Slurry Pump
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.
A new pump design uses the same sealing geometry as in U.S. Pat. No. 7,111,606 with some important modifications.
SUMMARYIn 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.
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:
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
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 ri divided by the outer reference circle ro (i.e. Λ/X=ri/ro) and ri/ro is <½.
As seen in
Now referring back to
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. 66d and 65c) 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,
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 ri divided by the outer reference circle ro (i.e. Λ/X=ri/ ro).
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
The center point 26 shown in
By having the inner radius ri one-half the length of the outer radius ro there 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 86d defines straight line 84d. 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
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
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.
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 112b 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 60a, the forward surface 32a, the rearward surface 34b the radially inward surface 112a 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
As seen in
As seen in
As the inner and outer rotors 22 and 24 are positioned in the matter shown in
As seen in
As seen in
In
There will now be a discussion of how air enters into the semi chamber regions 42 of the outer rotor 22. As seen in
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
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
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
The line 386a′ extends from the reference point 386a to the center point 326 of the outer reference circle 380 (see
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 382a′ 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
The apparatus 420 has a rotor assembly 421 that comprises an outer rotor 422 and a plurality of inner rotors 424a-424d. 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 ri divided by the outer reference circle ro (i.e. Λ/X=ri/ro).
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
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
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
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
There will now be a discussion of the geometric relationships between the inner and outer reference circles for the embodiments where the ratio of ri/ro is less than 1/2. For this example we will assume the inner reference circle radius, ri, is ⅓ of the outer reference circle, ro.
Referring to
Now referring to
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
It should be noted that the inner reference radius r,i0 is 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
Therefore as the perpendicular distance df changes 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 df that changes with respects to the rotational position of the inner and outer rotors.
The distance 471 in
Therefore a preferred method of constructing the first and second surfaces 434 and 432 is sketch out a CAD drawing such as that in
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 O1 and 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 O2 and 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:
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 O1 are 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 O2 in the first coordinate system is defined as:
The second coordinate system O2 is 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 O1 to the second coordinate system O2 the 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:
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 ri/ro is less than ½.
For this example we will assume the inner reference circle radius, ri, is ⅓ of the outer reference circle, ro.
As shown in
Referring to
Now referring to
Now referring back to
It should be noted that the inner reference radius r,i0 is 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 O1 and 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 O2 and 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 O1 coordinate 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:
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 622f 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.
In
In
In
As shown in
In
In
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:
- 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
3. 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.
4-22. (canceled)
Type: Application
Filed: Jun 27, 2012
Publication Date: Mar 21, 2013
Inventor: James Brent Klassen (Langley)
Application Number: 13/535,355
International Classification: F04C 2/00 (20060101);