using increasing cross sections along the flow path.
As Hydraulic Motor
By providing fluid pressure to the outlet port of the pump configuration described above and shown in the drawings, the device can also be used in reverse rotation as a hydraulic motor. In this case, the leading convex edges of the inner rotor feet contact the flat or substantially flat trailing surface of the outer rotor 622 which drives the output shaft.
As Multi Phase Pump
The pump is ideally suited to pump gases entrapped in a compressible fluid as follows: Gas bubbles that enter the pump will be centrifuged to the innermost area of each outer rotor cylinder chamber. When the inner rotor foot rapidly enters the chamber in the discharge port zone, it will create an acceleration force on the fluid which is in the opposite direction of the centrifugal force on the fluid up to that point. This is expected to cause the higher density fluid to swap positions with at least some of the entrained gas, effectively pushing a bubble of gas out ahead of the fluid as it exits the chamber. In a gas compatible design, the rotational axis is preferably (but not necessarily) vertical and the inner rotor 624 has a flow relief (which exists between the trailing convex contact surfaces 678 of each subsequent inner rotor foot) only on the bottom of the inner rotor 624 so gravity can bias the gas to the top of the chamber as it moves from the input to the output area of the pump. The top sealing surface of the inner rotor 624 is therefore more adequately sealed against gas leakage and is believed to be capable of pushing at least part of the entrained gas out of each chamber.
In the case of entrained gas, it may be preferable to not push all of the gas out of the chamber at once. This will reduce torque and pressure variations for longer service life.
In the case of entrained gas, it may be preferable to not push all of the gas out of the chamber at once. This will reduce torque and pressure variations for smoother operation and longer service life.
The pump is also ideally suited to pump grit such as sand. In this case, the port leading up to a pumping stage is preferably curved along an arced or helical path to centrifuge the heavier sand to the outer surface of the flow path. The will bias the sand away from the intake rotor sliding interaction. The sand then travels around the outer perimeter of the casing and cylinder volume to the discharge port 670 where centripetal force ejects and biases it away from the rotor sliding interaction.
The multiple seal of the cylinder wall outer surfaces and casing wall inner surface allows the perimeter area (where the sand will be sliding) to have a larger gap clearance while still preventing high leakage rates.
Many other configurations of the pump described here are possible and conceived by the inventor. Various features and advantages of the pump design are shown in the figures as described below.
FIG. 27 shows metal inserts 674 in plastic prototype casing are sharp on trailing edges to slice entrained ice. Arrow A shows the rotational direction of rotors when operated as a pump. As a hydraulic motor, the rotation would be in the opposite direction.
In FIG. 28 inner crescent 676 is held from rotating by shaft and provides bearing position for inner rotor 624.
In FIG. 29 a relief cut on inner rotor 624 allows leading surface 680 of inner rotor 624 to remain unsealed.
In FIG. 30 the inner crescent 676 is held from rotating by shaft and provides bearing position for inner rotor 624. Trailing surface 678 of driven inner rotor 624 seals against leading flat surface of driving outer rotor 622. Leading edges 682 of outer rotor 622 are sharp to break/slice/crush ice that enters the pump. Convex leading surface 680 of inner rotor foot does not seal against trailing surface of outer rotor cylinder wall. Sealed housing section 684 between intake and discharge. Extra material 686 on trailing (contact) surface 678 of inner rotor 624 maintains seal integrity as it wears.
As shown in FIG. 31, entrained gas 688 is centrifuged toward inside of outer rotor cylinders. When an inner rotor foot enters the chamber, the acceleration on the fluid is in the opposite direction and all or part of the lighter gas is pushed out of the chamber first. Arrow B shows the direction of rotation of outer rotor 622.
In FIG. 32, arrows C show the path of denser particles that enter the pump at preferably helical intake 690 on a helical path and are based away from the inner rotor 624 sliding interface by centripedal force.
In FIG. 33 the casing is not shown. Drive torque from the motor or shaft is provided to outer rotor member 692 which rotates and transmits torque to outer rotor of next stage Inner coaxial shaft 694 is secured to casing at opposite end from drive input and prevents inner members (which position inner rotors) from turning.
Immaterial modifications may be made to the embodiments described here without departing from what is covered by the claims.
In the claims, the word “comprising” is used in its inclusive sense and does not exclude other elements being present. The indefinite articles “a” and “an” before a claim feature do not exclude more than one of the feature being present. Each one of the individual features described here may be used in one or more embodiments and is not, by virtue only of being described here, to be construed as essential to all embodiments as defined by the claims.

Claims

1. A pump, comprising:

an outer housing having an inward facing cylindrical or partially cylindrical surface. an outer rotor with radial inward projections having at least a leading face which is, along any plane perpendicular to the outer rotor axis, offset from a radial line radiating from the outer rotor rotational axis;

a carrier secured for rotation at least partly within the outer housing;

an inner rotor secured for rotation about an axis within the carrier, the inner rotor having an outward facing surface and outward projections arranged around the outward facing surface;

the inward projections projecting inward and the outward projections projecting outward to mesh with each other and define variable volume chambers between the inward projections and the outward projections as the inner rotor rotates within the carrier;

the outward projections each having a leading edge and trailing edge;

fluid transfer passages on at least one of the outer housing and carrier to permit flow of fluid into and out of the variable volume chambers; and

the outer rotor is connected to be driven with a rotary shaft input, and convex trailing contact surfaces of the outward projections of the inner rotor contact the leading contact surfaces of the inward projections, the leading surface of each inner rotor outward projection does not seal and can be any shape as long as it prevents the rotors from locking up when the pump is freespinning or backturning.

2. A pump, comprising:

a carrier secured for rotation at least partly within the outer housing;

other advantages of driving the outer rotor include the ability to drive subsequent stages with a drive shaft that extends from both ends of one or more outer rotors to drive multiple similarly constructed outer rotors, coaxial stator shaft through the center of the drive shaft would be supported (at the opposite end from the drive shaft input) to the pump casing and would prevent the inner rotor housings from spinning

3. A pump, comprising:

a carrier secured for rotation at least partly within the outer housing;

in one configuration of the pump, it is designed to handle the admission and pumping of breakable solids such as but not limited to methane hydrate ice crystals, it does this with a combination of features such as sharp leading edges on spinning components and sharp trailing edges on stationary components which will slice the ice as it flows into and through the pump. It is also designed to minimized areas where ice could become wedged and restrict the flow by using increasing cross sections along the flow path.

4-22. (canceled)